DE112021004879T5 - HEAT EXCHANGER WITH MEANS FOR REDUCING THERMAL LOAD OR. TENSION - Google Patents

Abstract

The present invention relates to a heat exchanger having a thermal stress reducing means. An object of the present invention is to provide an integrated heat exchanger configured to cool two types of heat exchange media having different temperatures, the heat exchanger having a means of reducing thermal stress and a flow distribution structure in a vessel for effective distribution the thermal load or stress caused by the temperature difference.

Description

[Technical Field]

The present invention relates to a heat exchanger, and more particularly to an integrated heat exchanger configured to cool two types of heat exchange media having different temperatures, i.e., a heat exchanger with a thermal stress reducing agent capable of effectively resolving thermal stress caused by a temperature difference.

[Technical background]

In general, in an engine room of the vehicle, not only components such as a motor for running a vehicle are provided, but also various heat exchangers such as a radiator, an intercooler, an evaporator, and a condenser for cooling the components such as a condenser are provided. B. the engine in the vehicle or for setting an air temperature in an interior of the vehicle in the engine compartment of the vehicle. Heat exchange media generally flow in the heat exchangers. The heat exchange medium in the heat exchanger exchanges heat with outside air existing outside the heat exchanger so that the cooling operation or heat dissipation is performed.

In most cases, a single type of heat exchange medium flows in the heat exchanger. However, if necessary, heat exchangers in which two types of heat exchange media flow are sometimes integrated. For example, in the case of a radiator and an oil cooler of the vehicle, a coolant for cooling the engine flows in the radiator, and oil such as engine oil or transmission oil flows in the oil cooler. Of course, the radiator and oil cooler are sometimes configured as separate devices. However, in order to improve the space utilization of the engine room, the radiator and the oil cooler are often integrated as one structure, such as a water-cooled oil cooler structure configured to cool oil using a coolant.

A portion of the heat exchanger where heat exchange is mainly performed is a portion where tubes are juxtaposed, and this portion is generally called a core of the heat exchanger. In the prior art, the integrated heat exchanger in which two kinds of heat exchange media flow often has a structure in which cores in which the heat exchange media flow are arranged in series. However, structures in which the cores are connected in parallel have sometimes been used recently. 1 12 illustrates an example of a prior art integrated heat exchanger having a structure in which cores in which two kinds of heat exchange media flow are connected in parallel. With the integrated heat exchanger according to FIG. is the structure in which the two cores are connected in parallel, similar to a structure of a heat exchanger in which a single kind of heat exchange medium flows. More specifically, the heat exchangers are arranged in two rows, and a separator is provided in a header tank to isolate the heat exchange media. A configuration of a double row heat exchanger is disclosed in Korean Patent No. 0825709 ("HEAT EXCHANGER," April 22, 2008).

Specifically, a heat exchanger 100 comprises: a pair of header tanks 100 spaced a predetermined distance from each other and provided side by side; and a plurality of tubes 200 each having two opposite ends fixed to the header tanks 100 and configured to define flow paths for a heat exchange medium and additionally including a plurality of fins disposed between the tubes 200. In this case, the tubes 200 are provided in two rows in the front/rear direction. The header tanks 100 each include a partition wall 125 extending in a longitudinal direction in the header tank to partition a space communicating with the respective tubes. Therefore, first and second heat exchange media respectively flowing in the tubes 200 arranged in first and second rows can be separated and flow without impinging on each other. Of course, an inlet port and an outlet port that are paired are separately provided for each of the heat exchange media in the header tank 100 . 1 11 illustrates that first and second inlet ports and first and second outlet ports are provided in the header tanks in opposite directions in the form of a cross flow in which the heat exchange media flow in one direction. However, in the case of U-flow in which the heat exchange media flows in a U-shape, the first and second inlet ports and the first and second outlet ports may be provided in the same direction in the header tanks.

In the integrated heat exchanger provided as described above, two types of heat exchange media that differ in properties, such as a coolant and oil, or two types of heat exchange media that differ in temperature ranges, such as a low-temperature coolant and a high-temperature coolant, can flow so that the integrated heat exchanger in different ways is operated. In any case, since the heat exchange media have very different temperature ranges, there will be a significant temperature difference between the front and rear cores if the two types of heat exchange media flow. When a temperature distribution is unbalanced as described above, a degree of thermal deformation varies depending on each position. For this reason, there is a problem that thermal stresses (the terms are used alternatively herein with the same meaning) are concentrated at a certain point of the heat exchanger. In the case of the integrated heat exchanger mentioned above, the thermal stress concentration is highest at a portion where the front and rear cores are separated. Since the thermal stress concentration caused by thermal deformation is a major factor causing damage or breakage of the heat exchanger, there is a need for a configuration that copes with the thermal stress concentration.

[Related Art Document]

[patent document]

1. Korean Patent No. 0825709 ("HEAT EXCHANGER," April 22, 2008)

[Epiphany]

[Technical Task]

Therefore, the present invention has been made in an effort to solve the above-mentioned problems in the prior art, and an object of the present invention is to provide an integrated heat exchanger configured to cool two types of heat exchange media having different temperatures. i.e., a heat exchanger with thermal stress reducing means capable of effectively dissipating thermal stress caused by a temperature difference.

[Technical solution]

In order to achieve the above-mentioned object, a heat exchanger 1000 according to the present invention comprises: a pair of header tanks 100 each having a fluid flow space inside, which is defined by coupling a header 110 and a tank 120, the pair of header tanks being spaced a predetermined distance apart and provided side by side; and a plurality of tubes 200 each having two opposite ends fixed to the header tank 100 and configured to define flow paths for heat exchange media, the plurality of tubes being arranged in two rows in a front/rear direction, wherein an interior space of the header tank 100 is isolated and divided into front and rear heat exchange parts by a partition wall 125, wherein the heat exchange media having different average temperatures flow in the front and rear heat exchange parts, respectively, and the partition wall 125 has a means of reducing thermal stresses.

In an embodiment of the device for reducing thermal stress, the means for reducing thermal stress may be a flow distribution structure formed on the tank 120 in an area near the partition wall next to the partition wall 125, which is a boundary line between the front and rear heat exchanger parts, and the flow distribution structure may be formed such that a flow rate of the heat exchange medium flowing in the inner space of the tube 200 in the area near the partition wall is relatively lower than a flow rate of the heat exchange medium flowing in the inner space of the tube 200 in the remaining area.

In this case, the flow distribution structure may be a flow rate adjustment orifice 121 having one end fixed to an inner surface of the tank 120 and the other end arranged so as to be spaced from the inner space of the tube 200 at the flow rate, the flow rate adjustment orifice being formed to reduce a flow rate of the heat exchange medium flowing in the inner space of the tube 200 in the area near the partition wall.

Alternatively, the flow distribution structure may be a flow rate adjustment rib 122 formed as part of the tank 120 and protruding toward an inside of the header tank 100 with an end of a protruding portion arranged to be spaced from the interior of the tube 200, and the flow rate adjustment rib may be formed to reduce a flow rate of the heat exchange medium flowing in the interior of the tube 200 in the area near the partition wall t.

In addition, the flow distribution structure may be formed in one of the front and rear heat exchange parts where a temperature of the heat exchange medium is relatively high. More specifically, in the heat exchanger 1000, a temperature of the heat exchange medium flowing in the rear heat exchange part may be higher than a temperature of the heat exchange medium flowing in the front heat exchange part, and the heat exchange flow distribution structure may be formed in the rear heat exchange part.

In addition, the flow distribution structure can be applied to all positions of the tubes 200 .

Also, the flow distribution structure may be formed to be spaced only from a position opposite to a position of the tube 200 .

The flow distribution structure can be formed to correspond to a range of 10 to 20% of a width of the tube 200 .

In another embodiment of the thermal stress reducing means, the thermal stress reducing means may be an air pocket 123 formed in the partition wall 125 in the form of an empty space.

In this case, the air pocket 123 can extend in an extending direction of the partition wall 125 .

In addition, the air pocket 123 may be formed so that it is opened at an end directed toward the collector 120 .

In this case, an opened portion of the air pocket 123 can be sealed by a packing 150 provided at a portion where the collector 110 and the tank 120 are coupled.

In addition, in this case, the seal 150 may have a seal projection 151 protruding at a position corresponding to the opened portion of the air pocket 123 .

In addition, the heat exchanger 1000 may have a leak check path 124 formed in the tank 120 and provided in the form of a flow path that allows the air pocket 123 to communicate with the outside.

In addition, the heat exchanger 1000 may be a radiator in which a high-temperature coolant and a low-temperature coolant flow.

[Beneficial Effects]

According to the present invention, in the integrated heat exchanger configured to cool two types of heat exchange media with different temperatures, the flow distribution structure is provided in the tank or the air pocket is formed in the partition wall in the tank, which makes it possible to effectively relieve thermal stress caused by a temperature difference. More specifically, in the heat exchanger of the present invention, the cores of the heat exchanger include the front and rear cores to cool the two types of heat exchange media, and it is known that the thermal stress concentration is highest at the boundary portion between the front and rear cores. In this case, in one embodiment of the present invention, the concentration of thermal stress is alleviated by providing a structure in which the flow rate is reduced by partially blocking the end of the tube at the boundary portion where the tubes are juxtaposed. In particular, in the present invention, flow distribution is implemented by the orifice or inwardly projecting vessel structure formed adjacent to the partition formed in the vessel. Alternatively, as another embodiment, the air pocket is formed in the partition wall so that thermal insulation is effectively implemented between the front and back.

Since the flow distribution structure is provided as described above, a temperature gradient is more gently defined at the boundary portion during the process in which the heat exchange media having different temperature ranges flow in the front and rear cores, making it possible to solve the temperature imbalance problem. Of course, the thermal stress can be effectively dispersed, ultimately preventing the problem of damage and connection breakage between the header and the pipe.

character list

• 1 Fig. 12 is a view showing an example of a prior art integrated heat exchanger.
• 2 12 is a perspective view of a first embodiment of a tank structure of an integrated heat exchanger of the present invention.
• 3 Fig. 12 is a cross-sectional view of the first embodiment of the tank structure of an integrated heat exchanger of the present invention.
• 4 12 is a perspective view of a second embodiment of the tank structure of an integrated heat exchanger of the present invention.
• 5 Fig. 12 is a cross-sectional view of the second embodiment of the tank structure of an integrated heat exchanger of the present invention.
• 6 Figure 12 is an illustration of examples of temperature gradients in the prior art and in the present invention.
• 7 Fig. 12 is a graph for comparing temperature gradients between the prior art and the present invention.
• 8th 14 is a view illustrating deformation of an orifice caused when a temperature difference between heat exchange media on two sides of the integrated heat exchanger is large.
• 9 Fig. 12 is a cross-sectional view of a third embodiment of the tank structure of an integrated heat exchanger of the present invention.
• 10 Fig. 14 is a cross-sectional view of a fourth embodiment of the tank structure of an integrated heat exchanger of the present invention.

[Mode of carrying out the invention]

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

The heat exchanger described according to the present invention is an integrated heat exchanger configured so that various types of heat exchange media having different temperatures flow independently, particularly a heat exchanger in which tubes are arranged in two front and rear rows, and cores, that is, heat exchange parts where heat exchange mainly takes place, are doubled in front and back. In particular, as briefly referring to 1 , a heat exchanger 1000 may include: a pair of header tanks 100 each having inside a fluid flow space defined by coupling a header 110 and a tank 120, the pair of header tanks 100 being spaced a predetermined distance from each other and provided side by side; and a plurality of tubes 200 each having two opposite ends fixed to the header tanks 100 and arranged in two rows in a front/rear direction while defining flow paths for heat exchange media. Furthermore, the heat exchanger 1000 may also include a plurality of fins disposed between the tubes 200 .

In this case, in the heat exchanger 1000, an interior of the header tank 100 is partitioned and insulated by a partition wall 125 in the front/rear direction, so that the heat exchange media with different average temperatures flow in the front and rear heat exchange parts, respectively. That is, the heat exchanger has a shape similar to a general double-row heat exchanger. Since the partition wall 125 completely insulates the front heat exchange part and the rear heat exchange part, the different heat exchange media can flow into the front heat exchange part and the rear heat exchange part independently of each other. For example, a radiator or the like in which high-temperature refrigerant and low-temperature refrigerant flows are used can be used as the heat exchanger configured so that different types of heat exchange media having different average temperatures for respective areas flow. In this case, the high-temperature coolant may serve to remove heat from an engine while flowing through a coolant circuit that includes the engine. The low temperature coolant may serve to cool electrical components at a relatively low temperature while flowing through a coolant circuit that includes the electrical components.

In the heat exchanger described above, the degree of thermal expansion naturally differs between a portion where a high-temperature heat exchange medium flows and a portion where a low-temperature heat exchange medium flows. It is not a big problem if the degrees of thermal expansion are equal in all the components of the heat exchanger in the state where the components of the heat exchanger are firmly fixed to each other by welding. However, if the portions having greatly different degrees of thermal expansion are formed locally, the thermal stress is naturally and excessively concentrated at the corresponding portions, causing damage. In the case of the heat exchanger 1000 of the present invention, a portion near the partition wall 125, which is a boundary line between the front and rear heat exchanger parts, is the portion where thermal stress is most concentrated.

The present invention is intended to reduce thermal stress concentration at this portion. Since temperature range conditions of the heat exchange media flowing in the front and rear heat exchange parts respectively cannot be changed, it is impossible to eliminate a phenomenon in which thermal stress is concentrated. However, it is to be expected that the thermal stress con centering can be further reduced if a degree to which the temperature range before and after the boundary line is rapidly changed is further weakened, that is, if the temperature range near the boundary line is changed more gently.

That is, in the present invention, the partition wall 125 has a thermal stress reducing means, thereby solving the above-mentioned problem. In this case, in one embodiment, the means for reducing thermal stresses may be a flow distribution structure. In another embodiment, the thermal stress reducing means may be an air pocket. The flow distribution structure and the air pocket are described in more detail below.

[1] An embodiment of a means for reducing thermal stress: flow distribution structure

As an embodiment of the means for reducing thermal stress, in the present invention, the flow distribution structure is formed on the tank 120 in an area near the partition wall adjacent to the partition wall 125, which is the boundary line between the front and rear heat exchange parts, thereby reducing the flow rates of the heat exchange media. More specifically, a flow rate of the heat exchange medium that flows in an inner space of the tube 200 in the area near the partition wall is relatively lower than a flow rate of the heat exchange medium that flows in the inner space of the tube 200 in the remaining area. With the configuration mentioned above, the amount of heat exchange medium present in the area near the partition wall can be reduced, so that a temperature gradient is changed more gently, and as a result, thermal stress concentration can be further alleviated. That is, the flow distribution structure serves as a means of reducing thermal stresses.

The 2 Fig. 13 is a perspective view of a first embodiment of a tank structure of an integrated heat exchanger of the present invention, and Figs 3 Fig. 12 is a cross-sectional view of the first embodiment of the tank structure of an integrated heat exchanger of the present invention. (For reference, to implement the sealability, a general gasket is further provided at a portion where the header 110 and the tank 120 are coupled. However, to simplify the drawings, the gasket is omitted from the perspective view in FIG 2 omitted, and a seal 150 is in 3 shown.) In the first embodiment, the flow distribution structure is configured as a flow rate adjustment orifice 121, which has one end fixed to an inner surface of the container 120 and the other end is spaced from the interior of the tube 200, the flow rate adjustment orifice 121 is configured to reduce the flow rate of the heat exchange medium flowing in the interior of the tube 200 in the area near the partition wall. As in 3 1, the other end of the flow rate adjusting orifice 121 is illustrated as being spaced upwards from an end of the tube 200 by a predetermined distance and covering an opening portion of a part of the end of the tube 200, but the present invention is not limited thereto. For example, the other end of the flow rate adjustment orifice 121 may extend to the interior of the tube 200 . In this case, an outer diameter of the other end of the flow rate adjustment orifice 121 can be slightly smaller than an inner diameter of the tube 200. That is, in this case, the other end of the flow rate adjustment orifice 121 is fitted into the inner space of the tube 200 while defining a small gap. Therefore, it is possible to reduce the flow rate by reducing the area of the flow path. Meanwhile, the flow rate adjustment orifice 121 is a structure attached to the tank 120, and can be integrated with the tank 120 by being manufactured using a single mold. As in 3 1, one end of the flow rate adjusting orifice 121 may be extended and connected to a ceiling of the inner surface of the tank 120, considering ease of manufacture.

The 4 Fig. 12 is a perspective view of a second embodiment of the tank structure of an integrated heat exchanger of the present invention, and Figs 5 Fig. 12 is a cross-sectional view of the second embodiment of the tank structure of an integrated heat exchanger of the present invention. (Also in this case the seal is as in the 2 , 3 and 4 omitted, and the seal 150 is in 5 shown.) In the second embodiment, the flow distribution structure is configured as a flow rate adjustment rib 122, which is formed as part of the tank 120 and protrudes to the inside of the header tank 100, and one end of the protruding portion is arranged so that it is spaced from the interior of the pipe 200. The flow rate adjustment rib 122 is formed to reduce the flow rate of the heat exchange medium flowing in the interior of the tube 200 in the vicinity of the partition wall. Unlike the first embodiment in which the flow rate adjustment orifice 121 is configured as a separate member and mounted on the tank 120, the flow rate adjustment rib 122 can be attached to the tank as shown 120 be integrated. Like the flow rate adjustment orifice 121, the flow rate adjustment rib 122 is formed to cover the opening portion of a part of the end of the tube 200, thereby reducing the flow rate of the heat exchange medium flowing into the inner space of the tube 200.

The flow distribution structure may be formed at one of the front and rear heat exchange parts where a temperature of the heat exchange medium is relatively high. This is because a degree of thermal expansion increases as a temperature of the heat exchange medium increases, and the amount of thermal stress concentration increases. The drawings illustrate that a temperature of the heat exchange medium flowing in the rear heat exchange part is higher than a temperature of the heat exchange medium flowing in the front heat exchange part, and the flow distribution structure is formed in the rear heat exchange part. It is assumed herein that the direction in which outside air is blown in is defined as the forward direction and the direction in which outside air is blown out is defined as the backward direction. If the heat exchange medium having a higher temperature flows into the front heat exchange part, the air that has flowed through the front heat exchange part has already received an excessively large amount of heat. For this reason, the air in the rear heat exchanger cannot sufficiently absorb heat, which may raise a concern that the heat exchange performance in the rear heat exchanger deteriorates. Considering the above-mentioned situation, the heat exchange medium having a higher temperature generally flows in the rear heat exchange part in the heat exchanger in which the heat exchange parts are arranged in parallel in the forward/backward direction. That is, according to a general design trend, the flow distribution structure may be formed in the rear heat exchanger part.

Meanwhile, in the present invention, since the thermal stress concentration occurs over the entire front and rear heat exchanger parts, the flow distribution structure can be applied to all positions of the tube 200 . In addition, the flow distribution structure can be formed to be only spaced from the position opposite to the position of the tube 200 to prevent the flow distribution structure from occupying the internal space of the header tank 100 excessively.

In addition, the flow distribution structure may be formed so that the degrees to which the flow of the heat exchange medium is reduced at the positions of the tubes 200 are equal to each other. That is, the degrees of coverage of the ends of the tubes 200 are the same with respect to all the tubes 200 . However, the present invention is not necessarily limited to this. This configuration will be described in detail. In the heat exchange part, a temperature is lowered during a process in which the high-temperature heat exchange medium is introduced into an intake port and exchanges heat with outside air while flowing through the heat exchange part. The heat exchange medium having a temperature that has become a low temperature as described above is discharged to a discharge port. That is, even in the single heat exchange part, a temperature of the heat exchange medium at the inlet port is relatively high and a temperature of the heat exchange medium at the outlet port is relatively low. In this case, it is assumed that the high-temperature heat-exchanging part in which the high-temperature heat-exchanging medium with a high average temperature flows and the low-temperature heat-exchanging part in which the low-temperature heat-exchanging medium with a low average temperature flows are arranged in parallel. According to the principle mentioned above, in each of the high-temperature heat exchanging part and the low-temperature heat exchanging part, a temperature at the inlet port is highest and a temperature at the outlet port is lowest. In this case, if an outlet port side of the high-temperature heat exchange part (a portion where the temperature in the high-temperature heat exchange part is lowest) and an inlet port side of the low-temperature heat exchange part (a section where a temperature in the low-temperature heat exchange part is highest) are arranged adjacent to each other, a large temperature difference between the high-temperature heat exchange part and the low-temperature heat exchange part on the above sides will not occur. Meanwhile, in the above-mentioned configuration, on the opposite side, an inlet port side of the high-temperature heat exchange part (a portion where a temperature in the high-temperature heat exchange part is highest) and a discharge port side of the low-temperature heat exchange part (a section where a temperature in the low-temperature heat exchange part is lowest) are arranged adjacent to each other. In this case, the largest temperature difference can occur. In this case, the construction can be made so that it is possible to further reduce the flow rate of the heat exchange medium by increasing a degree to which the tube is covered at the portion where a temperature difference is large, and it is possible to reduce the flow rate of the heat exchange medium less by reducing a degree to which the tube is covered at the portion where a temperature difference is small. That is, as described above, the flow distribution structure may be formed so that the degrees to which the flow of the heat exchange medium is reduced at the positions of the tubes 200 are different from each other.

The 6 Figure 12 illustrates examples of temperature gradients according to the prior art and according to the present invention. As the relationship has been described above with reference to the arrangement of the heat exchanger parts according to the temperatures in the conventional double row heat exchanger, in the embodiment in FIG 6 shown that a temperature of the heat exchange medium flowing in the rear heat exchange part is higher than a temperature of the heat exchange medium flowing in the front heat exchange part. That is, a rear tube temperature is higher than a front tube temperature. As shown in the RELATED ART view on the left, there is a significantly large temperature difference between the front and back in the area near the bulkhead. Meanwhile, as shown in the right side view of "PRESENT INVENTION", it can be seen that a temperature difference spectrum between the front and back is widely distributed in the area near the partition wall, that is, a temperature is changed more smoothly compared to "RELATED ART".

7 FIG. 12 is a graph for comparing temperature gradients between the prior art and the present invention, ie, a graph showing the result of FIG 6 represents. The RELATED ART graph is indicated by the dotted line and the PRESENT INVENTION graph is indicated by the solid line. As in 7 As shown, in the case of "RELATED ART" in which no flow distribution structure is provided, there is a portion where a temperature gradient is sharply curved. In contrast, in the case of "PRESENT INVENTION" in which the flow distribution structure is provided, it can be seen that the portion that is largely curved in "RELATED ART" has a significantly gradual shape. Since the temperature gradient is made smooth as described above, the degree of thermal expansion can also be changed smoothly. Thereby, the thermal stress concentration can be further alleviated and reduced compared to the prior art.

Meanwhile, the flow distribution structure consequently reduces the flow rate of the heat exchange medium by covering part of the tube and preventing the heat exchange medium from flowing well into the tube. If the flow distribution structure is excessively large, the flow distribution structure adversely affects the overall flow of the heat exchange medium, which may degrade the heat exchange performance. In view of this situation, it is not preferable that the flow distribution structure is excessively large. In contrast, in the case where the flow distribution structure is excessively small, the above-mentioned effect of alleviating the thermal stress concentration cannot be obtained. Considering the situations mentioned above, together with the aspect shown in the diagram in 7 As shown, the flow distribution structure may be formed to correspond to a range of 10 to 20% of a width of the tube 200.

[2] Another embodiment of the thermal stress reducing agent: air pocket

In the present invention described above, the flow distribution structure of the present invention is used when the heat exchange media flow at different temperatures in the two spaces of the header tank separated by the partition wall, making it possible to solve the problem that a temperature gradient changes rapidly at the periphery of the partition wall, and thermal stress concentration is caused by a rapid change in the degree of thermal expansion. In the prior art, it is impossible to excessively increase a temperature difference between the heat exchange media flowing in the two spaces of the header tank due to the problem of thermal stress concentration. However, it is possible to develop and further increase a temperature difference between the heat exchange media by adopting the present invention compared to the prior art.

In this case, however, the temperature difference between the parts with the partition wall interposed therebetween is excessively large, which may raise concerns that significant unnecessary and undesirable heat transfer occurs between the heat exchange media through the partition wall. In addition, if the temperature difference between the two opposite sides of the partition wall is excessively large, the degrees of thermal expansion at the two opposite sides of the partition wall may be significantly unbalanced. Meanwhile, in general, in the heat exchanger header tank, in addition to the partition wall extending in the longitudinal direction of the header tank, a baffle extending in a cross-sectional direction of the header tank is often provided extends to set a flow path for the heat exchange medium. However, if the degrees of thermal expansion on the two opposite sides of the partition wall in the double-row header tank are different, there is a concern that the screen, which is designed to suit an internal shape of the header tank, will be deformed or the screen and the tank will be separated. The 8th 12 is a view showing an example of a deformation of the iris caused when a temperature difference between the heat exchange media on the two opposite sides of the integrated heat exchanger is large. When a gap is formed between the orifice 130 and the tank 120, the heat exchange medium flows into an undesirable space, which may cause a problem that the intended heat exchange performance cannot be obtained.

A third embodiment is provided to avoid this problem, that is, the problem that in case the temperature difference between the two opposite sides of the partition wall 125 is too large, the baffle plate 130 is deformed and distorted by a difference in thermal expansion degree between two opposite surfaces. The 9 Fig. 12 is a cross-sectional view of the third embodiment of the tank structure of an integrated heat exchanger of the present invention. As illustrated, in the third embodiment, an air pocket 123 is formed in the form of an empty space in the partition wall 125 or on the partition wall 125 . As illustrated, the air pocket 123 may extend in a direction of extension of the bulkhead. The inside of the air pocket 123 is an empty space filled with air, which can effectively prevent unnecessary heat transfer through the partition wall 125 . That is, in the present embodiment, the air pocket 123 is the thermal stress reducing means.

In addition, the air bag 123 can be applied to the heat exchanger having the flow distribution structure described above. However, only the air bag 123 can be deployed without the flow distribution structure. In this case as well, a thermal insulating effect can further alleviate the thermal stress concentration in the vicinity of the boundary line between the front and rear surfaces. That is, the heat exchanger 1000 of the present invention can suitably selectively adopt either the flow distribution structure described in [1] or the air pocket described in [2] as a thermal stress reducing means.

However, the air pocket 123 may be provided in the partition wall 125 only in the form of an empty space. There is no problem in forming the shape of the air bag 123 in case the container 120 is made by extrusion. However, considering the concern that a failure rate increases as the shape complexity increases, the air pocket 123 may be opened at the end directed toward the container 120 as shown in FIG 9 is shown. Since the partition wall 125 and the end of the air pocket 123 facing the tank 120 are completely sealed by the gasket 150 anyway, the configuration in which the end of the air pocket 123 facing the tank 120 is opened does not adversely affect the function of the partition wall 125 (the function of isolating the forward/backward flow space of the heat exchange medium). That is, the opened portion of the air pocket 123 is sealed by the packing 150 . In this case, the seal 150 may have a seal projection 151 protruding at a position corresponding to the opened portion of the air bag 123 to better ensure the sealability of the opened portion of the air bag 123 . The sealing projection 151 can be inserted into the opened portion of the air bag 123, so that the air bag 123 can be securely sealed. Further, since the opened portion of the air pocket 123 naturally guides the sealing projection 151 during the insertion process, the sealing projection 151 also serves to prevent a situation where the sealing 150 deviates from an accurate position and is defective at the time of assembling the sealing 150 .

Meanwhile, the first embodiment of the in 2 and 3 shown flow distribution structure in 9 shown, but the present invention is not limited thereto. The air bag 123 of the third embodiment can be used in the second embodiment. Alternatively, of course, the air pocket 123 can be used in a heat exchanger in which the first and second embodiments are not used.

The 10 Fig. 14 is a cross-sectional view of a fourth embodiment of the tank structure of an integrated heat exchanger of the present invention. If the air pocket 123 is formed in the partition wall 125 as described above, a leak check route 124 can be formed in the container 120 and provided in the form of a flow path that allows the air pocket 123 to communicate with the outside. During a manufacturing process of the head tank 100, a leak test is necessarily performed by blowing air and checking whether a portion with a gap occurs during the assembling process, that is, whether there is a concern that leakage occurs later when the heat exchange medium flows. In general, the leak test was carried out on the front and rear compartments. That is, the leak test was necessarily performed twice in the prior art. However, in the case that the leak check path 124 is formed as described above, air is necessarily discharged to the leak check path 124 along the air pocket 123 when there is a gap between the partition wall 125 and the header 120 . Therefore, the leak test can be performed on the front and rear rooms at the same time. That is, because the leak inspection path 124 is formed, the number of leak inspection processes can be reduced from two to one, making it possible to improve productivity.

The present invention is not limited to the above embodiments, and the scope of application is diverse. Of course, various modifications and implementations can be made by anyone skilled in the art to which the present invention pertains without departing from the subject matter of the present invention as claimed.

Reference List

1000

heat exchanger

100

head tank

110

Head

120

container

121

flow distribution screen

122

flow distribution fin

123

air pocket

124

leak test track

125

partition wall

150

poetry

155

sealing protrusion

200

Pipe

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• KR 0825709 [0004, 0007]

Claims (16)

Heat exchanger, which includes: a pair of header tanks each having a fluid flow space therein defined by coupling a header and a tank, the pair of header tanks being spaced apart from each other by a predetermined distance and provided side by side; and a plurality of tubes each having two opposite ends fixed to the header tank and configured to define flow paths for heat exchange media, the plurality of tubes being arranged in two rows in a front/rear direction, wherein an inner space of the head tank is isolated and divided into front and rear heat exchanger parts by a partition wall, wherein the heat exchange media having different average temperatures flow in the front and rear heat exchanger parts, respectively, and wherein the dividing wall has a means for reducing thermal stresses. heat exchanger after claim 1 , wherein the means for reducing thermal stress is a flow distribution structure formed on the container in a region near the partition wall adjacent to the partition wall that is a boundary line between the front and rear heat exchanger parts and the flow, and the flow distribution structure is formed such that a flow rate of the heat exchange medium flowing in the inner space of the tube in the region near the partition wall is relatively lower than a flow rate of the heat exchange medium flowing in the inner space of the tube otherwise area flows. heat exchanger after claim 2 , wherein the flow distribution structure the flow distribution structure is a flow rate adjustment orifice, one end of which is fixed to an inner surface of the container and the other end of which is arranged so that it is spaced from the interior of the tube the flow rate, the flow rate adjustment orifice is formed to reduce a flow rate of the heat exchange medium flowing in the interior of the tube in the area near the partition wall. heat exchanger after claim 2 , wherein the flow distribution structure is a flow rate adjustment rib, which is formed as part of the tank and protrudes to an inside of the header tank, wherein an end of a protruding portion is arranged so that it is spaced from the inner space of the tube, and the flow rate adjustment rib is formed to reduce a flow rate of the heat exchange medium flowing in the inner space of the tube in the area near the partition wall. heat exchanger after claim 2 wherein the flow distribution structure is formed in one of the front and rear heat exchange parts where a temperature of the heat exchange medium is relatively high. heat exchanger after claim 5 wherein a temperature of the heat exchange medium flowing in the rear heat exchange part is higher than a temperature of the heat exchange medium flowing in the front heat exchange part, and the heat exchange flow distribution structure is formed in the rear heat exchange part. heat exchanger after claim 2 wherein the flow distribution structure is attached to all positions of the tubes (200). heat exchanger after claim 2 wherein the flow distribution structure is formed to be spaced only from a position opposite to a position of the tube. heat exchanger after claim 2 wherein the flow distribution structure is formed to correspond to a range of 10 to 20% of a width of the tube. heat exchanger after claim 1 wherein the means for reducing thermal stresses is an air pocket formed in the form of a void in the bulkhead. heat exchanger after claim 10 , wherein the air pocket extends in a direction of extension of the partition wall. heat exchanger after claim 10 wherein the air bag is formed so that it is opened at a head end. heat exchanger after claim 12 wherein an opened portion of the air bag is sealed by a gasket provided at a portion where the head and the tank are coupled. heat exchanger after Claim 13 wherein the seal has a seal projection protruding at a position corresponding to the opened portion of the air bag. heat exchanger after claim 10 wherein the heat exchanger has a leak check route formed in the tank and provided in the form of a flow path that allows the air pocket to communicate with the outside. heat exchanger after claim 1 , wherein the heat exchanger is a radiator in which a high-temperature coolant and a low-temperature coolant flow.

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