WO2015020050A1

WO2015020050A1 - Heat exchanger and method for manufacturing heat exchanger

Info

Publication number: WO2015020050A1
Application number: PCT/JP2014/070609
Authority: WO
Inventors: 和田　博文; 智規原口
Original assignee: サンデン株式会社
Priority date: 2013-08-08
Filing date: 2014-08-05
Publication date: 2015-02-12
Also published as: JP2015034661A

Abstract

[Problem] To provide a heat exchanger which comprises a spiral partition wall and a spiral pipe and which can be assembled with improved work efficiency. [Solution] A heat exchanger has a spiral passage which is formed between adjacent turns of a spiral partition wall (3) provided within a container, a spiral pipe (4) having turns is disposed in the spiral passage with the turns arranged in vertical tiers, and a first fluid which flows through the spiral passage outside the spiral pipe and a second fluid which flows through the inside of the spiral pipe are caused to exchange heat. A groove (21) is formed in the partition wall, the width (W) of the portion of the partition wall which corresponds to the groove is set to be less than the distance (R) between adjacent turns of the spiral pipe, the spiral pipe is provided corresponding to the groove in the partition wall, and the spiral pipe is made to be in close contact with the groove by rotating the partition wall and/or the spiral pipe about the center of the spiral.

Description

HEAT EXCHANGER AND HEAT EXCHANGER MANUFACTURING METHOD

The present invention relates to a heat exchanger for exchanging heat between a first fluid and a second fluid flowing in a spiral shape, and a method for manufacturing the same.

In exchanging heat between the first fluid and the second fluid having different temperatures, a spiral partition plate is provided in a cylindrical container to form a spiral passage between the partition plates, and a plurality of spiral tubes are provided in the spiral passage. There is known a spiral heat exchanger that is arranged to exchange heat by flowing a first fluid in a spiral passage and a second fluid in a spiral tube (see, for example, Patent Document 1).

In this case, the first fluid and the second fluid are counterflows. And according to the structure which concerns, there existed an advantage which can be set as a compact heat exchanger with high heat exchange efficiency.

JP 2006-162157 A

However, the work of assembling the spiral partition plate and the spiral tube is complicated, and improvement has been desired. In addition, although dust and scale contained in the first fluid are attached to the spiral passage, it is extremely difficult to clean the spiral passage between the partition plates where the spiral pipe is present.

The present invention has been made to solve the conventional technical problems, and is a heat exchanger that improves the assembly workability of a heat exchanger composed of a spiral partition wall and a spiral tube, and heat exchange It aims at providing the manufacturing method of a vessel.

In order to solve the above problems, the heat exchanger of the invention of claim 1 comprises a spiral passage between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages. The first fluid flowing in the spiral passage outside the lever tube and the second fluid flowing in the spiral tube are heat-exchanged, and have a groove formed in the partition wall, and the width dimension of the partition wall of the groove portion W is configured to be smaller than the spiral interval R of the spiral tube. The spiral tube corresponds to the groove of the partition wall, and the partition wall and / or the spiral tube rotates about the center of the spiral. By being done, it is closely_contact | adhered to the groove | channel.

The heat exchanger of the invention of claim 2 is characterized in that, in the above invention, the spiral tube is detachably fitted in the groove of the partition wall.

According to a third aspect of the present invention, there is provided a heat exchanger manufacturing method in which a spiral passage is formed between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage so that the outside of the spiral tube is outside. In manufacturing a heat exchanger for exchanging heat between the first fluid flowing through the spiral passage and the second fluid flowing through the spiral tube, a groove is formed in the partition wall, and the width dimension W of the partition wall of this groove portion is defined as the spiral tube. A spiral tube is arranged corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral, so that the spiral tube is placed in the groove. It is characterized by being in close contact.

According to a fourth aspect of the present invention, there is provided a heat exchanger manufacturing method, wherein the spiral tube is detachably fitted in a groove of the partition wall in the above invention.

According to the first and third aspects of the present invention, the spiral passage is formed between the spiral partition walls provided in the container, and the spiral tubes are arranged in a plurality of upper and lower stages in the spiral passage, and the outer sides of the spiral tubes are arranged. In the heat exchanger for exchanging heat between the first fluid flowing in the spiral passage and the second fluid flowing in the spiral tube, a groove is formed in the partition wall, and the width dimension W of the partition wall of the groove portion is defined as the space between the spirals of the spiral tube. The spiral tube is arranged so as to be smaller than R and corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral so that the spiral tube is in close contact with the groove. Therefore, the heat exchanger can be easily assembled by assembling the spiral tube to the spiral partition wall by an extremely simple operation by simply rotating the partition wall and the spiral tube.

In this case, if the spiral tube is detachably fitted into the groove of the partition wall as in the inventions of claim 2 and claim 4, the heat that can easily decompose the partition wall portion and the spiral tube portion. The exchanger can be manufactured, and dust and scale attached to the heat exchanger can be easily washed.

It is a disassembled perspective view of the heat exchanger of one Example to which this invention is applied. It is a top view inside the heat exchanger of FIG. It is a figure explaining the flow of the 1st fluid of the heat exchanger of Drawing 1, and the 2nd fluid. It is a principal part expanded sectional view of the heat exchanger of FIG. It is a figure which shows the relationship between the flow path width PB / flow path width PA in FIG. 4, and the amount of heat exchange. It is a principal part expanded sectional view of the heat exchanger of another Example. It is a principal part expanded sectional view of the heat exchanger of FIG. 1 of the position corresponding to FIG. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part enlarged view of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. It is a front view of the spiral tube of FIG. It is a principal part expanded sectional view of the heat exchanger of the state which comprised the partition wall with the spiral pipe of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. It is a front view of the spiral tube of FIG. It is a principal part expanded sectional view of the heat exchanger of the state which comprised the partition wall with the spiral pipe of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. It is a front view of the spiral pipe of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. FIG. 20 is a front view of the spiral tube of FIG. 19. It is a principal part expanded sectional view of the heat exchanger comprised with the spiral tube of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. It is a front view of the spiral tube of FIG. It is a principal part expanded sectional view of the heat exchanger comprised with the spiral pipe of FIG. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part perspective view of the heat exchanger of FIG. It is a top view of the partition wall explaining one Example of the manufacturing method of the heat exchanger of this invention. It is a top view of the spiral tube explaining the method of FIG. FIG. 29 is a layout diagram of a partition wall and a spiral tube for explaining the method of FIG. 28. It is a top view of the heat exchanger assembled by the method of FIG. It is a top view of the partition wall explaining the other Example of the manufacturing method of the heat exchanger of this invention. It is a top view of the spiral tube explaining the method of FIG. It is a layout of the partition wall and the spiral tube for explaining the method of FIG. It is a top view of the heat exchanger assembled by the method of FIG. FIG. 36 is a cross-sectional view of the heat exchanger of FIG. 35 taken along line AA.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

In FIG. 1, reference numeral 1 denotes a spiral heat exchanger which is an embodiment to which the present invention can be applied. In the figure, a cylindrical container 2 having an open top and bottom, and a partition wall 3 as a spiral partition wall portion. And a spiral tube 4 as a spiral tube portion and

lids

6 and 6. The container 2, the partition wall 3, the spiral tube 4 and the lid 6 are all made of metal such as aluminum, and the spiral tube 4 is arranged in a plurality of stages inside the partition wall 3 and is in close contact by welding. A partition wall 3 in which the spiral tubes 4 are in close contact with each other is arranged in the container 2, and the upper and lower openings of the container 2 are closed by

lids

6 and 6.

In this case, the upper and lower ends of the partition wall 3 are in close contact with the inner surfaces of the

lids

6 and 6, and the space between them is sealed. As a result, a series of spiral passages 7 are formed between the spiral partition walls 3 toward the outside while rotating from the center of the spiral. The spiral tube 4 is disposed in the spiral passage 7 so as to be in contact with the space in the spiral passage 7. As a result, the spiral tube 4 comes into contact with a fluid (first fluid described later) flowing in the spiral passage 7. Further, the spiral tubes 4 in a plurality of stages are spaced from each other, and as shown in FIG. 2, the outer ends of the spiral tubes 4 are communicated with each other by a header 8, and the end portion on the center side of the spiral Are also communicated by the header 9.

When the heat exchanger 1 is used as, for example, a refrigerant condenser in the Rankine cycle, cold water as the first fluid flows into the heat exchanger 1 from the center of the spiral in the spiral passage 7. Then, the spiral passage 7 flows while rotating outward from the center of the spiral as indicated by a thick arrow in FIG. 3, and flows out of the heat exchanger 1 from the side surface of the container 2. Further, for example, a high-temperature refrigerant as the second fluid flows from the header 8 and flows in each spiral tube 4 while rotating from the outside toward the center of the spiral as indicated by a thin arrow in FIG. It flows out of the heat exchanger 1.

At this time, the flow of the cold water (first fluid) is counterclockwise in FIG. 3, and the flow of the refrigerant (second fluid) is counterclockwise, so the flows of the cold water and the refrigerant are opposite to each other. Therefore, the temperature difference between the refrigerant flowing in the spiral tube 4 and the water flowing in the outer spiral passage 7 increases over the entire range from the header 8 on the inlet side to the header 9 on the outlet side. Will improve. In particular, since the refrigerant (second fluid) flows through the spiral tube 4, high pressure resistance design is facilitated even when a high-pressure refrigerant flows.

Next, the structure of the partition wall 3, the spiral passage 7, and the spiral tube 4 will be described with reference to FIG. The partition wall 3 is formed by forming in parallel a plurality of curved grooves 11 that are curved and recessed in a flat plate to have a corrugated cross section, and processing the flat plate into a spiral shape. And each spiral tube 4 is arrange | positioned corresponding to the inner side of each groove | channel 11 of this partition wall 3, respectively, after making close_contact | adherence using the curved surface of the groove | channel 11, it braces and separates the partition wall 3 and several steps. The spiral tube 4 is integrated. Thereafter, the header 8 is welded to the outer end portion of each spiral tube 4, and the header 9 is welded to the end portion on the outlet side.

In the heat exchanger 1 of the embodiment, the center direction of the vortex of the partition wall 3 and the vortex tube 4 is the horizontal direction, and the vertical direction perpendicular thereto is the vertical direction. Further, a predetermined interval (flow path width PB) is formed between the upper and

lower spiral tubes

4 and 4, and the partition wall 3 (in the direction of the center of the spiral) and the partition wall 3 (on the outside of the groove 11). A space (flow path width PA) is also formed between the outer surface and the protruding outer surface (FIG. 4). That is, the channel width PA is the width of the spiral passage 7 in which cold water (first fluid) flows outside the spiral tube 4 in a direction (horizontal direction) parallel to the center direction of the spiral of the spiral tube 4. The width PB is the width of the spiral passage 4 through which cold water (first fluid) flows outside the spiral tube 4 in the direction orthogonal to the center direction of the spiral of the spiral tube 4.

And in the heat exchanger 1 of an Example, it sets to channel width PA = channel width PB. Here, FIG. 5 shows the heat of the refrigerant (second fluid) and cold water (first fluid) when the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is changed. The change in the exchange amount is shown. As is apparent from this figure, the amount of heat exchange decreases before and after the ratio = 1 (flow path width PB = flow path width PA).

The reason is that when the flow path width PB is smaller than the flow path width PA, the cold water (first fluid) easily flows in the spiral passage 7 between the spiral tube 4 and the inner partition wall 3. This is because it becomes difficult to flow in the spiral passage 7 between the upper and lower spiral tubes 4 and the heat transfer area of the spiral tube 4 cannot be effectively used. This also applies to the case where the flow path width PB becomes larger than the flow path width PA. In this case, the inside of the spiral passage 7 between the spiral tube 4 and the inner partition wall 3 is cooled with cold water ( This is because it becomes difficult for the first fluid) to flow, and it becomes easy to flow in the spiral passage 7 between the upper and lower spiral tubes 4, and the heat transfer area of the spiral tube 4 cannot be effectively used.

By making the flow path width PA the same as the flow path width PB as in the embodiment, the flow path width PA of the spiral passage 7 in the center direction (inward) of the spiral of the spiral tube 4 and the direction (vertical) The flow path width PB of the spiral passage 7 is the same, and the flow path is between the partition wall 3 that is in close contact with the outside of the spiral tube 4 and the spiral tube 4 on the outside (opposite direction to the center of the spiral). The width PA is also the same. As a result, cold water (first fluid) flows evenly outside the entire circumference of the spiral tube 4, so that the refrigerant (second fluid) and cold water (first fluid) that make the most of the heat transfer area of the spiral tube 4 are used. ) And heat exchange.

In the embodiment, the flow path width PA is equal to the flow path width PB. However, as is apparent from FIG. 5, the ratio of the flow path width PB / the flow path width PA is in the range of 0.7 to 1.3. Thus, a relatively high heat exchange amount can be secured without increasing the dead space. The reason is as follows. That is, since the peak of the heat exchange amount is 1, if it is defined that 0.98 or more is a high heat exchange amount, when the ratio of the channel width PB / channel width PA is less than 0.7, Since the flow path of the first fluid (cold water) is not sufficient, the amount of heat exchange is not sufficient, and is less than 0.98. Therefore, the lower limit of the ratio of the channel width PB / channel width PA is 0.7. On the other hand, the heat exchange amount is maintained at 0.98 or more until the ratio of the channel width PB / channel width PA is about 2.3, but when the ratio is 1.3 or more, the channel width PB is As a result, the dead space is generated in the spiral flow path 7, and the size of the heat exchanger 1 is unnecessarily enlarged, resulting in inefficiency in terms of capacity and space. Therefore, the upper limit of the ratio of the channel width PB / channel width PA is 1.3.

Thus, the flow path width PA of the spiral passage 7 through which the cold water (first fluid) flows outside the spiral tube 4 in the direction parallel to the spiral center direction of the spiral tube 4 and the center direction of the spiral of the spiral tube 4 The flow path width PB of the spiral passage 7 through which the cold water (first fluid) flows outside the spiral tube 4 in the direction perpendicular to the spiral pipe 4 is made substantially equal, so that the cold water (first fluid) flows outside the spiral tube 4. The flow path width of the spiral passage 7 can be made substantially equal over substantially the entire circumference of the spiral tube 4. That is, the flow path width of the spiral passage 7 around the spiral tube 4 is drawn concentrically with the spiral tube 4 around the axis of the spiral tube 4, and cold water (first fluid) is distributed around the entire circumference of the spiral tube 4. Since it flows evenly, the heat transfer area of the spiral tube 4 can be fully utilized, and the heat exchange performance between the cold water (first fluid) and the refrigerant (second fluid) can be greatly improved.

In particular, the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is set to 0.7 to 1.3 as described above, and preferably the channel width PA as in the embodiment. = By making the flow path width PB, the flow of cold water (first fluid) outside the spiral tube 4 is effectively uniformed, and the heat exchange amount between the first fluid (cold water) and the second fluid (refrigerant) is reduced. It becomes possible to improve the heat exchange performance as a certain value or more (0.98 or more).

Next, FIG. 6 shows a heat exchanger 1 of an embodiment using a partition wall 3 having another shape. In this embodiment, the partition wall 3 has a corrugated cross section. In the case of the embodiment of FIG. 4, in the portion farthest from the

adjacent spiral tubes

4, 4 indicated by X in FIG. 7, that is, in the portion X in the center direction of the spiral between the upper and

lower spiral tubes

4, 4, Since the space between the partition wall 3 and the spiral tube 4 becomes wider, the flow path width of this portion X is inevitably increased, and more cold water (first fluid) tends to flow.

Therefore, in this embodiment, the partition wall 3 in the middle (in the direction of the center of the spiral) of the middle position (height) between the upper and

lower spiral tubes

4, 4 is projected toward the

outer spiral tubes

4, 4, A protruding portion 12 is formed, and the partition wall 3 has a corrugated cross section having the protruding portion 12. As a result, the flow path width of the portion X can be set to or close to the flow path width PA = PB, and the flow path width of the spiral passage 7 through which the first fluid flows in the entire circumference of the spiral tube 4. The heat exchange performance can be improved by making cold water (first fluid) flow all over the circumference of the spiral tube 4 evenly.

Next, FIG. 8 shows another example of the heat exchanger 1. In this embodiment, the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3. In this case, the spiral tube 4 is held away from the partition wall 3 by using a holder (not shown) having the same structure as the holder 18 shown in FIGS. 26 and 27, for example. With such a configuration, since cold water (first fluid) flows in contact with the entire circumference of the spiral tube 4, the refrigerant (second fluid) that flows in the spiral tube 4 flows around the entire circumference of the spiral tube 4. It becomes possible to exchange heat with the cold water (first fluid) flowing in the spiral passage 7 by using.

However, since the cold water (first fluid) flows in the spiral passage 7 from the center of the heat exchanger 1 to the outside, the outer partition that forms the spiral passage 7 by centrifugal force applied in the direction opposite to the center direction of the spiral. Try to flow a lot closer to wall 3. Therefore, when the spiral tube 4 is disposed in the center of the spiral passage 7 between the inner and

outer partition walls

3 and 3, a large amount of cold water (first fluid) is formed in the flow path between the inner partition wall 3 and the outer partition wall 3. ) Flows and the effective use of the heat transfer area of the spiral tube 4 is hindered.

Therefore, in this embodiment, the flow path width on the spiral side of the spiral tube 4 is PA1, the flow path width outside the spiral is PA2 (PA1 + PA2 = PA = PB), and further, the flow path width PA1 and the flow path width PA2 are set. The relationship is channel width PA2 <channel width PA1. As a result, the flow of the cold water (first fluid) outside the spiral tube 4 that tends to flow more due to centrifugal force and the flow of the cold water (first fluid) on the center side of the spiral can be made uniform. The exchange performance is improved.

Next, FIGS. 9 and 10 show another embodiment. In this embodiment, the partition wall portion 13 and the spiral tube portion 14 corresponding to the partition wall 3 and the spiral tube 4 in each of the embodiments described above are integrally formed on the extruded material 15 by extrusion molding of a metal such as aluminum. It is. The extruded material 15 of the embodiment is formed with a plurality of upper and lower spiral tube portions 14 having a circular passage in the inside, and the spiral tube portions 14 are connected to each other by a partition wall portion 13. ing.

And the spiral channel | path 7 is comprised between the inner and outer partition wall part 13 and the spiral pipe part 14 by winding the flat extrusion material 15 which concerns in a spiral shape. Also in this case, the flow path width PA of the spiral passage 7 outside the spiral tube portion 14 in the direction parallel to the spiral center direction of the spiral tube portion 14 is in a direction orthogonal to the spiral center direction of the spiral tube portion 14. The flow path width PB of the spiral passage 7 outside the spiral tube portion 14 (substantially the height dimension of the partition wall portion 13 connecting the upper and lower spiral tube portions 14, 14) is substantially equivalent (same in the embodiment). (FIG. 10).

Thus, by integrally extruding the partition wall portion 13 and the spiral tube portion 14, the partition wall is formed and spirally wound as in the above-described embodiment, and a plurality of spiral tubes are wound spirally. The operations of turning and bringing them into close contact with a predetermined position of the partition wall are integrated into simple operations of extrusion molding and winding, so that the number of parts can be reduced and the assembly workability can be remarkably improved.

Next, FIGS. 11 to 18 show another embodiment. In this embodiment, a protrusion 16 is integrally formed at the upper end of the spiral tube 4 (FIGS. 11 and 12). The ridge 16 extends in the axial direction of the spiral tube 4 and is erected in a wall shape. When the spiral tube 4 is stacked in a plurality of stages, the upper end of the ridge 16 is the other spiral tube 4 above. Is in close contact with and in close contact with the lower end (FIG. 13). As a result, the spiral passage 7 is formed between the inner and outer protrusions 16 and the spiral tube 4, and in this case, the partition wall portion is constituted by the spiral tube 4 and the protrusion 16.

14 to 16 show an example in which the protrusion 16 is formed not only on the upper end but also on the side surface in the center direction (inner side) of the spiral. In this case as well, the upper ridge 16 contacts the lower end of the other spiral tube 4 above, but the side ridge 16 contacts the outer side surface of the inner spiral tube 4 and partitions the spiral passage 7 vertically. Therefore, the flow in the vertical direction of the spiral passage 7 is also made uniform.

Also in this case, the flow path width PA which is the distance between the

spiral tubes

4 and 4 arranged in the center direction of the spiral is substantially equal to the flow path width PB which is the distance between the upper and lower spiral tubes 4 and 4 (substantially the height of the protrusion 16). (Same dimension in the embodiment).

Thus, in this embodiment, the ridge 16 extending in the axial direction of the spiral tube 4 is provided on the spiral tube 4, and the ridge 16 is brought into contact with another spiral tube 4 adjacent in the vertical direction or the center direction of the spiral. Thus, since the partition wall 3 is configured, it is not necessary to provide a special partition wall, and the spiral tube 4 is positioned, so that the number of parts can be significantly reduced.

The side protrusion 16 may be a protrusion 17 as shown in FIGS. The protrusion 17 also has the effect of positioning the spiral tube 4.

19 to 24 show an example in which only the protrusion 17 is formed on the spiral tube 4. In this case, the partition wall 3 is required. Then, a protrusion 17 is formed to protrude at the upper end of the spiral tube 4, and the protrusion 17 contacts the lower end of the other upper spiral tube 4 when it is stacked in a plurality of stages. The spiral 4 is in close contact (brazing) with the surface of the spiral partition wall 3 in the central direction of the spiral.

19 to 21, the protrusion 17 is formed only at the upper end of the spiral tube 4, but it may be formed on the side surface in the center direction of the spiral as in FIGS. 22 to 24. The side projections 17 abut against the outer surface of the inner partition wall 3.

Also in this case, the flow path width PA (substantially the dimension of the protrusion 17 in the case of FIG. 24) which is the distance between the

spiral tubes

4 and 4 arranged in the center direction of the spiral is the distance between the upper and

lower spiral tubes

4 and 4. The flow path width PB (substantially the height dimension of the protrusion 17) is substantially the same (same in the embodiment).

As described above, if the spiral tube 4 is provided with the projection 17 and the projection 17 is brought into contact with another adjacent spiral tube 4 or the partition wall 3, the spiral tube 4 can be positioned more firmly and easily. It becomes.

The projection 17 may be provided not only on the spiral tube 4 but also on the partition wall 3 side. FIG. 25 shows an example in which the projection 17 is formed on the partition wall 3. In this case, a projection 17 projecting outward (opposite to the direction of the center of the spiral) is formed on the outer surface side of the groove 11 of the wave-shaped partition wall 3 similar to FIG. It contacts the inner side of the outer spiral tube 4 (side surface in the center direction of the spiral).

Also in this case, the flow path width PA (substantially the dimension of the projection 17 in the case of FIG. 25) which is the distance between the spiral tubes 4 arranged in the center direction of the spiral and the partition wall 3 is the same between the upper and

lower spiral tubes

4 and 4. The channel width PB, which is the interval, is substantially the same (same in the embodiment).

Thus, if the projection 17 is provided on the partition wall 3 and this projection 17 is brought into contact with the other spiral tube 4 adjacent to the outside, the spiral tube 4 can be positioned more firmly and easily. Become.

Next, FIG. 26 and FIG. 27 show another example of the attachment structure of the spiral tube 4. When the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3 as in the case of FIG. 8 described above, the inner surface of the partition wall 3 (the center of the spiral) The holder 18 is attached to the direction surface. The holder 18 extends in the vertical direction of the partition wall 3 and is provided at a plurality of locations so as to protrude from the partition wall 3. The holding groove 19 is semicircular (curved) at intervals where the spiral tube 4 is disposed. A plurality of (the bottom of the groove is separated from the partition wall 3) is formed.

Then, the spiral tube 4 is closely attached to the holding groove 19 and held. Accordingly, the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3.

At this time, the spiral tube 4 may be fixed to the holding groove 19 by welding, but may be detachably attached by fitting. When the spiral tube 4 is detachably attached to the holding groove 19 of the holder 18 provided on the partition wall 3, for example, when dust or scale in the first fluid adheres to the spiral tube 4 or the partition wall 3, the partition wall 3 and the spiral tube 4 can be easily disassembled and cleaned.

Next, FIG. 28 to FIG. 31 show an embodiment of the spiral heat exchanger 1 of the present invention and the manufacturing method thereof. In addition, the structure which is not shown by these figures shall be the same as that of each said Example. In this embodiment, the spiral tube 4 is attached to the inner surface of the partition wall 3 (the surface in the direction of the center of the spiral). FIG. 28 shows the partition wall 3 in this case, in which a spiral planar shape is shown on the upper side and a side sectional shape is shown on the lower side. The partition wall 3 of the embodiment has a corrugated cross-section in which

grooves

21 and 22 are formed alternately on the outer surface and the inner surface (the surface on the side of the center of the spiral).

FIG. 29 shows the planar shape of the spiral tube 4. In this case, the width dimension W of the groove 21 portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4. Then, the partition wall 3 is rotated 180 ° from FIG. 28, and the spiral tube 4 is meshed with the partition wall 3 in this state concentrically (the center of the spiral is the same) (FIG. 30). At this time, the spiral tube 4 is disposed corresponding to the groove 21 of the partition wall 3.

When the partition wall 3 and the spiral tube 4 are arranged as described above, the partition wall 3 is rotated clockwise in FIG. 30 (the direction in which the inner end of the partition wall 3 is further wound) about the center of the spiral as a partition. Since the wall 3 generally moves outward with respect to the spiral tube 4, the spiral tube 4 enters into and closely contacts the groove 21 on the outer surface of the partition wall 3 (FIG. 31). FIG. 31 also shows a plane on the top and a side section on the bottom.

In addition, what is necessary is just to rotate counterclockwise of FIG. Also in this case, the flow path width PA, which is the distance between the spiral tube 4 and the partition wall 3 aligned in the center direction of the spiral, and the distance between the upper and lower spiral tubes 4 and 4 (interval of the groove 21 in the case of FIG. 31). The channel width PB is substantially equivalent (same in the embodiment).

In this way, a continuous groove 21 is formed in the partition wall 3, and the width W of the partition wall 3 in the groove 21 portion is made smaller than the spiral interval R of the spiral tube 4 so as to correspond to the groove 21 of the partition wall 3. If the spiral tube 4 is disposed, and the partition wall 3 or the spiral tube 4 is rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 21, so that the partition wall 3 or the spiral tube 4 is rotated. The heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 with an extremely simple operation.

Next, FIGS. 32 to 36 show another embodiment of the method for manufacturing the spiral heat exchanger 1 of the present invention. In this embodiment, the spiral tube 4 is attached to the groove 24 of the hook 23 formed on the outer surface of the partition wall 3 (the surface on the side opposite to the center direction of the spiral). In this case, the hook 23 is formed at a plurality of locations on the partition wall 3, and a C-shaped groove 24 is formed at the tip thereof (FIG. 32).

FIG. 33 shows the planar shape of the spiral tube 4. Also in this case, the width dimension W of the hook 23 (groove 24) portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4. Then, the spiral tube 4 is concentrically engaged with the partition wall 3 (the center of the spiral is the same) (FIG. 34). At this time, the spiral tube 4 is disposed corresponding to the groove 24 of the hook 23 of the partition wall 3.

When the partition wall 3 and the spiral tube 4 are arranged as described above, the partition wall 3 is rotated clockwise in FIG. 34 around the center of the spiral (direction in which the inner end of the partition wall 3 is further wound). Since the wall 3 generally moves outward with respect to the spiral tube 4, the spiral tube 4 is detachably fitted into and closely attached to the groove 24 of the hook 23 on the outer surface of the partition wall 3 (FIG. 35, FIG. 36).

Incidentally, when the spiral tube 4 is rotated, it may be rotated counterclockwise in FIG. Further, the relationship between the channel widths PA1, PA2 (PA) and PB in this case is the same as in FIG. In this way, the groove 24 is formed in the hook 23 of the partition wall 3, and the width W of the partition wall 3 in the hook 23 (groove 24) portion is made smaller than the spiral interval R of the spiral tube 4. If the spiral tube 4 is arranged corresponding to the groove 24 of the 23, and the partition wall 3 and the spiral tube 4 are rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 24. The heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 by an extremely simple operation by simply rotating the wall 3 and the spiral tube 4.

In particular, in this embodiment, since the spiral tube 4 is detachably fitted into the groove 24 of the hook 23 of the partition wall 3, the heat exchanger 1 capable of easily disassembling the partition wall 3 and the spiral tube 4 is manufactured. As a result, dust and scale attached to the heat exchanger 1 can be easily washed.

In addition, although the Example demonstrated the heat exchanger which implement | achieves heat exchange with cold water and a refrigerant | coolant by Rankine cycle as an example, it is not restricted to this, This invention is effective for the spiral heat exchanger of all uses. In the embodiments, the first fluid is cold water and the second fluid is a refrigerant. However, the present invention is not limited to this, and the heat exchanger of the present invention can be used for heat exchange between various fluids having temperature differences.

1 Heat exchanger 2 Container 3 Partition wall (partition wall)
4 Spiral tube (spiral tube)
6 Lid 7

Spiral path

8, 9

Header

11, 21, 24 Groove 12 Projection 13 Partition wall 14 Spiral tube 15 Extrusion material 16 Projection 17 Projection 18 Holder 19 Holding groove 23 Hook

Claims

A spiral passage is formed between the spiral partition walls provided in the container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages, and the first fluid flowing in the spiral passage outside the spiral tube and the inside of the spiral tube are disposed. In a heat exchanger that exchanges heat with the flowing second fluid,
Comprising a groove formed in the partition wall;
A width dimension W of the partition wall of the groove portion is configured to be smaller than a spiral interval R of the spiral tube,
The spiral tube is in close contact with the groove by rotating the partition wall and / or the spiral tube around the center of the spiral in a state corresponding to the groove of the partition wall. A heat exchanger characterized by
The heat exchanger according to claim 1, wherein the spiral tube is detachably fitted in a groove of the partition wall.
A spiral passage is formed between the spiral partition walls provided in the container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages, and the first fluid flowing in the spiral passage outside the spiral tube and the inside of the spiral tube are disposed. In a heat exchanger that exchanges heat with the flowing second fluid,
Forming a groove in the partition wall;
The width W of the partition wall of the groove portion is made smaller than the spiral interval R of the spiral tube,
The spiral tube is arranged corresponding to the groove of the partition wall,
A method of manufacturing a heat exchanger, comprising: rotating the partition wall and / or the spiral tube around the center of the spiral to bring the spiral tube into close contact with the groove.
The method for manufacturing a heat exchanger according to claim 3, wherein the spiral tube is detachably fitted in a groove of the partition wall.