JPS61259097A - Spiral fin tube inserting structure - Google Patents

Abstract

PURPOSE:To provide a spiral fin tube inserting structure which is simple in construction and light in weight by using the spiral fin tube as a male screw and an insertion hole formed by a circular hole and a fan shaped slit as a thread of a female screw, and screw-fitting them. CONSTITUTION:A phantom circumference 4-3 is a circumference which corresponds to a bottom of a female screw on the imagination. A fan-shaped slit 4-2 is cut open in a fan shape which connects two points (a) and (b) on the phantom to two points (c) and (d) on the peripheral edge of a circular hole 4-1. In this case, when the thickness of each fin is represented by t1, that of a flat plate 4 by t2, the spiral pitch of the spiral fin by P, the condition under which the flat plate 5 and the fin tube 1 are screw-fitted to each other without resistance, is t2<=P/2-t. The tube 1 is inserted from the rear surface of the flat plate 4, and the fin 2 penetrated through the fan shaped slit 4-2 and makes 1/4 revolution and only the 1/4 pitch is exposed on the front side of the flat plate 4. As a result, the fin and the flat plate produce a deflection and display a suitable friction resistance and a suitable holding force. The flat plate can insert and hold the spiral fin tube by a proper holding force.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to the effective use of finned heat exchange tubes in shell-and-tube heat exchangers, heat pipe heat exchangers, and the like. In particular, the present invention relates to an improved application structure of a spiral fin tube in which annular fins are spirally formed at a predetermined pitch around the outer periphery of a hollow tube for heat exchange.

(b) Conventional technology Spiral fin tubes made by the roll rolling method are often used as fin tubes for heat exchange, and in the field of annular fin tubes, spiral fin tubes made by the conventional wrapping method are a thing of the past. It's starting to happen. The fins are manufactured by rolling and are formed integrally with the tube, so there is no contact thermal resistance between the tube and the fins, and the spiral fins are formed by rolling. It is advantageous that the effective fin area is large. Furthermore, since there is no gap between the fin base and the pipe, corrosive gas condensate and dust will not enter and remain there, which will not cause corrosion to accelerate, resulting in high reliability.

Furthermore, since the tube body and the fins are integrated, there are many advantages such as the fins being stronger compared to fins of the wrapping type or the driving type. On the other hand, a common problem with finchaves is the difficulty in mounting them, but in spiral fin tubes, the fins and tube body are integral and strong, so the difficulty in mounting them is increased. Also, aluminum fins are often used for rolled spiral fin tubes, and aluminum fins are often used by coating a copper tube with alumina wave and rolling the same.

This is because aluminum is the easiest to form and has good thermal conductivity. Also, in order to improve the mechanical strength of the aluminum fin tube and also to improve thermal conductivity, a double tube of an aluminum fin tube and a steel tube is often used. However, these materials also increase the difficulty of installation.

FIGS. 11 and 12 are basic configuration diagrams illustrating the problem. When installing the fin tube, since the spiral fin tube has integrated fins, it is necessary to remove the portion necessary for installing the fin portion by cutting. Further, the cutting operation requires an additional part to be attached to and removed from the cutting device, and this part is removed after the processing is completed. FIG. 11 shows this state.

1 is a tube body, 2 is a spiral fin, 4 is a seven flange, and 11 is a welded portion thereof. In the figure, the fins are removed at the part 1-1 in order to make explosive contact with the 7-lunge 4 for attaching the fin tube. Further, numeral 1-2 is an additional part for attaching to the chuck of the lathe, and is a part that will be removed later. In this way, in the case of fins based on wrapping or in the case of fins mounted by driving, the objective t- could be achieved by simply removing the fins, but processing costs and materials are wasted.

FIG. 12 shows an example of a double pipe structure made of aluminum and copper.

In this case, 2 is an aluminum fin, 4 is a steel flange, and inner tube 1-
6 is also copper. 1-1 is an aluminum fin removed portion.

Since the temperature of the wax in the steel flange is 700° C. or higher, which is higher than the melting temperature of aluminum, in order to prevent the aluminum from melting, the portion from which the aluminum coating is removed is provided as long as 15 to 20 meters, including the steel pipe portion 3. That is, the cutting cost is further increased compared to FIG. 11.

This increase in the area where no fins are provided means a decrease in performance as a finned tube for a heat exchanger.

The biggest problem when applying finned tubes is their application to shell-and-tube heat exchangers using heat pipes. This system uses a large number of fin tubes formed as sealed containers to transfer the thermal energy passing through the high-temperature fluid side to the low-temperature side fluid. The scope of use for heating and cooling equipment is extremely wide. In either case, it is necessary to pass a large number of finned heat pipes through a partition wall (partition plate) between the high-temperature side fluid and the low-temperature side fluid, and to maintain the penetrating portion in an airtight or nearly airtight state. Various structures have been put into practical use or proposed as means for this purpose. However, they all have a common problem structure; in other words, such a structure is unavoidably adopted as a common problem that cannot be overcome. The problem structure consists of the following three items.

(υIn order for the finned heat pipes to penetrate, the partition wall (partition plate) must be provided with a group of through holes with a diameter larger than the outer diameter L of the fin group.) The finned heat pipe group has its own heat receiving It is necessary that the fin group be removed in a predetermined range at the boundary of the heat section, and furthermore, the fin group removed portion must be larger than the diameter of the through hole provided in the partition wall. It is necessary to provide a 7-diameter flange or sleeve with a sufficient size and sufficient strength depending on the mounting means. (3) 7 above
Both the flange or sleeve and the bulkhead are provided with mutual attachment means, and a space between the finned heat pipes must be provided in accordance with the attachment means.

Although the above problem structure has no choice but to be adopted, the following points are required for a heat exchanger using a finned heat pipe to exhibit good performance.

The distance between each heat pipe in the array of heat vibrators with captive fins should be as small as possible, preferably so small that the outer diameters of the fins are in contact with each other. The purpose of this is to increase the efficiency and downsize the heat exchanger.

(2) It is desirable that each heat pipe be installed across the entire width of the high-temperature side fluid flow path and the low-temperature side fluid flow path, and that the fins be formed over the entire length of the heat pipe as much as possible. If there are areas where fins are not formed, not only will the heat transfer area of the fins decrease, but the efficiency of the heat exchanger will decrease as the fluid will flow more through those areas where there is less resistance.

(CJ After installing the finned heat pipe group, the mounting area should be as airtight as possible, and if necessary, completely airtight.

0 If possible, it should be possible to disassemble and clean it easily. For each of the items (A) to 0 required for heat exchangers, all three items of the problem structure common to multi-tube heat exchangers using finned heat pipes that are actually used are required items. It turns out that they are contradictory.

FIGS. 13 and 14 show a heat exchanger using a finned aluminum heat pipe and a heat pipe heat exchanger having a double tube of a steel tube and an aluminum tube with aluminum fins, respectively. The fluid flow path formed by the side walls 9 and 10 is separated into a high temperature side flow path and a low temperature side flow path by a partition wall (partition plate) 5, and the aluminum container 1° and the aluminum tube 1. A heat pipe consisting of a double tube container of copper tubes 6 is disposed perpendicular to the flow of fluid and supported by the partition wall 5. The partition wall 5 is provided with a through hole 5-1 through which a finned heat pipe is disposed. Naturally, the diameter of the through hole 5-1 is larger than the outer diameter of the fin.

This corresponds to problem structure (1). Also, near this attachment part, the fin group 2 has been cut away, and a 72 inch attachment pin 4 having a diameter larger than that of the through hole 5-1 is welded to that part. In the case of FIG. 14, the flange 4 is brazed or welded to the steel pipe 3. In order to prevent the aluminum part from melting due to the temperature of the copper wax, the fin removed part is wider in FIG. 14 than in FIG. 13. Although the configuration of the seven flange 4 is not shown, it is a complex structure.

7.7 It is usually necessary to divide the hinge into two pieces before soldering, and the three pieces are soldered together when soldering to the container. Another method of attaching a flange is to first attach the flange to the
A method may be used in which a finned tube as shown in the figure is formed, another finned tube is welded to this, and then a flanged or finned heat pipe as shown in FIG. 13 or 14 is constructed. The structure in which the fins have been removed and the seven grooves have been installed is the second problematic structure of heat exchangers for heat pipe applications, and its formation is complex and time-consuming.

In the figure, the attachment means, which is the third problematic structure, is shown in a fastened state using bolts 7 and a lug 8. 13th
In the figure, a reinforcing plate 6 is also used to reinforce the strength of the aluminum flange. Pubking, adhesives, etc. are often used in combination to strengthen the airtightness. Although this type of attachment means is convenient for attachment and detachment, it has the disadvantage of increasing the size of the 7-lunge. In order to prevent this, fastening using repept, explosive bonding using soft solder, etc. are sometimes used, but it becomes extremely difficult to attach and detach the heat pipe.

Conventional shell-and-tube heat exchangers that use heat pipes with fins have a problematic structure as described above, and even in shell-and-tube heat exchangers that are not heat pipes and are simply fin-tube heat exchangers, the fin tube attachment part The structure is almost similar to that described above. Common problems with such problem structures include the following:

(1) Center distance of heat pipe or fin tube is 7
, 7, it is impossible to make the diameters smaller than the distance where they touch each other, and it is impossible to arrange them in a high density arrangement.

(2) Furthermore, for assembly and disassembly, it is necessary to provide enough space to operate assembly means such as bolts and nuts.

(3) It is necessary to provide a large number of through holes in the partition 11 (partition plate), and since the through holes are larger than the outer diameter of the fin, the mechanical strength of the partition wall (partition plate) will be greatly reduced. To avoid this, it is necessary to have a thick and strong structure in advance.

(4) The structure for attaching the fin tube group is complicated, which causes an increase in the cost of the device.

(5) In the case of a double pipe structure, the number of fins to be removed increases and the heat exchange efficiency decreases. In other words, it is clear that the currently used fin tube mounting structure violates the above-mentioned requirements for shell-and-tube heat exchangers.

Many proposals have been made to solve these problems. Figures 15 and 16 are some of those proposals, and both aim to reduce the tube diameter and shorten the mounting interval t-/t of the fin tubes.

In Fig. 15, the 7 flange 4 is shaped like a truncated cone with a small diameter, and the partition wall 5 is
A female truncated cone-shaped through hole 5-1 that engages with the 7-flange truncated cone is provided in the through hole 5-1, and the finned heat pipe is held by the engagement between the two. This structure is effective in that it reduces the distance between the finned heat pipes and requires no space for installation work. It is also effective in that it is easy to disassemble and maintain. However, the remaining problem is that it is impossible to reduce the heat pipe spacing based on the diameter of the bottom circumference of the truncated cone and the spacing between the through holes to maintain the strength of the partition wall. Another new problem that arises is that it is necessary to increase the thickness of the partition wall in order to provide sufficient holding force, and it is extremely difficult to provide a large number of truncated conical through holes in the partition wall. Practically speaking, it is necessary to take measures such as dividing the partition wall into a large number of parts, forming through holes, and then assembling the partition wall. Furthermore, it is difficult to provide a truncated conical flange on a heat pipe, and it is necessary to form the heat pipe separately and assemble it before welding.

Figure 16 shows that the diameter of either the fin 2-2 on the high-temperature side or the low-temperature side is made smaller than the diameter of the fin 2-1 on the opposite side. By providing the mating sleeve 4, the heat distance can be reduced. This structure is effective for the fins on one side, but since the fin height is low on the other side, it is necessary to lengthen the heat pipe or increase the fin density in order to maintain the heat transfer area. Also, since two types of fin tubes are used, the container is tube 1-1 and tube 1-.
It is necessary to make explosive contact at the connection part 11 of No. 2, and in order to reduce the influence of welding temperature on the fins, it is necessary to increase the number of fin removal parts. Various other structures have been proposed, but in all of the proposals, the mounting structure of the fin tube to the partition wall is complicated, and no effective countermeasure has yet emerged to the extent that the outer diameter of the fins can be brought into close contact with each other. As a reference, Utility Model Publication No. 59-181981. Utsukai Showa 59-144372,
Utsukai Showa 59-59685. Jitsukō 60-5274.41
There is iF Kaisho 57-192792.

(c) Problems to be solved by the invention The conventional technology cannot overcome the scope of the problem structure in the above three items 0), (2), and (3), and the requirements for shell-and-tube heat exchangers are However, various structural problems still remain, such as the impossibility of satisfying the four requirements of the construction, complexity, high cost, and the impossibility of high-density piping.

The present invention provides a completely new structure for applying the sviral inch piping, which is completely free from the problem structure described above, and has a simple, simple and inexpensive structure, and enables high-density piping with less waste. This aims to improve the performance of the heat exchanger by doing so, and attempts to solve almost all of the conventional problems.

B) Means for solving the problem The present invention focuses on and utilizes a new function of the rolled spiral fin tube, which has been overlooked in the past, as a means for solving the problem.

Also, the present invention is a corner! The function of the partition plate (partition plate) has been designed with emphasis placed on the function of supporting the finch, rather than its original function as a partition plate between the high-temperature fluid flow path and the low-temperature fluid flow path. The conventional structure was reviewed and a new structure was completed with emphasis on its function as a partition plate.

Spiral fin tubes made by rolling are extremely strong compared to press-fit fins or wrapped spiral fin tubes because the tube and fins are rolled as one body, and there is no contact thermal resistance, resulting in good fin efficiency. points are important features. Also, in the case of double-pipe spiral fin tubes, the inner and outer tubes are in pressure contact with each other due to the high pressure applied by rolling, and there is no contact thermal resistance, so the nine-fin tube is formed integrally with the outer tube. There is almost no contact thermal resistance between it and the inner tube.

In the case of a conventional double-walled spiral fin tube,
Two-stage contact between the twin and the outer tube, and between the outer tube and the inner tube 1.In contrast to the thermal resistance that was generated, thermal efficiency is greatly improved.

Rolled spiral fin tubes have been used solely for their advantage in heat resistance and strength. However, the other characteristic of the rolled spiral fins is that they are formed with an extremely precise spiral pitch, which has not been noticed in the 6tb.

This is due to the fact that the exact pitch of the rolling rolls is accurately transcribed since it is a rolling process.In other words, the rolled spikele finch tip is a male thread that has been accurately rolled. I can say that there is. The present invention is Subai 2
It was developed with the primary focus on having a high-precision male screw.

The second point we focused on when developing the present invention was that the thin flat plate was simply provided with a circular through hole that engaged with the valley of the male screw, and a slit that was slightly wider than the width of the screw thread and longer than the height of the screw thread. It was to act as a female thread. The slit is concentric with the circular through hole and is formed along a line connecting one point on the circumference, assuming a circumference with a larger diameter than the outer diameter of the spiral fin chain.

In addition, the thickness of the flat plate is theoretically thinner than the thickness of the plate as tt = P/2 tt, where the pitch of the spiral fin is p, the thickness of the fin is t, and the thickness of the flat plate is t-tt. If so, the flat plate described above can be freely rotated and slid within the spiral fin as a female thread.

However, in reality, depending on the flexure of the fins and the flexure of the flat plate, the thickness of the flat plate is tt=p/2, so even if tb-p is used, rotational sliding is possible as a female thread.

The present invention is directed to these first aspects. Based on the second point of view, it relates to an insertion structure in which a bi-2 fin tube is attached by mating a swivel fin gourd with a male thread and a flat plate with a circular through hole and a slit with a female thread. It is something.

This basic structure is shown in Figure 1 and fH2 (aJ, (b)
This is shown below.

Both figures show the state in which the male screw of the spiral fin chain is screwed into the female screw of the flat plate with 1/4 pitch.
The figure is from the direction with the spiral fin tube as the side surface, and FIG. 2 (IL) is from the cross-sectional direction. 1 is a finch gourd, 2 is a rolled spiral fin,
4 is a flat plate, 4-1 is a through hole provided in the flat plate, and 4-2 is a slit provided in the flat plate. Further, reference numeral 4-3 denotes a virtual circumference, which corresponds to the trough of an imaginary female thread, and the slit 4-2 is cut from the virtual circumference to the inner circumference of the through hole. Further, t indicates the thickness of the fin, and t.

represents the thickness of the flat plate, and p represents the helical pitch of the spiral fin.

FIG. 1 shows that the condition for the flat plate 4 to engage the fin tube 1 at right angles is tl = P/2 tl. In FIG. 2(a), the spiral fin tube 1 is inserted from the back side of the flat plate 4, and the spiral fin 2 is screwed in 1/4 turn through the slit, and the spiral fin tube 1 is screwed in by 17 turns on the front side of the flat plate 40.
A state in which only 4 pitches are exposed is shown.

The width W of the slit into which the spiral fin can be screwed in with almost no resistance is expressed by the following equation.

Here, Dl is the diameter of the through hole, and Do is the diameter of the virtual circumference (root diameter of the female thread). Therefore, the shape of the slit is defined by an arc Wi depending on Dl, an arc Wo depending on Do, and two straight lines (Do
It is a fan shape surrounded by Di)
~ Formed as a narrow slit.

Due to this, the hinge and the flat plate exhibit strong frictional resistance and are screwed in while being bent. Due to this, the flat plate can fix the spiral fin tube with a strong holding force. FIG. 2(b) shows an example of the shapes of through holes and slits provided in a flat plate.

1 and 2 (aJ, (b)) show the case where the flat plate 4 is a completely flat surface and its thickness is approximately 1/2 or less of the helical pitch of the sospiral fin.

However, in the area surrounded by the virtual circumference 4-6, which is assumed to be the circle of the valley of the female thread in Fig. 2(a), one edge of the slit is the starting point of the thread, and the other edge is the thread l pitch. If the flat plate is formed by embossing with one female thread at the end of the spiral fin tube, the thickness of the flat plate is 11 to 1 p-tte between the fins of the spiral fin. It can be screwed in as a gold male screw. In that case, the slit does not need to have a wide width, and it is sufficient to simply form a cut. Further, the embossing of one thread on the thread can be formed by extremely simple sheet metal processing. Press molding is also possible in the same process as through-hole punching.

(e) Function The insertion structure of the spiral fin tube according to the present invention has a spiral fin tube with a male thread, and a through hole and a groove.
This is an insertion/connection structure in which the two screws are screwed together as one thread of the female thread. Therefore, the insertion structure can be formed extremely simply and easily by only punching out a flat plate using a press and screwing in the fin tube. A small flange (flat plate) is connected to a spiral finch terminal.
The case of 1Cm contact is the simplest, but the insertion of the intermediate portion of a long spiral fin tube and a flat plate can also be easily achieved by simply rotating the spiral fin tube using a rotating device such as a lathe. The position of the flat plate can be determined by setting the rotation speed. Since thermal processing such as explosion welding and brazing is not required, there is no need to take measures to melt the aluminum fins, and there is no need to remove them.

The diameter of the through hole is sufficient as long as the tube body excluding the fins of the spiral fin tube can be inserted, so even if multiple main tubes are inserted, the strength of the flat plate that is the inserted object will not decrease to a dangerous state. do not have. Moreover, since the attachment/detachment work only requires rotating the spiral fin tube, no space is required for attachment/detachment, and the disassembly and reassembly work is extremely easy. When multiple tubes are inserted in parallel, each fin tube can be inserted with high density up to the position where the fins touch each other.

The contact state of the insertion part is surface contact between the flat plate plane and the fin plane, so it is close to airtight and can be maintained airtight just by using a small amount of adhesive.If complete airtightness is required, a through hole is used. It is also easy to apply adhesive to the contact area between the flat plate surface and the fin surface to make it completely airtight. However, if an adhesive is used, disassembly and maintenance will be difficult, so it is desirable to use a non-hardening adhesive that is easy to remove.

The basic structure of the insertion part according to the present invention is that there is no need to install large 7-lunges, sleeves, etc., and it is possible to use bolts.

The structure is simple and does not require any nuts or rivets.
1. There is no need for welding work. The production cost is significantly reduced, and the structure is extremely lightweight compared to conventional structures.

(f) Example The spiral fin groove insertion structure according to the present invention was developed based on a completely different point of view from the conventional structure, and can completely solve most of the problems of the conventional structure. What you can do is the same as mentioned above.

Since the present invention was developed based on a completely new point of view, many novel structural application examples are constructed.

First Embodiment The inserting structure of the fin sheave according to the present invention supports the fin sheave by the clamping force between the spiral fin and the flat plate. Since it is strong, it has enough strength to withstand normal use, but it may be required to further strengthen the structure when it is made to withstand severe vibration or when a strong external force is applied. Furthermore, this structure can be formed in such a way that the fins are inserted into the ends of the spiral tubes without leaving any fin removal parts. However, in the case of inserting the terminal part in this manner, the clamping force of the fins is low, so it may be necessary to strengthen the clamping force.

Also, in this structure, since the surface of the fin is in surface contact with the six faces of the flat plate that is the object to be inserted, the structure itself can be fitted with good airtightness, but depending on the application, complete airtightness may be required. In such cases, in the structure according to the present invention, the strength and airtightness may be strengthened by pouring brazing material into the minute gap near the contact area between the fin surface and the bottom of the flat plate, or by coating the adhesive with gold. There is.

11 in FIG. 3 indicates such a reinforced portion. If only airtightness is required without increasing the strength, the structure 11 may be filled with adhesive paint.

For convenience of illustration, 11 appears to use a large amount of soldering material or adhesive, but in reality, it is only used to fill a small gap, and does not cause an increase in weight or increase in size.

Second Embodiment In the structure according to the present invention, loosening prevention against strong vibration,
Alternatively, in order to strengthen airtightness, a thin plate of rubber-like elastic material may be inserted and attached to the flat plate that is the object to be inserted. FIG. 4 is a diagram showing an embodiment thereof, and 12 is a rubber-like elastic plate.

The rubber-like elastic plate elastically fills the minute gap between the spiral fin surface and the flat plate surface to strengthen airtightness and also acts as a loosening preventer against vibration. The thin plate of the rubber-like elastic body is also provided with through holes and slits in the same way as the flat plate. Moreover, in order to provide these, the shape of the spiral fin is made larger than the outer diameter of the spiral fin. Note that when a rubber-like elastic body is used to improve airtightness, it is desirable to form the slit as narrow as possible.

Third Embodiment In the structure according to the present invention, it is standard that the thickness of the flat plate serving as the object to be inserted is approximately 172 or less than the helical pitch of the spiral fin. However, because the helical pitch is small, flat plates with a thickness of about 0.51E11 may be produced. Further, depending on the use of the heat exchanger, it may be necessary to sufficiently strengthen the partition walls or supporting plates. In such a case, it is easy to construct the structure according to the present invention using a plurality of flat plates.

Reference numeral 16 in FIG. 5 is a flat plate provided alongside the flat plate 4. If a plurality of flat plates are installed side by side and the flat plates are bonded together to form a laminated flat plate, the supporting flat plate or partition wall will be further strengthened.
Ru. In addition, the thread configuration of the through hole and slit, which are considered to be internal threads, is not a single thread structure, but is structured to have more than one thread, thereby making it possible to double the clamping force. Reference numeral 14 in FIG. 5 is an adhesive layer, and the flat plates 4 and 13 are laminated plates depending on this layer.

Fourth Embodiment In the structure according to the present invention, there are cases where it is unavoidable to reinforce the flat plate that is the inserted object. For example, when inserting a long finned heat vibrator or an extremely large number of finned heat pipes into a large-scale heat pipe type heat exchanger, or because of the structure, it is impossible to support the finned heat pipe at both ends. This is the case, for example, when it is necessary to provide the flat plate that is the object to be inserted with not only the function of a partition plate but also the function of a support body. In such a case, if the helical pitch of the fins is small and the thickness of the flat plate is thin, the clamping force for the finned heat vibrator will be insufficient and the strength of the flat plate will be insufficient.

FIG. 6 shows an embodiment in which the flat plate that is the object to be inserted and welded in such a case is constructed as a reinforced structure. In the figure, reference numeral 15 denotes a thick reinforcing plate, and the finned heat pipe insertion part has a through hole 16 with a diameter slightly larger than the outer diameter of the fin.
is provided.

4.13 is a flat plate which is an object to be inserted. This flat plate is desirably made of a thin but strong material.

In the figure, two flat plates are used, but they may be provided on only one side of the reinforcing plate. The outer diameter of the flat plate is slightly larger than the inner diameter of the through hole 16, and the periphery is welded or soldered to the reinforcing plate 15. If there is enough space between the adjacent fins and one dowel, make the diameter of the flat plate 4.13 larger and fasten with adhesive or rivet.

Either of the following methods may be used:

Fifth Embodiment The heat pipe may be inserted in an inclined position in order to improve the performance by utilizing gravity to circulate the working fluid sealed inside the container. The angle of inclination is generally about 5 degrees to 20 degrees. In the case of such a heat exchanger in which a large number of finned and doped pipes are inserted and connected, the insertion and connection structure in the partition wall becomes complicated.

FIG. 17 is a schematic diagram of a conventional insertion/connection structure proposed to avoid the complication. The partition wall 5 has a truncated conical through hole 5-1.
A truncated conical sleeve 4 holding a finned heat vibrator is fitted into this. The truncated conical sleeve has a 1-hide pipe container pipe 1.
A through hole with an inclined angle into which is inserted is provided, and the finned heat tube 1 is held in the through hole.

Although this insertion structure is an improved structure, it is necessary to make the bulkhead thicker, it is difficult to provide a truncated conical through hole in one large bulkhead, the removal of the fin group, and the problem of the truncated conical shape. There is no other way to attach the sleeve to the pipe body than to have a split structure, and the split structure of a truncated conical sleeve with an inclined through hole is extremely complicated.

FIG. 7 shows a ninth embodiment of the insertion structure according to the present invention. In this embodiment, the flat plate 4, which serves as the object to be inserted and also serves as a partition plate between the high-temperature side fluid flow path and the low-temperature side fluid flow path, is made of a thin, strong, and highly elastic flexible material. Therefore, the spiral fin tube heat pipe 1-1.1-2 inserted as the insertion/connection structure according to the present invention. The inclination angle can be freely determined depending on the flexibility of the thin flat plate 4.

In this embodiment, the flat plate 4 is given only the function of a partition plate for the flow path, and the function of supporting the heat pipe is given to the side plate 16 of the heat exchanger, and both ends of the heat pipe are provided with the side plate 16. It is inserted and supported. A heat exchanger using the insertion structure according to the present invention constructed in this manner can provide a group of finned heat pipes with an inclined attitude with an extremely simple construction. This embodiment is most suitable for a spiral fin tip heat pipe having high density fins with a small helical pitch.

Sixth Embodiment The insertion structure according to the present invention can also be constructed without using a thin flexible flat plate in a structure that provides flexibility in the inclination angle of the heat pipe group of the spiral finch 1-b as in the fifth embodiment. It is easy.

In Fig. 1, if a heat pipe using a fin chive with a large helical pitch p of the spiral fins 2 is used, the flat plate 4 drawn at t, = -2--tl is sufficient compared to the fin spacing. Even if it is thin, it has a wall thickness that provides sufficient strength. In such a case, it is impossible to provide flexibility in the angle of inclination by relying on the flexibility of the flat plate.

However, in the case where the fin spacing is 5 tm and the flat plate 111i+ is used, it is determined from FIG. 1 that the flat plate has a considerably wide degree of freedom in the inclination angle in the fin gap. However, for this purpose, the inner diameter of the through hole 4-1 needs to be provided with a gap corresponding to the inclination angle with respect to the outer diameter of the fin tube 1.

Therefore, if it is necessary to insert the Subai 2 Rufin + Ape heat vibrator at an angle of inclination, use a flat plate to be inserted that is sufficiently thin compared to the fin gap, and This objective is achieved by configuring the insertion structure according to the present invention such that the inner diameter of the insertion hole has a diameter that is loose with respect to the outer diameter of the root of the fin of the spiral fin tube. You can.

In this case, in order to maintain the airtightness of the high-temperature fluid flow path and the low-temperature fluid flow path, the above-mentioned gap should be filled with an adhesive material, an adhesive material, or a rubber-like elastic thin plate should be brought into close contact with the flat plate. It is sufficient to provide a means for insertion and connection.

Seventh Embodiment When the spiral fin tube insertion structure according to the present invention is applied to applications subject to strong vibrations, a locking structure is required. Disassembly in the insertion structure according to the present invention,
As mentioned above, if it is possible to sacrifice the features of easy maintenance such as reassembly, welding, adhesion, etc. can be used. In addition, for some weak vibrations, it is possible to insert and connect a thin plate of rubber-like elastic body.

FIGS. 8 and 9 are schematic diagrams showing an insertion structure having both a function of preventing loosening against strong vibrations and a function of maintaining ease of maintenance. In FIG. 8, 4 is a main flat plate which is an object to be inserted and welded, and 17 is a locking flat plate inserted alongside this. The anti-loosening plate is constructed to be stronger than the main plate by selecting the material or increasing the wall thickness, and is closely inserted and strongly fastened to the main plate, so that the main plate 4 and the spiral fin tube are tightly connected. It greatly strengthens the fastening force with the tube body 1 and the spiral fin, and exhibits the same effect as a locking nut. The locking plate 17 is formed to have a larger outer diameter than the fin outer diameter. Anti-loosening flat plate 1
In the vicinity of the outer periphery of 7, there may be provided an unevenness that fits with a fastening jig. Further, a reversal prevention means may be provided to increase the locking function. Anti-loosening flat plate 1
It goes without saying that the plate 7 is provided with full insertion holes and slits like the main plate, but when fitting them with the fin tube 1 and the spiral fin 2, the locking plate 17 is a stronger fit. It is more effective if they are formed so that they are aligned.

FIGS. 9(a) and 9(b) show the shapes of through holes and slits provided in the main flat plate and the locking flat plate, respectively, which are desirable for carrying out this embodiment. Dashed line circumference 4-6
is the virtual circumference to which the outer diameter of the fin is inserted. 4-1.
17-1. are the insertion holes of the main plate and the locking plate, respectively, and 1
7-1 is formed slightly smaller than 4-1. 4-2 is a slit in the main plate, which is a fan-shaped slit with a narrower width than the theoretically required width. Due to this, the main plate 4 can hold the spiral fin tube with an appropriate clamping force.

Reference numeral 17-2 denotes a slit in the locking flat plate, which is formed to have a width that is much smaller than the theoretically required slit width and the slit width of the main flat plate. When such a locking flat plate 17 is inserted, the spiral fin 2 is subjected to bending force at the slit 17-2, so a large torque is required for fastening.

After completion of the fastening, the spiral fin 2 bent within the narrow slit has the effect of maintaining the fastening force even in the case of strong vibrations. As long as the locking plate does not loosen, the clamping force between the main flat plate 4 and the spiral fin tube 1 will not decrease, so the locking flat plate 17 will function as a locking nut. If the insertion part does not require disassembly and maintenance, the main flat plate 4 and the locking flat plate 17 may be fixed together using an adhesive when they are fastened together.

Eighth Embodiment The spiral fin tube insertion/connection structure according to the present invention was originally developed to avoid complicated structures for insertion/connection such as 7-lunges and nullipes. However, there are cases where it is necessary to form seven flanges for insertion due to the configuration of the device. In such a case, the insertion structure according to the present invention may be implemented by using a small flat plate corresponding to 7 ranks in place of the flat plate in the insertion structure according to the present invention.

FIG. 10 shows this state. 4-1.4-2 is a small flat plate with a thickness of about one helical pitch of the spiral fin, and can be easily inserted into any position of the fin tube by the action of the through hole and slit. In particular, it is an advantage of the insertion and connection construction according to the present invention that the 79-inch can be inserted into a short and small portion corresponding to one fin at the end of the fin tube. Fig. 1θ shows a state in which the insertion has been completed and fixing means such as welding, brazing, adhesive bonding, etc. have been applied. In the figure, 11 and 12 are fixed parts.

Further, 18-1 and 18-2 are connection means for fixing the 7-lunge dependent viral fin tube to a predetermined part.

Ninth Embodiment In a multi-tubular heat exchanger, notches are provided as a means to improve heat exchange efficiency by regulating the heat medium liquid or heated fluid flowing through the body tubes to a flow perpendicular to the heat transfer tubes. A baffle plate, which is a bulkhead plate, is used. However, when using a spiral fin tube or a heat pipe with fins as a heat transfer tube, it is necessary to provide a group of through holes larger than the fin outer diameter for each baffle plate, which reduces the mechanical strength of the baffle plate. It is necessary to increase the distance between the tubes in the heat tube group To! As a result, the diameter of the trunk pipe becomes large, which has the disadvantage of making the heat exchanger large. On the other hand, when applying the insertion/connection structure according to the present invention, the through holes provided in the baffle plate may be implemented as equivalent to the insertion holes in the insertion/connection structure according to the present invention. The diameter of the hole can be made much smaller than the outer diameter of the tip 2, excluding the fins, or larger. In this embodiment, since there is a large difference in thermal expansion between the body tube and the spiral fin tube which is the heat transfer tube, the insertion hole (through hole) for inserting the baffle plate and the slit are formed in a loosely engaged state. FIG. 20 is a schematic diagram showing this embodiment, in which 1 is a spiral fin chain, 2 is a spiral fin, and the chains are arranged in the body tube 3 of the heat exchanger in the length direction of the body tube. Arrows indicate the direction of heat transfer fluid flow. The flow of fluid depends on the action of the baffle plates and their notches to flow perpendicularly to the shift inch groups to increase heat exchange efficiency. The overall flow of the fluid within the body pipe is a meandering or spiral flow depending on the position of the notch. In the figures, the support rods of the baffle plates, the state of attachment of the baffle plates and the support rods, etc. are omitted and not shown.

FIG. 21 shows the state of the baffle plate and the through holes provided therein.

10th Embodiment In the insertion and connection structure of the spy fin chip island according to the present invention, the flat plate that is the object to be inserted and connected can be configured to function as a heat receiving and dissipating fin. In this case, a metal flat plate having a predetermined shape, a predetermined surface area, and a predetermined thickness is used as the heat receiving and dissipating fin. The material of the metal flat plate is preferably a metal with good thermal conductivity such as copper or aluminum.

The spikele fin itself is formed as a heat receiving and dissipating fin, but because it is made integral with the tube body by rolling molding, there is a manufacturing limit to the height of the fin. Generally, the outer diameter of the fin is limited to 2 to 25 times the diameter of the tube body.
When used, the heat transfer area is often insufficient. In such cases, it is customary to increase the number of heat exchanger tubes used, which causes complexity of the device and increased cost.

In such a case, the spiral fin tube insertion structure according to the present invention may be applied to increase the number of fin groups. In the case of such an embodiment, the insertion hole is formed in a state of strong engagement with the fin root diameter of the fin tube in order to reduce the resistance to heat contact with the sexual fluid. It is also desirable to increase the contact pressure between the spiral fins and the additional fins by making the slits narrower.

In this fin structure, the contact area between the spiral fin tube and the additional fin is large, so the contact thermal resistance is small, and the additional fin exhibits good performance as a fin.

In order to further improve the fin effect in this embodiment, thermally conductive grease may be injected into the contact area between the additional fin and the spiral fin tube, and in order to increase the mechanical strength of the additional fin, thermally conductive grease may be injected into the contact area between the additional fin and the spiral fin tube. An adhesive may also be used. FIG. 22 shows the inserted state of the additional fins provided on the spikele fin tube according to this embodiment. Reference numeral 61 is a container for a spiral fin tube or a heat pipe with fins applied thereto. 2 is a spiral fin, and 4 is an additional fin.

(G) Effects of the Invention The present invention relates to an extremely simple fin tube connection structure consisting of a spiral finch breast with a male thread, a flat plate with a female thread, and only connecting the two with screws. It provides a number of new application implementation structures for

Spiral fin tubes are an excellent material for use as heat exchange tubes, but there are still various problems in their use. In particular, complicated processes and structures are required for insertion and connection, and equipment The biggest drawback was that it raised costs. Especially in the field of small heat exchangers and small electronic devices, the length of each fin tube or heat pipe using fin tube is short, and the complexity of the insertion part and the resulting increase in cost are significant. , was in a state of unavailability.

However, since the present invention has a structure in which the fins and the inserted body itself can be used as the insertion means, there is almost no need for complicated insertion parts, and only soldering is required for attaching these parts. , It is possible to omit most of the high-temperature work such as welding work and fin removal work, it is possible to reduce weight and cost, and it is possible to almost completely solve the problems in using the spikele fin tube. I can do it.

In particular, for multi-tubular heat exchangers and multi-tubular heat exchangers that apply heat pipes with fins, the benefits of improving the structure of the insertion part are extremely large, regardless of whether they are large or small. When the present invention is applied to these shell-and-tube heat exchangers, in addition to solving the various problems mentioned above, the following great effects are exhibited.

A. High-density piping becomes possible.

Since a flange is not required and there is no need to consider the work space required for installing the flange, adjacent fin tubes can be installed close to each other until the outer edges of the fins touch each other. This is extremely important and has the following effects.

(The volume of the aJ heat exchange section can be reduced by 20-35%.

(b) Since the flow path cross-sectional area of the heat exchange fluid can be reduced by 30% to 40%, the flow rate increases and the amount of heat exchange increases at the same flow rate.

(0) The turbulence effect increases because the distance between the cheeps becomes smaller, thus improving the heat transfer coefficient and improving the heat exchange efficiency.

FIGS. 18 and 19 are schematic diagrams showing the arrangement density of through holes on a flat plate serving as a partition wall (partition plate) in the conventional structure and the structure of the present invention, respectively. Although the fin tubes to be inserted and connected are shown to be of exactly the same size, the difference in piping density is obvious at a glance. It is also clear that a significant reduction in the size of the heat exchanger is possible. In the figure, 4-1 is a through hole, and 4-2 is a slit. Broken line 1 is the outer diameter of the chain 2
5 indicates the outer diameter of the fin, and 5 indicates the outer diameter of the flange.

B. Heat exchange efficiency is improved because there are almost no ineffective parts in the heat exchange fluid flow path.

Spiral fins must be removed near pipe welding points, and near 7 langes and sleeve brazing points. Such fin-removed portions, seven flange portions, sleeve portions, and other portions in the fluid flow path where there are no fins and low resistance become ineffective portions within the cross-sectional area of the heat exchange flow path. In the case of a multi-tubular type, the heat exchange loss due to this ineffective portion becomes large. In the insertion structure according to the present invention, the fins can be constructed so that partial fins are formed in close contact with the wall surfaces on every wall surface forming the flow path, so that there are no ineffective portions.

[Brief explanation of the drawing]

Figures 1 and 2 (a) and (b) show the basic structure of the present invention. Figure 1 is a front view, Figure 2 (&J is a sectional view,
Fig. 2(b) is a side view showing the shape of the through hole and the slit provided in the flat plate, and Figs. 3 to 8 and 10 show the first to eighth embodiments of the present invention. Front view, Figures 9(&) and (b) are side views showing the shapes of through holes and slits provided in the flat plate, Figures 11 to 17 are front views showing the conventional structure, and Figure 18 is the conventional structure. FIG. 19 is a side view showing the arrangement density of the through holes on the flat plate that is the partition wall in the structure, FIG. 20 is a side view showing the arrangement density in the present invention, and FIG. 21 is a side view of the baffle plate, and FIG. 22 is a front view showing the tenth embodiment. 1... Spiral fin tube 2°... Spiral fin 4... Flat plate 4-1... Penetration 4-2... Thrive 4-3... Virtual circumference 11-'. Fig. 5 Fig. 6 Punishment η1 Fig. 7 Fig. 8 Fig. 11 Fig. 12 Fig. 13 Fig. 14 Fig. 15 Fig. 16 Fig. 17 Procedure amendment form c) Insertion and connection structure of spiral fin tube 3. Relationship with the case of the person making the amendment Applicant: Actronics Co., Ltd. 4, Agent: 1-29 Akashi-cho, Chuo-ku, Tokyo, 104, Suiseikai Building, Tel: 03
(545) 2251 (Representative) -6, Contents of the amendment Il + Attachment correction The correction will be made going back 4m. 121, Figure 2 1al, Figure 42, Figure 111, Figure 18, Figure 21? Please make corrections in the attached sheet. Amended Description 1, Title of Invention Spiral Fin Tube Insertion Structure 2 Claims + 11 A spiral fin tube in which heat receiving and dissipating fins are integrally formed with a tube body in a spiral shape with a predetermined pitch on the outer periphery of the tube. In this insertion structure, there are few objects to be inserted, and in the part where the co-spiral fin tube is inserted, it is a flat plate that is thinner than the fin gap of the spiral fins, and the flat plate has a A circular hole approximately equal to the pipe diameter is provided, and from a predetermined portion of the inner edge of the circular hole,
The temporary circumferential arc @vwt is concentric with the circular hole and has a slightly larger diameter than the fin outer diameter, the outer circumferential arc width of the fan-shaped slit is Wo, the fin is caused by the screwing force during insertion, and Wl and W are flattened. The width is a predetermined width approximating Y, the inner edge of the circular hole is the thread of the female thread, and one thread of the virtual circular female thread corresponds to the male thread formed by the spiral fin of the spiral fin tube and the outer periphery of the tube body. A spiral fin tube insertion structure characterized in that the spiral fin tubes are inserted into each other by substantially a pair of male and female screws that match. (21 In the insertion structure of the spiral fin tube mentioned above, the surface of the flat plate that is the object to be inserted and the fin surface of the spiral fin tube that is the insertion object can be brought into contact by any means of contact using a contact material. They are fixed and integrated with each other, and this makes the insertion and connection of the insertion and connection structure strong.
The spiral fin tube insertion/connection structure according to claim 1, wherein the insertion/connection portion is made airtight. (3) The above-mentioned spiral fin tube insertion structure silkworm has a shape slightly larger than the outer diameter of the fin attached to the flat plate that is the object to be inserted, and has circular holes and slits for connection. 2. The spiral fin tube insertion structure according to claim 1, wherein a thin plate of a rubber-like elastic body is inserted in close contact with a flat plate of the object to be inserted. (4) In the insertion and connection structure of the spiral fin tube, a plurality of flat plates as objects to be connected are installed side by side and have a common 2/<(5" Twitch 7 is inserted and connected T" Y: The spiral fin tube insertion structure according to claim 1, characterized in that the spiral fin tube insertion structure is characterized in that the spiral fin tube has a diameter larger than the outer diameter of the spiral fin. Fin tube insertion structure. ・6) In the spiral fin tube insertion structure, the flat plate that is the object to be inserted and welded is made of a thin, delicate and elastic material, and the insertion and connection structure is as follows. The average plane of the entire flat plate and the center of the spiral fin tube at !11
The insertion and connection structure of the spiral fin chain has a relatively large degree of freedom in the angle formed with 1111 due to the flexibility of the flat plate. (7) In the insertion structure of the spiral fin tube, the thickness of the flat plate that is the object to be inserted is sufficiently thin compared to the area between the fins, and the inner diameter is the same as that of the spiral fin tube. The diameter of the fin is such that it fits loosely with the outside diameter of the fin's root, and this gives a large degree of freedom to the angle between the flat plate surface and the center axis of the swirl fin. The spiral fin tube insertion and connection structure according to claim 1, characterized in that n is t. (8) In the insertion structure of the spiral fin tube, a main flat plate which is an object to be inserted is provided together with a locking flat plate which is stronger than the main plate and which is connected to the structure according to the present invention in the same way as the main plate. It is constructed by being inserted into the spiral fin tube as a contact body, and the locking flat plate is slightly larger in shape than the outer diameter of the spiral fin, and the main flat plate and the locking flat plate are arranged in close contact with each other. In addition, they are strongly connected to each other, and the locking plate prevents the insertion force between the main plate and the spiral fin tube from loosening. (9) In the spiral fin tube insertion structure, the flat plate that is the object to be inserted has an outer diameter larger than the outer diameter of the spiral fin, and is screwed into the spiral fin tube to a predetermined position, so that the flat plate surface and the spiral fin The surface contact surfaces shall be firmly bonded and integrated by any means of soldering, soldering, or adhesive bonding, and the flat plate shall be configured as a 7-lunge for mounting a spiral fin tube.'4I: A spiral fin tube insertion and connection structure according to claim m1. (1 (I) The spiral fin tube insertion structure described above is a spiral fin tube or spiral fin tube T container with a μ-doped pipe that has a length of the body tube in the body tube that is the heat medium fluid flow path of the heat exchanger. A predetermined number of spiral fin tubes are arranged in the horizontal direction, and a predetermined number of flat plates, which are common objects to be inserted, are inserted into these spiral fin tubes. The spiral fin tube insertion structure according to claim 1, characterized in that the baffle plate has a temperature of 0.degree. As the flat plate to be inserted, a group of metal flat plates of a predetermined shape are mutually inserted and connected with a spiral fin tube or a fin-to-ship pipe of application 7, and the metal flat plate group has a thermally conductive material. It is made of a good material and is constructed as an additional fin for expanding the heat transfer area.'%: The insertion and connection structure of the spiral fin tube as described in the characterized claim @ Item 1. Insertion and connection of the tube Structure. λ Detailed Description of the Invention (A1 Field of Industrial Use) The present invention relates to the effective use of finned heat exchange tubes in shell-and-tube heat exchangers, heat pipe heat exchangers, etc. t! The present invention is a heat exchange agent in which annular fins are spirally formed at a predetermined pitch on the outer periphery of a hollow tube.
The present invention relates to an improved application technique for certain snow irradiation tubes. (b) Conventional technology Spiral fin tubes made by the roll rolling method are often used as fin tubes for heat conversion, and in the field of annular fin tubes, the spiral annular fins made by the conventional winding method are a thing of the past. I'm getting older. Since the spiral fins are manufactured by rolling and are formed integrally with the tube body, there is no contact heat resistance between the tube body and the fins, which prevents corrosion. High affordability <1! Compared to I-type or driven-in type fins, there are many advantages such as the two fins being tougher. On the other hand, a common problem with fin tubes is the difficulty in mounting them, but in the case of spiral fin tubes, the fins and tube body are integral and strong, so the difficulty of the surface layer increases on the contrary. Aluminum fin tubes are often used for rolled spiral fin tubes, and bimetallic fin tubes are also often used, which are aluminum tubes made from copper chains and then rolled to form aluminum fins. . This is because aluminum and copper are the easiest to work with and have good thermal conductivity. However, the use of grade 8 materials also increases the difficulty of mounting. @Figure 11 and Figure 412 are basic configuration diagrams explaining the problem. When installing the fin tube, since the fins of the spiral fin tube are integrated, it is necessary to remove the portion necessary for installing the fin portion by cutting. Further, the cutting operation requires an additional part to be attached to and removed from the cutting device, and this part is removed for convenience after the processing is completed. FIG. 11 shows this state. 1
2 is a tube body, 2 is a spiral fin, 4 is a 7-lunge, and 11 is a welded portion thereof. In the figure, the part 1-1 is a fin! It is removed by cutting. Also, 1-2 is an additional part for attaching to the chuck of the disc, and is a part that will be removed later. In this way, in the case of fins that are wrapped or driven in, it is easy to remove them, and it is also easy to form unfinned parts, but in the case of rolled spiral fins, the fins are removed. This results in a lot of waste in processing costs and materials. FIG. 12 shows an example of a double pipe structure made of aluminum and copper. In this case, e2 is an aluminum fin, 4 is a copper flange, and inner tube 1-
3 is also copper. 1-1 is the aluminum fin-excluding part. Since the brazing temperature of the steel flange is 700° C. or higher, which is higher than the melting temperature of aluminum, in order to prevent Al ξ from melting, the portion from which the aluminum coating is removed is provided as long as 15 to 20 a1, including the steel pipe portion 3. That is, compared to FIG. 11, the cutting blade Roe cost is further increased. This increase in the portion where no fins are provided means a decrease in performance as a finned tube for a heat exchanger. The application of finned tubes that has the greatest disadvantage is its application to multi-tube heat exchangers using heat pipes. A fin tube is formed as a sealed container, and a large number of these are used to transfer the thermal energy passing through the high temperature fluid 9111Y to the low temperature 1llll fluid,
Exhaust heat recovery device I! , cooling devices inside sealed equipment casings, fluid heating, cooling devices, etc.7 have an extremely wide range of uses. In either case, a partition wall (partition plate) between the high-temperature side fluid and the low-temperature side fluid.
A heat vibun with many fins! JJjL, please
It is necessary to maintain the penetrating portion in an airtight or nearly airtight state. Various structures have been put into practical use or have been proposed as means for this purpose. However, they all have a common problem structure; in other words, such a structure is inevitably adopted as a common point that cannot be crossed.Meanwhile, the M structure has the following three items. (In order to allow the heat pipe with fins to pass through, the partition plate must be provided with a hole group with a diameter larger than the outer diameter of the fin group. (The heat pipe group with 21 fins is It is necessary that the fin group be removed over a predetermined range at the boundary between the number of heat receiving parts and the heat receiving part, and - the fin group removed part must have a diameter larger than the diameter of the through hole provided in the partition wall. The above-mentioned 7 langes or sleeves are provided with 7 langes or sleeves with a diameter that has a sufficient size and sufficient strength depending on the mounting means. Both the bulkhead and the partition wall are provided with mutual attachment means, and a space between the nine fin heat pipes must be prepared according to that means.The above problem structure has no choice but to be adopted. In order to achieve better performance, heat exchangers using finned heat pipes are required to meet the following requirements. The m spacing should be as small as possible, preferably so small that the outer diameters of the fins are in contact with each other.The purpose of this is to increase the efficiency and downsize the heat exchanger. (B) Height of each heat pipe! 1all The fluid R is installed across the entire length of the flow path across the connection and the low temperature side fluid flow path,
It is desirable that the fins be formed as wide as possible over their entire length. If there are parts where the fins are not formed, not only will the heat transfer area of the fins decrease, but the fluid will flow more through those parts with less resistance, reducing the efficiency of the heat exchanger.With rat fins After the heat pipe group has been installed, the mounting area should be as completely airtight as possible, and depending on the need (℃).■1 If possible, it should be possible to easily disassemble and clean it.Required for heat exchangers. (For each item of DI, the three items of the problem structure common to shell-and-tube heat exchangers applying finned heat pipes that are actually practically used are contradictory to the requirements) Figures I@13 and 14 respectively show a heat exchanger using an aluminum heat pipe with fins, and a shape in which aluminum fins are formed on a double pipe of steel pipes and aluminum pipes. This is a heat pipe heat exchanger.The fluid flow path formed by GA99, 10 is a partition wall (
A heat pipe consisting of a double pipe container consisting of a high-temperature side R, channel and a low-temperature side flow channel N, an aluminum container L or (aluminum tube), and a copper pipe 3 is divided into a high temperature side channel R and a low temperature channel by a partition plate 5.
It is supported by the partition wall 5 and is arranged n. The partition wall 5 is provided with a through hole 5-1 through which the finned heat pipe ytWK is placed. Of course, it's a rental hole!
The diameter of -1 is larger than the outer diameter of the fin. This corresponds to problem structure +r+ 4C. Also, near this attachment part, the fin group 2 is cut and removed,
At that part, there is a mounting flange 4 with a larger diameter than the through hole 5-1. I contact rt''C. In the case of Fig. 14, 7
The flange 4 is brazed or welded to the steel pipe 3. In order to prevent the aluminum part from melting due to the copper soldering temperature, the 14th
In the figure, the area where the fins have been removed is wider than in Figure 13. Although the configuration of this 7-lunge 4 is not shown, a
It has a rough structure. -7 Lange usually needs to be divided into two pieces before soldering, and when soldering to the container, these three pieces are integrated with each other by 5-weld. Another 7 lange installation method is to first form a fin chain 7'Y as shown in Figure 11 or @12 before forming it as a heat pipe, weld the fin tube to it, and then A method of configuring the heat pipe as a heat pipe with seven lunges and fins as shown in the figure may also be used. The structure in which the fins have been removed and the flanges have been attached is the second most problematic structure of heat exchangers for heat pipe applications, and its formation requires time due to multiple passages. In the figure, the mounting means, which is the third problematic structure, is shown in a fastened state using bolts 7 and nuts 8. 13th
The figure shows the strength of aluminum 7 langes [11i and reinforcing plates 6 are used together to make them stronger. Backings, adhesives, etc. are often used in combination to strengthen airtightness. Although this type of attachment means is convenient for attachment and detachment, it has the disadvantage of increasing the size of the flange. In order to prevent this, fastening using rivets, explosive bonding using soft solder, etc. may be used, but attaching and detaching the heat pipe becomes extremely difficult. Conventional shell-and-tube heat exchangers that use heat pipes with fins have a problematic structure as described above, and even in shell-and-tube heat exchangers that are not heat pipes and are a single type of shell and tube heat exchanger, fin tubes are used. The mounting part has a structure similar to that described above. Common problems with such problem structures include the following: It is impossible to make the center distance of the 111 heat pipe or fin tube smaller than the distance a where the flange diameters touch each other, and it is impossible to arrange them in a high density arrangement. (2) Furthermore, for assembly and disassembly, it is necessary to provide enough space to operate assembly means such as bolts and nuts. (3) Interval! ! It is necessary to provide a large number of through holes in the (partition plate), and since the through holes are larger than the outer diameter of the fin, the mechanical strength of the partition plate will be greatly reduced. Therefore, it is necessary to have a strong structure within the thickness in advance. (4) The structure for attaching the fin tube group is rough and causes an increase in equipment price. (In the case of a 512 double tube structure, fins must be removed. In other words, it is clear that the currently used fin tube mounting structure violates the four requirements IAI to IDI for shell-and-tube heat exchangers. Many proposals have been made to solve the problem. Figures WJ15 and 16 are some of those proposals, including reducing the diameter of the 7 langes and reducing the spacing between fin tube installations. In Fig. 15, the 7 langes 4 are shaped like truncated cones with a small diameter, and the partition wall 5 is
A female truncated cone-shaped through hole 5-1 is provided in the flange to engage with the truncated cone of the flange, and the finned heat pipe is left open so as to be held by the engagement of the two. This structure is effective in that it reduces the distance between the finned heat pipes and requires no space for installation work. It is also effective in that it is easy to disassemble and maintain. However, the remaining problem is that it is impossible to make the distance between the heat pipes smaller than the sum of the diameter of the bottom circumference of the truncated cone and the distance between the through holes to maintain the strength of the partition. Another problem that arises is that it is necessary to increase the thickness of the septum in order to provide sufficient holding force, and it is an extremely difficult task to provide a large number of truncated conical through holes in the septum. However, for practical purposes, it is necessary to take measures such as dividing the partition wall into a large number of parts, forming the through holes Y, and then assembling them. Furthermore, it is difficult to provide seven truncated conical piping in the heat pipe, and it is necessary to form the heat pipe separately and assemble it before welding. Figure 16 shows that by making the diameters of some of the fins 2-2 on the high-temperature side or the low-temperature side smaller than the diameters of the fins 2-1 on the opposite side, the through holes χ can be made smaller. The distance between the heat pipes is reduced by providing sleeves 4 that meet each other.This structure is effective for the fins on one side, but the height of the fins on the other side is low, so the heat transfer area Y: a is kept small. In order to do this, it is necessary to lengthen the heat tube or increase the fin density χ.Also, since two types of fin tubes are used once, the container is made of tube 1-1.
and IIZ, which is explosively connected at the connection part 11 of the pipe 1-2.
There is a need for p, so give it to Finn! ! ! Fin removal part for horses to reduce the influence of degree? The need arises to increase. Various other structures have been proposed for 2"L'C, but in all the proposals, the mounting structure of the fin tube to the partition wall is complicated, and no effective countermeasure that allows the fin outer diameter to be brought in close contact has yet emerged. (As a reference, Utility Model Application Publication No. 59-181981
, Utility Model 59-144372, Utility Model 59-59685
．． Jikko Sho 60-5274. Japanese Patent Application Publication No. 57-192792)
(c) Problems to be solved by the invention The prior art cannot overcome the range of the interstitial structure that covers the three terms 11) (21) (31), and the problems required for a multi-tube type converter tA) (B) lI:!l■)
It was impossible to satisfy the above four conditions, and various structural problems still remained, such as being crude, expensive, and impossible to construct high-density piping. The present invention provides a completely new structure to which a spiral fin tube is applied, which is completely out of step with the above-mentioned problem structure, and attempts to solve almost all of the conventional problems. B) Means for Solving the Problems The present invention focuses on and utilizes a new function of the rolled spiral fin tube, which has been overlooked in the past, as a means for solving the problems. 1. Also, in the present invention, the partition wall (partition plate) is constructed with emphasis on the fin tube support function rather than its original function as a partition plate between the high temperature fluid flow path and the low temperature fluid optical path. We reviewed the conventional structure that had been developed and completed a new structure that emphasizes its function as a partition plate. Rolled spiral fin tube has the advantage of #11 resistance and 51! It has been applied only by focusing on it. However, the other feature of rolled spiral fins, that they are formed with an extremely accurate spiral pitch, has not received much attention. This is due to the fact that the exact pitch of the rolling rolls and the exact depth of the grooves are accurately transferred because it is rolling forming.If we change the table @, the rolled spiral fin tube is accurately rolled. It can be said that it is a type rL nine-fold semi-screw. The present invention was developed with the first consideration being that the spiral fin tube is a male thread with high precision. The 20th important point made in developing the present invention is to provide a circular hole in the thick inner flat plate 3 into which the trough of the male screw fits, and radially form a screw thread slightly wider than the width of the thread on the periphery of the hole. The height of the fan-shaped thread (longer than the height of the thread) is Y-formed and the insertion hole is provided so that it essentially acts as a female thread. Such an insertion part does not require any complicated machining such as spiral thread machining as a female thread. Hypothetically, it is a triple fan-shaped slit that is formed by cutting out a portion surrounded by a line connecting four points: two predetermined points on the circumference and two predetermined points on the periphery of the circular hole. In this way, when a spiral fin tube is screwed into an insertion hole that is essentially internally threaded while being held perpendicular to the surface of a flat plate, the thickness of the flat plate is theoretically If p is the pitch of the spiral fin, tl is the thickness of the fin, and the thickness of the flat plate is y, -t, then tl =
If it is thinner than the thickness n given by p/2-t, the above-mentioned flat plate can be made internally threaded and can freely rotate and slide inside the spiral fin. However, in reality, the thickness of the C flat plate is t* =
, Q/2 or more and °C can also be rotated and slid as a female screw. The present invention is directed to these first aspects. Based on the second point of view, we decided to make the spiral fin tube a male thread, and the flat plate with an insertion hole consisting of a circular hole and a fan-shaped slit to be an approximate and substantial female thread, and to fit them into each other. This invention relates to an insertion structure for mounting a spiral fin tube onto a predetermined flat plate. This basic structure is shown in Figures 1 and 2.
Figure 1a). The temperature is shown in (b). The figure shows a state in which the spiral fin tube is screwed 174 pitches into the insertion hole formed on a flat plate, and the figure '1li41 shows the spiral fin tube 1.
1: From the direction of the s-plane, FIG. 2(a) is a representation from the cross-sectional direction. 1 is a fin tube, 2 is a rolled spiral fin, and 4 is a flat plate. 4-1 is a nine circular hole provided in the flat plate, and 4-2 is a fan-shaped slit provided in the flat plate. Further, 4-3 is a virtual circumference, which corresponds to the valley of an imaginary female thread, and the fan-shaped slits 4-2 are at two points (a) on the virtual circumference. A fan-shaped incision is made connecting (b) to two points &p-4 on the circumference of the circular hole. Further, t1 indicates the thickness of the fin. t indicates the thickness of the flat plate, and p indicates the helical pitch of the spiral fin. From FIG. 1, the conditions for WIAIFC between the flat plate 4 and the fin tube 1 at right angles with no resistance are t, ≦p/2-tl, or n. In FIG. 2(a), the spiral fin tube 1 is inserted from the back side of the flat plate 4, and the spiral fin 2 is screwed in 1/4 turn through the fan-shaped slit, so that only 174 pitches are exposed on the front side of the flat plate 40. There is. FIG. 2 1fil shows only the insertion holes provided in the flat plate at n°C. The arcuate length L of the slit that allows the spiral fin tube to be vertically screwed into the flat plate run with almost no resistance is expressed by the following equation. (Inner circumference arc length) v9P circumference arc length)
Here, DI is the diameter of the through-hole, and Do is the diameter of the virtual circumference (root diameter of the female thread). Therefore, one dimension of the fan-shaped slit is the arc Ll depending on Dl, the arc L0 depending on Do, and two straight lines (Do -Di)X t/2. However, this shape is such that the spiral fin tube can be screwed in without resistance. In reality, LLeLo is formed as a narrow slit with a calculated value of i to T. As a result, the fins and the flat plate each bend and exert appropriate friction resistance and clamping force against each other, and the flat plate can be inserted into the spiral fin tube with an appropriate holding force. In this case, the amount of thickness correction due to compensation in the thickness direction of the fin and flat plate is σ1, respectively. If the circumferential arc width of the fan-shaped slit is 'f: W t, and the outer circumferential arc mvw, then when the slit width is small,
It can be considered as Wo in Lo, so the slit width is W from the cutting allowance.
is expressed by the following equation. Figure 1 and Figure 2 (1a), lbl is that the flat plate 4 is completely flat, its thickness is approximately 172 or less than the helical pitch of the spiral fin, and the insertion hole has nothing other than a circular hole and a fan-shaped slit. There is also no means for screwing in. Another possible solution to the problem is to form the slit as an extremely thin linear slit, and to form the entire pressing group as one thread of a spiral female thread. However, in this case, the female thread works well with the male thread of the spiral fin tube! l
1i1 Machining into the fitted state requires very high precision, resulting in an expensive structure compared to the machining of the insertion portion according to the present invention. In addition, with this type of internal thread structure, it is difficult to figure out the friction S resistance and clamping force that occur when screwing, and a single spiral fin tube has a large number of flat plates to be inserted and welded! In this case, screwing may become extremely difficult due to the frictional force in the X direction. On the other hand, in the case of the insertion hole according to the present invention, the width of the fan-shaped slit can be easily increased, and thereby the tightening force Y required for screw fitting can be increased to 1 ga very easily. (E) Function The insertion structure of the spiral fin tube according to the present invention is such that the spiral fin tube has a male thread, and the insertion hole consisting of a circular hole and a fan-shaped slit is substantially one thread of the female thread and is connected to each other by 4e. It is a structure. Therefore, the insertion structure is formed by punching a flat plate using a press and using a spiral fin chain WJ14I! It is possible to form an extremely simple package using only IC work. Even when a flat plate is inserted into the middle part of a long spiral fin tube, it can be easily inserted and connected by rotating the spiral fin tube using a rotating device such as a lathe. Accurate positioning of the flat plate is possible by setting the rotation speed. Since heat processing such as explosion welding and brazing is not required, there is no need to take measures to melt the aluminum fins, and there is no need to remove them. The diameter of the circular hole is large enough to allow the companion tube body to be inserted, excluding the fins of the spiral fin tube, so even if a large number of tubes are inserted into one flat plate, the strength of the flat plate to be inserted will be compromised. The state name will not be degraded. In addition, since the attachment/detachment work only requires one turn of the spiral fin tube, no space is required for attachment/detachment, and the work is extremely easy to do by disassembling and assembling. Multi fY: When inserting m rows, each fin chain has a high density F! until the fins overlap each other. tK can be inserted. In other intermediate means for solving the problem, in which a fan-shaped slit and a spiral female thread structure are used in combination, the outer diameter becomes large to form the female thread, so the outer diameter of the fins, such as the insertion structure according to the present invention, are in contact with each other. Such high-density insertion is impossible. Since the contact state of the insertion part according to the present invention is surface contact between the flat plate plane and the fin plane, airtightness can be maintained simply by using a small amount of adhesive sealing material, and complete airtightness is not required.
If this is the case, it is easy to apply an adhesive between the passage hole and the pipe body and the contact area between the flat plate surface and the fin surface to make it completely airtight. However, if adhesive is used, disassembly and maintenance will be difficult, so it is desirable to use non-hardening adhesive that is easy to remove. The basic structure of the insertion part according to the present invention is that there is no need to attach large 7-lunges, sleeves, etc., and it is possible to use bolts. The structure is simple and does not require any nuts or rivets.
Since no welding work is required, manufacturing costs are significantly reduced, and the structure is extremely lightweight compared to conventional structures. (f) Example
1 The present invention is developed based on a completely new 7III eye point.
As a result, many novel structural applications can be constructed. First Embodiment The fin chain insertion structure according to the present invention supports the fin chain by the clamping force between the spiral fin and the flat plate, and the spiral fin formed integrally with the tube body by rolling is extremely strong. Therefore, it has sufficient strength to withstand normal use, but if it is to withstand severe shock or is subjected to strong external force, the structure may be required to be strengthened. Moreover, this structure can be formed in such a manner that the fins are inserted into the ends of the spiral fin tubes without leaving any fin removal parts. However, when inserting the terminal part like this, the clamping force of the fins is low, so it must be strengthened t4! ! may be required. Further, in this structure, since the surface of the fin is in surface contact with the surface of the flat plate which is the object to be inserted, the structure itself has good airtightness, but depending on the application, complete airtightness may be required. In such cases, in the structure according to the present invention, a soldering material may be inserted into the gap between the fins and the plate surface near the contact area, and soldering may be performed at °C, or an adhesive or adhesive sealing material may be applied. In some cases, the strength and airtightness of such materials may be strengthened. 11 in Fig. 3 indicates such a reinforced part, which is 6°C.
When only airtightness is required without strengthening the strength, 1
1 may have a structure filled with adhesive sealant. Second Embodiment In the structure according to the present invention, loosening prevention against ℃1 strong motion,
Alternatively, in order to strengthen airtightness, a thin plate of rubber-like elastic material may be inserted and attached to the flat plate that is the object to be inserted. FIG. 4 is a diagram showing an embodiment thereof, and 12 is a rubber-like elastic plate. The rubber-like elastic plate elastically fills a minute gap between the surface of the spiral fin and the surface of the flat plate, thereby strengthening airtightness at °C and acting as a loosening preventer against vibration. This thin plate of rubber-like elastic material is also provided with insertion holes consisting of circular holes and slits similar to those of the flat plate. In addition, in order to provide LrL, etc., its shape is made larger than the outer diameter of the spiral fin. Note that when a rubber-like elastic body is used to improve airtightness, it is desirable that the slit provided here be formed as narrow as possible. 3rd % Example In the structure according to the present invention, it is standard that the thickness of the flat plate serving as the object to be inserted is approximately 172 or less than the helical pitch of the spiral fin. However, because the helical pitch is small, the thickness of the flat plate may be about 1 m. Further, depending on the use of the heat exchanger, it may be necessary to sufficiently strengthen the partition walls or supporting plates. Such a case can be easily solved by increasing the number of flat plates to a plurality of plates in the insertion structure according to the present invention. Reference numeral 13 in FIG. 5 indicates nine flat plates provided alongside the flat plate 4. If a plurality of flat plates provided with the insertion structure according to the present invention are installed side by side or the flat plates are bonded to each other to form a laminated flat plate, the supporting flat plate or the partition wall can be strengthened to the necessary strength. In addition, the insertion hole consisting of a circular hole and a fan-shaped slit is not configured with a single-thread screw structure but with a thread of more than Mita r'L''C, which can double the clamping force. 14 in Fig. 5 is an adhesive layer. Therefore, the insertion structure of the flat plates 4 and 13 of the horizontal laminates is a Mita screw.Fourth Embodiment In the structure according to the present invention, it is necessary to significantly strengthen the flat plate that is the inserted body. For example, when inserting a long finned heat pipe or an extremely large number of finned heat pipes into a large-scale heat pipe type heat exchanger, or when installing a large number of finned heat pipes in a large-scale heat pipe type heat exchanger, This is the case when it is impossible to support the flat plate to be inserted, and there is a need to attach the flat plate to the partition plate and provide not only the function of ℃ but also the function of the support.In such cases, the fin If the helical pitch is small and the wall thickness of the flat plate is thin, the clamping force against the finned heat pipe will be insufficient, and the strength of the flat plate will be insufficient. ゛Figure 6 shows the objects to be inserted in such a case. The figure shows an example in which a flat plate is constructed with a reinforced structure.In the figure, 15 is a thick reinforcing plate, and the finned heat pipe insertion part has a diameter that is only 1 larger than the fin outer diameter. Through hole 16
is set n. 4.degree. 13 is a flat plate which is an object to be inserted. This flat plate is preferably made of a thin but strong material. Although two flat plates are used for the reinforcing plate, they may be provided on only one side of the reinforcing plate. The outer diameter of the flat plate is formed to be slightly larger than the inner diameter of the through hole 16, and is welded or soldered to the peripheral Z reinforcing plate 15 by 5a. If there is enough space between the adjacent finned heat pipes, the flat plates 4 and 13 are formed with a large diameter, and are fastened by using liquid reservoirs using adhesive and rivets. Either fastening using bolts or nuts may be used. Fifth Embodiment The heat pipe may be inserted in a container in a diagonal position in order to improve the performance of the sealed working fluid with the help of gravity. The angle of inclination is generally about 5 degrees to 20 degrees. A heat pipe with fins like this? In the case of a heat exchanger having a large number of connections, the insertion and connection structure in the partition wall becomes complicated. FIG. 17 is a schematic diagram of a conventional insertion/connection structure proposed to avoid such complication. The partition wall 5 has a truncated conical through hole 5-
1 is provided, and a frustoconical sleeve 4 holding a finned heat pipe is fitted into this. The conical sleeve is provided with an inclined through hole into which the heat pipe container tube 1 is inserted, and the finned heat pipe 1 is held in the through hole at a temperature of .degree. Although the insertion structure is an improved structure, it is necessary to make the partition wall within the thickness, and it is necessary to rotate the truncated conical through hole in one large partition wall and remove the fin group. The only way to attach the sleeve to the tube body is to use a split structure, and there are still problems such as the split structure of a truncated conical sleeve with a slanted through hole is extremely complicated. This is an embodiment in which the insertion structure according to the present invention is applied.In this embodiment, the flat plate 4, which is the object to be inserted and which is the partition plate between the high temperature side fluid flow path and the low temperature side fluid flow path, is thin, strong, and elastic. Therefore, the heat vias 1-1, 1-2 of the spiral fin chain which are inserted and connected as the insertion and connection structure according to the present invention are made of a thin flat plate 4.
The angle of inclination can be freely determined depending on the capacitance of the object. In this embodiment, the flat plate 4 is given only the function of a partition plate for the flow path, and the function of supporting the heat pipe is given to the side plate 16 of the heat exchanger. is inserted into the side plate and supported at ℃. The heat exchanger constructed in this manner and applying the insertion and connection structure according to the present invention to rL7 can give an inclination and posture to the finned heat pipe group with an extremely simple construction. This embodiment is most suitable for a spiral fin tube heat pipe having a high density fin χ with a small helical pitch. Sixth Embodiment In a structure that provides flexibility in the inclination angle of the spiral fin tube heat pipe group as in the fifth embodiment, the insertion and connection structure according to the present invention can be constructed without using the Atsunai flexible plate. The smell is easy. In FIG. 1, if a heat pipe using a fin tube with a large helical pitch p of the spiral fins 2 is convenient n, then 1. Even if the flat plate 4 expressed by ≦0-t is sufficiently smaller than the fin spacing, it will still have a wall thickness with sufficient strength. In such a case, it is impossible to provide flexibility in the angle of inclination by relying on the flexibility of the flat plate. However, in the case where the fin spacing is 5+as and the flat plate is 1ss at °C, it is determined from Figure @1 that the flat plate has a fairly wide degree of freedom in the tilt angle at the fin gap. However, in order to do this, the inner diameter of the circular hole 4-1 needs to have a gap rL''C with respect to the outer diameter of the fin tube 1, which corresponds to the angle of inclination. If it is necessary to insert the T-fin into the inserting hole, use one that is sufficiently thin compared to the flat plate T-fin gap, and the inner diameter of the circular hole in the insertion hole provided in the flat plate is as follows:
The object can be achieved by configuring the insertion structure according to the present invention to have a diameter of 1 [diameter] that is loosely fitted to the outer diameter of the root of the fin of the spiral fin tube. In this case, is the airtightness of the high temperature fluid flow path and the low tJA fluid flow path?
In order to maintain this, it is sufficient to fill the gap with an adhesive sealing material, fill it with an adhesive, or provide a means such as bringing a thin rubber-like elastic plate into close contact with the flat plate and joining them at ℃. Seventh Embodiment When the spiral fin tube insertion structure according to the present invention is applied to applications subject to strong shaking, a locking structure is required. Disassembly in the insertion structure according to the present invention,
As mentioned above, reassembling beans can be easily handled by welding, gluing, etc., at the cost of sacrificing the feature of easy maintenance. Also, for some weak gripping movements, it is possible to insert and connect a thin plate of rubber-like elastic material. FIG. 48 and FIG. 9 are schematic diagrams showing a nine-insertion structure having both a function of preventing loosening against strong vibrations and a function of maintaining ease of maintenance. 8 In Figure 8, 4 is the main flat plate which is the object to be inserted, and 17 is the loosening plate inserted next to this, which is provided with an insertion hole having a fan-shaped slit like the main plate. be. The anti-loosening flat plate is made stronger than the main flat plate depending on the choice of material or increase in wall thickness, etc., and is closely inserted and strongly fastened to the main flat plate 4. Fastening force t between the spiral fin tube and the spiral fin
7: Reinforced in width and exhibits the same effect as a locking nut. The locking flat plate 17 is formed to have a larger external shape than the outer fin. There is an unevenness near the outer periphery of 4 stop flat & 17 that meets the fastening jig and tllIC.
'C may be provided, or a reverse prevention means may be provided to increase the loosening prevention function.The loosening prevention plate 17 is provided with circular holes and slits for insertion like the main plate. Although it is natural that the fin tube 1 and the spiral fin 2 are formed in such a manner that the loosening plate 17 is tightly fitted, it is effective. be. Figure 9 1al and Figure 9+bl show the shapes of the circular holes and slits provided in the main plate and the anti-loosening plate, respectively, which are desirable for the horse implementing this embodiment. This is an indication. Broken line circumference 4-3
is an imaginary circumference on which the outer diameter of the fin is inserted. 4-1.
．． 17-1. are the insertion holes of the main plate and the locking plate, respectively.
17-1 is formed to be smaller than 4-1. 4-2
is a slit in the main plate, which is a fan-shaped slit with a width narrower than the theoretically necessary width. This allows the main flat plate 4 to hold the spiral fin tube with appropriate clamping force. Reference numeral 17-2 denotes a slit in the locking flat plate, which is formed to have a width that is much smaller than the theoretically required slit width and the slit width of the main flat plate. When such a locking flat plate 17g is inserted and connected, the spiral fin 2 receives a bending force at the slit 17-2, so a large torque V is required for fastening. , 'a After completion of the tying, the spiral fin 2 bent with a narrow slit circle has the effect of maintaining the tying force even under heavy shooting conditions. As long as the locking plate does not loosen, the clamping force between the main plate 4 and the spiral fin tube 1 will not decrease, so the locking flat plate 17 will function as a locking nut. If the insertion part does not require disassembly and maintenance, the main flat plate 4 and the locking flat plate 17 can be used together with a bonding material to form a fixed structure. Eighth Embodiment The spiral fin tube insertion structure according to the present invention was originally developed in order to avoid complicated structures for insertion such as seven flanges and sleeves. However, there are cases where it is necessary to form a flange for insertion due to the configuration of the device. In such a case, instead of the flat plate in the insertion structure according to the present invention, a small flat plate corresponding to 7 lunges may be used to implement the insertion structure according to the present invention. Is that the state in Figure 10? show. 4-1.4-2 is a small flat plate with a thickness approximately equal to the pitch of the spiral fin, and can be easily inserted into any position of the fin tube by virtue of the circular holes and slits. In particular, it is an advantage of the insertion structure according to the present invention that the seven flange can be inserted into a short and small portion corresponding to one fin at the end of the fin tube. Fig. 10 shows a state in which the insertion has been completed, and solidifying means such as welding, brazing, adhesive welding, etc. have been applied. In the figure, 11 and 12 are fixed parts. Further, 18-1 and 18-2 are connection means for fixing the spiral fin tube to a fixed portion of the spiral fin tube tS by means of seven flange. Ninth Embodiment In a shell-and-tube heat exchanger, notches are used as a means to improve heat exchange efficiency by restricting the heat medium liquid or heated fluid flowing through the body tubes to R and n perpendicular to the heat transfer tubes. For installation, baffle boards, which are nine bulkhead boards, are used. However, when using a spiral fin tube or a finned heat pipe as a heat transfer tube, each baffle plate has an f larger than the fin outer diameter.
It is necessary to provide a through hole mt, which reduces the mechanical strength of the baffle plate. Therefore, it is necessary to increase the distance between the tubes of the heat transfer group IiF, and as a result, the diameter of the body tube becomes large, making the heat exchanger large. There were some drawbacks. On the other hand, when applying the insertion structure according to the present invention, the through hole provided in the baffle plate may be equivalent to the circular hole in the insertion structure according to the present invention, and therefore the diameter of the circular hole is spiral. The diameter of the through hole provided in the baffle plate can be made very small as long as it has a diameter that allows sliding insertion relative to the outer diameter of the fin root of the fin tube. Furthermore, when a large number of baffle plates are inserted, the resistance of each baffle plate when screwed in may be accumulated and the screwing resistance may be so great that it may be difficult to insert the spiral fin tube. In such a case, either form the fan-shaped slit wide in advance or bend the slit image to create a slit! This can be easily solved by reducing the individual resistances by enlarging 't'. FIG. 20 is a schematic diagram showing this embodiment, in which 1 is a spiral fin tube, 2 is a spiral fin, and the tubes are arranged in the body tube 3 of the heat exchanger in the length direction of the body tube. The arrow indicates the direction of Rn of the heat transfer fluid. The fluid flows perpendicularly to the fin tube group due to the action of the baffle plates and their notches, thereby increasing heat exchange efficiency. The overall flow of the fluid in the body pipe becomes a meandering or spiral flow depending on the position of the notch. The figure shows the support rod for the baffle plate. The mounting states of the baffle plates and support rods are omitted and not shown. FIG. 21 shows the state of the baffle plate and the through holes provided therein. 10th Embodiment In the spiral fin tube insertion structure according to the present invention, the flat plate serving as the object to be inserted at ℃ can be configured to function as a heat receiving and dissipating fin. In this case, a flat metal plate having a predetermined shape, a predetermined surface area, and a predetermined thickness is used for heat receiving and dissipating fins. The material for the synthetic fiber plate is preferably a metal with good thermal conductivity such as copper or aluminum.
The spiral fin itself is formed as a heat receiving and dissipating fin, but because it is made integral with the tube body by rolling, there is a manufacturing limit to the fin height. Generally, the outer diameter of the fin is limited to 2 to 5 times the diameter of the tube body.
There is often a lack of heat transfer area when using the toilet. In such a case, it is customary to increase the number of heat exchanger tubes by one replacement, and this causes complexity of the apparatus and increased cost. Is such a +iJI meeting the spiral fin tube insertion/connection structure according to the present invention? You can take advantage of this by adding more fin groups. In such an embodiment, in order to reduce the contact heat resistance, the circular hole in the insertion hole is formed in a strong engagement with the fin root diameter of the fin tube. It is also desirable to increase the contact pressure between the spiral fins and the additional fins by making the fan-shaped slits narrower. In order to further improve the fin effect in this embodiment, it is sufficient to inject thermally conductive grease into the contact parts of the additional fins and the spiral fin tube, and to increase the mechanical strength of the additional fins, A conductive adhesive may also be used. FIG. 22 shows a state in which the additional fins provided on the spiral fin tube according to this embodiment are inserted and connected. 1 is a container for a spiral fin tube or a finned heat pipe that is an application thereof. 2 is a spiral fin, and 4 is an additional fin. FIGS. 18 and 19 are schematic diagrams showing the arrangement density of circular holes on a flat plate serving as a partition wall (partition plate) in the conventional structure and the structure of the present invention, respectively. The fin tubes to be inserted and connected are exactly the same size and are 1M! The difference in piping density is obvious at a glance. It is also clear that a significant reduction in the size of the heat exchanger is possible. In the figure, 4-1 is a circular hole, and 4-2 is a picture-shaped slit. Broken line 1 indicates the outer diameter of the fin tube, broken line 2 indicates the fin outer diameter in %, and 5 indicates the outer diameter of the 7 flange. In each of the above embodiments, the shape of the fan-shaped slit in the insertion hole is not limited to the fan shape. Even a short fence-shaped slit can sufficiently achieve the purpose as long as it approximates the fan-shaped slit with the required dimensions. (G) Effects of the Invention The present invention uses the fin and the inserted object itself as an insertion means II2! Because it has a structure that can be used for many applications, there is almost no need for complicated insertion parts, and most of the heat work such as soldering and welding work for fitting such parts and the work of removing fins can be omitted. This makes it possible to reduce weight and cost, and almost completely solves the problems in using spiral fin tubes. In particular, whether multi-tube heat exchangers or multi-tube heat exchangers that use finned heat vibrators are large or small, the benefits of improving the structure of the insertion part are extremely large, such as Kohachi. By applying the present invention to the above, the following great effects are exhibited in solving the various problems mentioned above. AA density arrangement becomes possible. Since no 7-lunges are required and there is no need to consider the working space for flange installation, adjacent fin tubes can be installed close to each other to a point where the outer edges of their fins contact each other. This is extremely important and has the following effects. The volume of the heat exchanger section is 7 x 0. Since the cross-sectional area of the IHL heat exchange fluid can be reduced by 30% to 40%, the flow rate increases and the amount of heat exchange increases at the same flow rate. lc) The reduced distance between the tubes increases the turbulence effect and therefore increases the heat transfer coefficient and improves the heat exchange efficiency. B. Ineffective parts in the heat exchange fluid flow path are almost eliminated, improving heat exchange efficiency. Spiral fins need to be removed near pipe welding points, and near 7 langes and sleeve brazing points. Such fin-removed portions, flanges, sleeve portions, and other portions of the fluid fL circuit where there are no fins and have low resistance become ineffective portions in the cross-sectional area of the heat exchange flow path. In the case of a multi-tube type, the heat exchange loss due to this ineffective part is large.In the insertion structure according to the present invention, fins are formed up to the part that is in close contact with the wall surface on every surface forming the flow W&. Since the structure can be configured as follows, there are no invalid parts. BRIEF DESCRIPTION OF TABLE DRAWINGS Figures 1 and 2 1a) and lb) show the basic structure of the present invention. Figure 1 is a front view, and Figure 2 1al is a sectional view. Figure 2 +1) l is a side view showing the shape of the circular hole and fan-shaped slit provided in the flat plate, from Figure 8 to Figure 1.
0 is a front view showing the first to eighth embodiments of the present invention, FIGS. 9(a) and 9(b) are side views showing the shapes of circular holes and fan-shaped slits provided in a flat plate, and FIG. 1st from the figure
Fig. 7 is a front view showing the conventional structure, Fig. 18 is a side view showing the arrangement density of through holes on a flat plate that is a partition wall in the conventional structure, Fig. 19 is a side view showing the arrangement density in the present invention, and Fig. 20. 2 is a partially sectional front view showing the ninth embodiment;
FIG. 1 is a side view of the baffle plate, and FIG. 22 is a front view showing the tenth embodiment. 1... Spiral fin tube, 2... Spiral fin, 4... Flat plate, 4-1... Circular hole, 4-2
... Surits), 4-3... Virtual circumference, 5-1...
Through hole. Figure 18, 2λ embroidery

Claims (12)

[Claims] (1) A spiral fin tube insertion structure in which heat receiving and dissipating fins are spirally formed at a predetermined pitch on the outer periphery of the tube and are integrated with the tube body. The part where they are in contact is a flat plate with a thickness thinner than the fin gap of the spiral fin, and this flat plate is provided with an insertion hole approximately equal to the tube diameter, and furthermore, from the inner edge of the insertion hole, Either a cut or a slit of a predetermined width is formed over an imaginary circumference that is concentric with the insertion hole and has a diameter slightly larger than the outer diameter of the fin, and the inner edge of the insertion hole is used as the thread of the female thread. , the virtual circumference is the valley of the female thread, and one thread of the female thread that starts from one edge of the cut or slit, goes around and ends at the other edge corresponds to the male thread formed by the spiral fin of the spiral fin tube and the outer periphery of the tube body. The spiral fin tubes are formed so as to form a pair of male and female threads, and the spiral fin tubes are screwed into a predetermined position of the spiral fin tubes using the male threads as the male threads and the insertion holes as the female threads, and are inserted into each other. A spiral fin tube insertion structure characterized by: (2) In the spiral fin tube insertion structure according to claim 1, the insertion hole and the cut or slit provided in the flat plate that is the object to be inserted are surrounded by an imaginary circumference. An insertion structure for a spiral fin tube, characterized in that the portion is formed by pressure molding into the shape of one pitch of a female thread corresponding to the spiral fin. (3) In the spiral fin tube insertion structure according to claim 1, the contact surface between the surface of the flat plate that is the object to be inserted and the fin surface of the spiral fin tube that is the insertion object is made of hard solder. They are fixedly integrated with each other by soldering, soft solder bonding, or adhesive bonding, thereby making the insertion and connection of the insertion and connection structure strong, or A spiral fin tube insertion structure characterized by an airtight insertion section. (4) The spiral fin tube insertion structure as set forth in claim 1, wherein the spiral fin tube has a shape slightly larger than the outer diameter of the fin, which is attached to a flat plate that is an object to be inserted and welded, and which is used for insertion and connection. A spiral fin tube insertion structure characterized in that a thin plate of a rubber-like elastic body provided with through-holes and slits is inserted and connected in close contact with a flat plate of an object to be inserted. (5) In the spiral fin tube insertion structure according to claim 1, the flat plate serving as the object to be inserted and connected has a plurality of plates arranged side by side or a laminated structure of a plurality of plates. A spiral fin tube insertion structure characterized in that a common spiral fin tube is inserted into these. (6) In the spiral fin tube insertion structure according to claim 1, the insertion and connection of the spiral fin tube is achieved by a reinforcing plate provided with an insertion hole having a diameter larger than the outer diameter of the spiral fin. A spiral fin tube insertion structure characterized by a reinforced flat plate. (7) In the spiral fin tube insertion structure according to claim 1, the flat plate as the object to be inserted is made of a thin, highly flexible and highly elastic material, Insertion and connection of a spiral fin tube, characterized in that the angle between the average plane of the entire flat plate and the central axis of the spiral fin tube at the insertion part is given a relatively large degree of freedom due to the flexibility of the flat plate. structure. (8) In the spiral fin tube insertion structure according to claim 1, the thickness of the flat plate that is the object to be inserted is sufficiently thin compared to the fin gap. In addition, the inner diameter of the insertion hole provided in the flat plate is a diameter that allows loose engagement with the outer diameter of the root of the fin of the spiral fin tube, and the flat plate surface and the central axis of the spiral fin tube are connected. A spiral fin tube insertion/connection structure characterized by being constructed with a wide degree of freedom in the angle of the spiral fin tube. (9) In the spiral fin tube insertion structure according to claim 1, the main flat plate, which is the object to be inserted, has a locking flat plate that is stronger than the main plate and is common to the main flat plate. The main flat plate and the locking flat plate are in close contact with each other, and the locking flat plate is slightly larger than the outer diameter of the spiral fin. A spiral fin tube insertion/connection structure characterized in that the main flat plate and the spiral fin tube are arranged so as to be strongly fastened to each other, and the locking plate serves to prevent the insertion force between the main flat plate and the spiral fin tube from loosening. (10) In the spiral fin tube insertion structure according to claim 1, the flat plate that is the object to be inserted has a larger external shape than the spiral fin, and is screwed into the spiral fin tube to a predetermined position. The contact surface between the flat plate surface and the spiral fin surface shall be firmly bonded and integrated by any means of brazing, soldering, or adhesive bonding, and the flat plate shall be configured as a flange for mounting the spiral fin tube. Spiral fin tube insertion structure featuring (11) In the spiral fin tube insertion structure according to claim 1, the spiral fin tube or the heat pipe using the spiral fin tube as a container is a body that is a heat medium fluid flow path of a heat exchanger. A predetermined number of spiral fin tubes are arranged in the lengthwise direction of the body tube, and a predetermined number of flat plates, which are objects to be inserted and connected to this or these spiral fin tubes, have a diameter approximately close to the inner diameter of the body tube. It forms a disk partition, and the disk partition is partially provided with a cutout, and the partition and the cutout allow the flow direction of the heat transfer liquid to be perpendicular to the spiral fin tube and the length of the tube. A spiral fin tube insertion structure characterized in that the structure serves as a baffle plate that regulates the flow direction as a meandering flow or a spiral flow depending on a combination of flow directions. (12) The spiral fin tube insertion/connection structure according to claim 1, wherein the flat plate serving as the object to be inserted and connected is a group of metal flat plates having a predetermined shape, or a spiral fin tube or an application fin thereof. 1. A spiral fin, which is inserted into and connected to a heat pipe attached to the spiral fin, and the group of metal flat plates is made of a material with good thermal conductivity and is configured as an additional fin for expanding the heat transfer area. Tube insertion structure.