JP2016176678A - Cold storage heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure a wide ventilation area, and joint a plurality of plates airtightly.SOLUTION: In a heat transfer member 30, flow passages T1, T2 in which refrigerant circulates, and a storage space T3 storing a cold storage material are aligned in a flow direction of outside air. The heat transfer member 30 includes plates C1, C3 for flow passage formation, and a plate C2 for storage space formation. One end parts of the plates C1, C3 for flow passage formation are fitted to the plate C2 for storage space formation with brazing.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a cooling heat exchanger that is used in, for example, a vehicle air conditioner to cool air-conditioning air, and particularly relates to the technical field of a cold storage heat exchanger having a cold storage material that stores the cold heat of a refrigerant.

  The heat exchanger for cooling of the vehicle air conditioner is composed of an evaporator that is one element of the refrigeration cycle apparatus. In recent years, for example, the number of vehicles with an idling stop function for temporarily improving the fuel consumption by temporarily stopping the engine has increased. In such a vehicle, when the refrigeration cycle apparatus is stopped when the engine is stopped, the heat for cooling is increased. Since the cooling capacity of the air by the exchanger decreases and may cause discomfort to the occupant, a cold storage heat exchanger that stores the cold heat of the refrigerant when the refrigeration cycle apparatus is operating may be used. (For example, refer to Patent Documents 1 and 2).

  The cold storage heat exchangers disclosed in Patent Documents 1 and 2 are laminated in a direction in which a refrigerant pipe through which refrigerant flows, fins, and a cold storage container that stores the cold storage material intersect with the flow direction of external air. The headers are disposed at both ends of the refrigerant pipe. The refrigerant flowing into the header cools the external air by exchanging heat with the external air through the fins while flowing through the refrigerant pipe, and cools the cold storage material through the cold storage material container so that the cold heat becomes the cold storage material. Stored. Then, when the refrigeration cycle apparatus is stopped by idling stop and the flow of the refrigerant is stopped, the cold heat stored in the cold storage material is released and the external air can be cooled, so that the passenger's discomfort is reduced.

JP 2011-12947 A JP 2014-40958 A

  By the way, in the cool storage heat exchanger of patent document 1, 2, a refrigerant | coolant pipe | tube and a cool storage material container are laminated | stacked on the direction which cross | intersects the flow direction of external air. Since the outside air does not flow in the part where the refrigerant pipe and the cool storage material container exist, the ventilation area is reduced by the amount of the cool storage function compared to the conventional heat exchanger without the cool storage function. Increase and decrease in cooling performance.

  Moreover, in the cool storage heat exchanger of patent document 1, 2, since a refrigerant | coolant pipe | tube and a cool storage material container are separate components and each must be assembled | attached to a header, there also exists a problem that the assembly | attachment work to a header becomes complicated. Therefore, it is conceivable to integrate the refrigerant pipe and the regenerator container into one part. However, in the case of one part, considering the moldability, the part constituting the refrigerant flow path and the regenerator material It is preferable that the portion constituting the housing space is made of a separate plate material. If the plates are made of separate plates, sufficient airtightness must be secured when the plates are joined.

  This invention is made | formed in view of this point, and the place made into the objective is to comprise a heat-transfer member by air-tightly joining a some board | plate material while ensuring a large ventilation area.

  In order to achieve the above object, in the present invention, the end portion of the plate member that forms the refrigerant flow passage by providing the refrigerant flow passage and the storage space for the regenerator material in the heat transfer member so as to be aligned in the flow direction of external air Is fitted to a plate material forming a storage space for the regenerator material.

The first invention is
In the cold storage heat exchanger having the cold storage material for storing the cold heat of the refrigerant,
A heat transfer member provided such that a flow path through which the refrigerant flows and a storage space for storing the cold storage material are arranged in the flow direction of the external air;
Fins arranged on the outer surface of the heat transfer member so as to line up in a direction intersecting the flow direction of the external air;
A header tank connected to the end of the flow path,
The heat transfer member includes a plate material for forming a flow path that forms the flow channel, and a plate material for forming a storage space that forms the storage space.
One end of the flow path forming plate is fitted and brazed to the housing space forming plate.

  According to this configuration, since the refrigerant flow path and the storage space for the regenerator material are arranged in the direction of the flow of external air, the refrigerant flow path and the storage space for the regenerator material when viewed in the direction of the external air flow. And are arranged so as to overlap. Thereby, a wide ventilation area is ensured.

  Then, by fitting one end portion of the flow path forming plate material to the accommodating space forming plate material and brazing, positional deviation between the flow path forming plate material and the accommodating space forming plate material is suppressed, and the flow path forming plate material is formed. The plate member and the storage space forming plate member are joined in an airtight manner.

According to a second invention, in the first invention,
The housing space forming plate is formed with a first step portion into which one end of the flow path forming plate is fitted.

  According to this configuration, one end portion of the flow path forming plate member is fitted to the first step portion of the housing space forming plate member, thereby suppressing the displacement of the one end portion of the flow path forming plate member to form the flow passage. It becomes possible to braze the one end part of the plate material for a predetermined position.

According to a third invention, in the second invention,
The housing space forming plate is formed with a second step portion into which the other end of the flow path forming plate is fitted.

  According to this configuration, the other end portion of the flow path forming plate member is fitted to the second step portion of the accommodation space forming plate member, thereby suppressing the displacement of the other end portion of the flow path forming plate member. It becomes possible.

  According to the first aspect of the invention, since the refrigerant flow passage and the storage space for the regenerator material are provided in the heat transfer member so as to be aligned in the flow direction of the external air, a wide ventilation area can be secured. And since one end part of the plate material for flow passage formation is fitted and brazed to the plate material for accommodation space formation, the plate material for flow passage formation and the plate material for accommodation space formation are joined airtightly, and the heat transfer member is Can be configured.

  According to the second invention, since the first step portion into which the one end of the flow path forming plate is fitted is formed on the housing space forming plate, the one end of the flow path forming plate is brazed at a predetermined position. can do.

  According to the third invention, since the second step portion in which the other end portion of the flow path forming plate material is fitted is formed in the housing space forming plate material, both end portions of the flow path forming plate material are placed at predetermined positions. Can be attached.

It is a fragmentary sectional view of the cool storage heat exchanger concerning an embodiment. It is the A section enlarged view of FIG. It is a schematic diagram which shows the flow of the refrigerant | coolant inside a cool storage heat exchanger. It is sectional drawing of an upper header tank. It is a side view of a heat-transfer member. It is sectional drawing in the VI-VI line of FIG. It is a top view of a heat-transfer member. It is a bottom view of a heat transfer member. It is an expanded view of a 2nd board | plate material. FIG. 7 is a view corresponding to FIG. 6 according to Modification 1 of the embodiment. FIG. 7 is a view corresponding to FIG. 6 according to a second modification of the embodiment. FIG. 7 is a view corresponding to FIG. 6 according to Modification 3 of the embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  FIG. 1 is a perspective view of a regenerator heat exchanger 1 according to an embodiment of the present invention as viewed from the downstream side in the flow direction of external air (indicated by arrow B in FIGS. 1 and 3). The cold storage heat exchanger 1 is used as a cooling heat exchanger of a vehicle air conditioner (not shown) mounted on an automobile with an idling stop function. That is, the regenerative heat exchanger 1 functions as an evaporator of a refrigeration cycle apparatus (not shown) that is a part of the vehicle air conditioner, and the refrigerant compressed by the compressor of the refrigeration cycle apparatus is a condenser. It is comprised so that it may flow in, after expanding through an expansion valve. The compressor is driven by a vehicle engine.

  The idling stop function has been conventionally known, and when the vehicle control device (not shown) detects, for example, that the vehicle speed is 0 and the occupant has depressed the brake pedal, the engine idling is stopped. It is configured to stop and restart the engine when the brake pedal is released. Therefore, in this automobile, the engine is stopped by the idling stop function when the vehicle air conditioner is operated, and the compressor may be stopped. At this time, as will be described later, the regenerator material of the regenerator heat exchanger 1 releases the cold heat, so that the external air can be cooled for a predetermined time. The compressor can be driven by restarting the engine according to the required degree of air conditioning.

  The cold storage heat exchanger 1 includes a core 2, a lower header tank 10, and an upper header tank 20. The core 2 is a part mainly for cooling the external air, and is formed by brazing the end plate 3, the numerous fins 4 and the heat transfer member 30 to each other. The fins 4 and the heat transfer members 30 are arranged so as to be alternately arranged in a direction intersecting with the flow direction of the external air. In this embodiment, the arrangement direction of the fins 4 and the heat transfer member 30 is the left-right direction of the regenerator heat exchanger 1, the right side in FIGS. 1 and 3 is called the right side of the regenerator heat exchanger 1, and the left side is the regenerator heat exchanger. Although it is called the left side of 1, the left and right sides may be reversed while mounted on the vehicle.

  The fins 4 are corrugated fins extending in the vertical direction, and are formed by forming a plate made of aluminum alloy. The fins 4 are continuous from the upper part to the lower part of the heat transfer member 30, and are brazed to the side surfaces of the heat transfer member 30. The arrangement range of the fins 4 is a range from the upstream end portion to the downstream end portion of the external air in the heat transfer member 30.

  The end plates 3 are respectively disposed at both outer ends of the fins 4 and the heat transfer members 30 in the arrangement direction, i.e., both left and right sides of the core 2, and are formed by forming a plate made of an aluminum alloy. The end plate 3 is brazed to the fins 4.

  The lower header tank 10 is formed of a cylindrical member that is long in the left-right direction. Caps 11 are attached to both left and right ends, and both ends are closed by the cap 11. As shown in FIG. 3, a lower first partition plate 12 extending in the left-right direction and a lower second partition plate 13 extending in the flow direction of the external air are provided in the lower header tank 10. ing. The lower first partition plate 12 partitions the inside of the lower header tank 10 into an upstream space R1 on the upstream side in the flow direction of the external air and a downstream space R2 on the downstream side. The upstream space R1 and the downstream space R2 are spaces through which the refrigerant flows. The lower second partition plate 13 partitions the upstream space R1 and the downstream space R2 in the left-right direction. The lower second partition plate 13 is disposed on the right side of the central portion in the left-right direction of the lower header tank 10. Further, a communication port 12a is formed on the lower first partition plate 12 on the right side of the lower second partition plate 13, and the upstream space R1 and the downstream space R2 communicate with each other via the communication port 12a. It is supposed to be.

  An upstream insertion hole (not shown) that communicates with the upstream space R1 is formed on the upstream side of the upper wall portion of the lower header tank 10 in the flow direction of the external air. The lower end portion of the upstream pipe portion 31 of the heat transfer member 30 described later is inserted into the upstream insertion hole. A downstream insertion hole 10a (shown in FIG. 1) communicating with the downstream space R2 is formed on the downstream side of the upper wall portion of the lower header tank 10 in the flow direction of the external air. A lower end portion of a downstream pipe portion 32 of a heat transfer member 30 to be described later is inserted into the downstream insertion hole 10a.

  Similar to the lower header tank 10, the upper header tank 20 extends in the left-right direction. As shown in FIG. 4, the upper header tank 20 includes a header 21, an upstream tank portion 22 disposed on the upstream side in the flow direction of the external air, a downstream tank portion 23 disposed on the downstream side, and a blockage. The header part 21, the upstream tank part 22, the downstream tank part 23, and the closing plate part 24 are made of an aluminum alloy plate material.

  The header 21 extends in the left-right direction, and protrusions 21 a that protrude upward and extend in the left-right direction are formed at both ends of the external air flow direction. The space between the protrusions 21a and 21a in the header 21 is substantially flat. As shown in FIG. 2, an upstream insertion hole 21 b is formed on the upstream side in the flow direction of the external air, and a downstream insertion hole 21 c is formed on the downstream side in the portion between the protrusions 21 a and 21 a of the header 21. In addition, a central insertion hole 21d is formed between the upstream insertion hole 21b and the downstream insertion hole 21c. The upstream insertion hole 21b has a shape that is long in the flow direction of the external air. The downstream insertion hole 21c is long in the flow direction of the external air, and its longitudinal dimension is set shorter than the longitudinal dimension of the upstream insertion hole 21b. The central insertion hole 21d is long in the flow direction of the external air, and its longitudinal dimension is set shorter than the longitudinal dimension of the downstream insertion hole 21c. The upstream insertion hole 21b, the downstream insertion hole 21c, and the central insertion hole 21d are arranged in a straight line in the flow direction of the external air. Further, the left and right dimensions of the upstream insertion hole 21b, the downstream insertion hole 21c, and the central insertion hole 21d are set to be the same.

  The upstream tank portion 22 is a concave member that opens downward, and the open side is joined and closed to the upper surface of the header 21, thereby forming an upstream space S <b> 1 extending in the left-right direction inside. The upstream space S1 is a space through which the refrigerant flows, and is formed on the upstream side in the external air flow direction with respect to the central insertion hole 21d of the header 21. A recess 22 a is formed in the wall portion of the upstream tank portion 22 on the downstream side in the external air flow direction.

  The downstream tank portion 23 is a concave member that opens downward, and the open side is joined to and closed by the upper surface of the header 21, thereby forming a downstream space S <b> 2 extending in the left-right direction inside. The downstream tank portion 23 is disposed away from the upstream tank portion 22 on the downstream side in the flow direction of the external air. The downstream space S2 is a space through which the refrigerant flows, and is formed downstream of the central insertion hole 21d of the header 21 in the external air flow direction. A recess 23 a is formed in the wall portion on the upstream side in the external air flow direction of the downstream tank portion 23.

  The blocking plate portion 24 is disposed away from the upper surface of the header 21 and is formed to fit into the recess 22 a of the upstream tank portion 22 and the recess 23 a of the downstream tank portion 23. A regenerator filling space S <b> 3 is partitioned and formed in a portion sandwiched between the upstream tank portion 22 and the downstream tank portion 23 between the closing plate portion 24 and the header 21. The dimension in the external air flow direction on the upper side of the regenerator filling space S3 is set longer than the dimension in the external air flow direction on the lower side.

  The regenerator material filled in the regenerator material filling space S3 may be a conventionally known regenerator material, such as paraffin that changes its state from a liquid phase to a solid phase and from a solid phase to a liquid phase in a normal temperature range. . The volume of the regenerator material filling space S3 is set smaller than each volume of the upstream space S1 and the downstream space S2.

  Caps 25 (only the right one is shown) are attached to the left and right ends of the upper header tank 20, respectively. The cap 25 closes the left and right ends of the upstream space S1, the downstream space S2, and the cool storage material filling space S3. Although not shown, the left cap is provided with a refrigerant supply pipe and a refrigerant discharge pipe. The refrigerant supply pipe is a pipe that is connected to the downstream space S2 of the upper header tank 20 and supplies the refrigerant decompressed through the expansion valve to the downstream space S2. The refrigerant discharge pipe is a pipe that is connected to the upstream space S1 of the upper header tank 20 and discharges the refrigerant circulated in the cold storage heat exchanger 1 from the upstream space S1. The refrigerant supply pipe and the refrigerant discharge pipe are cooler pipes.

  The upstream space S1 of the upper header tank 20 is provided with an upstream partition plate 26 for partitioning the upstream space S1 to the left and right. The upstream partition plate 26 is disposed to the left of the lower second partition plate 13 of the lower header tank 10. In the downstream space S2 of the upper header tank 20, a downstream partition plate 27 for partitioning the downstream space S2 to the left and right is provided. The downstream partition plate 27 is disposed on the left side of the lower second partition plate 13 of the lower header tank 10.

  Next, the structure of the heat transfer member 30 will be described. As shown in FIG. 5, the heat transfer member 30 extends in the vertical direction. As shown in FIG. 6, the heat transfer member 30 includes an upstream refrigerant flow passage T1 and a downstream refrigerant flow passage T2 through which a refrigerant flows, and a cold storage material accommodation space T3 in which a cold storage material is accommodated. It is provided to line up in the direction. That is, the heat transfer member 30 includes an upstream pipe portion 31 in which an upstream refrigerant flow passage T1 located on the upstream side in the external air flow direction is formed, and a downstream refrigerant flow passage located on the downstream side in the external air flow direction. A downstream pipe portion 32 in which T2 is formed; and an intermediate pipe portion 33 in which a cool storage material accommodation space T3 located between the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage T2 is formed. ing. The upstream side pipe part 31, the downstream side pipe part 32, and the intermediate pipe part 33 are integrated, and become one component when assembled to the lower header tank 10 and the upper header tank 20.

  The heat transfer member 30 includes an aluminum alloy first plate (flow passage forming plate) C1, a second plate (accommodating space forming plate) C2, and a third plate (flow passage forming plate) C3 (FIGS. 6 to 6). 8). The first plate material C1 constitutes the peripheral wall portion of the upstream side pipe portion 31. The second plate member C2 includes a peripheral wall portion of the intermediate pipe portion 33, an upstream protruding plate portion 38, a downstream protruding plate portion 39, an upstream extending plate portion 40, and a downstream extending plate portion that are integrally formed therewith. 41, an upstream flow passage inner plate portion 42, and a downstream flow passage inner plate portion 43 (described later). The third plate member C3 constitutes the peripheral wall portion of the downstream side pipe portion 32. The first plate member C1, the second plate member C2, and the third plate member C3 can be formed by, for example, a roll forming method so as to have a cross-sectional shape described later. The first plate material C1, the second plate material C2, and the third plate material C3 are joined by brazing.

  The upstream pipe section 31, the downstream pipe section 32, and the intermediate pipe section 33 extend in the vertical direction. As shown in FIG. 2, the upper portion of the upstream pipe portion 31 is inserted into the upstream insertion hole 21b of the upper header tank 20 and protrudes upward from the upstream insertion hole 21b. The upstream refrigerant flow passage T <b> 1 is connected to the upstream space S <b> 1 of the upper header tank 20. The lower part of the upstream pipe portion 31 is inserted into an upstream insertion hole (not shown) of the lower header tank 10, and in this state, the upstream refrigerant flow passage T <b> 1 of the upstream pipe portion 31 is connected to the lower header tank 10. It communicates with the upstream space R1 (shown in FIG. 3). As shown in FIG. 2, the upper portion of the downstream pipe portion 32 is inserted into the downstream insertion hole 21c of the upper header tank 20 and protrudes upward from the downstream insertion hole 21c. The downstream refrigerant flow passage T2 communicates with the downstream space S2 of the upper header tank 20. As shown in FIG. 3, the lower part of the downstream pipe part 32 is inserted into the downstream insertion hole 10a of the lower header tank 10, and in this state, the downstream refrigerant flow passage T2 of the downstream pipe part 32 serves as the lower header. It communicates with the downstream space R2 of the tank 10.

  As shown in FIG. 6, the cross section of the upstream pipe portion 31 is a flat shape extending from the upstream end portion in the external air flow direction in the heat transfer member 30 to the vicinity of the center portion. The dimension in the major axis direction (external air flow direction) is longer than the dimension in the horizontal direction (minor axis direction).

  The upstream end portion in the external air flow direction of the wall portion of the upstream pipe portion 31 is configured by a curved wall portion 31a that curves toward the upstream side. The left side wall part 31b and the right side wall part 31c of the upstream side pipe part 31 extend substantially parallel to each other in the external air flow direction. An inclined wall portion 31d and a joining wall portion 31e are formed on the downstream side in the external air flow direction of the left side wall portion 31b of the upstream side pipe portion 31. The inclined wall portion 31d is inclined so as to be located to the right as it goes downstream in the external air flow direction. As a result, the upstream side pipe portion 31 has a dimension in the left-right direction that is lower on the downstream side in the external air flow direction than on the upstream side. Become shorter. The joining wall portion 31e extends from the downstream end in the external air flow direction of the inclined wall portion 31d to the downstream side, and is substantially parallel to the right side wall portion 31c of the upstream pipe portion 31. Further, the end wall portion 31f on the downstream side in the external air flow direction in the upstream side pipe portion 31 extends substantially flat in the left-right direction.

  Further, the cross section of the downstream side pipe portion 32 has a flat shape extending from the downstream end portion in the external air flow direction in the heat transfer member 30 toward the central portion, and accordingly, in the major axis direction (external air flow in the downstream side pipe portion 32). The dimension in the (direction) is longer than the dimension in the left-right direction (minor axis direction). The dimension in the major axis direction of the downstream side pipe part 32 is set shorter than the dimension in the major axis direction of the upstream side pipe part 31. The horizontal cross-sectional area of the downstream pipe part 32 is set narrower than the horizontal cross-sectional area of the upstream pipe part 31.

  The downstream end portion in the external air flow direction of the wall portion of the downstream pipe portion 32 is configured by a curved wall portion 32a that curves toward the downstream side. The left side wall part 32b and the right side wall part 32c of the downstream side pipe part 32 extend substantially parallel to each other in the external air flow direction. An inclined wall portion 32d and a joining wall portion 32e are formed on the upstream side in the external air flow direction of the right side wall portion 32c of the downstream side pipe portion 32. The inclined wall portion 32d is inclined so as to be located on the left side toward the upstream side in the external air flow direction. As a result, the dimension in the left-right direction of the downstream pipe portion 32 is larger on the upstream side in the external air flow direction than on the downstream side. Become shorter. The joining wall portion 32e extends from the upstream end in the external air flow direction of the inclined wall portion 32d to the upstream side, and is substantially parallel to the left side wall portion 32b of the downstream side pipe portion 32. Further, the end wall portion 32f on the upstream side in the external air flow direction in the downstream side pipe portion 32 extends substantially flat in the left-right direction.

  The cross section of the intermediate tube portion 33 is different between the intermediate portion in the vertical direction of the intermediate tube portion 33, the upper portion, and the lower portion. The cross section of the intermediate portion in the vertical direction of the intermediate pipe portion 33 has a shape that is long in the direction of external air flow. The horizontal cross-sectional area of the intermediate pipe part 33 is set narrower than the horizontal cross-sectional areas of the downstream pipe part 32 and the upstream pipe part 31.

  The left side wall part 33a and the right side wall part 33b of the intermediate pipe part 33 extend substantially parallel to each other in the external air flow direction. The left side wall part 33a and the right side wall part 33b have the same length. The dimension in the direction of external air flow in the right side wall part 33 b of the intermediate pipe part 33 is longer than the dimension in the direction of external air flow in the right side wall part 32 c of the downstream side pipe part 32.

  In addition, the upstream end wall portion 33c and the downstream end wall portion 33d of the intermediate pipe portion 33 in the external air flow direction extend substantially in parallel in the left-right direction. The upstream end wall portion 33 c of the intermediate pipe portion 33 is in contact with the downstream end wall portion 31 f of the upstream pipe portion 31. The downstream end wall portion 33d of the intermediate tube portion 33 and the upstream end wall portion 32f of the downstream tube portion 32 are in contact with each other.

  As shown in FIG. 5, the upper portion of the intermediate pipe portion 33 is formed so that the cross section becomes smaller toward the upper end, and is open at the upper end. As shown in FIG. 7, the horizontal dimension of the upper part of the intermediate pipe part 33 is set to be substantially the same as the horizontal dimension of the intermediate part of the intermediate pipe part 33 in the vertical direction. The dimension in the external air flow direction is set shorter than the dimension in the external air flow direction in the intermediate part in the vertical direction of the intermediate pipe part 33, and the dimension becomes shorter as it approaches the upper end of the intermediate pipe part 33. As a result, a gap is formed between the upstream end wall portion 33 c and the downstream end wall portion 31 f of the upstream pipe portion 31 at the upper portion of the intermediate pipe portion 33, and the upper portion of the intermediate pipe portion 33. In FIG. 5, a gap is also formed between the downstream end wall portion 33 d and the upstream end wall portion 32 f of the downstream pipe portion 32.

  As shown in FIG. 2, the upper portion of the intermediate pipe portion 33 is inserted into the central insertion hole 21d of the upper header tank 20, and the upper end portion protrudes upward from the central insertion hole 21d. That is, the upper part of the intermediate pipe part 33 is a part that communicates with the cold storage material filling space S3 in a state of being inserted into the cold storage material filling space S3. The outer shape of the upper end portion of the intermediate pipe portion 33 is set smaller than the shape of the central insertion hole 21d. The vicinity of the central portion in the vertical direction on the outer peripheral surface of the upper portion of the intermediate pipe portion 33 is brought into contact with the inner peripheral surface of the central insertion hole 21 d of the upper header tank 20 and brazed.

  By reducing the cross section of the upper part of the intermediate pipe part 33 toward the upper end as described above, the upper part of the intermediate pipe part 33 is tapered toward the regenerator filling space S3. Thereby, when inserting the upper part of the intermediate pipe part 33 in the cool storage material filling space 3 of the upper header tank 20, workability at the time of insertion becomes good.

  On the other hand, as shown in FIG. 8, the lower part of the intermediate pipe part 33 is closed. As shown in FIG. 5, the cross-sectional area of the lower portion of the intermediate pipe portion 33 gradually decreases toward the lower end. As shown in FIG. 8, the lower portion of the intermediate pipe portion 33 is formed by bending the second plate member C2, so that a portion extending in the flow direction of the external air and a portion extending in the left-right direction intersect with each other to form a substantially cross shape. The cross-sectional shape is formed so as to have a cross section, and the internal regenerator material is prevented from leaking out without providing a blocking member or the like separately. Thus, the end on the side opposite to the insertion side into the regenerator filling space S3 is formed to have a substantially cross-shaped cross section. Of the cross shape at the lower part of the intermediate pipe part 33, the part extending in the flow direction of the external air extends to the end wall part 31f of the upstream side pipe part 31 and extends to the end wall part 32f of the downstream side pipe part 32. It has become.

  As shown in FIG. 6, an internal plate 35 is provided in the intermediate pipe portion 33, that is, in the cold storage material accommodation space T <b> 3. The inner plate 35 extends in the direction of external air flow, and is disposed in the middle portion in the left-right direction inside the intermediate pipe portion 33. Both ends of the inner plate 35 in the direction of external air flow are connected to the inner surfaces of the upstream and downstream end wall portions 33c and 33d of the intermediate pipe portion 33. As shown in FIG. 7, the inner plate 35 extends to the upper end opening of the intermediate tube portion 33. The internal plate 35 divides the cool storage material accommodation space T3 into two regions, a left region and a right region. The inner plate 35 is integrally formed with the second plate material C2. The inner plate 35 may be bent, or dimples may be formed on the inner plate 35.

  Projections 36 projecting inward from the regenerator space T3 are formed on the left wall 33a and the right wall 33b of the intermediate pipe 33, respectively. The protrusions 36 are arranged in the external air flow direction in the left side wall part 33a and the right side wall part 33b and also in the vertical direction, and the left side wall part 33a and the right side wall part 33b are recessed from the outside to the inside. It was made by. Therefore, the recessed part 37 is formed in the outer surface of the left side wall part 33a and the right side wall part 33b of the intermediate | middle pipe part 33 corresponding to the formation position of the protrusion part 36. FIG.

  A gap capable of accommodating the regenerator material is formed between the protruding portion 36 in the protruding direction and the inner plate 35. By forming the protruding portion 36, the contact area between the cold storage material and the inner surface of the intermediate tube portion 33 is widened.

  In this embodiment, the projecting portion 36 is not formed on the upper and lower portions of the intermediate tube portion 33, but can be formed on the upper and lower portions. Moreover, although the protrusion part 36 becomes a shape long in an up-down direction, it is not restricted to this, A circular protrusion part may be sufficient. Further, the protrusions 36 may be provided in only one row in the external air flow direction, or may be provided in three or more rows. The interval between the protrusions 36 and 36 aligned in the direction of the external air flow is set to be narrower than the interval between the protrusions 36 and 36 aligned in the vertical direction, but is not limited thereto, and may be the same interval. You may make the space | interval of the protrusion parts 36 and 36 located in a line wider. Further, the protruding portion 36 may be omitted.

  An upstream protruding plate portion 38 is provided on the end wall portion 33 c on the upstream side of the intermediate pipe portion 33. The upstream projecting plate portion 38 is a portion formed by the second plate material C2 constituting the intermediate tube portion 33, and the second plate material C2 is folded and has a thickness corresponding to two sheets of the second plate material C2. The upstream projecting plate portion 38 protrudes from the central portion in the left-right direction on the outer surface of the end wall portion 33c to the upstream side in the external air flow direction, and extends in the vertical direction along the joining wall portion 31e of the upstream tube portion 31. It is joined to the joining wall 31e by brazing. By joining the upstream protruding plate part 38 to the joining wall part 31e, the contact area between the intermediate pipe part 33 and the upstream pipe part 31 is increased, and the cold heat of the refrigerant flowing through the upstream refrigerant flow passage T1 is reduced to the intermediate pipe part. It becomes easy to transmit to 33.

  A downstream protruding plate 39 is provided on the downstream end wall 33 d of the intermediate pipe 33. The downstream protruding plate portion 39 is a portion formed by the second plate member C2 constituting the intermediate pipe portion 33, as with the upstream protruding plate portion 38, and has a thickness corresponding to two sheets of the second plate member C2. ing. The downstream protruding plate portion 39 protrudes from the central portion in the left-right direction on the outer surface of the end wall portion 33d to the downstream side in the external air flow direction and extends in the vertical direction along the joining wall portion 32e of the downstream tube portion 32. It is joined to the joining wall 32e by brazing. By joining the downstream protruding plate part 39 to the joining wall part 32e, the contact area between the intermediate pipe part 33 and the downstream pipe part 32 is increased, and the cold heat of the refrigerant flowing through the downstream refrigerant flow passage T2 is reduced to the intermediate pipe part. It becomes easy to transmit to 33.

  The intermediate pipe portion 33 is provided with an upstream extension plate portion 40 and a downstream extension plate portion 41. The upstream extending plate portion 40 is a portion formed by the second plate member C2 constituting the intermediate tube portion 33, and extends so as to extend the left side wall portion 33a of the intermediate tube portion 33 to the upstream side in the external air flow direction. ing. The upstream extending plate part 40 and the left side wall part 31 b of the upstream pipe part 31 are located on substantially the same plane. The inclined wall portion 31d is covered from the left side by the upstream extending plate portion 40. A closed cross-sectional space is formed between the upstream extending plate portion 40 and the inclined wall portion 31d.

  An upstream first fitting portion 40a and an upstream second fitting portion in which one end portion and the other end portion in the circumferential direction of the first plate material C1 are fitted to the distal end portion of the upstream extending plate portion 40, respectively. 40b is formed close to each other. The upstream first fitting portion 40 a is a first step portion formed on the left side surface (the outer surface of the heat transfer member 30) of the upstream side extension plate portion 40. The depth of the upstream first fitting portion 40a is set to be substantially the same as the thickness of one end portion of the first plate material C1. One end of the first plate member C1 is brazed in a state of being fitted and positioned in the upstream first fitting portion 40a. The upstream second fitting portion 40 b is a second step portion formed on the right side surface (the inner surface of the heat transfer member 30) of the upstream side extension plate portion 40. The depth of the upstream second fitting portion 40b is set to be substantially the same as the thickness of the other end of the first plate material C1. The other end portion of the first plate member C1 is brazed in a state where the other end portion is fitted and positioned in the upstream second fitting portion 40b. One end portion and the other end portion of the first plate member C1 are disposed so as to sandwich the upstream extending plate portion 40 in the thickness direction, and are airtightly joined via the upstream extending plate portion 40.

  The downstream extending plate portion 41 is also a portion configured by the second plate material C <b> 2 constituting the intermediate tube portion 33. The downstream extending plate portion 41 extends so as to extend the right side wall portion 33b of the intermediate pipe portion 33 to the downstream side in the external air flow direction. The downstream side extension plate part 41 and the right side wall part 32c of the downstream side pipe part 32 are located on substantially the same plane. The inclined wall portion 32d is covered from the right side by the downstream extending plate portion 41. A closed cross-section space is formed between the downstream extension plate portion 41 and the inclined wall portion 32d.

  A downstream first fitting portion 41a and a downstream second fitting portion 41b are fitted to the distal end portion of the downstream extending plate portion 41, respectively, with one end portion and the other end portion in the circumferential direction of the third plate material C3. Are formed close to each other. The downstream first fitting portion 41 a is a first step portion formed on the right side surface (the outer surface of the heat transfer member 30) of the downstream side extension plate portion 41. The depth of the downstream first fitting portion 41a is set to be substantially the same as the thickness of one end portion of the third plate material C3. One end of the third plate member C3 is brazed in a state of being positioned by being fitted to the downstream first fitting portion 41a. The downstream second fitting portion 41 b is a second step portion formed on the right side surface (the inner surface of the heat transfer member 30) of the downstream side extension plate portion 41. The depth of the downstream second fitting portion 41b is set to be substantially the same as the thickness of the other end of the third plate member C3. The other end portion of the third plate member C3 is brazed in a state of being fitted and positioned in the downstream second fitting portion 41b. One end portion and the other end portion of the third plate member C3 are disposed so as to sandwich the downstream extension plate portion 41 in the thickness direction, and are airtightly joined via the downstream extension plate portion 41.

  An upstream flow passage inner plate portion 42 disposed in the upstream refrigerant flow passage T1 is provided at the distal end portion of the upstream extension plate portion 40. The upstream flow passage inner plate portion 42 continuously extends from the downstream side in the external air flow direction to the upstream side in the upstream refrigerant flow passage T1, and the tip thereof is on the inner surface of the curved wall portion 31a of the upstream pipe portion 31. It is brazed. The upstream side flow passage inner plate portion 42 has a base end portion disposed on the left side, and extends upstream from the base end portion toward the right side in the external air flow direction, and then is directed to the opposite side, that is, toward the left side. It extends upstream and repeats this to form a waveform bent in the left-right direction. The upstream flow passage inner plate portion 42 is brazed to the inner surfaces of the left side wall portion 31 b and the right side wall portion 31 c, and the upstream side flow passage inner plate portion 42 is brazed to the inner surface of the upstream side pipe portion 31. The left side wall part 31b and the right side wall part 31c can be connected, and the pressure resistance of the upstream side pipe part 31 can be improved.

  Further, a downstream side flow passage inner plate portion 43 disposed in the downstream side refrigerant flow passage T2 is provided at the distal end portion of the downstream side extension plate portion 41. The downstream flow passage inner plate portion 43 extends from the upstream side toward the downstream side in the external air flow direction in the downstream refrigerant flow passage T2, and the tip portion is brazed to the inner surface of the curved wall portion 32a of the downstream pipe portion 32. Has been. The downstream flow passage inner plate portion 43 is also bent in the same manner as the upstream flow passage inner plate portion 42, and is brazed to the inner surfaces of the left wall portion 32b and the right wall portion 32c. By brazing the downstream side flow passage inner plate part 43 to the inner surface of the downstream side pipe part 32, the pressure resistance of the downstream side pipe part 32 can be improved.

  The developed shape of the second plate member C2 constituting the intermediate pipe portion 33 is the shape shown in FIG. Upper notch portions 100 and 100 and lower notch portions 101 and 101 are formed in the upper and lower portions of the second plate member C2, respectively. A portion between the upper notch portions 100 and 100 in the second plate member C2 is a portion that becomes an upper portion of the intermediate tube portion 33. By forming the upper notch portions 100 and 100, the sectional shape of the upper portion of the intermediate tube portion 33 is changed in the vertical direction. While being smaller than the cross-sectional shape of the intermediate part, between the upper part of the intermediate pipe part 33 and the upper part of the upstream pipe part 31, and between the upper part of the intermediate pipe part 33 and the upper part of the downstream pipe part 32 In addition, a gap can be formed. Further, by forming the lower notches 101, 101, the cross-sectional shape of the lower portion of the intermediate tube portion 33 can be reduced to a substantially cross shape.

  In addition, in the second plate member C2 shown in FIG. 9, the upstream protruding plate portion 38, the upstream extending plate portion 40, and the upstream flow passage inner plate at the portion 102 on the left side of the upper cutout portion 100 and the lower cutout portion 101. And the downstream protruding plate portion 39, the downstream extending plate portion 41, and the downstream flow passage inner plate portion 43 are formed by the portion 103 on the right side of the upper cutout portion 100 and the lower cutout portion 101. .

  Since the 1st board | plate material C1, the 2nd board | plate material C2, and the 3rd board | plate material C3 are mutually joined when comprising the heat-transfer member 30, upstream refrigerant | coolant flow path T1, downstream refrigerant | coolant flow path T2, and cool storage material accommodation space T3 is formed as one component, and the number of components when assembled to the lower header tank 10 and the upper header tank 20 is reduced. And since the upstream side refrigerant | coolant flow path T1 and the downstream side refrigerant | coolant flow path T2 are comprised with the 1st board | plate material C1 and the 3rd board | plate material C3, and the cool storage material accommodation space T3 is comprised with the 2nd board | plate material C2, refrigerant | coolant flow path T1. , T2 and the cold storage material accommodation space T3 can be formed of separate plate materials. Accordingly, the degree of freedom in forming the first plate material C1, the second plate material C2, and the third plate material C3 is improved, and the refrigerant flow passages T1, T2 and the cold storage are formed according to the shapes of the first plate material C1, the second plate material C2, and the third plate material C3. Each sealing property with the material accommodation space T3 can be ensured.

  Further, as described above, the first plate material C1 and the third plate material C3 constituting the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage T2, and the second plate material C2 constituting the cold storage material accommodation space T3 are separate members. Therefore, the upstream refrigerant flow passage T1, the downstream refrigerant flow passage T2, and the cold storage material accommodation space T3 can be completely independent. Thereby, it can suppress that a cool storage material mixes with a refrigerant | coolant, and generation | occurrence | production of inferior goods can be avoided.

  As shown in FIG. 2, the upper part of the upstream pipe part 31 and the downstream pipe part 32 of the heat transfer member 30 configured as described above are connected to the upstream insertion hole 21b and the downstream insertion hole 21c of the upper header tank 20, respectively. By inserting, the upstream refrigerant flow passage T1 and the upstream space S1 communicate with each other, and the downstream refrigerant flow passage T2 and the downstream space S2 communicate with each other. Moreover, the cool storage material accommodation space T3 and the cool storage material filling space S3 communicate with each other by inserting the upper portion of the intermediate pipe portion 33 of the heat transfer member 30 into the central insertion hole 21d. When the regenerator material is filled into the regenerator material filling space S3, the regenerator material flows into each regenerator material filling space S3. The regenerator material can be filled in the regenerator material accommodation space T3 with the closing plate portion 24 removed. After the filling, the closing plate portion 24 is attached to close the cool storage material accommodation space T3. In addition, it is preferable to provide the part which does not fill a cool storage material in a part of cool storage material filling space S3, and, thereby, the volume change of a cool storage material can be accept | permitted.

  Moreover, the upstream refrigerant | coolant is inserted by inserting the lower part of the upstream pipe part 31 and the downstream pipe part 32 of the heat-transfer member 30 in the upstream insertion hole (not shown) and the downstream insertion hole 10a of the lower header tank 10. The flow passage T1 and the upstream space R1 (shown in FIG. 3) communicate with each other, and the downstream refrigerant flow passage T2 and the downstream space R2 communicate with each other.

  Next, the flow of the refrigerant in the regenerator heat exchanger 1 configured as described above will be described with reference to FIG. The refrigerant supplied by a refrigerant supply pipe (not shown) flows into the downstream space S2 of the upper header tank 20 as indicated by an arrow D1. Then, as shown by an arrow D2, the refrigerant flows into the downstream refrigerant flow passage T2 of the heat transfer member 30 on the left side of the downstream partition plate 27 and flows downward. The refrigerant that has flowed through the downstream refrigerant flow passage T2 flows to the left side of the lower second partition plate 13 in the downstream space R2 of the lower header tank 10, and then the downstream partition plate 27 and the lower second partition plate. The refrigerant flows into the downstream refrigerant flow passage T2 of the heat transfer member 30 located between the partition plate 13 and flows upward as indicated by an arrow D3 and flows into the downstream space S2 of the upper header tank 20. The refrigerant flowing into the downstream space S2 of the upper header tank 20 flows to the right and flows into the downstream refrigerant flow passage T2 of the heat transfer member 30 located on the right side of the lower second partition plate 13, and is indicated by an arrow D4. As shown, it flows downward and flows into the downstream space R <b> 2 of the lower header tank 10. The refrigerant that has flowed into the downstream space R2 of the lower header tank 10 flows into the upstream space R1 through the communication port 12a, and is upstream of the heat transfer member 30 located on the right side of the lower second partition plate 13. The refrigerant flows into the refrigerant flow passage T1, flows upward as indicated by an arrow D5, and flows into the upstream space S1 of the upper header tank 20. The refrigerant flowing into the upstream space S1 of the upper header tank 20 flows into the upstream refrigerant flow passage T1 of the heat transfer member 30 located between the upstream partition plate 26 and the lower second partition plate 13, and the arrow As shown by D6, it flows downward and flows into the upstream space R1 of the lower header tank 10. The refrigerant flowing into the upstream space R1 of the lower header tank 10 flows to the left side, flows into the upstream refrigerant flow passage T1 of the heat transfer member 30 on the left side of the upstream partition plate 26, and as indicated by an arrow D7. It flows upward, flows into the upstream space S1 of the upper header tank 20, and is discharged from the refrigerant discharge pipe to the outside as indicated by an arrow D8.

  Next, the case where the cold storage heat exchanger 1 comprised as mentioned above is used is demonstrated. When the vehicle engine is in operation, the compressor of the refrigeration cycle apparatus operates. Note that the refrigeration cycle apparatus is controlled to stop the compressor when the surface temperature of the regenerator heat exchanger 1 is below a predetermined temperature and the condensed water may freeze.

  Air-conditioning air is blown to the cold storage heat exchanger 1 by a blower fan (not shown). At this time, the upstream refrigerant flow passage T1, the downstream refrigerant flow passage T2, and the cool storage material accommodation space T3 are aligned in the direction of the external air flow and have the same thickness. When viewed, the upstream refrigerant flow passage T1, the downstream refrigerant flow passage T2, and the cold storage material accommodation space T3 are arranged so as to overlap. Thereby, since the ventilation area of the cool storage heat exchanger 1 is ensured widely, ventilation resistance can be reduced and the mounting property to a vehicle can be made favorable, without enlarging the cool storage heat exchanger 1.

  And the refrigerant | coolant which flows through the upstream refrigerant | coolant flow path T1 and the upstream refrigerant | coolant flow path T2 of the heat-transfer member 30 cools external air by mainly heat-exchanging with external air via the fin 4. FIG. At this time, the cold heat of the refrigerant is also transmitted to the cold storage material and stored in the cold storage material. At this time, since the upstream flow passage inner plate portion 42 and the downstream flow passage inner plate portion 43 are provided in the upstream refrigerant flow passage T1 and the upstream refrigerant flow passage T2, respectively, the refrigerant cold heat flows upstream. It is efficiently transmitted to the regenerator material in the regenerator material accommodation space T3 via the inboard plate part 42 and the downstream side flow passage inner plate part 43. Moreover, since the upstream-side flow passage inner plate portion 42 and the downstream-side flow passage inner plate portion 43 are integrally formed with the second plate material C2 that forms the cold storage material accommodation space T3, the cold heat of the refrigerant causes the second plate material C2 to cool. It becomes easy to be transmitted to a cool storage material. Furthermore, since the upstream flow passage inner plate portion 42 and the downstream flow passage inner plate portion 43 are bent, a large contact area with the refrigerant can be secured, so that the cold heat of the refrigerant is further transmitted to the cold storage material. It becomes easy. Moreover, since the internal plate 35 is provided in the inside of the cool storage material accommodation space T3, cold heat can be transmitted also to the cool storage material that exists in the center in the left-right direction of the cool storage material accommodation space T3. As described above, since the cold heat of the refrigerant can be efficiently transmitted to the cold storage material, a sufficient amount of cold storage can be obtained in a short time.

  When the engine is stopped by the idling stop function of the vehicle, the compressor of the refrigeration cycle apparatus is also stopped. When the compressor is stopped, the refrigerant is not supplied. However, since the cold storage material of the cold storage heat exchanger 1 stores a sufficient amount of cold heat as described above, the cold energy of the cold storage material is released and external air is discharged. To be cooled. As a result, passenger discomfort is reduced.

  As described above, according to the cold storage heat exchanger 1 according to this embodiment, the upstream refrigerant flow passage T1, the downstream refrigerant flow passage T2, and the cold storage material accommodation space T3 are provided so as to be aligned in the flow direction of the external air. Therefore, a wide ventilation area can be secured. And since the 1st board | plate material C1, the 2nd board | plate material C2, and the 3rd board | plate material C3 were bend-molded and it mutually joined, the upstream refrigerant | coolant flow path T1, the downstream refrigerant | coolant flow path T2, and the cool storage material accommodation space T3 are 1. It is possible to reduce the number of parts by providing in one part, and it is possible to ensure the sealing performance of the upstream refrigerant flow passage T1, the downstream refrigerant flow passage T2, and the cold storage material accommodation space T3.

  Further, since the heat transfer member 30 is provided with the upstream flow passage inner plate portion 42 and the downstream flow passage inner plate portion 43 disposed in the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage T2, Cold heat can be efficiently transmitted to the regenerator material to further enhance the effect of the regenerator material.

  Further, since one end portion and the other end portion of the first plate member C1 in the circumferential direction are fitted and brazed to the second plate member C2, the first plate member C1 and the second plate member C2 are hermetically joined and transmitted. The thermal member 30 can be configured. Similarly, the second plate material C2 and the third plate material C3 can be joined in an airtight manner.

  As in Modification 1 of the embodiment shown in FIG. 10, the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage are dimensioned in the direction intersecting the flow direction of the external air in the cool storage material accommodation space T3 of the heat transfer member 30. You may set shorter than the dimension of the direction which cross | intersects the flow direction of the external air in T2. Thereby, it is possible to easily cope with the case where the storage amount of the regenerator material may be small. Further, as in Modification 1, the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage T2 can have the same dimensions in the external air flow direction. Moreover, although the protrusion part which protrudes inward of the intermediate pipe part 33 is abbreviate | omitted in the modification 1, a protrusion part can also be provided like the said embodiment.

  As in Modification 2 of the embodiment shown in FIG. 11, the end wall portions 33 c and 33 d in the upper portion of the intermediate pipe portion 33 of the heat transfer member 30 may be formed so as to bulge in the flow direction of the external air.

  As in the third modification of the embodiment shown in FIG. 12, the dimensions of the heat transfer member 30 in the direction intersecting the flow direction of the external air in the cool storage material accommodation space T3, the upstream refrigerant flow passage T1, and the downstream refrigerant flow passage. The dimension in the direction crossing the flow direction of the external air at T2 may be the same, and the dimensions of the upstream refrigerant flow passage T1 and the downstream refrigerant flow passage T2 in the external air flow direction may be the same.

  Moreover, in the said embodiment, although the cool storage material accommodation space T3 is provided in all the heat transfer members 30, it is not restricted to this, For example, it cools every other heat transfer member 30 arranged in the left-right direction, or every plurality. A material accommodation space T3 may be provided.

  Moreover, in the said embodiment, although two flow paths, upstream refrigerant flow path T1 and downstream refrigerant flow path T2, are provided in the heat transfer member 30, it is not restricted to this, You may provide only one flow path. . Also in this case, the flow path and the cold storage material accommodation space T3 are provided so as to be aligned in the flow direction of the external air.

  The above-described embodiment is merely an example in all respects and should not be interpreted in a limited manner. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

  As described above, the regenerative heat exchanger according to the present invention can be used as a cooling heat exchanger of a vehicle air conditioner mounted on, for example, an automobile with an idling stop function.

DESCRIPTION OF SYMBOLS 1 Cold storage heat exchanger 4 Fin 10 Lower header tank 20 Upper header tank 30 Heat-transfer member 36 Protrusion part 40a Upstream 1st fitting part (1st step part)
40b 2nd downstream fitting part (2nd step part)
C1 1st plate (flow path forming plate)
C2 2nd plate material (plate material for accommodating space formation)
C3 Third plate (flow passage forming plate)
T1 Upstream refrigerant flow passage T2 Downstream refrigerant flow passage T3 Cold storage material accommodation space

Claims (3)

In the cold storage heat exchanger having the cold storage material for storing the cold heat of the refrigerant,
A heat transfer member provided such that a flow path through which the refrigerant flows and a storage space for storing the cold storage material are arranged in the flow direction of the external air;
Fins arranged on the outer surface of the heat transfer member so as to line up in a direction intersecting the flow direction of the external air;
A header tank connected to the end of the flow path,
The heat transfer member includes a plate material for forming a flow path that forms the flow channel, and a plate material for forming a storage space that forms the storage space.
One end of the flow path forming plate is fitted and brazed to the housing space forming plate, and the cold storage heat exchanger is characterized in that it is brazed. The regenerative heat exchanger according to claim 1,
The regenerative heat exchanger according to claim 1, wherein the housing space forming plate is formed with a first step portion into which one end of the flow path forming plate is fitted. The cold storage heat exchanger according to claim 2,
The regenerative heat exchanger, wherein the housing space forming plate is formed with a second step portion into which the other end of the flow path forming plate is fitted.

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