CN113227702A

CN113227702A - Heat exchanger

Info

Publication number: CN113227702A
Application number: CN201980085447.4A
Authority: CN
Inventors: 尹韩吉; 白承树; 李相沃; 李相容; 郑贤姬
Original assignee: Hanon Systems Corp
Current assignee: Hanon Systems Corp
Priority date: 2018-12-26
Filing date: 2019-12-20
Publication date: 2021-08-06
Anticipated expiration: 2039-12-20
Also published as: CN113227702B; DE112019006476T5; KR20200080157A

Abstract

The present invention provides a heat exchanger, comprising: a 1 st header tank and a 2 nd header tank which are arranged at a predetermined distance in a height direction; and a core portion disposed between the 1 st header tank and the 2 nd header tank, and including a plurality of tubes and fins, wherein the 1 st header tank includes a 1 st header plate, a 1 st tank, and a 1 st partition wall, the 1 st partition wall divides a space formed by joining the 1 st header plate and the 1 st tank to form a plurality of flow paths, a bypass pipe including an inflow flow path and an outflow flow path is connected to an outer side of the 1 st header tank, the inflow flow path and the outflow flow path have different sizes from each other, and the outflow flow path has a cross-sectional area larger than that of the inflow flow path.

Description

Heat exchanger

Technical Field

Embodiments relate to heat exchangers. And more particularly, to a heat exchanger such as an evaporator which is improved in performance by modifying the structure.

Background

With the worldwide increasing interest in energy and environmental issues, in recent years, improvements in efficiency of various parts including fuel consumption rate have been achieved in the automobile production industry, and the appearance of automobiles tends to be diversified in order to meet the demands of different consumers. With such a tendency, various parts of vehicles have been developed to achieve weight reduction, size reduction, and high functionality. In particular, in a cooling device for a vehicle, it is actually difficult to secure a sufficient space inside an engine room, and therefore efforts have been made to manufacture a heat exchange system having a small size and a high efficiency.

On the other hand, a heat exchange system is generally composed of a heat exchanger that absorbs heat from the surroundings, a compressor that compresses a refrigerant or a heat medium, a condenser that discharges heat to the surroundings, and an expansion valve that expands the refrigerant or the heat medium.

In the cooling system, the refrigerant in a gaseous state flowing from the heat exchanger to the compressor is compressed in the compressor to a high temperature and a high pressure, the heat of vaporization is released to the surroundings while the compressed refrigerant in a gaseous state is liquefied by the condenser, the liquefied refrigerant is brought into a low-temperature and low-pressure wet vapor state by the expansion valve again and then flows into the heat exchanger again to be vaporized, thereby forming a cycle, and a substantial cooling action is achieved by the heat exchanger in which the refrigerant in a liquid state absorbs heat of the degree of the heat of vaporization to the surroundings and is vaporized.

As described above, the low-temperature and low-pressure refrigerant having passed through the expansion valve flows into the heat exchanger through the connection pipe, and the refrigerant absorbs ambient heat in the heat exchanger to be in a high-temperature and high-pressure state. Therefore, the heat exchanger needs to be made of a material and structure capable of withstanding a rapid phase change, a high temperature, and a high pressure of the refrigerant stored therein.

Thus, the heat exchanger is equivalent to the core structure of the cooling system, and continuous development is currently carried out.

Disclosure of Invention

Technical subject

The embodiment aims to improve efficiency and save cost by changing the structure of the heat exchanger.

The problems to be solved by the present invention are not limited to the above-mentioned problems, and other problems not mentioned here can be understood by those skilled in the art from the following description.

Means for solving the problems

An embodiment of the present invention provides a heat exchanger, including: a 1 st header tank and a 2 nd header tank which are arranged at a predetermined distance in a height direction; and a core portion disposed between the 1 st header tank and the 2 nd header tank, and including a plurality of tubes and fins, wherein the 1 st header tank includes a 1 st header plate, a 1 st tank, and a 1 st partition wall, the 1 st partition wall divides a space formed by joining the 1 st header plate and the 1 st tank to form a plurality of flow paths, a bypass pipe including an inflow flow path and an outflow flow path is connected to an outer side of the 1 st header tank, the inflow flow path and the outflow flow path have different sizes from each other, and the outflow flow path has a cross-sectional area larger than that of the inflow flow path.

Preferably, the cross section of the inflow channel and the outflow channel has a ratio of 1:3.5 to 4.9.

Preferably, an end cap is connected to an end of the 1 st header tank, the end cap includes an end cap plate, and an inflow coupling protrusion and an outflow coupling protrusion protruding to the outside of the 1 st header tank, the bypass pipe includes an inflow channel protrusion and an outflow channel protrusion, the inflow channel protrusion is inserted into the inside of the inflow coupling protrusion and coupled thereto, and the outflow channel protrusion is inserted into the inside of the outflow coupling protrusion.

Preferably, the inflow channel protrusion and the outflow channel protrusion have an insertion depth of 3.8 to 4.2 mm.

Preferably, the inflow channel protrusion and the outflow channel protrusion include coupling protrusions, the inflow coupling protrusion and the outflow coupling protrusion include coupling grooves, and the coupling protrusions are inserted into the coupling grooves and coupled to each other.

Preferably, an insertion groove is disposed between the inflow coupling protrusion and the outflow coupling protrusion of the end cap, and the 1 st partition wall is inserted into the insertion groove.

Preferably, the core includes a 1 st end plate and a 2 nd end plate on both sides thereof, and the 2 nd end plate is disposed outside the end cap.

Preferably, the 1 st header plate is inclined with respect to a center portion thereof, and the inclination has a bilaterally symmetrical structure.

Preferably, the maximum height of the 1 st header tank and the height of the region to which the 1 st header plate and the 1 st tank are welded have a ratio of 1:0.115 to 0.125.

Preferably, the first end plate 1 and the second end plate 2 have a plurality of first fixing protrusions 1 and a plurality of second fixing protrusions 2 at both side ends thereof, respectively, and the first fixing protrusions 1 have first inclined portions on side surfaces thereof, and the second fixing protrusions 2 have second inclined portions on side surfaces thereof.

Preferably, the 1 st inclined portion disposed at one side of the 1 st end plate is disposed at the 1 st fixing protrusion in the same direction as the 1 st fixing protrusion, and the 1 st inclined portion disposed at the other side is disposed at the 1 st fixing protrusion in the opposite direction to the 1 st fixing protrusion.

Preferably, the inclination is formed at 4 to 6 degrees.

Preferably, the 1 st header plate has a plurality of tube coupling holes, and embossments are disposed between the plurality of tube coupling holes.

Preferably, the first tank 1 is provided with embossments opposed to the embossments formed on the first header plate 1.

Preferably, a baffle plate forming a flow path is disposed between the embosses disposed to face each other in the vertical direction.

Effects of the invention

According to the embodiment, the manufacturing cost of the heat exchanger can be saved compared with the conventional one.

In addition, the leakage can be prevented or the coupling force can be improved, thereby improving the quality.

In addition, the heat exchange performance of the heat exchanger can be improved.

The diversification and excellent advantages and effects of the present invention are not limited to the above, and can be more easily understood in the description of the embodiments of the present invention.

Drawings

Fig. 1 is a diagram showing the structure of a heat exchanger of an embodiment of the present invention.

Fig. 2 is a diagram showing a coupling structure of the 1 st header tank, which is a component of fig. 1.

Fig. 3 is a diagram showing the structure of the partition wall, which is a constituent element of fig. 1.

Fig. 4 and 5 are diagrams showing the structure of a header (header) which is a component of fig. 1.

Fig. 6 is a table showing the degree of improvement in heat dissipation performance achieved by the provision of the auxiliary communication holes.

Fig. 7 is a perspective view of the combination of the first header tank 1 and the end plate among the components of fig. 1.

Fig. 8 is a side view of fig. 7.

Fig. 9 is a front view of fig. 7.

Fig. 10 is a perspective view of the end cap as a constituent element of fig. 7.

Fig. 11 is a side view of fig. 10.

Fig. 12 is a perspective view of a shunt (harness) as a structural element of fig. 1.

Fig. 13 is an exploded view of fig. 12.

Fig. 14 is a diagram illustrating the coupling of the shunt tube and the end cap, which are structural elements of fig. 1.

Fig. 15 is a cross-sectional view a-a' of fig. 14.

Fig. 16 is a view showing a structure in which a throttle (throttle) is coupled to the header tank of fig. 1.

Fig. 17 is a sectional view of the throttle member as a constituent element of fig. 16.

Fig. 18 is a diagram showing the structure of the baffle plate as a constituent element of fig. 1.

Fig. 19 is a diagram showing the structure of the 1 st end plate which is a constituent element of fig. 1.

Fig. 20 is a cross-sectional view of fig. 19.

Fig. 21 is a diagram showing the structure of the 2 nd end plate which is a constituent element of fig. 1.

Fig. 22 is a cross-sectional view of fig. 21.

Fig. 23 is a sectional view of a tube as a constituent element of fig. 1.

Fig. 24 is a side view of fig. 1.

Fig. 25 is a diagram showing a coupling structure of the baffle plates as a constituent element of fig. 1.

Fig. 26 is a diagram showing the structure of the flow path formed by fig. 1.

Detailed Description

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

However, the technical idea of the present invention is not limited to the embodiments described in some of the embodiments, and various forms different from each other may be implemented, and one or more of the components of the embodiments may be selectively combined and replaced within the technical idea of the present invention.

In addition, terms (including technical and scientific terms) used in the embodiments of the present invention may be interpreted as meaning that a person skilled in the art can understand in a general case unless specifically defined otherwise, and the meaning of terms used in a general case, such as terms defined in a dictionary, is interpreted in consideration of the meaning in the context of the related art.

The terms used in the examples of the present invention are used for the description of the examples, and the present invention is not limited thereto.

In this specification, unless otherwise specified, singular terms include a plurality, and in the case of being described as "at least one (or more than one) of a and (and) B, C", one or more than one of all combinations combined by A, B, C may be included.

In addition, in describing the components of the embodiment of the present invention, terms such as 1 st, 2 nd, A, B nd, (a), (b) and the like may be used.

Such terms are used only to distinguish the constituent elements from other constituent elements, and the terms do not limit the nature, sequence, order, and the like of the constituent elements.

Further, the description that a certain component is "connected", "connected" or "connected" to another component includes not only a case where the component is directly connected, connected or connected to another component, but also a case where the component is "connected", "connected" or "connected" to another component via another different component.

In addition, when the description is made as "upper (upper) or lower (lower)" of each of the constituent elements, the upper (upper) or lower (lower) includes not only a case where the two constituent elements are in direct contact with each other but also a case where one or more other different constituent elements are formed or arranged between the two constituent elements. In addition, when the expression "upper (upper) or lower (lower)" is used, not only an upper direction but also a lower direction with respect to one component is included.

Hereinafter, the embodiments will be described in detail with reference to the drawings, and the same or corresponding components are given the same reference numerals regardless of the reference numerals, and redundant description thereof will be omitted.

In fig. 1 to 26, only the main features are clearly illustrated in order to clearly understand the present invention conceptually, and various modifications are conceivable as a result of the illustration.

Referring to fig. 1, a heat exchanger of an embodiment of the present invention includes: a 1 st header tank 100 and a 2 nd header tank 200 arranged at a predetermined distance in a height direction; and a core 900 disposed between the 1 st header tank 100 and the 2 nd header tank 200, and including a tube 910 and a fin (fin) 930.

The 1 st and 2

nd header tanks

100 and 200 are partitioned into the 1 st and 2 nd flow paths by partition walls. The baffles 300 are provided inside the 1 st and 2

nd header tanks

100 and 200 to regulate the flow of the refrigerant.

An end cap 400 is connected to one side of the 1 st header tank 100, and a bypass pipe 500 is connected to the end cap 400, and a refrigerant flows in and out.

The 2 nd header tank 200 is provided with a throttle 800 to regulate the flow of the refrigerant.

A core 900 including tubes 910 and fins 930 is disposed between the 1 st header tank 100 and the 2 nd header tank 200, thereby generating heat exchange.

A 1 st end plate 600 and a 2 nd end plate 700 are coupled to one side and the other side of the core 900.

Fig. 2 is a diagram showing a coupling structure of the first header tank 100 which is a component of fig. 1, fig. 3 is a diagram showing a structure of a partition which is a component of fig. 1, and fig. 4 and 5 are diagrams showing a structure of a header which is a component of fig. 1.

Referring to fig. 2 to 5, the 1 st header tank 100 forms a header tank by the combination of the 1 st header plate 110 and the 1 st tank 130.

Both side end portions of the 1 st header plate 110 are bent and inclined toward the center portion. In one embodiment, the 1 st header plate 110 has a bilaterally symmetrical structure with respect to a center portion. The 1 st header plate 110 may have an inclination angle of 4 to 6 degrees, preferably an inclination angle of 5 degrees, and has a bilaterally symmetrical structure with respect to the 1 st partition wall 150. In the 1 st header plate 110 having such an inclination, the condensed water flows along the inclination and is discharged.

A 2 nd end cap fixing hole 111 for fixing the end cap 400 is formed at one side end of the 1 st header plate 110. In one embodiment, the 2 nd cap fixing holes 111 are formed on both sides of the 1 st partition wall 150.

The 1 st partition wall 150 is provided at the center of the 1 st header plate 110. The 1 st partition wall 150 may be configured as a separate structure and coupled to the 1 st header plate 110, but the 1 st header plate 110 and the 1 st partition wall 150 may be integrally coupled in order to prevent leakage of the refrigerant moving inside the 1 st header tank 100.

The 1 st partition wall 150 is connected to the 1 st header plate 110 and formed to protrude by a certain height. The 1 st partition wall 150 divides the 1 st header 100 into a form having a pair of flow paths.

The 1 st header plate 110 includes a plurality of tube coupling holes 113 on both sides with respect to the 1 st partition wall 150.

The pipe coupling hole 113 is formed in a direction perpendicular to the 1 st partition wall 150, and the pipe 910 is inserted into the pipe coupling hole 113 to be coupled. The shape of the plurality of tube coupling holes 113 is not limited, but it is preferable that the plurality of tube coupling holes 113 are formed in a left-right symmetrical manner with respect to the 1 st partition wall 150 and have the same shape for uniform movement of the refrigerant and easy production.

Further, embossments 115 are disposed between the tube coupling holes 113. As an example, the embossments 115 are formed in the same direction as the tube coupling holes 113, thereby supplementing the rigidity of the 1 st header plate 110.

The 1 st partition 150 includes a main communication hole 151 and an auxiliary communication hole 153. The main communication hole 151 and the auxiliary communication hole 153 connect the 1 st channel and the 2 nd channel formed by the 1 st partition wall 150 to allow the refrigerant to move.

Fig. 6 is a table showing the degree of improvement in heat dissipation performance achieved by the provision of the auxiliary communication hole 153.

Fig. 6 compares the heat radiation performance in the case of using only the conventional main communication hole 151 with the heat radiation performance in the case of using the auxiliary communication hole 153.

The effect of the auxiliary communication hole 153 was tested with respect to the heat dissipation performance in the case of using the conventional main communication hole 151.

Referring to the experimental data #1, when the auxiliary communication hole 153 has an area of 20% based on the area of the main communication hole 151, the heat radiation performance decreases to 97.9%.

Referring to experimental data #2, when the auxiliary communication hole 153 has an area of 14.7% based on the area of the main communication hole 151, the heat radiation performance decreases to 98.8%.

Referring to experimental data #3, when the auxiliary communication hole 153 has an area of 10.8% with respect to the area of the main communication hole 151, the heat radiation performance decreases to 98.7%.

Referring to the experimental data #4, when the auxiliary communication hole 153 has an area of 6.5% based on the area of the main communication hole 151, the heat radiation performance increases to 100.8%.

Referring to the experimental data #5, when the auxiliary communication hole 153 has an area of 3.7% based on the area of the main communication hole 151, the heat radiation performance increases to 101.7%.

Referring to the above experimental data #1 to #5, it was confirmed that the auxiliary communication hole 153 disposed at a predetermined distance from the main communication hole 151 disposed in the partition wall for passing the refrigerant changes the heat radiation performance depending on the area. The performance is improved only within a certain area range with respect to the main communication hole 151 without simply improving the heat radiation performance by providing the auxiliary communication hole 153.

In the present invention, the shape of the auxiliary communication hole 153 is illustrated as a circle, which is merely an example and may be implemented by being deformed into various shapes.

When the area ratio of the auxiliary communication hole 153 to the surface of the main communication hole 151 is 10% or more, the refrigerant is concentrated in the auxiliary communication hole 153 to a degree of a necessary degree or more, and a refrigerant distribution failure is caused, whereby a decrease in heat radiation performance can be confirmed.

In the present invention, when the area ratio of the auxiliary communication hole 153 to the main communication hole 151 is 3 to 7%, the distribution of the refrigerant passing through the communication hole is improved, and thus the heat radiation performance is improved in the range of 0.8 to 1.7%.

The 1 st case 130 may have a structure in which both side ends are bent, and a concave portion 131 into which a partition is inserted and disposed may be provided in one central region.

The concave portion 131 is provided along the longitudinal direction of the 1 st header tank 100, and is closely attached to and coupled to the 1 st partition wall 150. The recessed portion 131 and the 1 st partition wall 150 are closely bonded to each other to define a flow path defined by the 1 st partition wall 150, but the present invention is not limited thereto, and may be bonded by brazing. In addition, the concave portion 131 is configured in a structure in which valleys and ridges are repeated, thereby increasing the effective utilization of the defined space.

The embossments 135 disposed opposite to the embossments 115 formed on the 1 st header plate 110 are disposed on the 1 st case 130. The embossments 135 can supplement the rigidity of the 1 st case 130.

Further, a 1 st cover fixing hole 133 for coupling to the cover 400 is provided at one side of the 1 st case 130.

The 1 st header plate 110 and the 1 st case 130 are arranged so as to overlap each other, and the overlapping regions are brazed to form a seal structure.

In this case, the maximum height H of the 1 st header tank 100 and the height H of the region to which the 1 st header plate 110 and the 1 st tank 130 are welded may be arranged in a ratio ranging from 1:0.115 to 1: 0.125.

In a conventional header tank, a header plate has a planar structure, and the height of the header tank and the height of a region to which the header plate and the tank are welded are arranged at a ratio of 1:0.15 to 1: 0.16.

However, in the present invention, the 1 st header plate 110 is provided to be inclined in order to discharge condensed water, and the height of the welded region is secured without changing the height.

The 1 st header tank 100 is provided with various passages by baffles 300. Conventionally, the baffle 300 is inserted into a groove formed in a case.

However, such a conventional structure has a problem that durability is lowered because an embossed structure is not applied to form grooves.

In order to solve the problem of durability, the present invention improves durability compared to the prior art by replacing the conventional groove with an embossed structure and assembling the baffle 300 by inserting it into the embossing.

Fig. 7 is a combined perspective view of the first header tank 100 and the first end plate 1 among the structural elements of fig. 1, fig. 8 is a side view of fig. 7, fig. 9 is a front view of fig. 7, fig. 10 is a perspective view of the end cap 400, which is the structural element of fig. 7, fig. 11 is a side view of fig. 10, fig. 12 is a perspective view of the shunt 500, which is the structural element of fig. 1, fig. 13 is an exploded view of fig. 12, fig. 14 is a view showing the combination of the shunt 500 and the end cap 400, which are the structural elements of fig. 1, and fig. 15 is a sectional view showing the combined state of fig. 14.

Referring to fig. 7 to 15, an end cap 400 is connected to one side of the 1 st header tank 100, and the end cap 400 is coupled to a bypass pipe 500 to allow inflow and outflow of refrigerant.

The end cap 400 includes an end cap plate 410, an inlet 431 penetrating the end cap plate 410 and allowing the refrigerant to flow into the 1 st header tank 100, and an outlet 451 allowing the refrigerant in the 1 st header tank 100 to flow out.

The end cover 410 is inserted into and fixed to the inside of the 1 st header tank 100 at a predetermined distance from the end thereof. The end cover plate 410 is formed in the same sectional shape as the inner space of the 1 st header tank 100.

The end cover 410 includes a plurality of fixing portions for fixing to the 1 st header tank 100. In one embodiment, the 1 st fixing portion 411 is provided on a surface of the end cap plate 410 contacting the 1 st case 130, and the pair of 2 nd fixing portions 413 are provided on a surface of the end cap plate 410 contacting the 1 st header plate 110.

The 1 st fixing portion 411 is inserted into the 1 st end cap fixing hole 133 formed in the 1 st case 130 and fixed. The 1 st fixing section 411 is formed across the 1 st flow path and the 2 nd flow path divided by the partition wall, and includes a confusion preventing section 412 for preventing confusion in the insertion direction on one side. As an example, the confusion preventing part 412 is formed to have a step to prevent misassembly at the time of assembly.

An insertion groove 415 into which the 1 st partition wall 150 is inserted is formed at a lower portion of the 1 st fixing portion 411. The insertion groove 415 is configured to have the same height as the 1 st partition wall 150 in the region where the end cover plate 410 is disposed, thereby forming a sealing structure.

The 2 nd fixing portions 413 are disposed on both sides of the insertion groove 415, and are inserted into and fixed to the 2 nd header fixing holes 111 formed in the 1 st header plate 110.

The surface of the end cover plate 410 that contacts the 1 st header plate 110 is formed to have the same inclination as the inclined surface formed on the 1 st header plate 110.

Further, the end cover 410 is provided with a close-contact joint 416 on each side. The tight joint 416 performs the function of sealing the stepped region that occurs in the case where the 1 st tank 130 and the 1 st header plate 110 are joined. The close contact joint 416 is formed in the same shape as a stepped region generated by the joint of the 1 st tank 130 and the 1 st header plate 110.

An inlet 431 through which the refrigerant moves is formed at the center of the inlet coupling protrusion 430, is coupled to the inlet flow path 510 provided in the bypass pipe 500, and protrudes outward when coupled to the 1 st header tank 100. The inflow coupling protrusion 430 is formed in the same shape as the inflow channel 510 formed in the shunt 500.

An outlet 451 through which the refrigerant flows out is formed at the center of the outlet coupling protrusion 450, is coupled to the outlet flow path 530 provided in the bypass pipe 500, and protrudes outward when coupled to the 1 st header tank 100.

The bypass pipe 500 includes an inflow channel 510 through which the refrigerant flows into the 1 st header tank 100 and an outflow channel 530 through which the refrigerant flows out of the 2 nd header tank 200.

The inflow coupling protrusion 430 and the outflow coupling protrusion 450 are connected to the ends of the inflow channel 510 and the outflow channel 530.

As an example, the inflow channel protrusion 511 is inserted into the inside of the inflow coupling protrusion 430 and coupled thereto, and the outflow channel protrusion 531 is inserted into the outflow coupling protrusion 450 and coupled thereto. At this time, the inflow channel 510 is connected to the inflow port 431, and the outflow channel 530 is connected to the outflow port 451, so that the refrigerant flows into and out of the 1 st header tank 100.

The inflow channel 510 and the outflow channel 530 may have different areas from each other. The inflow channel 510 may have a smaller area than the outflow channel 530. The cross-section of the inflow channel 510 and the outflow channel 530 may have a ratio of 1:3.5 to 4.9.

As an example, the area of the outflow channel 530 is set to 138mm²In the case of (3), the inflow channel 510 may have a length of 28 to 38mm²The area of (a).

The shapes of the inflow channel 510 and the outflow channel 530 are not limited, and the inflow channel 510 is formed to have a circular shape so that the refrigerant flowing in flows smoothly.

The outflow coupling protrusion 450 and the outflow channel 530 are coupled in the same structure as the coupling structure of the inflow coupling protrusion 430 and the inflow channel 510. Next, a coupling structure between the inflow coupling protrusion 430 and the inflow channel 510 will be mainly described.

The inflow channel protrusion 511 is inserted into the inflow coupling protrusion 430 and coupled thereto. The inner side surface of the inflow coupling protrusion 430 and the outer side surface of the inflow coupling protrusion 430 are formed in the same shape and are closely coupled.

At this time, the insertion depth D of the inflow path protrusion 511 is set in a range of 3.8 to 4.2mm, thereby securing the assembly strength and maximizing the space efficiency.

The end of the inner side surface of the inflow coupling protrusion 430 has a curved surface or an inclination. This makes it possible to easily couple the inflow channel protrusion 511.

In addition, a coupling protrusion 512 is provided in one region of the outer peripheral surface of the inflow passage protrusion 511. Thereby increasing the coupling force to prevent detachment. The coupling protrusion 512 is provided at an end portion of the inflow channel protrusion 511 or at one region provided at the center.

When the coupling protrusion 512 is provided at the end of the inflow channel protrusion 511, the coupling protrusion 512 is supported by the inner wall of the inflow coupling protrusion 430. In addition, when the coupling protrusion 512 is provided in one region of the central portion of the inflow channel protrusion 511, a coupling groove 433 is formed on the inner surface of the inflow coupling protrusion 430. The coupling groove 433 is formed in a shape matching the coupling protrusion 512, and may be modified into various shapes.

Fig. 16 is a diagram showing a configuration in which a throttle member 800 is coupled to the 2 nd header tank 200 of fig. 1, and fig. 17 is a sectional view of the throttle member 800, which is a structural element of fig. 16.

Referring to fig. 16 and 17, the orifice (throttle)800 is disposed in one region partitioned by the 2 nd partition wall 250 in the 2 nd header tank 200. The 2 nd header tank 200 has the same configuration as the 1 st header tank 100.

The orifice 800 has a basic structure that is inserted into and fixed to the 1 st flow path or the 2 nd flow path partitioned by the 2 nd partition wall 250, and includes a close contact joint 416 for sealing the outside.

An orifice 810 is disposed in one region in the center of the orifice 800 to regulate the flow of the refrigerant. The orifice 800 prevents the refrigerant from tending to end when moving, increasing the refrigerant distribution efficiency. The orifice 800 is disposed at a position spaced apart from an end of the flow path of the 2 nd header tank 200 (based on the flow of the flow path) by a predetermined distance. In one embodiment, the orifice 800 is disposed at a distance of 55 to 70mm from one side of the 2 nd header tank 200.

The orifice 810 may have a size of 10 to 20% of the entire area of the orifice 800. The orifice 810 is not limited in shape and is preferably disposed at the center of the area of the orifice 800.

The orifice 800 includes a 3 rd fixing portion 820 and a 4 th fixing portion 830 for fixing the orifice 800.

The 3 rd fixing portion 820 is inserted into the fixing hole 211 of the 1 st throttle member 800 formed at the 2 nd header plate 210.

The 4 th fixing part 830 is inserted into the 2 nd throttle fixing hole 231 formed in the 2 nd case 230, and the 2 nd throttle fixing hole 231 is disposed in the 2 nd case 230 so as to extend over the space defined by the 2 nd partition 250.

The 4 th fixing part 830 includes a 4 th fixing groove 831 into which one region of the 2 nd partition 250 is inserted. At this time, the 4 th fixing part 830 is formed in a hook structure.

The throttle member 800 has a bilaterally symmetrical structure, and can be used in common when the position is changed to the 1 st flow path and the 2 nd flow path.

Fig. 18 is a diagram showing the structure of the baffle 300, which is a constituent element of fig. 1.

Referring to fig. 18, the baffle 300 is provided inside the 1 st header tank 100 or the 2 nd header tank 200 to regulate the flow of the refrigerant. The baffle 300 is formed in a plate shape blocking the flow of the refrigerant in the longitudinal direction of the 1 st or 2

nd header tank

100 or 200, and regulates the flow of the refrigerant moving through the core 900.

A 1 st partition wall insertion groove 320 is formed in one region of the center of the baffle 300, and the 1 st partition wall 150 is inserted into the groove, and a concave portion insertion portion 310 closely coupled to a concave portion 131 formed in the 1 st casing 130 is disposed on the opposite side of the 1 st partition wall insertion groove 320.

The baffle 300 is configured to be closely coupled to the internal space where the 1 st header plate 110 and the 1 st tank 130 are coupled, and thus the baffle 300 is disposed at various positions.

Fig. 19 is a diagram showing the structure of the 1 st end plate 600 which is a constituent element of fig. 1, and fig. 20 is a sectional view of fig. 19.

Referring to fig. 7, 9, 19 and 20, the 1 st end plate 600 supports the core 900 at one side of the core 900 composed of the tube 910 and the fin 930. The No. 1 endplate 600 is configured opposite the side to which the shunt tubes 500 are coupled.

The 1 st end plate 600 includes a plurality of 1 st fixing protrusions 610 at both side ends thereof, the plurality of 1 st fixing protrusions 610 are inserted into the 1 st fixing grooves provided in the 1 st header tank 100 and the 2 nd header tank 200, respectively, and the 1 st inclined portions 620 are provided at side surfaces of the 1 st fixing protrusions 610.

The arrangement of the 1 st fixing protrusion 610 and the 1 st inclined part 620 coupled to the 1 st header tank 100 is different from the arrangement of the 1 st fixing protrusion 610 and the 1 st inclined part 620 coupled to the 2 nd header tank 200.

In one embodiment, the 1 st fixing protrusion 610 coupled to the 1 st header tank 100 is provided with a 1 st inclined part 620 on the same side surface. The 1 st inclined portion 620 is disposed with the same inclination as that of the 1 st header plate 110. In addition, the 1 st fixing protrusion 610 coupled to the 2 nd header tank 200 is provided with a 1 st inclined part 620 on the opposite side to each other. Thereby performing the function of the stopper while preventing misassembly when the 1 st end plate 600 is assembled.

The 1 st fixing protrusion 610 is vertically combined with the 1 st header plate 110. At this time, the 1 st fixing projection 610 is disposed at a position outside the end cover plate 410, thereby preventing leakage due to poor welding occurring at the time of brazing.

The 1 st end plate 600 increases a supporting force using a plurality of bending structures. The bending structure is configured as a bending structure or a structure in which one region is recessed.

The 1 st end plate 600 includes 1 st outer bend portions 640 at both side ends of the 1 st central bend portion 630 and the 1 st central bend portion 630, and at least one 1 st additional bend portion between the 1 st central bend portion 630 and the 1 st outer bend portion 640.

The height of the 1 st central bent portion 630 may be lower than the height of the 1 st outer bent portion 640. The 1 st outer bent portion 640 is provided at both sides of the 1 st central bent portion 630, and may be bent at an angle of 90 degrees.

In one embodiment, when the 1 st outer bent portion 640 has a height of 2.5mm, the 1 st center bent portion 630 may have a height of 1.8 to 2.3 mm.

Fig. 21 is a view showing the structure of the 2 nd end plate which is a constituent element of fig. 1, and fig. 22 is a sectional view of fig. 21.

Referring to fig. 21 and 22, the 2 nd end plate 700 supports the core 900 on the opposite side of the 1 st end plate 600. In order to secure a space for coupling the shunt tubes 500, the 2 nd endplate 700 has a structure in which one central region protrudes.

The 2 nd fixing protrusion 710 and the 2 nd inclined portion 720 provided in the 2 nd end plate 700 have the same configuration as the 1 st end plate 600.

The 2 nd end plate 700 includes 2 nd outer bent portions 740 respectively provided at both sides of the 2 nd central bent portion 730 and the 2 nd central bent portion 730.

The 2 nd central bending portion 730 may have a height higher than that of the 1 st central bending portion 630, and a flat area having a certain width in order to secure a supporting force.

As an example, the 2 nd central bending part 730 may have a height h of 13.0 to 13.5mm₂₁And may include a planar area d of 10mm or more₂₁。

In addition, the height h of the 2 nd outside bend 740₂₂May be greater than the height h of the 2 nd central bend 730₂₁Low. As an example, the 2 nd outside bent portion 740 may have a height of 2.5 mm.

Fig. 23 is a sectional view of a tube 910 which is a constituent element of fig. 1, and fig. 24 is a side view of fig. 1.

Referring to fig. 23 and 24, the tube 910, which is a core component, is connected to the 1 st header tank 100 and the 2 nd header tank 200 to provide a passage through which the refrigerant moves.

The plurality of tubes 910 are inserted into and fixed to tube coupling holes 113 formed in the header plates disposed so as to face each other in the 1 st header tank 100 and the 2 nd header tank 200.

In the conventional heat exchanger structure, about 30 tubes 910 are arranged, and in the present invention, the thickness h of the tubes 910 is reduced₃And the number of tubes 910 is increased. This increases the area for heat exchange by the refrigerant, and improves the efficiency of the heat exchanger. The width of the tube and the height of the tube can have a ratio of 1: 0.08-0.085.

As an example, height h of tube 910₃The height of the device can be 1.75-1.85 mm.

A plurality of flow holes 913 are arranged in the tube 910. The tube 910 is reduced in height in the present invention, thereby increasing the number of flow holes 913. The number of holes is increased compared to the structure of the conventional tube 910, thereby increasing the resistance of the fluid, thereby improving the heat exchange performance.

As an example, the tube 910 may be configured with 14 flow holes 913.

Thickness t of upper wall 911 and lower wall 912 of tube 910₃₁May be 0.22mm, dividing the thickness t of the wall 914₃₂May be 0.15 mm. This can save cost as compared with the conventional tube structure.

Further, outermost walls 915 disposed on both sides of the tube 910 may be thicker than the thicknesses of the upper wall 911 and the lower wall 912. This is to solve the problem of leakage due to corrosion at the outermost wall 915 when the heat exchanger is used.

As one example, the outermost wall 915 of the tube 910 may have a thickness that is 1.9 to 2.1 times the thickness of the dividing wall 914. In the case where the dividing wall 914 has a thickness of 0.15mm, the outermost wall 915 may have a thickness of 0.3 mm.

The tube 910 may be provided with stops 916 at both ends. This is to adjust the depth of insertion of the tube 910 into the tube coupling hole 113, and the end portion may have an inclined or curved structure for easy insertion.

Referring to fig. 25, the baffle 300 is disposed between the

embossings

115, 135 oppositely disposed at the 1 st header plate 110 and the 1 st tank 130.

Conventionally, grooves have been provided in the 1 st header plate and the 1 st tank, respectively, for fixing the baffle. In such a structure, it is difficult to form embossments in the portions where the baffle is inserted, and there is a problem that the rigidity is weakened in the regions where embossments are not formed.

In order to solve such problems, the present invention provides rigidity by forming

embossments

115 and 135 on the entire 1 st header plate 110 and the 1 st tank 130, and fixes the

embossments

115 and 135 by disposing the baffle 300 therebetween.

As an example, the baffle 300 is disposed closely to the inside of the

embossments

115, 135 by surface contact.

Thus, the conventional coupling groove is omitted, the position of the baffle 300 can be adjusted as necessary, and the number and position of the various flow paths can be formed.

Fig. 26 is a diagram showing the structure of the flow path formed by fig. 1.

Referring to fig. 26, the 1 st header tank 100 has a 2-row structure by the 1 st partition wall 150, and the 2 nd header tank 200 has a 2-row structure by the 2 nd partition wall 250. At this time, the baffle 300 is disposed in one region of the 1 st header tank 100 to form a flow path.

As shown in fig. 26, the refrigerant flowing into the 1 st row of the 1 st header tank 100 moves downward and then moves and rises in the 1 st row of the 2 nd header tank 200. Thereafter, the refrigerant moves from the 1 st row to the 2 nd row of the 1 st header tank 100, and the refrigerant that has moved to the 2 nd row moves down and then along the 2 nd row of the 2 nd header tank 200, and then rises and flows out through the 2 nd row of the 1 st header tank 100.

In this case, the 2 nd header tank 200 is divided into 4 regions by the baffle plates disposed in the 1 st header tank 100, and the dampers 800 may be disposed in the 1 st row and the 2 nd row of the 2 nd header tank 200, respectively.

The orifice 800 may be disposed in the 2 nd and 4 th regions of the 2 nd header tank 200, respectively.

In this case, the orifice 800 may be disposed in the center of the 2 nd and 4 th regions.

As an example, when the heat exchanger has a 33-row structure (N), the baffles 300 are arranged in regions that are divided into 15 rows (N1) and 18 rows (N2) with respect to the inflow side of the refrigerant. At this time, the chokes arranged in the 2 nd area are arranged so as to be divided into 9 rows (N21) and 9 rows (N22), and the chokes arranged in the 4 th area are arranged at positions divided into 7 rows (N11) and 8 rows (N12).

When the heat exchanger has a 37-row configuration (N), the baffles 300 are arranged in a region that divides 18 rows (N1) and 19 rows (N2) with respect to the inflow side of the refrigerant. In this case, the chokes arranged in the 2 nd zone are arranged in the zone divided into the 10 th row (N21) and the 9 th row (N22), and the chokes arranged in the 4 th zone are arranged in the zone divided into the 9 th row (N11) and the 9 th row (N12).

The embodiments of the present invention have been specifically described above with reference to the drawings.

The above description is merely an exemplary description of the technical idea of the present invention, and those skilled in the art can make various modifications, alterations, and substitutions without departing from the scope of the essential characteristics of the present invention. Therefore, the embodiments and drawings disclosed in the present invention do not limit the technical idea of the present invention, but explain the technical idea of the present invention, and the technical idea of the present invention is not limited to the embodiments and drawings. The scope of the present invention should be construed by the claims which follow, and all technical ideas within the same scope thereof are included in the scope of the claims.

(notation) 100: 1 st header, 110: 1 st header plate, 111: 2 nd end cap fixing hole, 113: tube coupling hole, 115, 135: embossing, 130: 1 st box, 131: recessed portion, 133: 1 st end cap fixing hole, 150: 1 st partition wall, 151: main communication hole, 153: auxiliary communication hole, 200: 2 nd header tank, 210: header plate 2, 211: 1 st orifice, 230: 2 nd case, 231: throttle fixing hole 2, 250: no. 2 partition wall, 300: baffle, 400: end cap, 410: end cover plate, 411: 1 st fixing section, 412: confusion preventing portion, 413: 2 nd fixing part, 415: insertion slot, 416: tight joint, 430: inflow coupling protrusion, 431: inflow port, 433: binding groove portion, 450: outflow coupling projection, 451: outflow port, 500: shunt, 510: inflow channel, 511: inflow channel protrusion, 512: bonding protrusions, 530: outflow channel, 531: outflow channel protrusion, 600: end plate 1, 610: 1 st fixing protrusion, 620: 1 st inclined part, 630: 1 st central curved portion, 640: 1 st outside bend, 700: end plate 2, 710: fixing protrusion No. 2, 720: slope 2, 730: center bend 2, 740: 2 nd outside bend, 800: throttle, 810: orifice, 820: 3 rd fixing part, 830: 4 th fixing portion, 831: 4 th fixing groove, 900: core, 910: tube, 911: upper wall, 912: lower wall, 913: flow bore, 914: dividing wall, 915: outermost wall, 916: a stopper portion, 930: and (4) warping.

Claims

1. A heat exchanger, comprising: a 1 st header tank and a 2 nd header tank which are arranged at a predetermined distance in a height direction; and a core part disposed between the 1 st header tank and the 2 nd header tank and including a plurality of tubes and fins,

the 1 st header tank includes a 1 st header plate, a 1 st tank, and 1 st partition walls, the 1 st partition walls dividing a space formed by the combination of the 1 st header plate and the 1 st tank to form a plurality of flow paths,

a bypass pipe having an inflow channel and an outflow channel, which are different in size from each other, is connected to the outside of the 1 st header tank,

the outflow channel has a larger cross-sectional area than the inflow channel.

2. The heat exchanger of claim 1,

the cross section of the inflow channel and the outflow channel has a ratio of 1: 3.5-4.9.

3. The heat exchanger of claim 1,

an end cover is connected with the end part of the 1 st header tank,

the end cap includes an end cap plate, an inflow coupling protrusion and an outflow coupling protrusion protruding to the outside of the 1 st header tank,

the flow dividing pipe is provided with an inflow channel protruding part and an outflow channel protruding part,

the inflow channel protrusion is inserted into the inflow coupling protrusion to be coupled thereto, and the outflow channel protrusion is inserted into the outflow coupling protrusion.

4. The heat exchanger of claim 3,

the inflow channel protrusion and the outflow channel protrusion have an insertion depth of 3.8 to 4.2 mm.

5. The heat exchanger of claim 3,

the inflow channel protrusion and the outflow channel protrusion are provided with coupling protrusions,

the inflow coupling protrusion and the outflow coupling protrusion are provided with coupling grooves,

the coupling protrusion is inserted into the coupling groove portion and coupled.

6. The heat exchanger of claim 3,

an insertion groove is disposed between the inflow coupling protrusion and the outflow coupling protrusion of the end cap,

the 1 st partition wall is inserted into the insertion groove.

7. The heat exchanger of claim 3,

the core is provided with a 1 st end plate and a 2 nd end plate on both sides,

the 2 nd end plate is disposed outside the end cap.

8. The heat exchanger of claim 7,

the 1 st header plate is inclined with respect to a center portion thereof, and the inclination has a bilaterally symmetrical structure.

9. The heat exchanger of claim 8,

the maximum height of the 1 st header tank and the height of the region where the 1 st header plate and the 1 st tank are welded have a ratio of 1: 0.115-0.125.

10. The heat exchanger of claim 8,

a plurality of 1 st fixing protrusions and a plurality of 2 nd fixing protrusions are respectively arranged on both side end portions of the 1 st end plate and the 2 nd end plate,

the side surface of the 1 st fixing protrusion is provided with a 1 st inclined part, and the side surface of the 2 nd fixing protrusion is provided with a 2 nd inclined part.

11. The heat exchanger of claim 10,

the 1 st inclined portion disposed at one side of the 1 st end plate is disposed at the 1 st fixing protrusion in the same direction as the 1 st fixing protrusion, and the 1 st inclined portion disposed at the other side is disposed at the 1 st fixing protrusion in the opposite direction to the 1 st fixing protrusion.

12. The heat exchanger of claim 8,

the inclination is formed at 4 to 6 degrees.

13. The heat exchanger of claim 1,

a plurality of tube coupling holes are disposed in the 1 st header plate, and embossments are disposed between the plurality of tube coupling holes.

14. The heat exchanger of claim 13,

the first tank 1 is provided with embossments opposed to the embossments formed on the first header plate 1.

15. The heat exchanger of claim 14,

between the embosses arranged to face each other in the vertical direction, a baffle plate forming a flow path is arranged.