KR20100066633A - A finless cooling-storage heat exchanger - Google Patents

Abstract

PURPOSE: A finless cold storage heat exchanger is provided to efficiently process cooling by storing cold storage material in a part of a tube. CONSTITUTION: A finless cold storage heat exchanger(100) comprises: a plurality of tubes(11); a tank part(12) which is connected to an internal flow channel(13) of the tube; an inlet(31) and an outlet(32) which are formed in an end plate(20); a cold storage material inlet(41) which is formed in the end plate; a cold storage material circulating line(42) which is interlinked to the cold storage material inlet and is formed in the top of the tube and the bottom of the tube or in the one which is selected between the top or the bottom; and a cold storage material storage line(43) which stores cold storage material in the inside, is connected to the cold storage material circulating line, and is parallelly formed with the internal flow channel.

Description

Finless Cooling-Storage Heat Exchanger

The present invention relates to a finless accumulator heat exchanger.

The heat exchanger generally includes a pair of header tanks through which the heat exchange medium is introduced and discharged, and a tube which connects the header tanks and distributes the heat exchange medium therein to perform heat exchange. 1 shows a conventional fin-tube type heat exchanger. The heat exchanger (100 ') includes a plurality of tubes (20') in which a heat exchange medium flows therein and arranged in parallel in a line at a predetermined interval in parallel to the air blowing direction; An inlet header tank (11 ') for distributing the heat exchange medium through the inlet (11'a) and distributing the heat exchange medium to the plurality of tubes (20'); A heat dissipation fin (30 ') interposed between the tubes (20') and increasing a heat transfer area with air flowing between the tubes (20 '); The heat exchange medium moving in the tube 20 'is collected, and is composed of a discharge header tank 12' for discharging the collected heat exchange medium through the outlet 12'a.

In general, a fin-tube type heat exchanger having a header tank, a tube, and a heat dissipation fin has been widely used as described above. However, in the fin-tube type heat exchanger, since the heat dissipation fins become an essential component, manufacturing costs by the heat dissipation fins increase, the weight becomes heavy, and the number of assembly operations increases.

In particular, when using a conventional fin-tube type heat exchanger, condensed water may be generated in the heat dissipation fin portion, which may cause deterioration of heat exchange performance of the heat exchanger. In addition, not only corrosion of the components may be caused by the accumulated moisture, and an unpleasant smell may occur due to breeding of bacteria, and such odor may be introduced into the vehicle, thereby degrading the interior comfort of the vehicle.

In order to solve this problem, a finless type heat exchanger has been proposed. Similar to the fin-tube type heat exchanger, the finless type heat exchanger has components corresponding to the header tank and the tube but excludes the heat dissipation fins. The finless heat exchanger exchanges heat only by the heat pipe corresponding to the tube of the fin-tube type heat exchanger. As the heat exchanger, there are various kinds such as plate stacked type, curved extruded tube type, and round multi-tube type.

2 shows a conventional plate stacked finless type heat exchanger. As shown in FIG. 2, the conventional plate stacking finless type heat exchanger 100 ″ is capable of heat exchange with air flowing outwardly and allows the heat exchange medium to flow through the inner flow passage 13 ″. A plurality of tubes 11 ", which are coupled to each other by a pair of plates 10 ", are connected to the flow path 13 ", and communicate with each other at upper and lower portions of the pair of plates 10 ". The tank portion 12 '' to be installed and the tube 11 '' are formed on the end plate 20 '' coupled to the outermost part of the laminated body in which a plurality of tubes are stacked to heat exchange the tube 11 ''. And an inlet 31 " and an outlet 32 " for introducing and discharging the medium. FIG. 2B shows a cross-sectional view of the conventional plate stack finless heat exchanger 100 ″. As shown, the pair of plates 10 ″ are coupled to each other to form one tube 11 ″, and the heat exchange medium flows through the flow path 13 ″ formed on the plate 10 ″. Will be.

On the other hand, in the case of idling, driving, and the like during driving of the vehicle, the cooling performance of the in-vehicle air conditioner is lowered as compared with normal driving. Therefore, in this case, in order to cool the air in the vehicle, the compressor and the blower fan are often driven by separate power sources. Accordingly, the power consumption of the battery is generated, and as a result, the overall fuel efficiency of the vehicle may be reduced. .

In the case of the finless heat exchanger, since the heat radiation fins do not exist, condensed water accumulates in the heat radiation fins in this case, and thus there is a problem in the occurrence of odor and consequent deterioration of comfort in the vehicle, but it has the following problems. That is, since the heat exchange area with the outside air is smaller than that of the tube-fin type heat exchanger, the effect of deterioration of the cooling performance is further increased in the case of an idle state, a stop state, and the like. Therefore, cooling in the vehicle is not effectively performed, and thus there is a problem in that the comfort deterioration problem in the vehicle occurs again.

Therefore, the present invention has been made to solve the problems of the prior art as described above, the object of the present invention has a plate-type heat exchanger structure, the coolant is stored in a portion of the tube when idling at idle, start, It is to provide a finless heat storage heat exchanger that can be effectively cooled even in the case of the initial time. Another object of the present invention is to take the role of the heat radiation fins by forming an unevenness in the air flow direction on the outer surface forming the tube instead of taking the structure of the external heat radiation fins sandwiched between the tubes, thereby maintaining heat exchange performance The present invention provides a finless heat storage heat exchanger that smoothly drains condensate and thereby blocks problems such as odor generation.

Finless heat storage heat exchanger of the present invention for achieving the object as described above, the pair of plates 10 are mutually coupled so that heat exchange with the air flowing to the outside and the heat exchange medium can flow through the inner passage (13) A plurality of tubes (11), a tank portion (12) connected to the flow path (13) and installed on top and bottom of the pair of plates (10) so as to communicate with each other, and a plurality of tubes (11). Finless accumulator heat exchanger formed on the end plate (20) coupled to the outermost of the laminated assembly comprising an inlet (31) and outlet (32) for introducing and discharging the heat exchange medium to the tube (11) 100, wherein the finless heat storage heat exchanger (100) is formed on the end plate (20) to the coolant inlet for introducing the coolant; A coolant flow passage (42) which is in communication with the coolant inlet (41) and formed at any one position selected from the top, bottom, and top and bottom of the tube (11), and is installed in communication with each other; A coolant storage path 43 connected to the coolant flow path 42 and formed in parallel with the flow path 13 so that the coolant is stored therein; And further comprising:

In this case, the tube 10 has the same symmetrical shape in a direction in which the pair of plates 10 constituting the one tube 11 face each other, and the flow paths 13 are disposed to be offset from each other so that air is zigzag. It is characterized in that the two kinds of tubes 11 are arranged to cross a plurality of flow.

Alternatively, the tube 10 is disposed so that the recesses forming the flow path 13 or the coolant storage passage 43 are displaced from each other in a direction in which the pair of plates 10 constituting the one tube 11 face each other. It is characterized in that a plurality of single-type tube 11 forming a shape that is arranged.

In addition, the coolant storage path 43 is formed in the same shape as the flow path 11 or is characterized in that it is formed to have a wider width than the flow path (11).

In addition, the coolant storage passage 43 is formed in the center of the tube 11, is formed in the air flow upstream direction, characterized in that formed in the air flow downstream direction.

In addition, the tube 10 has a recess formed in one plate so that the refrigerant flows to form the flow path 13, and the recess formed in the other plate has a coolant stored therein to form the coolant storage passage 43. It is characterized in that it further comprises a partition plate 55 interposed between the plate 10 of the pair.

In addition, the finless heat storage heat exchanger 100 includes at least one tube 10 having only the flow path 13 through which a refrigerant flows, and a heat storage tube 50 having only the heat storage agent storage path 43 in which the heat storage agent is stored. It is characterized by consisting of alternating rows or more.

In addition, the coolant inlet 41 is characterized in that it is provided with a lid to be easily opened and closed.

According to the present invention, since the coolant is stored in a part of the tube, the cooling effect can be effectively achieved even when idling, stopping, starting up, etc. Therefore, the cooling effect and comfort in the vehicle can be There is an effect that can be maintained to a certain degree regardless. In addition, in the case of the present invention, instead of taking the structure of omitting the external heat dissipation fins interposed between the tubes in the conventional fin-tube type heat exchanger, by acting as a heat dissipation fin by forming an unevenness in the air flow direction on the outer surface forming the tube In addition, there is an effect of maintaining the heat exchange performance and at the same time smooth the drainage of condensate. In addition, since the heat radiation fins are omitted in the structure of the heat exchanger, problems such as corrosion of parts and odors due to bacterial propagation are eliminated by condensation, thus improving durability of the product and in-vehicle. Comfort effect can also be obtained.

Hereinafter, with reference to the accompanying drawings the finless heat storage heat exchanger according to the present invention having the configuration as described above will be described in detail.

3 is an exploded perspective view of the finless heat storage heat exchanger of the present invention. As shown, the finless heat storage heat exchanger (100) of the present invention is basically capable of heat exchange with air flowing to the outside and allows the heat exchange medium to flow through the inner flow passage (13), similarly to the existing heat storage heat exchanger. A plurality of tubes 11 having a pair of plates 10 coupled to each other, a tank portion 12 connected to the flow path 13 and installed in upper and lower portions of the pair of plates 10 so as to communicate with each other; The inlet 31 and the outlet 32 are formed on the end plate 20 coupled to the outermost part of the plurality of laminated bodies, the inlet and outlet of the heat exchange medium to the tube 11. It is made, including, further comprising a coolant inlet 41, a coolant flow passage 42 and a coolant storage passage 43.

The coolant inlet 41 is formed on the end plate 20 to inject the coolant, and as shown, the coolant inlet 41 may be formed in a shape similar to the inlet 31 and the outlet 32 through which the coolant is introduced or discharged. Can be. The coolant flowing into the coolant inlet 41 is introduced into each of the coolant storage paths 43 through the coolant flow path 42, and when the appropriate amount is filled, the coolant inlet 41 is filled. Is closed so that the coolant is stored in the coolant flow passage 42 and the coolant storage path 43. In addition, since the coolant may need to be replaced or replenished, the coolant inlet 41 may be formed to be easily opened and closed by a structure such as a lid.

The coolant flow passage 42 is in communication with the coolant inlet 41, is formed at any one position selected from the top, bottom or top and bottom of the tube 11, it is installed so as to communicate with each other. That is, the coolant flow passage 42 is formed in a shape similar to that of the tank part 12 having a structure in which a coolant is circulated throughout the inside of the finless heat storage heat exchanger 100. Since the refrigerant and the coolant should not be mixed, the coolant flow passage 42 and the tank portion 12 should be formed completely independently of each other.

The coolant storage path 43 is connected to the coolant flow path 42 so that the coolant is stored therein and is formed in parallel with the flow path 13. In other words, the coolant storage passage 43 is formed to have a shape similar to the tube 11 arranged in the height direction so that the refrigerant inside may cause heat exchange with the outside air flow. In summary, the coolant flow passage 42 is the tank portion 12, and the coolant storage passage 43 corresponds to the tube 11, respectively, are formed in a similar shape to each other. Of course, the coolant storage passage 43 should also be formed in a completely independent form, which is not in communication with the tube 11 or the tank portion 12, which is a portion through which the refrigerant flows.

In FIG. 3, the inlet 31 and the outlet 32 are shown as being gathered at an upper portion of one of the end plates 20, but of course, this is due to the flow path design of the finless heat storage heat exchanger 100. The position can be changed accordingly. Similarly, in FIG. 3, the coolant inlet 41 is illustrated in the lower center of the end plate 20 provided with the inlet 31 and the outlet 32. The position of the furnace 42 and the coolant storage passage 43 may be appropriately changed depending on the shape, design conditions, and the like.

4A-4M illustrate various embodiments of the coolant flow passage 42 and the coolant storage passage 43. 4A to 4M are cross-sectional views taken along line AA ′ of FIG. 3, and each of (B) or (C) shows plates constituting each tube, and the plates face each other shown in the drawing. To be combined.

A first embodiment of FIG. 4A will be described. In the first embodiment, two types of tubes 11 as shown in FIG. 4A are arranged in a cross arrangement. In more detail, the plates 10 shown on the left and right sides of FIG. 4A (B), respectively, are coupled to face each other to form the tubes 11a-A shown on the upper side of FIG. 4A (A). The plates 10 shown on the left and right sides of FIG. 4A (C), respectively, are coupled to face each other to form the tubes 11a-B shown below in FIG. 4A (A). In the first embodiment, the plates 10 forming the tubes 11a-A and 11a-B are formed in the same shape as each other.

In this first embodiment, the coolant storage passage 43 is located at the center of the tube 11a, and the coolant storage passage 43 has the same width and height as the flow passage 13. In addition, the tubes 11a-A shown in FIG. 4A (A) or in FIG. 4A (B) and the tubes 11a-B shown in FIG. 4A (B) or in FIG. The flow path 13 and the coolant storage path 43 are disposed at positions that are displaced to form a flow path in which the air flowing therebetween proceeds in a zigzag form.

The second embodiment of Fig. 4B will be described. In the second embodiment, two types of tubes 11 as shown in FIG. 4B are arranged in an alternating manner. In more detail, the plates 10 respectively shown on the left and right sides of FIG. 4B (B) are coupled to face each other to form the tubes 11b-A shown on the upper side of FIG. 4B (A). The plates 10 shown on the left and right sides of FIG. 4B (C), respectively, are coupled to face each other to form the tubes 11b-B shown below in FIG. 4B (A). In the second embodiment, the plates 10 forming the tubes 11b-A and 11b-B are formed in the same shape in the flow path 13 portion of the tube.

In this second embodiment, the coolant storage passage 43 is located at the center of the tube 11b, and the coolant storage passage 43 is symmetrically in a direction in which the plates 10 face each other. It is not formed, the recessed portion is formed in one plate 10 and the other plate 10 has a flat shape without the recessed portion, when the two plate 10 is combined, the recessed portion of one plate is the refrigerant storage path And (43). Therefore, the heat storage coolant storage path 43 in the second embodiment has a height of 1/2 of the height of the flow path 13, instead, the width is formed wider than the flow path (13).

The tubes 11b-A shown in FIG. 4B (A) or in FIG. 4B (B) and the tubes 11b-B shown in FIG. 4B (A) or in FIG. 13 is disposed at an offset position, so that the air flowing therebetween forms a flow path in a zigzag form at the portion where the flow paths 13 are formed. When the coolant storage path 43 is formed at both sides, the coolant storage paths 43 meet each other so that air cannot flow or the gap between the tubes 11b must be widened, thereby degrading heat exchange performance. In the second embodiment, each side of the plate 10 forming the coolant storage path 43 for a smooth flow of air has a non-symmetrical shape (one side is a main portion and the other side is a plane). It must be formed.

A third embodiment of FIG. 4C will be described. In the third embodiment, two types of tubes 11 as shown in FIG. 4C are arranged in a cross. More specifically, the plates 10 shown on the left and right sides of FIG. 4C (B), respectively, are coupled to face each other to form the tubes 11c-A shown on the upper side of FIG. 4C (A). The plates 10 shown on the left and right sides of FIG. 4C (C) are coupled to face each other to form the tubes 11c-B shown on the lower side of FIG. 4C (A). In the third embodiment, the plates 10 forming the tubes 11c-A and 11c-B are formed in the same shape in the opposite direction.

In this third embodiment, the coolant storage passage 43 is arranged on the left side (air flow upstream direction) or the right side (air flow downstream direction) of the tube 11c, and is also arranged above the flow passage 13. It is formed to have a wide width. In addition, the tubes 11c-A shown in the upper side of FIG. 4C (A) or FIG. 4C (B) and the tubes 11c-B shown in the lower side of FIG. 4C (A) or FIG. The flow path 13 and the coolant storage path 43 are disposed at positions that are displaced to form a flow path in which the air flowing therebetween proceeds in a zigzag form.

A fourth embodiment of FIG. 4D and a fourth embodiment of FIG. 4E will be described. In the fourth and fifth embodiments, two types of tubes 11 as shown in FIGS. 4D and 4E are alternately arranged. In more detail, the plates 10 shown on the left and right sides of FIG. 4D (B), respectively, are coupled to face each other to form the tubes 11d-A shown on the upper side of FIG. 4D (A). The plates 10 shown on the left and right sides of FIG. 4D (C), respectively, are coupled to face each other to form the tubes 11d-B shown on the lower side of FIG. 4D (A). In the fourth embodiment, the plates 10 forming the tubes 11d-A and 11d-B are formed in the same shape as each other. The same applies to the fifth embodiment.

In this fourth and fifth embodiments, the coolant storage passage 43 is located on the right side (air flow downstream direction) of the tube 11d (fourth embodiment) or the tube 11e. (5th embodiment) and the coolant storage passage 43 has the same width and height as the flow path 13. That is, in the fourth embodiment and the fifth embodiment, the coolant storage path 43 is formed to be biased toward one side of the upstream or downstream direction of the air flow, and the finless heat storage heat exchanger 100 is used as a heat exchanger. It is possible to choose an advantageous side according to the.

In addition, the tubes 11d-A shown in FIG. 4D (A) or in FIG. 4D (B) and the tubes 11d-B shown in FIG. 4D (A) or in FIG. The flow path 13 and the coolant storage path 43 are disposed at positions that are displaced to form a flow path in which the air flowing therebetween proceeds in a zigzag form. The same applies to the fifth embodiment.

In the first to fifth embodiments, the pair of plates 10 constituting one tube 11 form the same symmetrical shape in a direction facing each other, and the flow paths 13 are disposed to be offset from each other. It is an embodiment of the shape of the coolant storage unit in the case where a plurality of the two kinds of tubes 11 are arranged crosswise to flow in a zigzag.

Unlike the sixth to ninth embodiments, the pair of plates 10 constituting one tube 11 face each other (e.g., the flow path 13 or the coolant storage path 43). These are embodiments of the shape of the coolant storage unit in the case where a plurality of single-type tubes 11 forming a shape in which recesses are formed to be offset from each other are arranged. To describe the tube 11 in more detail, the concave portion forming portion of one plate and the planar portion of the other plate are coupled to face each other, so that only the concave portion forming portion of the one plate has a flow path 13 or a coolant storage passage 43. Will be formed.

A sixth embodiment of Fig. 4F will be described. In the sixth embodiment, tubes formed by combining two types of plates as shown in FIG. 4F (B) are arranged to form a heat exchanger core. In more detail, the plates 10f-A and 10f-B respectively shown on the left and right sides of FIG. 4F (B) are coupled to face each other to constitute the tube 11f shown on the upper side of FIG. 4F (A). Done.

In this sixth embodiment, the coolant storage passage 43 is located at the center of the tube 11f, and the coolant storage passage 43 is also formed to have a wider width than the flow passage 13. do. As shown, the shape of the tube 11f itself forms a flow path in which air flowing between the tubes 11f is arranged in a zigzag form.

The seventh embodiment of Fig. 4G to the ninth embodiment of Fig. 4I will be described. In each embodiment, as in the sixth embodiment, tubes formed by combining two types of plates are arranged to form a heat exchanger core.

In the seventh to ninth embodiments, the coolant storage path 43 has the same width and height as the flow path 13. In addition, in the seventh embodiment, the coolant storage path 43 is located at the center of the tube 11f. In the eighth embodiment, the coolant storage path 43 is the left side of the tube 11f (air flow). Upstream), and in the ninth embodiment, the coolant storage passage 43 is located on the right side (air flow downstream direction) of the tube 11f. As shown, the shape of the tube 11f itself forms a flow path in which air flowing between the tubes 11f is arranged in a zigzag form.

In the first to ninth embodiments, all the channels 11 are formed with the flow paths 13 and the coolant storage path 43, but in the following tenth and eleventh embodiments, only the refrigerant flows. The cold storage tube 51 in which only the tube 11 and the coolant are stored is alternately arranged in one or more rows. In other words, the tube 11 and the cold storage tube 51 may be alternately arranged, or one cold storage tube 51 may be arranged per number of the tube 11. The plate which comprises the storage cooling tube 51 is called a storage cooling tube plate below.

Fig. 4J shows the tenth embodiment and Fig. 4K shows the eleventh embodiment. In the tenth embodiment of FIG. 4J, the main parts (that form the flow passage 13 or the coolant storage passage 43) are arranged in the direction in which the pair of plates 10 constituting the one tube 11 face each other. This is a case where a plurality of single-type tubes 11 constituting a displaced shape are arranged. In the eleventh embodiment of FIG. 4K, a pair of plates 10 constituting one tube 11 face each other. The same symmetrical shape is provided in which a plurality of two kinds of tubes 11 are arranged to cross each other so that the flow paths 13 are arranged to be offset from each other so that air flows in a zigzag.

As shown in both embodiments, in each of the cold storage tubes 51, the coolant storage passages 43 are formed in a path communicating with each other without mixing with the refrigerant flowing in the tube 11, and thus, each tube 11 ), The flow paths 13 are formed to form a U-flow.

In the first to eleventh embodiments, in forming one tube 11, two plates 10 each having recesses for forming the flow passage 13 or the coolant storage passage 43 are formed. Combined. In the following twelfth and thirteenth embodiments, the tubes 11 are provided with two plates 10 each having recesses for forming the flow passage 13 or the coolant storage passage 43, respectively. The partition plate 55 interposed between the plates 10 is coupled to be further coupled to each other, and a refrigerant flows into one side of the compartment plate 55 in one tube 11 and a coolant flows into the other side. Will be.

4L shows the twelfth embodiment and FIG. 4M shows the thirteenth embodiment. In the twelfth embodiment of FIG. 4L, the main parts (that form the flow passage 13 or the coolant storage passage 43) in the direction in which the pair of plates 10 constituting the one tube 11 face each other are different from each other. This is a case where a plurality of single-type tubes 11 arranged in a shape arranged to be displaced are arranged, and in the thirteenth embodiment of FIG. 4M, a pair of plates 10 constituting one tube 11 face each other. The same symmetrical shape is provided in which a plurality of two kinds of tubes 11 are arranged to cross each other so that the flow paths 13 are arranged to be offset from each other so that air flows in a zigzag.

As shown in both embodiments, each compartment plate 55 has a tank portion 12 and a coolant communication passage so that the coolant storage passages 43 can communicate with each other without mixing with the refrigerant flowing in the tube 11. 42 is formed, so that the flow paths 13 in each tube 11 are formed to form a U-flow.

The present invention is not limited to the above-described embodiments, and the scope of application of the present invention is not limited to those of ordinary skill in the art to which the present invention pertains without departing from the gist of the present invention as claimed in the claims. Of course, various modifications can be made.

1 is a perspective view of a conventional fin-tube type heat exchanger.

Figure 2 is an exploded perspective view of a conventional plate type heat exchanger.

3 is an exploded perspective view of one embodiment of a finless accumulator heat exchanger of the present invention;

4A-4M illustrate several embodiments of the finless quench heat exchanger of the present invention.

** Description of the symbols for the main parts of the drawings **

100: finless heat exchanger

10: Plate 11: Tube

12: tank part 13: euro

20: end plate 31: inlet

32: outlet 41: coolant inlet

42: coolant distribution channel 43: coolant storage channel

50: cold storage tube plate 51: cold storage tube

55: compartment plate

Claims (8)

It is connected to the plurality of tubes (11), the pair of plates (10) formed of a pair of plates 10 are mutually coupled to each other to exchange heat with the air flowing to the outside and to allow the heat exchange medium to flow through the inner passage (13), It is formed on the tank portion 12 which is installed in communication with each other in the upper and lower portions of the pair of plates 10, and the end plate 20 is coupled to the outermost of the plurality of laminated body of the tube 11 In the finless accumulator heat exchanger (100) comprising an inlet (31) and an outlet (32) for introducing and discharging the heat exchange medium into the tube (11), The finless heat storage heat exchanger 100 A coolant inlet (41) formed on the end plate (20) to introduce a coolant; A coolant flow passage (42) which is in communication with the coolant inlet (41) and formed at any one position selected from the top, bottom, and top and bottom of the tube (11), and is installed in communication with each other; A coolant storage path 43 connected to the coolant flow path 42 and formed in parallel with the flow path 13 so that the coolant is stored therein; Finless accumulator heat exchanger, characterized in that further comprises. The method of claim 1, wherein the tube (10) The pair of plates 10 constituting one tube 11 form the same symmetrical shape in a direction facing each other, the two kinds of tubes 11 so that the flow paths 13 are arranged to be offset from each other so that air flows in a zigzag. Fins storage cold heat exchanger characterized in that a plurality of crossover arrangement. The method of claim 1, wherein the tube (10) A single type of tube having a shape in which the recesses forming the flow path 13 or the coolant storage passage 43 are arranged to be offset from each other in a direction in which the pair of plates 10 constituting one tube 11 face each other ( A finless heat storage heat exchanger characterized in that a plurality of 11) are arranged. According to claim 1, wherein the coolant storage passage 43 is Finless storage heat exchanger, characterized in that formed in the same shape as the flow path (11) or having a wider width than the flow path (11). According to claim 1, wherein the coolant storage passage 43 is Finless accumulator heat exchanger, characterized in that formed in the center of the tube (11), in the upstream of the air flow, or in the downstream direction of the air flow. The method of claim 1, wherein the tube (10) The recess formed in one plate has a refrigerant flowing therein to form the flow path 13, and the recess formed in the other plate has a coolant stored therein so as to form the coolant storage path 43, between the pair of plates 10. Finless storage heat exchanger characterized in that it further comprises a partition plate (55) interposed. According to claim 1, wherein the finless heat storage heat exchanger (100) Fins, characterized in that the tube 10 formed only the flow path 13 through which the refrigerant flows and the accumulator tube 50 formed only of the coolant storage path 43 in which the coolant is stored are alternately arranged in at least one row. Heatless heat exchanger. The method of claim 1, wherein the coolant inlet 41 is Finless accumulator heat exchanger, characterized in that the lid is provided to be easily opened and closed.

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