CN110087922B - Cold storage heat exchanger - Google Patents

Abstract

The cold storage heat exchanger (1) includes a plurality of refrigerant pipes including a first refrigerant pipe (2) and a second refrigerant pipe (2A to 2J) through which a refrigerant that exchanges heat with air flowing around flows. ; and a plurality of cold storage housings (4), which contain a cold storage medium (42) for storing cold and heat. The first refrigerant pipes (2) and the second refrigerant pipes (2A to 2J) are respectively in contact with both surfaces of the plurality of regenerator casings (4). The second refrigerant tubes ( 2A to 2J) are provided with restricting portions ( 26 , 260 ) that restrict the amount of refrigerant flowing in the first refrigerant tubes ( 2 ) to the second refrigerant tubes ( 2 ). The amount of refrigerant flowing in (2A to 2J).

Description

Cold storage heat exchanger

technical field

The present invention relates to a cold-storage heat exchanger provided with refrigerant tubes and cold storage cases.

Background technique

The cold storage heat exchanger disclosed in the following Patent Document 1 includes: a plurality of refrigerant tubes arranged in parallel at intervals; a plurality of outer fins arranged between adjacent refrigerant tubes; and a plurality of cold storage tubes The casing is arranged in a gap between adjacent refrigerant tubes where the outer fins are not interposed. The refrigerant flowing in the refrigerant pipe exchanges heat with the air flowing outside the refrigerant pipe, and the air is cooled. The outer fins facilitate heat exchange between the refrigerant and the air. The cold storage case stores the cold and heat of the refrigerant transferred from the refrigerant pipes. When the temperature of the refrigerant pipe rises (when the refrigerant does not flow), the refrigerant pipe is cooled by the stored cold and heat. In the case where the cold storage heat exchanger is used for vehicle air conditioning, even when the refrigerant hardly flows in the refrigerant pipe (for example, during an idle-stop of avehicle), the air can be cooled, and the cooled Air is supplied to the vehicle interior.

prior art literature

Patent Literature

Patent Document 1: Japanese Patent Laid-Open No. 2008-68827

SUMMARY OF THE INVENTION

Invention to solve problem

However, in the cool storage heat exchanger disclosed in Patent Document 1, since both surfaces of the cool storage case are in contact with the refrigerant tubes, not only the air but also the refrigerant in the refrigerant tubes tends to be cooled. That is, the cold and heat stored in the cold storage agent are not effectively used for cooling the air. In addition, when two heat transfer plates are brazed to form a refrigerant pipe, there is also a problem that poor brazing cannot be easily detected.

An object of the present invention is to provide a cold storage heat exchanger capable of efficiently cooling air by cold and heat stored in a cold storage casing, and capable of easily detecting poor brazing.

solution to the problem

A first feature of the present invention is to provide a cold storage heat exchanger including: a plurality of refrigerant pipes including first and second refrigerant pipes that flow a refrigerant that exchanges heat with air flowing around; and a plurality of refrigerant pipes. a regenerator housing containing a regenerator for storing cold and heat, wherein the first and second refrigerant pipes are respectively abutted on both surfaces of the regenerator housings, and the second refrigerant A restriction portion is provided in the tube, and the restriction portion restricts the amount of refrigerant flowing in the second refrigerant tube compared to 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 comprising: a plurality of refrigerant pipes formed by brazing a pair of heat transfer plates, with communication holes provided at both end portions, A refrigerant passage is provided between the holes and includes first and second refrigerant pipes; and a cold storage casing that accommodates a cold storage medium, wherein the first and second refrigerant pipes are respectively abutted on the cold storage casing On both sides of the body, the second refrigerant pipe is provided with restricting portions that restrict the amount of refrigerant flowing in the second refrigerant pipe compared to the amount of refrigerant flowing in the first refrigerant pipe , a shielding wall that prevents refrigerant from flowing between the communication hole and the refrigerant passage is provided in the second refrigerant pipe as the restricting portion, and the plurality of refrigerant pipes are In the refrigerant passage, inner fins brazed to the inner surface of the refrigerant pipe are arranged, and a void region where the inner fins are not arranged is provided in the refrigerant passage.

effect of invention

According to the above-mentioned first or second feature, the cold and heat stored in the cold storage case is conducted to the refrigerant pipe when the temperature of the refrigerant pipe rises (when the refrigerant does not flow), but the cold and heat are transferred to both surfaces of the refrigerant case. Conduction of the second refrigerant pipe among the contacting first and second refrigerant pipes is reduced (or not conducted to the second refrigerant pipe). Therefore, the cold and heat stored in the cooling medium can be effectively used for cooling the air.

Description of drawings

FIG. 1 is a partially exploded perspective view of the cold storage heat exchanger according to the first embodiment.

FIG. 2 is a perspective view showing a refrigerant path of the above-mentioned cold storage heat exchanger.

FIG. 3 is a sectional view taken along the line III-III in FIG. 1 .

4 is an exploded perspective view of a second refrigerant pipe in the above-mentioned cold storage heat exchanger.

5 is an exploded perspective view of a second refrigerant pipe in the cold storage heat exchanger according to the second embodiment.

6 is an exploded perspective view of a second refrigerant pipe in the cold storage heat exchanger according to the third embodiment.

7 is a partial cross-sectional perspective view of a heat transfer plate of a second refrigerant tube in a cold storage heat exchanger according to a fourth embodiment.

8 is a partial cross-sectional perspective view of a heat transfer plate of a second refrigerant tube in a cold storage heat exchanger according to a fifth embodiment.

FIG. 9 is a cross-sectional view of the second refrigerant pipe.

10 is a partial cross-sectional view of a second refrigerant pipe in a modification of the fifth embodiment.

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

12 is a partial cross-sectional perspective view of the heat transfer plate of the second refrigerant tube in the cold storage heat exchanger according to the sixth embodiment.

13 is a partial cross-sectional perspective view of a heat transfer plate of a second refrigerant tube in a cold storage heat exchanger according to an eighth embodiment.

FIGS. 14( a ) to ( c ) are plan views showing an example of the heat transfer plate of the second refrigerant pipe.

15 is a plan view of a heat transfer plate of a second refrigerant pipe of a comparative example.

FIGS. 16( a ) and ( b ) are explanatory diagrams showing the state of the airtightness inspection of the second refrigerant pipe according to the eighth embodiment.

17 is a partial cross-sectional perspective view of a heat transfer plate of a second refrigerant tube in a cold storage heat exchanger according to a ninth embodiment.

FIG. 18 is a cross-sectional view taken along line XVIII-XVIII in FIG. 17 .

FIG. 19 is a cross-sectional view showing the support structure in the lamination direction.

20 is a partial cross-sectional perspective view of a heat transfer plate of a second refrigerant pipe in a modification of the ninth embodiment.

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

Detailed ways

Hereinafter, embodiments will be described with reference to the drawings. In addition, in embodiment, the same code|symbol is attached|subjected to the same or equivalent element, and the overlapping description is abbreviate|omitted.

(first embodiment)

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

As shown in FIG. 1 , the cold storage heat exchanger 1 includes: a plurality of refrigerant pipes 2 and 2A arranged in parallel with an interval therebetween; and a plurality of outer fins 3 arranged between the adjacent refrigerant pipes 2 and 2A. and a plurality of regenerator casings 4, which are arranged in the gaps between the adjacent refrigerant pipes 2 and 2A where the outer fins 3 are not sandwiched. The cold storage heat exchanger 1 is arranged so that the refrigerant flows in the up-down direction (refer to the arrow V in FIG. 1 ) in the refrigerant pipe 2 (the direction shown in FIG. 2 ). The components of the cold storage heat exchanger 1 are welded by brazing at locations where they come into contact with each other.

The refrigerant pipe 2 is formed of an aluminum material. The refrigerant pipe 2 is formed by overlapping two heat transfer plates 21 . Two communication holes 22 are formed at both ends of the refrigerant pipe 2 , respectively. In addition, as will be described later, some of the refrigerant pipes 2 are not formed with the communication holes 22, but the ends are closed so that the refrigerant flows through a plurality of paths [paths].

The refrigerant pipe 2 internally has a pair of refrigerant passages 23 that communicate between the two communication holes 22 at both ends. The two refrigerant passages 23 are completely divided by being partitioned by a depressed wall 24 of each heat transfer plate 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 passage 23 extends in a direction at right angles to the air flow direction. In each refrigerant passage 23, inner fins 25 as heat transfer members are arranged. The inner fin 25 is composed of a metal plate such as aluminum, and protruded portions 25 a and depressed portions 25 b extending in the longitudinal direction are alternately formed on the inner fin 25 (see FIG. 7 ).

In the stack of refrigerant pipes 2, as shown in FIG. 2, the first heat exchange portion 11 is formed on the upstream side (refrigerant passage group) of the air flow, and the first heat exchange portion 11 is formed on the downstream side (refrigerant passage) of the air flow. group) is formed with the second heat exchange portion 12 . The outlet of the second heat exchange part 12 is communicated with the inlet of the first heat exchange part 11 through the communication pipe 13 . As indicated by the arrows in FIG. 2 , the refrigerant that has flowed in from the outside flows in a meandering manner in the laminated body of the refrigerant pipes 2 . For example, in the plurality of refrigerant pipes 2 in the range X in FIG. 2 , the refrigerant flows upward from the bottom as indicated by the arrows (=1 path). The refrigerant flows in the first heat exchange part 11 (3 paths) after flowing through the second heat exchange part 12 (3 paths) and flows out to the outside. In addition, as described above, the communication hole 22 is not formed in the portion where the closing portion 14 is provided, and the direction of the passage of the refrigerant is changed by the closing portion 14 .

The configuration of the second refrigerant pipe 2A on one side (upper side in FIG. 3 ) of the regenerator casing 4 is different from the configuration of the first refrigerant pipe 2 on the other side (lower side in FIG. 3 ) (however, FIG. 3 The difference in composition is not shown). These configurations will be described in detail below. In addition, all the refrigerant pipes that are not in contact with the cool storage case 4 are the first refrigerant pipes 2 .

The outer fins 3 are formed of an aluminum material. The outer fins 3 are wave-shaped when viewed from the direction of air flow. 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 cool storage casings 4 is smaller than the number of the stacked refrigerant tubes 2 and 2A. In the present embodiment, one cool storage case 4 is provided with respect to five to six refrigerant pipes 2 and 2A. The cool storage casings 4 are arranged at equal intervals. The cool storage case 4 is formed of an aluminum material. The inside of the cool storage case 4 is filled with the cool storage medium 42 (refer FIG. 3). The cool storage case 4 is formed by overlapping two case plates 41 . The cool storage case 4 is in contact with the refrigerant pipes 2 and 2A on both sides. Therefore, air does not pass between the regenerator casing 4 and the refrigerant pipes 2 and 2A. In order to increase the heat transfer efficiency with the refrigerant pipes 2 and 2A as much as possible, the regenerator case 4 is in surface contact with the refrigerant pipes 2 and 2A over substantially the entire area of the side surface.

In the second refrigerant pipe 2A of the regenerator casing 4, as shown in FIG. 4, a shield portion 26 that prevents the refrigerant from flowing at all is provided in the refrigerant passage 23. As shown in FIG. The shielding portion 26 is arranged on the upper portion of the refrigerant passage 23 of the second refrigerant pipe 2A. The shielding portion 26 is formed by press-molding each of the heat transfer plates 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 part 26 has a vertical wall 26a and a pair of lateral walls 26b and 26c respectively extending obliquely from both ends of the vertical wall 26a. The shielding portion 26 partitions the refrigerant passage 23 into two layers by the two lateral wall portions 26b, 26c. Thereby, even if one of the lateral wall portions 26b (or 26c) is defective in brazing, the refrigerant can be prevented from flowing from the communication hole 22 in the vicinity of the shielding portion 26 to the refrigerant passage 23 (the refrigerant can also be prevented from flowing from the refrigerant passage 23 to the shielding). communication hole 22 in the vicinity of part 26).

In addition, in the first refrigerant pipe 2 , the shielding portion 26 is not provided in the refrigerant passage 23 , and the refrigerant freely flows in the refrigerant passage 23 . In addition, the shielding portion 26 is provided as a restrictor that restricts the amount of refrigerant flowing in the second refrigerant pipe 2A compared to the amount of refrigerant flowing in the first refrigerant pipe 2 .

The cold storage heat exchanger 1 configured as described above performs heat exchange between the refrigerant flowing in the refrigerant pipes 2 and the air flowing outside the refrigerant pipes 2, and the air is cooled. The outer fins 3 promote heat exchange between the refrigerant and the air. The cold storage case 4 stores the cold and 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 and heat. Therefore, 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, when the vehicle is idling stop), (by the The heat exchange of the refrigerant pipe 2 ) cools the air, and the cooled air can be supplied into the vehicle interior.

Here, in the cold storage heat exchanger 1, the first and second refrigerant pipes 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 pipe 2A. As described above, when the temperature of the refrigerant pipes 2 and 2A increases (when the refrigerant does not flow), the refrigerant pipes 2 and 2A are cooled by the stored cold and heat. However, since the refrigerant does not flow in the second refrigerant pipe 2A, only the refrigerant in the first refrigerant pipe 2 is cooled. (The stored cold and heat are prevented from being absorbed by the refrigerant in the second refrigerant pipe 2A as much as possible.) As a result, the cold and heat stored in the cold storage medium 42 (via the second refrigerant pipe 2A) is effectively used for air cooling .

In addition, since the compressor of the refrigerant cycle is stopped at the time of the idling stop of the vehicle, the refrigerant hardly flows in the refrigeration cycle. However, immediately after the compressor is stopped, the refrigerant is not completely circulated, and the pressure of the refrigerant in the refrigeration cycle has a height difference, and the refrigerant circulates due to the pressure difference. Therefore, the flow of the refrigerant exists in the first refrigerant pipe 2 , and the cold and heat stored in the cool storage case 4 are absorbed. In the present embodiment, by providing the second refrigerant pipe 2A, the cold and heat absorbed by the refrigerant via the first refrigerant pipe 2 is reduced.

In the present embodiment, the shielding portion 26 is arranged above the second refrigerant pipe 2A. Therefore, the refrigerant is prevented from flowing into the refrigerant passage 23 from the upper communication hole 22 of the refrigerant pipe 2A (the refrigerant is also prevented from flowing into the upper communication hole 22 from the refrigerant passage 23). This also prevents the stored cold and heat from being absorbed by the refrigerant in the second refrigerant pipe 2A. In addition, if the shielding portion 26 is provided only in the lower part of the second refrigerant pipe 2A, oil mixed in the refrigerant in the refrigeration cycle will accumulate in the lower part of the second refrigerant pipe 2A. As a result, the amount of oil mixed into the refrigerant decreases, and there is a concern that problems such as hot sticking of the compressor will occur. Therefore, it is preferable to arrange|position the shield part 26 in the upper part of 2 A of 2nd refrigerant|coolant pipes.

In addition, inner fins 25 are provided in the refrigerant passages 23 of the second refrigerant pipes 2A. Since the cold and heat stored in the cool storage case 4 are also transferred to the air via the inner fins 25 (the second refrigerant pipes 2A), the air can be cooled more efficiently. In addition, in the present embodiment, the inner fins 25 are also provided in the first refrigerant pipes 2 , and the evaporator (cold storage heat exchanger) 1 is made to function normally when the refrigerant flows in the first refrigerant pipes 2 . When functioning, the heat exchange between the refrigerant and the air is promoted by the inner fins 25 in the first refrigerant pipe 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 pipe 2B is different from the configuration of the second refrigerant pipe 2A of the first embodiment described above.

In the present embodiment, the shielding portion 26 (restriction portion) is not only arranged at the upper portion of the second refrigerant pipe 2B but also at the lower portion. The configuration of each shielding portion 26 is the same as that of the shielding portion 26 of the first embodiment, and thus detailed description thereof is omitted.

According to the present embodiment, when the temperature of the refrigerant pipes 2 and 2B increases (when the refrigerant does not flow), the refrigerant pipes 2 and 2B are also cooled by the cold and heat stored in the cool storage case 4 . However, since the refrigerant does not flow in the second refrigerant pipe 2B at all, only the refrigerant in the first refrigerant pipe 2 is cooled. (The stored cold and heat are prevented from being absorbed by the refrigerant in the second refrigerant pipe 2B as much as possible.) As a result, the cold and heat stored in the cold storage medium 42 (via the first refrigerant pipe 2 ) is effectively used for air cooling .

The shielding parts 26 are arranged at the upper and lower parts of the second refrigerant pipe 2B. Therefore, even if the refrigerant leaks in any one of the shielding portions 26, the refrigerant can be prevented from flowing in the second refrigerant pipe 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 pipe 2C is different from the configuration of the second refrigerant pipe 2A of the first embodiment described above and the second refrigerant pipe 2B of the second embodiment described above.

Also in the present embodiment, the shielding portions 26 (restricting portions) are arranged at the upper and lower portions of the second refrigerant pipe 2C, but a cutout 27 is formed between the shielding portions 26 . The cutout portion 27 is formed by notching one of the pair of heat transfer plates 21 . The cutout portion 27 opens the inside of one of the pair of refrigerant passages 23 to the atmosphere. (In addition, in the present embodiment, although the refrigerant does not flow through the refrigerant passage 23 of the second refrigerant pipe 2C, it will be described as a refrigerant passage. The same applies to the embodiments to be described later.)

According to the present embodiment, when the temperature of the refrigerant pipes 2 and 2C increases (when the refrigerant does not flow), the refrigerant pipes 2 and 2C are also cooled by the cold and heat stored in the cool storage case 4 . However, since the refrigerant does not flow in the second refrigerant pipe 2C at all, only the refrigerant in the first refrigerant pipe 2 is cooled. (The stored cold and heat are prevented from being absorbed by the refrigerant in the second refrigerant pipe 2C as much as possible.) As a result, the cold and heat stored in the cold storage medium 42 (via the first refrigerant pipe 2 ) is effectively used for air cooling .

In addition, in the present embodiment, the inside of one of the pair of refrigerant passages 23 is opened to the atmosphere. Therefore, no refrigerant exists in the refrigerant passage 23 open to the atmosphere, and in the refrigerant passage 23 open to the atmosphere, the cold and heat stored in the cool storage case 4 is not absorbed by the refrigerant. In addition, in the refrigerant passage 23 open to the atmosphere, the air is cooled by the cold and heat stored in the cool storage case 4 . Furthermore, when the refrigerant pipes 2 and 2C are filled with refrigerant after brazing the cold storage heat exchanger 1 , the leakage of the refrigerant from the cutout portion 27 can easily lead to the detection of defective brazing of the shielding portion 26 .

(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 pipe 2D. In the present embodiment, the shield portion of the second refrigerant pipe 2D is constituted by a shield wall 260 formed in the vicinity of the communication hole 22 . (The shielding wall 260 is one form of the shielding portion, that is, the restricting portion.) Specifically, the shielding wall 260 standing up between the communication hole 22 and the inner fin 25 is provided instead of the shielding shown in FIGS. 4 and 5 . Section 26.

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

(Fifth Embodiment)

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 pipe 2E of the cold storage heat exchanger according to the fifth embodiment, each shielding wall 260 (restriction portion) is constituted by a pair of wall portions [a pair of walls] 260a, 260b. The pair of wall portions 260a and 260b are parallel to each other, and are aligned in the longitudinal direction of the heat transfer plate 21B. The wall portions 260a and 260b extend in directions at right angles to the longitudinal direction of the heat transfer plate 21B, respectively. In this embodiment, two wall parts 260a and 260b are provided in each shielding wall 260, but three or more wall parts may be provided.

The end portions (upper surfaces in FIG. 8 ) of the shielding wall 260 (the wall portions 260 a and 260 b ) are configured to be connected with the peripheral portion 22 a of the communication hole 22 , the edge portions 261 a and 261 b extending in the longitudinal direction of the heat transfer plate 21B, and the recesses. The end surfaces of the wall portion 24 are in the same plane. They are respectively brazed to the respective ones of the opposing heat transfer plates 21B. By providing the shielding wall 260 composed of the pair of wall portions 260a and 260b, the flow of the refrigerant in the refrigerant passage 23 can be more reliably prevented (the refrigerant can also be prevented from flowing from the refrigerant passage 23 to the vicinity of the shielding wall 260 more reliably. flow through the communication hole 22).

In addition, in this embodiment, as shown in FIG. 9, the brazing material 240 is arrange|positioned in the space 300 between a pair of wall parts 260a, 260b. Therefore, when brazing the heat transfer plates 21B to each other, the space [chamber] 300 between the pair of wall portions 260a and 260b is also reliably brazed by the brazing material 240 . As a result, the flow of the refrigerant in the refrigerant passage 23 can be prevented more reliably (the flow of the refrigerant from the refrigerant passage 23 to the communication hole 22 in the vicinity of the shielding wall 260 can also be prevented more reliably).

In addition, in the modification of the fifth embodiment shown in FIG. 10 , in the middle of the second refrigerant pipe 2E (a pair of heat transfer plates 21 ), there is provided a measure for the leakage of the refrigerant into the second refrigerant pipe 2E. Confirmed confirmation hole 400 . By checking the hole 400 , it is possible to visually check whether the leakage of the refrigerant is reliably prevented by the brazing of the pair of wall portions 260 a and 260 b and the space 300 . Therefore, defective products can be found reliably.

(Sixth Embodiment)

Fig. 11(b) and Fig. 12 show the heat transfer plate 21C of the second refrigerant pipe 2F according to the sixth embodiment. In addition, the inner fin 25A is not shown in FIG. 12 . In addition, for comparison, the heat transfer plate 21A of the above-mentioned fourth embodiment is shown in FIG. 11( a ). In the present embodiment, positioning protrusions 200 that regulate the positions of the inner fins 25A in the longitudinal direction are provided inside the second refrigerant pipes 2F (heat transfer plates 21C). The positioning protrusions 200 are integrally formed on the inner walls of the edge portions 261 a and 261 b of the heat transfer plate 21C and the side walls of the recessed wall portion 24 by press molding. The configuration of the second refrigerant pipe 2F other than the positioning protrusions 200 is the same as that of the heat transfer plate 21A of the fourth embodiment.

Therefore, when using the inner fins 25A that are shorter than the inner fins 25 of the fourth embodiment, by forming the positioning protrusions 200 at appropriate locations on the heat transfer plate 21C, the inner fins 25A can be easily positioned, and the Efficient assembly work. In addition, by holding the ends of the inner fins 25A between the positioning protrusions 200 , rattling of the inner fins 25A can be prevented. Further, by using the short inner fins 25A, the cost can be reduced.

(Seventh Embodiment)

Fig. 11(c) shows the heat transfer plate 21D of the second refrigerant pipe 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 described above. The partition wall 500 is formed at the center in the longitudinal direction of each refrigerant passage 23 .

Four accommodation chambers 502a to 502d are formed by the peripheral portion 22a of the communication hole 22, the edge portions 261a, 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 that are shorter than the inner fins 25A of the sixth embodiment are accommodated in the respective accommodating portions 502a to 502d.

According to the above configuration, the inner fins 25B can be easily positioned, and the assembly work can be improved. In addition, by holding the inner fins 25B by the accommodating portions 502a to 502d, the rattling of the inner fins 25B can be prevented. Further, by using the short inner fins 25B, the cost can be reduced. Furthermore, the rigidity of the lamination direction of the heat transfer plates 21D (second refrigerant tubes) can be improved by the partition wall 500, and as a result, the rigidity of the cold storage heat exchanger can be improved.

(Eighth Embodiment)

An eighth embodiment and a comparative example will be described with reference to FIGS. 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. FIGS. 14( a ) to ( c ) show examples ( 21Ea to 21Ec ) of the heat transfer plate 21E. Figure 15 shows a comparative example (700) of the heat transfer plate. FIGS. 16( a ) and ( b ) show the configuration of the refrigerant pipe 2G according to the eighth embodiment and the state during the airtight inspection.

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. In the heat transfer plate 21E of the present embodiment, the shielding wall 260 (restriction portion) similar to that of the fourth embodiment (refer to FIG. 7 ) is provided. (The shape of the shielding wall 260 of FIG. 13 is slightly different from the shape of the shielding wall 260 of FIG. 7, but may be the same.)

The end portion (upper surface in FIG. 13 ) of the shielding wall 260 is flush with the peripheral portion 22 a of the communication hole 22 , the edge portions 261 a and 261 b extending in the longitudinal direction of the heat transfer plate 21E, and the end surface of the recessed wall portion 24 . They are respectively brazed to the respective ones of the opposing heat transfer plates 21E. Therefore, the refrigerant can be prevented from flowing in the refrigerant passage 23 (the refrigerant can also be prevented from flowing from the refrigerant passage 23 to the communication hole 22 in the vicinity of the shielding wall 260 ) with a relatively simple configuration.

In addition, as described above, in FIG. 13 , the area 610 surrounded by the one-dot chain line and the area 610 of the opposing heat transfer plate 21E are brazed with the brazing material. As shown in FIGS. 14( a ) to ( c ), in the refrigerant passages 23 of the heat transfer plates 21Ea to 21Ec (the second refrigerant pipes 2G), brazed to both inner surfaces of the second refrigerant pipes 2G is arranged. 25A (25A1, 25A2) on the inner fins. In addition, the heat transfer plates 21Ea to 21Ec are also provided with positioning protrusions 200 for positioning the inner fins 25A. In addition, the refrigerant passage 23 is provided with a void area 600 in which the inner fins 25A are not arranged.

Specifically, in the heat transfer plate 21Ea shown in FIG. 14( a ), void regions 600 are provided at both ends of the two parallel inner fins 25A1 and 25A2 . In the heat transfer plate 21Eb shown in FIG. 14( b ), void regions 600 are provided at one end (right end) of the inner fin 25A1 and the other end (left end) of the inner fin 25A2 . In the heat transfer plate 21Ec shown in FIG. 14( c ), the one end (left end) of the inner fins 25A1 and 25A2 is provided with a void region 600 , respectively.

According to the above configuration, the inner fins 25A ( 25A1 , 25A2 ) can be easily positioned, and the assembling work can be improved. In addition, by holding the ends of the inner fins 25A between the positioning protrusions 200 , rattling of the inner fins 25A can be prevented. Further, by using the short inner fins 25A, the cost can be reduced.

Here, the defective brazing of the heat transfer plate 700 (refrigerant tube) of the comparative example will be described with reference to FIG. 15 . In addition, about the heat transfer plate 700, the same reference numerals are attached|subjected to the structure which is the same as or equivalent to the said heat transfer plate 21E, and the repeated description is abbreviate|omitted.

As shown in FIG. 15 , when defective brazing occurs in shielding wall 260, oil 710 in the air-conditioning cycle penetrates into refrigerant passage 23 through the portion where defective brazing occurs (see arrow D10). The oil 710 stays in the refrigerant passages 23 in which the inner fins 25A2 are accommodated, and causes problems such as hot sticking of the compressor. Therefore, in this embodiment, the void region 600 formed in the end portion of the inner fin 25A is used in a targeted manner, and the brazing defect of the shielding wall 260 is found in advance. Specifically, the airtightness inspection in which the inspection gas was pressed into the void region 600 was performed, and it was found that the brazing of the shielding wall 260 was defective.

When defective brazing occurs in the shielding wall 260 inside the refrigerant pipe 2G, in the airtight inspection, as shown in FIGS. 16( a ) and ( b ), the void region 600 expands due to the press-in of the inspection gas , thereby forming the expansion portion 750 (750a and/or 750b). Therefore, by confirming the presence or absence of the expansion portion 750, it is possible to find out the poor brazing of the shielding wall 260 in the heat transfer plate 21E (refrigerant tube 2G). The inner fins 25A ( 25A1 , 25A2 ) are brazed to the inner surface of the heat transfer plate 21E, and the expansion portion 750 can be formed in the void region 600 where the inner fin 25A is not arranged (the inner fin 25A prevents the formation of the expansion portion 750 ). 16( a ) and ( b ) also show a filling port 900 for filling the cool storage case 4 with the cool storage medium 42 (irrelevant to the airtight inspection).

In addition, the void region 600 is arranged at a position not in contact with the cool storage case 4 . That is, as shown in FIG.16(a), the space 800 is formed in the edge part vicinity of the refrigerant pipe 2G which consists of a pair of heat transfer plate 21E. When poor soldering occurs, as shown in FIG. 16( b ), the swollen portion 750a can be swollen in the space 800 , and the swollen portion 750a can be easily found by visual confirmation. That is, the brazing defect can be easily found.

When the expansion portion 750b expands downward (opposite to the cool storage case 4), a part of the fins 801 of the outer fins 3 abuts against the expansion portion 750b and bends. By forming the bent portions 801a on the fins 801, poor soldering can be easily found.

(Ninth Embodiment)

17 to 20 show a ninth embodiment and a modification thereof. FIG. 17 partially shows one of the pair of heat transfer plates 21F constituting the second refrigerant pipe 2H. In the second refrigerant tube 2H of the cold storage heat exchanger according to the ninth embodiment, a heat transfer portion having a plurality of small recesses 250 protruding in the stacking direction is provided in place of the above-described inner fins 25 as heat transfer members.

In the above-described embodiment, the inner fins 25 are accommodated in the refrigerant passages 23 of the second refrigerant pipes 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 FIGS. 17 and 18 , the refrigerant passage 23 between the edge portion 261 a and the recessed wall portion 24 of the heat transfer plate 21F, and the refrigerant passage 23 between the opposite side edge portion 261 b and the recessed wall portion 24 On the top, a row of small recesses 250 is formed at equal intervals along the length direction of the heat transfer plate 21F. In addition, in the refrigerant passage 23 between the two recessed wall portions 262, two rows of small recessed portions 250 are formed at equal intervals along the longitudinal direction of the heat transfer plate 21F.

The small recesses 250 are formed when the heat transfer plate 21F is press-formed. The height of each small concave portion 250 is the height at which the end (upper surface in FIG. 17 ) 250a of the small concave portion 250 contacts the opposing member (for example, the end portion 250a of the small concave portion 250 of the opposing heat transfer plate 21F). Moreover, as shown in FIG. 17, the shielding wall 260 (restriction part) is formed in the vicinity of the communication hole 22 formed in the edge part of the heat transfer plate 21F (refrigerant tube 2H).

According to the present embodiment, since the cold and heat stored in the cool storage case 4 is also transferred to the air via the small recessed portion 250 (the second refrigerant pipe 2H), the air can be cooled more efficiently. In addition, as shown in FIG. 19 , it is preferable to extend the position of the side portion 250b of the small recess 250 ( 250A and 250B) along the stacking direction of the case plates 41 of the regenerator case 4 (the stacking direction of the refrigerant tubes 2 and 2H). The position of the wall portion 41a is aligned. According to this structure, the rigidity of the lamination direction of a cold storage heat exchanger can be improved.

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

According to the present embodiment and its modification, since the inner fins 25 as heat transfer members are not used, the number of parts can be reduced and the cost can be reduced. In addition, by providing the shielding wall 260 (restriction portion), the refrigerant can be prevented from flowing in the refrigerant passage 23 (the refrigerant can also 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 the pair of heat transfer plates 21H constituting the second refrigerant pipe 2J. The heat transfer plate 21H of the tenth embodiment has a configuration similar to that of the heat transfer plate 21A of the fourth embodiment shown in FIG. 7 . The shielding wall 260 (shielding part/restricting part) of the heat transfer plate 21A of the fourth embodiment completely blocks the flow of the refrigerant, but the shielding wall 260 of the present embodiment only restricts (reduces) the amount of refrigerant flowing, and does not completely block.

The shielding wall 260 of the present embodiment includes 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 are formed, the amount of refrigerant flowing is restricted compared to the case where the pair of shielding wall portions 260c is not formed (the first refrigerant pipe 2). Even in this way, by the restricting portion (the pair of shielding wall portions 260c), the amount of refrigerant flowing in the second refrigerant pipe 2J can be restricted compared to the amount of refrigerant flowing in the first refrigerant pipe 2, and the amount of refrigerant flowing in the second refrigerant pipe 2J can be reduced. The cold and heat absorbed by the refrigerant through the second refrigerant pipe 2J to the regenerator 42 in the regenerator case 4 .

In the second refrigerant pipes 2A to 2I of the above-described embodiments, the flow of the refrigerant is completely blocked, but the second refrigerant pipes may be configured such that the amount of refrigerant flowing in the second refrigerant pipes is higher than The amount of refrigerant flowing in the first refrigerant pipe 2 is small. In other words, it is sufficient to limit the amount of refrigerant flowing in the second refrigerant pipe compared to the amount of refrigerant flowing in the first refrigerant pipe 2 . In addition, the state of "the amount of refrigerant flowing in the second refrigerant pipe is limited compared to the amount of refrigerant flowing in the first refrigerant pipe 2" also includes the case where the refrigerant in the second refrigerant pipe does not flow (refer to the first refrigerant pipe 2). One embodiment), the case where no refrigerant exists in the second refrigerant pipe (refer to the second embodiment). If the cold storage heat exchanger is configured in this way, the cold and heat stored in the cold storage case 4 can be prevented from being absorbed by the refrigerant in the second refrigerant pipe as much as possible, so that the cold and heat can be effectively used for air cooling.

In addition, in the cold storage heat exchanger 1 of the above-described embodiment, the refrigerant passages 23 are formed between the communication holes 22 provided at both ends of the refrigerant pipe as its constituent member. That is, a connecting passage is formed through the communication holes 22 of the plurality of refrigerant pipes, and a pair of connecting passages are communicated 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.

Moreover, in the said embodiment, the cold storage heat exchanger 1 consists of the 1st heat exchange part 11 and the 2nd heat exchange part 12 (refer FIG. 2). However, the cold storage heat exchanger may be constituted by three or more heat exchange parts. Alternatively, the cold storage heat exchanger may be constituted by one heat exchange part.

Claims (17)

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

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,

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,

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.

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