KR102161528B1 - Cold reserving heat exchanger - Google Patents

Abstract

The present invention relates to a storage cooling heat exchanger, and in more detail, among the tubes arranged in three rows in the width direction, a storage cooling material is stored in the second row tube, and the cooling fluid flowing in the first row and the third row tube can move to each other. It is formed so that it effectively stores the cool air of the cooling fluid and releases cool air when the engine is stopped, thereby preventing a sudden temperature increase in the interior of the vehicle, thereby improving the user's cooling comfort, and energy and time consumed during recooling. It relates to a heat storage heat exchanger that can minimize the.

Description

Cold storage heat exchanger {Cold reserving heat exchanger}

The present invention relates to a storage cooling heat exchanger, and in more detail, among the tubes arranged in three rows in the width direction, a storage cooling material is stored in the second row tube, and the cooling fluid flowing in the first row and the third row tube can move to each other. It is formed so that it effectively stores the cool air of the cooling fluid and releases cool air when the engine is stopped, thereby preventing a sudden temperature increase in the interior of the vehicle, thereby improving the user's cooling comfort, and energy and time consumed during recooling. It relates to a heat storage heat exchanger that can minimize the.

In recent years, as interest in the environment and energy increases worldwide, research to improve fuel efficiency is being conducted, and research and development for light weight, miniaturization, and high functionality are continuously being conducted to satisfy the needs of various consumers.

In many cases, the hybrid vehicle employs an idle stop/go system in which the engine is automatically stopped when the vehicle is stopped, such as waiting for a signal, and the engine is restarted by operating the transmission again. However, even in the case of the hybrid vehicle, since the cooling device is operated by the engine, when the engine is stopped, the compressor is also stopped, and accordingly, the temperature of the evaporator rises, thereby reducing user comfort. In addition, since the refrigerant inside the evaporator is easily evaporated even at room temperature, the refrigerant is vaporized for a short period of time when the compressor is not operated and the engine is operated again, and even if the compressor and evaporator are operated, the vaporized refrigerant must be compressed and liquefied. As well as taking a long time, there is a problem of increasing the total energy consumption.

In this case, the hybrid vehicle may further include a storage cooling evaporator, thereby improving cooling performance and extending or delaying the engine restart time.

As a technology related to this, Japanese Patent Laid-Open Publication No. 2000-205777 (name of the invention: 　 cold storage heat exchanger) has been proposed, which is shown in FIG. 1.

The refrigerant heat storage heat exchanger 90 as shown in FIG. 1 integrates the refrigerant passage 91e through which refrigerant flows and the refrigerant storage compartments 91f and 91f' in which refrigerant is stored by a tube 91 having a double tube structure. And a passage 94 for the fluid to be heat-exchanged with the refrigerant outside the tube 91 of the double tube structure.

However, in the heat storage heat exchanger as shown in FIG. 1, since the tube is formed by bonding several plates, the occurrence of bonding failure is high, and as it is formed in a double tube shape, there is difficulty in manufacturing. There may be a problem that the refrigerant inside and the storage coolant are mixed. In addition, even if a bonding failure occurs, there is a problem that it is difficult to find the part.

In order to solve the above-described problem, as shown in FIG. 2, three rows are arranged in the width direction, the cooling fluid is circulated in the first row and the third row tube, and a plurality of coolant is stored in the second row tube. tube; Fixed at both ends in the longitudinal direction of the tube, and separated into three spaces in the width direction, a first space part communicating with the first row tube, a second space part communicating with the second row tube, and the third A storage cooling heat exchanger including an upper header tank and a lower header tank in which a header and a tank are coupled, and consisting of a third space portion communicating with the heat tube has been developed.

The storage space for the heat storage heat exchanger is limited, and in particular, spaces for the upper header tank and the lower header tank are also limited. In the case of prioritizing the heat dissipation performance over the heat storage performance in the heat storage heat exchanger, the spaces of the first and third spaces must be enlarged to increase the heat dissipation performance, and when prioritizing the storage cooling performance, a second space capable of storing cold air There is a limit to increasing the space uniformly by increasing the size of the wealth.

In addition, there is a difficulty in making an optimal design so that both heat dissipation performance and storage cooling performance can be improved.

Therefore, it is necessary to develop a storage cooling heat exchanger capable of improving both heat dissipation performance and storage cooling performance by optimizing the areas of the first, second and third spaces in the header tank of the storage cooling heat exchanger.

Japanese Patent Laid-Open Publication No. 2000-205777 (Name of invention: 　 Cold storage heat exchanger)

The present invention was conceived to solve the above-described problems, and an object of the present invention is that of the tubes arranged in three rows, a regenerator material is stored in a second row tube, and flows in the first row and third row tubes. As the cooling fluids are formed to be movable with each other, it effectively stores the cool air of the cooling fluid and releases cool air when the engine is stopped, preventing a sudden temperature increase in the interior of the vehicle, thereby improving the user's cooling comfort and re-cooling. It is to provide a heat storage heat exchanger that can minimize the energy and time consumed during the period.

In addition, an object of the present invention is to provide a storage cooling heat exchanger capable of improving both heat dissipation performance and storage cooling performance by optimizing the areas of the first space part, the second space part, and the third space part in the header tank of the storage cooling heat exchanger. .

The storage cooling heat exchanger according to the embodiment of the present invention is arranged in three rows in the width direction, the cooling fluid is circulated in the first and third row tubes 130, and a plurality of coolant storage materials are stored in the second row tube 120. Dog tubes 100; A first space part 231 and a second row tube 120 are fixed to both ends in the length direction of the tube 100 and are separated into three spaces in the width direction, and communicate with the first row tube 110. ) And a second space part 232 communicating with and a third space part 233 communicating with the third row tube 130, and an upper header tank to which the header 210 and the tank 220 are coupled ( 201) and a lower header tank 202; Two header-side bulkheads 310 that are provided inside the upper header tank 201 and the lower header tank 201 to separate the space, surround the second row tube 120 and extend toward the tank 220 ), the header-side bulkhead part 310 meets at a certain point and extends in the same direction so that the other end thereof is fixed to any one point of the tank 220, and the bulkhead part 300 includes a tank-side bulkhead part 320 ; And an inlet 410 through which the cooling fluid is introduced and an outlet 420 formed in the first space 231 or the third space 233. Including, wherein the second row tube 120 is inserted into the header 210 for a predetermined length, and the two header-side partition walls 310 are bent at the ends of the second row tube 120, In the tank 220, it is characterized in that it meets one end of the tank-side bulkhead 320 having a predetermined length in the direction toward the header 210.

In this case, the area of the first space part 231, the second space part 232, and the third space part 233 is a tube insertion length into which the second row tube 120 is inserted into the header 210 It may be determined by (A), the length (B) of the tank-side partition part 320 and the width (C) of the first row tube 110 and the second row tube 120.

In addition, the first row tube 110 and the second row tube 120 may have the same shape.

In addition, it is preferable that the ratio of the area occupied by the first space part 231 and the third space part 233 among the total cross-sectional area of the header tank 201 is 0.75 to 0.88.

In addition, the ratio of the tube insertion length (A) to the height of the header tank 200 is 0.38 to 0.51, and the length (B) of the tank-side bulkhead portion 320 relative to the height of the header tank 200 is 0.45 To 0.57, and the width C of the first row tube 110 and the third row tube 130 relative to the width of the header tank 200 is preferably 0.25 to 0.33, respectively.

Accordingly, in the regenerator heat exchanger according to the embodiment of the present invention, the regenerator material is stored in the center tube, thereby effectively storing cool air of the refrigerant, and releasing cool air when the engine is stopped to prevent a sudden temperature increase in the vehicle interior. By maintaining the air constant, the user's cooling comfort can be improved, and energy and time consumed during re-cooling can be minimized.

In addition, by optimizing the areas of the first, second, and third spaces in the header tank of the regenerator heat exchanger through the present invention, it is possible to stably provide a storage cooling heat exchanger capable of improving both heat dissipation performance and storage cooling performance. I can.

1 is a cross-sectional view showing a conventional double-tube heat storage heat exchanger.
2 is a perspective view showing a conventional three-row heat storage heat exchanger.
3 is a perspective view of the heat storage heat exchanger according to the present invention.
4 is a cross-sectional view of an upper header tank according to the present invention.
5 is a graph showing heat dissipation performance, fast-acting performance, and storage cooling performance according to the area ratio.

Hereinafter, a heat storage heat exchanger according to an embodiment of the present invention as described above will be described in detail with reference to the accompanying drawings.

As shown in FIG. 3, the heat storage heat exchanger 1 according to the present invention comprises a plurality of tubes 100, an upper header tank 201, a lower header tank 202, a partition wall portion 300, and an inlet 410. ), is formed including an outlet 420.

First, the tubes 100 are arranged in three rows in the width direction, the cooling fluid is circulated in the first row tube 110 and the third row tube 130, and the cold storage material is stored in the second row tube 100. .

At this time, the tube 100 is formed so that the three rows of tubes 100 are connected to each other, and can be simultaneously manufactured through an extrusion process. In this case, there is an advantage in that manufacturing is simple and assembly is easy.

In the heat storage heat exchanger 1, fins may be further interposed between adjacent tubes 100, and fins interposed between the tubes 100 arranged in three rows are integrally formed so that the cooling fluid flows. Heat exchange between the first row tube 110 and the third row tube 130 and the second row tube 120 in which the cool storage material is stored may be performed through the fins.

In addition, the tube 100 has the same width as the first row tube 110, the second row tube 120, and the third row tube 130, or the second row tube 120 is formed to be thinner. Although it may be, the width or width of the second row tube 120 may be formed to be thicker so that the storage space for the storage coolant in the second row tube 120 is sufficiently secured, and within the second row tube 120 The number of partition walls formed to improve pressure resistance may be formed to be less than that of the first row tube 110 and the third row tube 130.

to the next. 3 and 4, the upper header tank 201 and the lower header tank 202 are fixed at both ends in the length direction of the tube 100, and the space is separated into three in the width direction, A first space part 231 communicating with the first row tube 110, a second space part 232 communicating with the second row tube 120, and a third space communicating with the third row tube 130 It consists of a portion 233 and is formed by a combination of the header 210 and the tank 220.

The header 210 and the tank 220 are each formed by a press process and brazed to each other to form one upper header tank 201 or a lower header tank 202.

In the upper header tank 201 and the lower header tank 202, a partition wall part 300 is further provided to separate the first space part 231, the second space part 232, and the third space part 233. It is equipped.

The partition wall part 300 may be largely composed of two header-side bulkhead parts 310 and a tank-side bulkhead part 320, wherein the header-side bulkhead part 310 is inserted into a second row of tubes of the header 210 One end is fixed between the hole 212 and the first row tube insertion hole 211, the second row tube insertion hole 212 and the third row tube insertion hole 213, and the second row tube 120 It surrounds and extends in the direction of the tank 220.

The tank-side bulkhead part 320 is extended in the same direction as the header-side bulkhead part 310 meets at a certain point, and the other end is fixed to any one point of the tank 220.

At this time, the second row tube 120 is inserted into the header 210 for a predetermined length, and the two header-side partition walls 310 are bent at the ends of the second row tube 120, so that the tank At 220, it encounters one end of the tank-side bulkhead 320 having a predetermined length in the direction toward the header 210.

As shown in FIG. 4, the first space part 231 and the third space part 233 communicate with the first row tube 110 and the third row tube 130, respectively, and are spaces in which the cooling fluid moves. .

When the storage cooling heat exchanger serves as an evaporator, in order to improve the heat dissipation performance of the storage cooling heat exchanger, the amount of cooling fluid can be increased, and the heat transfer area can be increased so that heat exchange is well performed from the cooling fluid to air or a storage material. The sizes of the first and third spaces 231 and 233 may be increased.

The second space part 232 communicates with the second row tube 232 and is a space in which cool storage material is stored. In order to improve the storage cooling performance of the storage cooling heat exchanger, it is necessary to increase the amount of the storage cooling material stored in the second space part 232 and the second heat tube 120, and for this purpose, the second space part 232 You can increase the size of.

The storage space for the heat storage heat exchanger is limited, and in particular, spaces for the upper header tank 201 and the lower header tank 202 are also limited. Therefore, there is a limit to uniformly increasing the size of the first space part 231 to the third space part 233 of the header tank for the heat dissipation performance and storage cooling performance of the heat storage heat exchanger, so that the heat dissipation performance and the storage cooling performance are simultaneously maximized. It is possible to optimize the size of the first space part 231 to the third space part 233 so as to be pulled up.

The sizes of the first space part 231, the second space part 232, and the third space part 233 may be represented by a cross-sectional area perpendicular to the width direction, as shown in FIG. The tube insertion length (A) into which the column tube 120 is inserted into the header 210, the length (B) of the tank-side partition part 320, and the first column tube 110 and the third row It may be determined by the width (C) of the tube 130.

In this case, like the second row tube 120, the first row tube 110 and the third row tube 130 may be inserted into the header 210. In addition, the first row tube 110 and the third row tube 130 may have the same shape.

5 is a ratio of the cross-sectional areas of the first and third spaces 231 to 233 to the total cross-sectional area of the first to third spaces 231 (hereinafter referred to as'area ratio'). It is a graph showing the heat dissipation performance, fast-acting performance, and storage cooling performance of the regenerated cooling heat exchanger according to). The ratio can also be seen as representing the ratio of the cooling fluid and the storage material in the storage cooling heat exchanger.

As shown in FIG. 5, it can be seen that the greater the area ratio, the higher the heat dissipation performance. This is because as the area ratio increases, the sizes of the first heat tube 110 and the third heat tube 130 through which the cooling fluid circulates increases, and the heat exchange area between the cooling fluid and external air increases.

On the other hand, the fast-acting performance can be expressed as the time it takes for the cold storage material at room temperature to decrease to a certain temperature, and in FIG. 5, the fast-acting performance is expressed as a ratio of the time it takes to decrease to a certain temperature. As shown in FIG. 5, it can be seen that as the area ratio increases, the time taken for the cold storage material to be lowered to a certain temperature decreases, thereby increasing the fast-acting performance. This is because the larger the area ratio, the larger the amount of cooling fluid and the higher the heat dissipation performance.

On the other hand, the storage cooling performance can be expressed as the duration for cooling the air passing through the storage cooling heat exchanger using cold air stored in the storage cooling material, not the cooling fluid, and in FIG. 5, the storage cooling performance is the ratio of the duration for cooling the air. Represented by As shown in Fig. 5, it can be seen that as the area ratio increases, the duration for cooling the air by the regenerator increases, so that the storage cooling performance increases, and the area ratio exceeds 0.83, and the storage cooling performance decreases. This is because the larger the area ratio, the less the amount of cold storage material.

Taken together, as shown in FIG. 5, it is preferable that the area ratio is 0.75 to 0.88 so that not only the heat dissipation performance of the heat storage heat exchanger but also the quick-acting performance and the storage cooling performance are all close to the maximum value. If the area ratio is less than 0.75, the size of the first heat tube 110 and the third heat tube 130 through which the cooling fluid of the regenerator heat exchanger circulates is small, and the heat exchange area is small, so that the heat dissipation performance is low. Accordingly, since the cooling storage material cannot be sufficiently cooled, the storage cooling performance and the fast-acting performance are significantly lowered, and the overall performance of the storage cooling heat exchanger is lowered. In addition, when the area ratio is more than 0.88, the size of the second heat tube 120 in which the regenerator is stored is reduced, and the amount of the stored refrigerant is small, so that the refrigeration performance is significantly lowered. Therefore, when the area ratio is 0.75 to 0.88, it is possible to stably provide a heat storage heat exchanger having excellent heat dissipation performance, quick-acting performance, and storage cooling performance.

In the experimental example of the present invention, the width of the upper header tank 201 is 45.4mm and the height is 15.7mm. When the area ratio is 0.75, the tube insertion length (A) into which the second row tube 120 is inserted into the header 210 is 8 mm, and the length (B) of the tank-side bulkhead 320 is 7 mm. , The first row tube 110 and the second row tube 120 have a width C of 11.5 mm, respectively. In addition, when the area ratio is 0.88, the tube insertion length (A) into which the second row tube 120 is inserted into the header 210 is 6 mm, and the length (B) of the tank-side bulkhead 320 is 9mm, and the width C of the first row tube 110 and the second row tube 120 is 15mm, respectively. Accordingly, the ratio of the tube insertion length (A) to the height of the header tank 200 is 0.38 to 0.51 so as to correspond to the area ratio of 0.75 to 0.88, The length (B) of (320) is 0.45 to 0.57, and the width (C) of the first row tube 110 and the third row tube 130 compared to the width of the header tank 200 is 0.25 to 0.33, respectively It is preferable to be.

In this way, by optimizing the areas of the first, second, and third spaces in the header tank of the heat storage heat exchanger, it is possible to stably provide a storage cooling heat exchanger capable of improving both heat dissipation performance and storage cooling performance.

The present invention is not limited to the above-described embodiments, and the scope of application thereof is diverse, as well as anyone with ordinary knowledge in the field to which the present invention belongs without departing from the gist of the present invention claimed in the claims. Of course, various modifications are possible.

1: heat storage heat exchanger
100: tube
110, 120, 130: first to third row tubes
201, 202: upper header tank, lower header tank
210: header
211, 212, 213: 1st to 3rd row tube insertion holes
214: projection insertion groove
220: tank
231, 232, 233: first space part, second space part, third space part
300: bulkhead
310: header side bulkhead part 320: tank side bulkhead part
340: communication hall
410, 420: inlet, outlet

Claims (5)

A plurality of tubes 100 arranged in three rows in the width direction, in which cooling fluid is circulated in the first row and third row tubes 130, and the coolant storage material is stored in the second row tube 120;
A first space part 231 and a second row tube 120 are fixed to both ends in the length direction of the tube 100 and are separated into three spaces in the width direction, and communicate with the first row tube 110. ) And a second space part 232 communicating with and a third space part 233 communicating with the third row tube 130, and an upper header tank to which the header 210 and the tank 220 are coupled ( 201) and a lower header tank 202;
Two header-side bulkhead portions 310 that are provided inside the upper header tank 201 and the lower header tank 202 to separate the space, surround the second row tube 120 and extend toward the tank 220 ), the header-side bulkhead part 310 meets at a certain point and extends in the same direction so that the other end is fixed to any one point of the tank 220, and the bulkhead part 300 includes ; And
An inlet 410 through which the cooling fluid is introduced and an outlet 420 formed in the first space 231 or the third space 233; Including,
The second row tube 120 is inserted into the header 210 for a predetermined length,
The two header-side partitions 310 are bent at the ends of the second row tube 120 to have a predetermined length from the tank 220 toward the header 210. ), characterized in that it meets one end of the heat storage heat exchanger.
The method of claim 1,
The first space part 231, the second space part 232, and the third space part 233 have an area of a tube insertion length (A) into which the second row tube 120 is inserted into the header 210 ), and the length (B) of the tank-side bulkhead portion 320, and the width (C) of the first row tube 110 and the second row tube 120. .
The method of claim 2,
The heat storage heat exchanger, characterized in that the first heat tube 110 and the second heat tube 120 have the same shape.
The method of claim 3,
Heat storage heat exchange, characterized in that the ratio of the area occupied by the first space 231 and the third space 233 among the total cross-sectional areas of the upper header tank 201 or the lower header tank 202 is 0.75 to 0.88 group.
The method of claim 3,
The ratio of the tube insertion length (A) to the height of the upper header tank 201 or the lower header tank 202 is 0.38 to 0.51,
The length (B) of the bulkhead portion 320 on the tank side compared to the height of the upper header tank 201 or the lower header tank 202 is 0.45 to 0.57,
Cold storage, characterized in that the width (C) of the first row tube 110 and the third row tube 130 compared to the width of the upper header tank 201 or the lower header tank 202 is 0.25 to 0.33, respectively heat exchanger.

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