CN110087922B

CN110087922B - Cold storage heat exchanger

Info

Publication number: CN110087922B
Application number: CN201880005217.8A
Authority: CN
Inventors: 冈田武人; 丹野良城
Original assignee: Marelli China Automotive Air Conditioner Co Ltd
Current assignee: Haili Marelli Wuxi Automotive Thermal Management System Co ltd
Priority date: 2017-03-30
Filing date: 2018-03-22
Publication date: 2022-05-17
Anticipated expiration: 2038-03-22
Also published as: WO2018180894A1; CN110087922A

Abstract

A cold storage heat exchanger (1) is provided with: a plurality of refrigerant tubes including a first refrigerant tube (2) and second refrigerant tubes (2A-2J) through which a refrigerant that exchanges heat with air flowing around flows; and a plurality of cold storage cases (4) which contain a cold storage agent (42) for storing cold and heat. The first refrigerant pipe (2) and the second refrigerant pipes (2A-2J) are respectively abutted against the two surfaces of the plurality of cold storage cases (4). The second refrigerant tubes (2A-2J) are provided with restrictions (26, 260) that restrict the amount of refrigerant flowing in the second refrigerant tubes (2A-2J) compared to the amount of refrigerant flowing in the first refrigerant tubes (2).

Description

Cold storage heat exchanger

Technical Field

The present invention relates to a cold-storage heat exchanger (cold-storage heat exchanger) including refrigerant tubes (refrigerant tubes) and a cold-storage case (cold-storage cases).

Background

The cold storage heat exchanger disclosed in patent document 1 includes: a plurality of refrigerant tubes arranged in parallel at intervals; a plurality of outer fins disposed between adjacent refrigerant tubes; and a plurality of cold storage cases disposed in gaps between adjacent refrigerant tubes, the gaps being free from external fins. The refrigerant flowing inside the refrigerant pipe exchanges heat with air flowing outside the refrigerant pipe, and the air is cooled. The outer fins promote heat exchange between the refrigerant and the air. The cold storage housing stores cold heat [ cold ] of the refrigerant transferred from the refrigerant pipe. When the temperature of the refrigerant pipe rises (when the refrigerant does not flow), the refrigerant pipe is cooled by the stored cold heat. In the case where the cold storage heat exchanger is used for a vehicle air conditioner, even when the refrigerant hardly flows in the refrigerant pipe (for example, during idling-stop of the vehicle), the air can be cooled and the cooled air can be supplied into the vehicle interior.

Documents of the prior art

Patent document

Patent document 1: japanese laid-open patent publication No. 2008-68827

Disclosure of Invention

Problems to be solved by the invention

However, in the cold storage heat exchanger disclosed in patent document 1, since both surfaces of the cold storage case are in contact with the refrigerant tubes, the refrigerant in the refrigerant tubes is likely to be cooled in addition to the air. That is, the cool and heat stored in the cool storage agent is not effectively used for cooling the air. Further, when two heat transfer plates are brazed to form a refrigerant tube, there is also a problem that a brazing defect cannot be easily detected.

The invention provides a cold storage heat exchanger which can effectively cool air through cold and heat stored in a cold storage shell and can easily detect poor brazing.

Means for solving the problems

A first feature of the present invention is to provide a cold storage heat exchanger including: a plurality of refrigerant tubes including first and second refrigerant tubes through which a refrigerant that exchanges heat with air flowing around flows; and a plurality of cold storage cases for storing cold and hot cold storage agents, wherein the first and second refrigerant tubes are respectively abutted against both surfaces of the cold storage cases, and the second refrigerant tube is provided with a restriction portion for restricting the amount of refrigerant flowing in the second refrigerant tube compared with the amount of refrigerant flowing in the first refrigerant tube.

A second feature of the present invention is to provide a cold storage heat exchanger including: a plurality of refrigerant tubes formed by brazing a pair of heat transfer plates, each refrigerant tube including a first refrigerant tube and a second refrigerant tube, the refrigerant tubes being provided with communication holes at both ends, and a refrigerant passage being provided between the communication holes; and a cold storage case that houses a cold storage agent, wherein the first and second refrigerant tubes are in contact with both surfaces of the cold storage case, respectively, a restriction portion that restricts an amount of refrigerant flowing in the second refrigerant tube as compared with an amount of refrigerant flowing in the first refrigerant tube is provided in the second refrigerant tube, a shielding wall that prevents refrigerant from flowing between the communication hole and the refrigerant passage is provided as the restriction portion in the second refrigerant tube, inner fins brazed to inner surfaces of the refrigerant tubes are disposed in the refrigerant passages of the plurality of refrigerant tubes, and a void region where the inner fins are not disposed is provided in the refrigerant passage.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the first or second feature, the cold heat stored in the cold storage case is conducted to the refrigerant tubes when the temperature of the refrigerant tubes rises (when the refrigerant does not flow), but the conduction of the cold heat to the second refrigerant tube among the first and second refrigerant tubes in contact with both surfaces of the refrigerant case is reduced (or is not conducted to the second refrigerant tube). Therefore, the cold stored in the coolant can be effectively used for cooling the air.

Drawings

Fig. 1 is a partially exploded perspective view of a cold-storage heat exchanger of a first embodiment.

Fig. 2 is a perspective view showing a refrigerant path of the cold storage heat exchanger.

Fig. 3 is a sectional view taken along line III-III of fig. 1.

Fig. 4 is an exploded perspective view of the second refrigerant tube in the cold storage heat exchanger.

Fig. 5 is an exploded perspective view of the second refrigerant tube in the cold storage heat exchanger of the second embodiment.

Fig. 6 is an exploded perspective view of the second refrigerant tube in the cold storage heat exchanger of the third embodiment.

Fig. 7 is a partially sectional perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the fourth embodiment.

Fig. 8 is a partially sectional perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the fifth embodiment.

Fig. 9 is a sectional view of the second refrigerant pipe.

Fig. 10 is a partial sectional view of a second refrigerant tube in a modification of the fifth embodiment.

Fig. 11(a) is a plan view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the fourth embodiment, (b) is a plan view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the sixth embodiment, and (c) is a plan view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the seventh embodiment.

Fig. 12 is a partially sectional perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the sixth embodiment.

Fig. 13 is a partially sectional perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the eighth embodiment.

Fig. 14(a) to (c) are plan views showing examples of the heat transfer plate of the second refrigerant tube.

Fig. 15 is a plan view of a heat transfer plate of the second refrigerant tube of the comparative example.

Fig. 16(a) and (b) are explanatory views showing a state of the airtightness inspection of the second refrigerant tube according to the eighth embodiment.

Fig. 17 is a partially sectional perspective view of a heat transfer plate of a second refrigerant tube in the cold storage heat exchanger of the ninth embodiment.

Fig. 18 is a sectional view taken along line XVIII-XVIII in fig. 17.

Fig. 19 is a sectional view showing the support structure in the stacking direction.

Fig. 20 is a partially cutaway perspective view of a heat transfer plate of a second refrigerant tube in a modification of the ninth embodiment.

Fig. 21 is an enlarged perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger of the tenth embodiment.

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings. In the embodiments, the same or equivalent elements are denoted by the same reference numerals, and redundant description thereof is omitted.

(first embodiment)

Fig. 1 to 4 show a first embodiment. The cold storage heat exchanger 1 as an evaporator [ evaporator ] constitutes a refrigeration cycle together with a compressor, a condenser, an expansion valve, and the like (not shown). A refrigeration cycle is applied to an air-conditioning apparatus of a vehicle. The compressor is driven by the rotational force of the engine and is stopped when the engine is stopped. That is, at the time of the idling stop, the compressor is stopped, and the flow of the refrigerant to the cold storage heat exchanger 1 is (substantially) stopped. The cold-storage heat exchanger 1 is disposed in an air duct of an air conditioning unit (not shown). The air supplied to the air supply duct is blown out into the vehicle interior through the cold storage heat exchanger 1 and the like. The structure of the cold-storage heat exchanger 1 will be described below.

As shown in fig. 1, the cold-storage heat exchanger 1 includes: a plurality of

refrigerant tubes

2, 2A arranged in parallel at intervals; a plurality of outer fins 3 disposed between the

adjacent refrigerant tubes

2, 2A; and a plurality of cold storage cases 4 disposed in gaps between the

adjacent refrigerant tubes

2 and 2A, the gaps being not provided with the outer fins 3. The cold-storage heat exchanger 1 is disposed such that the refrigerant flows in the refrigerant tube 2 in the vertical direction (see arrow V in fig. 1) (the direction shown in fig. 2). The components of the cold-storage heat exchanger 1 are joined by brazing (soldered) at the portions where they are in contact with each other.

The refrigerant tube 2 is formed of an aluminum material. The refrigerant tube 2 is formed by stacking two heat transfer plates 21. Two communication holes 22 are formed at both ends of the refrigerant tube 2, respectively. As described later, the refrigerant tube 2 is partially closed at its end without forming the communication hole 22, and the refrigerant flows through the plurality of paths.

The refrigerant tube 2 has a pair of refrigerant passages 23 therein that communicate between the two communication holes 22 at both ends. The two refrigerant passages 23 are completely divided by being partitioned by the depressed wall portions 24 of the respective heat transfer plates 21. The recessed wall portion 24 is formed as a recess when viewed from the outer surface of the heat transfer plate 21, and protrudes as a wall portion when viewed from the inner surface of the heat transfer plate 21. Each refrigerant channel 23 extends in a direction at right angles to the air flow direction. Inner fins 25 as heat transfer members are disposed in the respective refrigerant passages 23. The inner fin 25 is formed of a metal plate such as aluminum, and projections 25a and recesses 25b (see fig. 7) extending in the longitudinal direction are alternately formed in the inner fin 25.

In the stacked body [ stack ] of the refrigerant tubes 2, as shown in fig. 2, a first heat exchange portion 11 is formed on the upstream side of the air flow (refrigerant passage group), and a second heat exchange portion 12 is formed on the downstream side of the air flow (refrigerant passage group). The outlet of the second heat exchange portion 12 communicates with the inlet of the first heat exchange portion 11 through a communication pipe 13. As shown by arrows in fig. 2, the refrigerant flowing from the outside flows in a zigzag manner in the stacked body of refrigerant tubes 2. For example, in the plurality of refrigerant tubes 2 in the range X in fig. 2, the refrigerant flows from the bottom to the top (1 route) as indicated by arrows. The refrigerant flows through the second heat exchange portion 12(3 pass), then flows through the first heat exchange portion 11(3 pass), and flows out to the outside. As described above, the communication hole 22 is not formed at the portion where the closing portion 14 is provided, and the direction of the path of the refrigerant is changed by the closing portion 14.

The second refrigerant tubes 2A of one side (upper side in fig. 3) of the cold storage housing 4 are different in configuration from the first refrigerant tubes 2 of the other side (lower side in fig. 3) (however, fig. 3 does not show the difference in configuration). These configurations will be described in detail below. In addition, all the refrigerant tubes that are not in contact with the cold storage housing 4 are the first refrigerant tubes 2.

The outer fin 3 is formed of an aluminum material. The outer fin 3 is wave-shaped as viewed from the direction of the air flow. The air passing between the adjacent refrigerant tubes 2 in which the outer fins 3 are arranged passes through the gaps formed by the outer fins 3 and the refrigerant tubes 2.

The number of the cold storage cases 4 is smaller than the number of the stacked

refrigerant tubes

2, 2A. In the present embodiment, 1 cold storage case 4 is provided for 5 to 6

refrigerant tubes

2, 2A. The cold storage cases 4 are arranged at equal intervals. The cold storage case 4 is formed of an aluminum material. The cold storage case 4 is filled with a cold storage agent 42 (see fig. 3). The cold storage case 4 is formed by stacking two case plates 41. The cold storage case 4 abuts on the

refrigerant pipes

2 and 2A on both sides. Therefore, the air does not pass between the cold storage case 4 and the

refrigerant tubes

2, 2A. In order to improve the heat conduction efficiency with the

refrigerant tubes

2, 2A as much as possible, the cold storage case 4 is in surface contact with the

refrigerant tubes

2, 2A over substantially the entire area of the side surfaces thereof.

As shown in fig. 4, a shield portion 26 that prevents the refrigerant from flowing at all is provided in the refrigerant passage 23 in the second refrigerant pipe 2A of the cold storage housing 4. The shielding portion 26 is disposed above the refrigerant passage 23 of the second refrigerant tube 2A. The shielding portion 26 is formed by press-forming each heat transfer plate 21. The ridge lines of the shielding portions 26 of the two heat transfer plates 21 are joined to each other by brazing. The shielding portion 26 has a vertical wall portion 26a and a pair of

lateral wall portions

26b and 26c extending obliquely from both ends of the vertical wall portion 26 a. The shielding portion 26 divides the refrigerant passage 23 into two layers by two

lateral wall portions

26b, 26 c. Thus, even if a brazing failure occurs in one of the lateral wall portions 26b (or 26c), the refrigerant can be prevented from flowing from the communication hole 22 near the shielding portion 26 to the refrigerant passage 23 (the refrigerant can be prevented from flowing from the refrigerant passage 23 to the communication hole 22 near the shielding portion 26).

In the first refrigerant tube 2, the shielding portion 26 is not provided in the refrigerant passage 23, and the refrigerant freely flows in the refrigerant passage 23. The shielding portion 26 is provided as a restriction portion [ restrictor ] that restricts the amount of refrigerant flowing through the second refrigerant tube 2A compared to the amount of refrigerant flowing through the first refrigerant tube 2.

The cold storage heat exchanger 1 configured as described above exchanges heat between the refrigerant flowing through the refrigerant tubes 2 and the air flowing through the refrigerant tubes 2, and cools the air. The outer fins 3 promote heat exchange between the refrigerant and the air. The cold storage case 4 stores cold heat of the refrigerant transferred from the refrigerant pipe 2. When the temperature of the refrigerant pipe 2 rises (when the refrigerant does not flow), the refrigerant pipe 2 is cooled by the stored cold heat. Thus, when the cold storage heat exchanger 1 is used for vehicle air conditioning, even when the refrigerant hardly flows in the refrigerant pipe 2 (for example, at the time of idling stop of the vehicle), the air is cooled (by heat exchange with the refrigerant pipe 2 cooled by cold heat), and the cooled air can be supplied into the vehicle interior.

Here, in the cold storage heat exchanger 1, the first and second

refrigerant tubes

2 and 2A are in contact with both surfaces of the cold storage case 4, and the refrigerant does not flow in the second refrigerant tube 2A. As described above, when the temperature of the

refrigerant tubes

2, 2A rises (when the refrigerant does not flow), the

refrigerant tubes

2, 2A are cooled by the stored cold heat. However, since the refrigerant does not flow in the second refrigerant tube 2A, only the refrigerant in the first refrigerant tube 2 is cooled. (the stored cold heat is prevented from being absorbed by the refrigerant in the second refrigerant tube 2A as much as possible.) as a result, the cold heat stored in the cold storage agent 42 is effectively used for cooling the air (via the second refrigerant tube 2A).

In addition, at the time of idling stop of the vehicle, since the compressor for circulating the refrigerant is stopped, the refrigerant hardly flows in the refrigeration cycle. However, the refrigerant does not completely circulate immediately after the compressor is stopped, and a difference in pressure occurs in the refrigerant in the refrigeration cycle, and the refrigerant circulates due to the difference in pressure. Therefore, the refrigerant flows in the first refrigerant tube 2, and the cold stored in the cold storage housing 4 is absorbed. In the present embodiment, the provision of the second refrigerant tubes 2A reduces the cold and heat absorbed by the refrigerant via the first refrigerant tubes 2.

In the present embodiment, the shielding portion 26 is disposed above the second refrigerant tube 2A. Therefore, the refrigerant is prevented from flowing into the refrigerant channel 23 from the communication hole 22 above the refrigerant pipe 2A (the refrigerant is also prevented from flowing into the communication hole 22 above from the refrigerant channel 23). This also prevents the stored cold heat from being absorbed by the refrigerant in the second refrigerant tube 2A. Further, if the shielding portion 26 is provided only in the lower portion of the second refrigerant tube 2A, oil mixed in the refrigerant in the refrigeration cycle accumulates in the lower portion of the second refrigerant tube 2A. As a result, the amount of oil mixed into the refrigerant is reduced, and there is a concern that troubles such as compressor heat sticking may occur. Therefore, the shielding portion 26 is preferably disposed above the second refrigerant tube 2A.

Further, inner fins 25 are provided in the refrigerant passages 23 of the second refrigerant tubes 2A. The cold and heat stored in the cold storage housing 4 is also transferred to the air via the inner fins 25 (second refrigerant tubes 2A), and therefore the air can be cooled more efficiently. In the present embodiment, the inner fins 25 are also provided in the first refrigerant tubes 2, and when the refrigerant flows in the first refrigerant tubes 2 and the evaporator (cold storage heat exchanger) 1 performs a normal function, the heat exchange between the refrigerant and the air is promoted by the inner fins 25 in the first refrigerant tubes 2.

(second embodiment)

Fig. 5 shows a second embodiment. In the cold storage heat exchanger of the second embodiment, the configuration of the second refrigerant tubes 2B is different from the configuration of the second refrigerant tubes 2A of the first embodiment described above.

In the present embodiment, the shielding portion 26 (restricting portion) is disposed not only above but also below the second refrigerant tube 2B. The configuration of each shielding portion 26 is the same as that of the shielding portion 26 of the first embodiment, and therefore, detailed description thereof is omitted.

According to the present embodiment, even when the temperature of the

refrigerant tubes

2, 2B rises (when the refrigerant does not flow), the

refrigerant tubes

2, 2B are cooled by the cold stored in the cold storage case 4. However, since the refrigerant does not flow at all in the second refrigerant tubes 2B, only the refrigerant in the first refrigerant tubes 2 is cooled. (the stored cold heat is prevented as much as possible from being absorbed by the refrigerant in the second refrigerant tube 2B.) as a result, the cold heat stored in the cold storage agent 42 is effectively used for cooling the air (via the first refrigerant tube 2).

The shielding portions 26 are disposed above and below the second refrigerant tube 2B. Therefore, even if the refrigerant leaks in any of the shielding portions 26, the refrigerant can be prevented from flowing through the second refrigerant tube 2B.

(third embodiment)

Fig. 6 shows a third embodiment. In the cold storage heat exchanger of the third embodiment, the configuration of the second refrigerant tubes 2C is different from the configuration of the second refrigerant tubes 2A of the first embodiment and the second refrigerant tubes 2B of the second embodiment.

In the present embodiment, the shielding portions 26 (restricting portions) are also disposed at the upper and lower portions of the second refrigerant pipe 2C, but a cutout portion [ cutoff ]27 is formed between the two shielding portions 26. The cutout portion 27 is formed by notching one of the pair of heat transfer plates 21. One of the pair of refrigerant passages 23 is opened to the atmosphere by the cutout portion 27. (although the refrigerant does not flow through the refrigerant channel 23 of the second refrigerant tube 2C in the present embodiment, it will be referred to as a refrigerant channel for explanation, and the same shall apply to the embodiment described later.)

According to the present embodiment, even when the temperature of the

refrigerant tubes

2, 2C rises (when the refrigerant does not flow), the

refrigerant tubes

2, 2C are cooled by the cold stored in the cold storage case 4. However, since the refrigerant does not flow at all in the second refrigerant tube 2C, only the refrigerant in the first refrigerant tube 2 is cooled. (the stored cold heat is prevented as much as possible from being absorbed by the refrigerant in the second refrigerant tube 2℃) as a result, the cold heat stored in the cold storage agent 42 is effectively used for cooling the air (via the first refrigerant tube 2).

In the present embodiment, one of the pair of refrigerant passages 23 is open to the atmosphere. Therefore, no refrigerant exists in the refrigerant passage 23 open to the atmosphere, and the cold and heat stored in the cold storage housing 4 is not absorbed by the refrigerant in the refrigerant passage 23 open to the atmosphere. Further, in the refrigerant passage 23 opened to the atmosphere, the air is cooled by the cold heat stored in the cold storage housing 4. Further, when the refrigerant is filled into the

refrigerant tubes

2, 2C after brazing the cold storage heat exchanger 1, the brazing defect of the shielding portion 26 can be easily found by the refrigerant leakage from the notch portion 27.

(fourth embodiment)

Fig. 7 shows a fourth embodiment. Fig. 7 partially shows one of the pair of heat transfer plates 21A constituting the second refrigerant tube 2D. In the present embodiment, the shielding portion of the second refrigerant tube 2D is constituted by a shielding wall 260 formed in the vicinity of the communication hole 22. Specifically, a shielding wall 260 rising between the communication hole 22 and the inner fin 25 is provided instead of the shielding portion 26 shown in fig. 4 and 5 (the shielding wall 260 is one of the forms of the shielding portion, i.e., the restricting portion).

The end (upper surface in fig. 7) of the shielding wall 260 is flush with the peripheral portion 22a of the communication hole 22, the edge portions 261A and 261b extending in the longitudinal direction of the heat transfer plate 21A, and the end surface of the recessed wall portion 24. Which are brazed to the respective opposed heat transfer plates 21A. Therefore, the flow of the refrigerant through the refrigerant passage 23 (the flow of the refrigerant from the refrigerant passage 23 to the communication hole 22 in the vicinity of the shielding wall 260) can be prevented with a relatively simple configuration.

(fifth embodiment)

Fig. 8 to 10 show a fifth embodiment and a modification thereof. Fig. 8 partially shows one of the pair of heat transfer plates 21B constituting the second refrigerant pipe. In the second refrigerant tube 2E of the cold storage heat exchanger of the fifth embodiment, each shielding wall 260 (restriction portion) is constituted by a pair of wall portions [ a pair of walls ]260a, 260 b. The pair of wall portions 260a and 260B are parallel to each other and arranged in the longitudinal direction of the heat transfer plate 21B. Wall portions 260a, 260B extend in a direction perpendicular to the longitudinal direction of heat transfer plate 21B. In the present embodiment, two

wall portions

260a and 260b are provided on each shielding wall 260, but three or more wall portions may be provided.

The end portions (upper surfaces in fig. 8) of the shielding walls 260 (wall portions 260a, 260B) are configured to be flush with the peripheral portion 22a of the communication hole 22, the edge portions 261a, 261B extending in the longitudinal direction of the heat transfer plate 21B, and the end surfaces of the recessed wall portion 24. Which are brazed to the respective opposed heat transfer plates 21B. By providing the shielding wall 260 composed of the pair of

wall portions

260a, 260b, the refrigerant can be more reliably prevented from flowing through the refrigerant passage 23 (the refrigerant can also be more reliably prevented from flowing from the refrigerant passage 23 to the communication hole 22 near the shielding wall 260).

In the present embodiment, as shown in fig. 9, a brazing material 240 is disposed in a space 300 between a pair of

wall portions

260a, 260 b. Therefore, when the heat transfer plates 21B are brazed to each other, the space [ chamber ]300 between the pair of wall portions 260a, 260B is also reliably brazed by the brazing material 240. As a result, the flow of the refrigerant through the refrigerant passage 23 can be more reliably prevented (the flow of the refrigerant from the refrigerant passage 23 to the communication hole 22 near the shielding wall 260 can also be more reliably prevented).

In the modification of the fifth embodiment shown in fig. 10, a confirmation hole 400 for confirming leakage of the refrigerant into the second refrigerant tube 2E is opened in the middle of the second refrigerant tube 2E (the pair of heat transfer plates 21). By checking the hole 400, it can be visually checked whether or not the brazing of the pair of

wall portions

260a and 260b and the space 300 surely prevents the leakage of the refrigerant. Therefore, defective products can be reliably found.

(sixth embodiment)

Fig. 11(b) and 12 show a heat transfer plate 21C of the second refrigerant tube 2F according to the sixth embodiment. In addition, fig. 12 does not show the inner fin 25A. For comparison, fig. 11(a) shows a heat transfer plate 21A according to the fourth embodiment. In the present embodiment, a positioning protrusion 200 that regulates the position of the inner fin 25A in the longitudinal direction is provided inside the second refrigerant tube 2F (heat transfer plate 21C). Positioning projections 200 are formed integrally by press forming on the inner walls of the

edge portions

261a and 261b of the heat transfer plate 21C and the side walls of the recessed wall portion 24. The configuration of the second refrigerant tube 2F other than the positioning projection 200 is the same as the configuration of the heat transfer plate 21A of the fourth embodiment.

Therefore, when the inner fin 25A shorter than the inner fin 25 of the fourth embodiment is used, the positioning projection 200 is formed at an appropriate position of the heat transfer plate 21C, whereby the inner fin 25A can be easily positioned, and the assembly work can be made efficient. In addition, by holding the end portions of the inner fins 25A between the positioning projections 200, the inner fins 25A can be prevented from wobbling. Further, by using the short inner fin 25A, the cost can be reduced.

(seventh embodiment)

Fig. 11(c) shows a heat transfer plate 21D of the second refrigerant tube of the seventh embodiment. The heat transfer plate 21D of the present embodiment is configured by providing the partition wall 500 on the heat transfer plate 21C of the sixth embodiment. The partition wall 500 is formed at the center in the longitudinal direction of each refrigerant passage 23.

Four receiving portions 502a to 502D are formed by the peripheral portion 22a of the communication hole 22, the

edge portions

261a and 261b extending in the longitudinal direction of the heat transfer plate 21D, the recessed wall portion 24, and the partition wall 500. The inner fins 25B shorter than the inner fins 25A of the sixth embodiment are received in the receiving portions 502a to 502 d.

According to the above configuration, the inner fin 25B can be easily positioned, and the assembly work can be made efficient. Further, by holding the inner fins 25B by the receiving portions 502a to 502d, the inner fins 25B can be prevented from wobbling. Further, by using the short inner fin 25B, the cost can be reduced. Still further, the rigidity of the heat transfer plate 21D (second refrigerant tube) in the stacking direction can be increased by the partition wall 500, and as a result, the rigidity of the cold storage heat exchanger can be increased.

(eighth embodiment)

The eighth embodiment and the comparative example will be described with reference to fig. 13 to 16. Fig. 13 shows an eighth embodiment. Fig. 13 partially shows one of the pair of heat transfer plates 21E constituting the second refrigerant pipe 2G. Fig. 14(a) to (c) show examples (21Ea to 21Ec) of the heat transfer plate 21E. Fig. 15 shows a comparative example (700) of the heat transfer plate. Fig. 16(a) and (b) show the configuration of the refrigerant tube 2G and the state in the airtightness test according to the eighth embodiment.

The basic configuration of the cold storage heat exchanger 1 of the eighth embodiment is the same as that of the cold storage heat exchanger 1 of the first or fourth embodiment described above. The heat transfer plate 21E of the present embodiment is also provided with a shielding wall 260 (restriction portion) similar to that of the fourth embodiment (see fig. 7). (the shape of the shielding wall 260 of FIG. 13 is slightly different from, but may be the same as, the shape of the shielding wall 260 of FIG. 7.)

The end (upper surface in fig. 13) of the shielding wall 260 is flush with the peripheral portion 22a of the communication hole 22, the

edge portions

261a and 261b extending in the longitudinal direction of the heat transfer plate 21E, and the end surface of the recessed wall portion 24. Which are brazed to the respective opposed heat transfer plates 21E. Therefore, the flow of the refrigerant through the refrigerant passage 23 (the flow of the refrigerant from the refrigerant passage 23 to the communication hole 22 in the vicinity of the shielding wall 260) can be prevented with a relatively simple configuration.

As described above, in fig. 13, the range 610 surrounded by the one-dot chain line and the range 610 of the opposite heat transfer plate 21E are brazed by the brazing material. As shown in fig. 14(a) to (c), inner fins 25A (25A1, 25A2) brazed to both inner surfaces of the second refrigerant tube 2G are disposed in the refrigerant passage 23 of the heat transfer plates 21Ea to 21Ec (second refrigerant tube 2G). Further, the heat transfer plates 21Ea to 21Ec are also provided with positioning projections 200 for positioning the inner fins 25A. Further, a void region 600 where the inner fin 25A is not disposed is provided in the refrigerant passage 23.

Specifically, in the heat transfer plate 21Ea shown in fig. 14(a), a void area 600 is provided at both ends of the two inner fins 25a1, 25a2 arranged in parallel. In the heat transfer plate 21Eb shown in fig. 14(b), a void area 600 is provided at one end (right end) of the inner fin 25a1 and the other end (left end) of the inner fin 25a 2. In the heat transfer plate 21Ec shown in fig. 14(c), a void area 600 is provided at one end (left end) of each of the inner fins 25a1, 25a 2.

With the above configuration, the inner fins 25A (25A1, 25A2) can be easily positioned, and the assembly operation can be made efficient. In addition, by holding the end portions of the inner fins 25A between the positioning projections 200, wobbling of the inner fins 25A can be prevented. Further, by using the short inner fin 25A, the cost can be reduced.

Here, a brazing defect of the heat transfer plate 700 (refrigerant pipe) of the comparative example will be described with reference to fig. 15. The heat transfer plate 700 is given the same reference numerals as or similar to the heat transfer plate 21E, and redundant description thereof will be omitted.

As shown in fig. 15, when the brazing defect occurs in the shielding wall 260, the oil 710 in the air-conditioning cycle enters the refrigerant passage 23 through the portion where the brazing defect occurs (see arrow D10). The oil 710 stays in the refrigerant passage 23 that houses the inner fin 25a2, and causes troubles such as heat sticking of the compressor. Therefore, in the present embodiment, the brazing defect of the shielding wall 260 is found in advance using the void region 600 formed in a targeted manner at the end of the inner fin 25A. Specifically, the air-tightness test in which the test gas is pushed into the gap area 600 is performed, and the brazing defect of the shielding wall 260 is found.

When a brazing defect occurs in the shield wall 260 inside the refrigerant tube 2G, as shown in fig. 16(a) and (b), the void region 600 is expanded by the pressing of the inspection gas in the air-tightness inspection, and an expanded portion 750(750a and/or 750b) is formed. Therefore, by checking the presence or absence of expansion portion 750, a brazing defect of shielding wall 260 in heat transfer plate 21E (refrigerant pipe 2G) can be found. The inner fins 25A (25A1, 25A2) are brazed to the inner surface of the heat transfer plate 21E, and the expanded portion 750 can be formed in the void region 600 where the inner fins 25A are not disposed (the inner fins 25A inhibit the formation of the expanded portion 750). Fig. 16(a) and (b) also show a filling port 900 for filling the cold storage housing 4 with the cold storage agent 42 (not related to the airtightness test).

The void region 600 is disposed at a position not in contact with the cold storage housing 4. That is, as shown in fig. 16(a), a space 800 is formed near the end of refrigerant pipe 2G formed of a pair of heat transfer plates 21E. When the brazing defect occurs, as shown in fig. 16(b), the expansion portion 750a can expand in the space 800, and the expansion portion 750a can be easily found by visual confirmation. That is, a brazing defect can be easily found.

When the expansion portion 750b expands downward (on the opposite side of the cold storage housing 4), a part of the fin 801 of the outer fin 3 abuts against the expansion portion 750b and bends. By forming the bent portion 801a in the fin 801, a brazing defect can be easily found.

(ninth embodiment)

Fig. 17 to 20 show a ninth embodiment and a modification thereof. Fig. 17 partially shows one of a pair of heat transfer plates 21F constituting the second refrigerant tube 2H. In the second refrigerant tube 2H of the cold storage heat exchanger of the ninth embodiment, a heat transfer portion provided with a plurality of small recesses 250 protruding in the stacking direction is provided instead of the inner fin 25 as the heat transfer member described above.

In the above embodiment, the inner fins 25 are accommodated in the refrigerant passages 23 of the second refrigerant tubes 2A to 2G. However, in the present embodiment, a plurality of small recesses 250 protruding in the stacking direction are formed in the heat transfer plate 21F (the inner surface of the refrigerant passage 23). As shown in fig. 17 and 18, a row of small recesses 250 is formed at equal intervals in the longitudinal direction of the heat transfer plate 21F in the refrigerant passage 23 between the edge portion 261a of the heat transfer plate 21F and the recessed wall portion 24 and in the refrigerant passage 23 between the opposite edge portion 261b and the recessed wall portion 24. Two rows of small concave portions 250 are formed at equal intervals in the longitudinal direction of heat transfer plate 21F in refrigerant passage 23 between two concave wall portions 262.

The small recess 250 is formed when the heat transfer plate 21F is press-formed. The height of each small concave portion 250 is a height at which an end portion (upper surface in fig. 17) 250a of the small concave portion 250 comes into contact with an opposing member (for example, an end portion 250a of the small concave portion 250 of the opposing heat transfer plate 21F). As shown in fig. 17, shielding wall 260 (restricting portion) is formed near communication hole 22 formed at the end of heat transfer plate 21F (refrigerant pipe 2H).

According to the present embodiment, the cold stored in the cold storage housing 4 is also transferred to the air via the small recess 250 (second refrigerant pipe 2H), and therefore the air can be cooled more efficiently. As shown in fig. 19, the position of side portion 250B of small recess 250(250A and 250B) may be aligned with the position of wall portion 41a extending in the stacking direction of case plate 41 of cold storage case 4 (stacking direction of

refrigerant tubes

2 and 2H). With this configuration, the rigidity of the cold storage heat exchanger in the stacking direction can be improved.

Fig. 20 shows a modification of the ninth embodiment. In this modification, two rows of small recesses 250 are formed at equal intervals in the longitudinal direction of the heat transfer plate 21F in the refrigerant passage 23 between the edge portion 261a of the second refrigerant tube 2I extending in the longitudinal direction of the heat transfer plate 21G and the recessed wall portion 262 and in the refrigerant passage 23 between the edge portion 261b on the opposite side and the recessed wall portion 24.

According to the present embodiment and the modifications thereof, since the inner fins 25 as the heat transfer member are not used, the number of parts can be reduced and the cost can be reduced. Further, by providing the shielding wall 260 (restricting portion), the refrigerant can be prevented from flowing through the refrigerant passage 23 (the refrigerant can be prevented from flowing from the refrigerant passage 23 to the communication hole 22 near the shielding wall 260).

(tenth embodiment)

Fig. 21 shows a tenth embodiment. Fig. 21 partially shows one of a pair of heat transfer plates 21H constituting the second refrigerant pipe 2J. A heat transfer plate 21H of the tenth embodiment has a similar configuration to the heat transfer plate 21A of the fourth embodiment shown in fig. 7. Although shielding wall 260 (shielding portion/restricting portion) of heat transfer plate 21A according to the fourth embodiment is a member that completely blocks the flow of the refrigerant, shielding wall 260 according to the present embodiment only restricts (reduces) the amount of the refrigerant that flows, and does not completely block the refrigerant.

The shielding wall 260 of the present embodiment is composed of a pair of shielding wall portions 260c extending toward each other. A gap is formed between the pair of shielding wall portions 260c, and the refrigerant can flow through the gap. However, since the pair of shielding wall portions 260c is formed, the amount of refrigerant flowing is restricted as compared with the case (first refrigerant pipe 2) where the pair of shielding wall portions 260c is not formed. Even in this case, the amount of refrigerant flowing through the second refrigerant tubes 2J can be restricted by the restricting portions (the pair of shielding wall portions 260c) as compared with the amount of refrigerant flowing through the first refrigerant tubes 2, and the amount of cold and heat absorbed by the refrigerant from the cold storage agent 42 in the cold storage housing 4 through the second refrigerant tubes 2J can be reduced.

In the second refrigerant tubes 2A to 2I of the above embodiments, the flow of the refrigerant is completely blocked, but the second refrigerant tubes may be configured such that the amount of the refrigerant flowing through the second refrigerant tubes is smaller than the amount of the refrigerant flowing through the first refrigerant tubes 2. In other words, the amount of refrigerant flowing through the second refrigerant pipe may be limited compared to the amount of refrigerant flowing through the first refrigerant pipe 2. The state of "restricting the amount of refrigerant flowing through the second refrigerant tube as compared with the amount of refrigerant flowing through the first refrigerant tube 2" includes a case where no refrigerant flows through the second refrigerant tube (see the first embodiment) and a case where no refrigerant exists in the second refrigerant tube (see the second embodiment). If the cold storage heat exchanger is configured as described above, cold heat stored in the cold storage housing 4 can be effectively used for cooling air by preventing the cold heat from being absorbed by the refrigerant in the second refrigerant pipe as much as possible.

In addition, in the cold storage heat exchanger 1 of the above embodiment, the refrigerant passage 23 is formed between the communication holes 22 provided at both end portions of the refrigerant tube as a constituent member thereof. That is, communication passages are formed through the communication holes 22 of the plurality of refrigerant tubes, and the pair of communication passages communicate through the refrigerant passage 23. However, the cold-storage heat exchanger may be constituted by a refrigerant pipe having the refrigerant passage 23 and a pipe (tank) forming a communication passage separate from the refrigerant pipe.

In the above embodiment, the cold-storage heat exchanger 1 is configured by the first heat exchange portion 11 and the second heat exchange portion 12 (see fig. 2). However, the cold-storage heat exchanger may be constituted by three or more heat exchange portions. Alternatively, the cold storage heat exchanger may be constituted by one heat exchange portion.

Claims

1. A cold-storage heat exchanger is provided with:

a plurality of refrigerant pipes including a first refrigerant pipe and a second refrigerant pipe through which a refrigerant for exchanging heat with air flowing around flows; and

a plurality of cold accumulation cases which accommodate cold accumulation agent for storing cold and heat,

wherein the first refrigerant pipe and the second refrigerant pipe are respectively abutted against two surfaces of the plurality of cold accumulation shells,

a restriction portion that restricts an amount of refrigerant flowing in the second refrigerant pipe compared to an amount of refrigerant flowing in the first refrigerant pipe is provided in the second refrigerant pipe,

the second refrigerant pipe has a shield portion as the restricting portion that prevents the refrigerant from flowing at all.

2. The cold-storage heat exchanger of claim 1 wherein,

the refrigerant pipe is disposed in an orientation in which the refrigerant flows in an up-down direction,

the shielding portion is disposed above the refrigerant passage of the second refrigerant tube.

3. The cold-storage heat exchanger of claim 1 wherein,

the shielding portions are disposed above and below the refrigerant passage of the second refrigerant tube.

4. The cold-storage heat exchanger of claim 3 wherein,

the refrigerant passage between the shielding portions is open to the atmosphere.

5. The cold-storage heat exchanger as claimed in any one of claims 1 to 4,

the second refrigerant pipe has a heat transfer member therein.

6. The cold-storage heat exchanger of claim 5 wherein,

the refrigerant pipe has communication holes at both ends for flowing the refrigerant into/out of the inside,

the shielding portion is formed of a wall portion formed in the vicinity of the communication hole.

7. The cold-storage heat exchanger of claim 6 wherein,

the wall portion is provided in a plurality of numbers,

the plurality of wall portions are arranged in parallel with each other in the longitudinal direction of the refrigerant tube.

8. The cold-storage heat exchanger of claim 7 wherein,

a brazing material is disposed between the plurality of wall portions.

9. The cold-storage heat exchanger of claim 5 wherein,

the heat transfer member is an inner fin formed by alternately arranging convex portions and concave portions extending in a longitudinal direction of the refrigerant tube in a direction perpendicular to the longitudinal direction.

10. The cold-storage heat exchanger of claim 9, wherein,

a positioning protrusion that restricts a position of the inner fin in the longitudinal direction is provided inside the second refrigerant tube.

11. The cold-storage heat exchanger of claim 5 wherein,

a confirmation hole for confirming leakage of the refrigerant into the refrigerant pipe is opened in the middle of the second refrigerant pipe.

12. The cold-storage heat exchanger as claimed in any one of claims 1 to 4,

the second refrigerant pipe has a heat transfer portion therein,

the heat transfer portion has a plurality of small recesses protruding in the stacking direction of the plurality of refrigerant tubes.

13. The cold-storage heat exchanger of claim 12 wherein,

the height of each of the small recesses is a height at which the end of each of the small recesses comes into contact with the opposing member.

14. The cold-storage heat exchanger of claim 12 wherein,

the positions of the side portions of the small recessed portions are aligned with the positions of the wall portions extending in the stacking direction of the plurality of refrigerant tubes.

15. A cold-storage heat exchanger is provided with:

a plurality of refrigerant tubes including a first refrigerant tube and a second refrigerant tube, the refrigerant tubes being formed by brazing a pair of heat transfer plates, communication holes being provided at both ends, and a refrigerant passage being provided between the communication holes; and

a cold storage housing which accommodates a cold storage agent,

wherein the first refrigerant pipe and the second refrigerant pipe are respectively abutted against two surfaces of the cold accumulation shell,

in the second refrigerant pipe, a shielding wall that prevents the refrigerant from flowing between the communication hole and the refrigerant passage is provided as the restricting portion,

inner fins brazed to inner surfaces of the refrigerant tubes are disposed in the refrigerant passages of the plurality of refrigerant tubes,

a void region where the inner fin is not disposed is provided in the refrigerant passage.

16. The cold-storage heat exchanger of claim 15 wherein,

the void region is disposed at a position not in contact with the cold storage housing.

17. The cold-storage heat exchanger of claim 16 wherein,

a positioning protrusion that restricts a position of the inner fin in a longitudinal direction of the refrigerant tube is provided inside the refrigerant tube.