CN113227702B

CN113227702B - Heat Exchanger

Info

Publication number: CN113227702B
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: 2023-10-03
Anticipated expiration: 2039-12-20
Also published as: DE112019006476T5; KR20200080157A; CN113227702A

Abstract

The present invention provides a heat exchanger comprising: a 1 st header tank and a 2 nd header tank disposed at a distance from each other in the height direction; and a core portion that is disposed between the 1 st header tank and the 2 nd header tank and that includes a plurality of tubes and fins, wherein the 1 st header tank includes a 1 st header plate, a 1 st tank body, and a 1 st partition wall that divides a space formed by joining the 1 st header plate and the 1 st tank body into a plurality of flow paths, a shunt tube 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 larger cross-sectional area than the inflow flow path.

Description

Heat exchanger

Technical Field

Embodiments relate to heat exchangers. And more particularly to heat exchangers, such as evaporators, that improve performance by altering the configuration.

Background

With the increasing worldwide interest in energy and environmental problems, in recent years, improvement of efficiency in various parts including fuel consumption rate has been achieved in the automobile production industry, and in addition, the appearance of automobiles has been diversified in order to meet the demands of different consumers. With such a trend, various parts of a vehicle are being developed and reduced in weight, size and high functionality are being achieved. In particular, in the cooling device for a vehicle, it is actually difficult to ensure a sufficient space inside the engine room, and therefore, there is a continuous effort to manufacture a heat exchanging system having a high efficiency in a small size.

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

In a cooling system, a refrigerant in a gas state flowing from the heat exchanger to a compressor is compressed to a high temperature and a high pressure in the compressor, liquefied heat is released to the periphery in the process that the compressed refrigerant is liquefied by a condenser, and the liquefied refrigerant is vaporized by passing through an expansion valve again to a low-temperature and low-pressure wet vapor state and then flowing back into the heat exchanger again, whereby a cycle is formed, and a substantial cooling effect is achieved by the heat exchanger gasifying by absorbing heat of a degree of vaporization heat in the periphery by the refrigerant in a liquid state.

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 a structure that can withstand rapid phase changes and high temperatures and high pressures of the refrigerant contained therein.

Thus, the heat exchanger corresponds to the core structure of the cooling system, and continuous development is being conducted.

Disclosure of Invention

Technical problem

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 disposed at a distance from each other in the height direction; and a core portion that is disposed between the 1 st header tank and the 2 nd header tank and that includes a plurality of tubes and fins, wherein the 1 st header tank includes a 1 st header plate, a 1 st tank body, and a 1 st partition wall that divides a space formed by joining the 1 st header plate and the 1 st tank body into a plurality of flow paths, a shunt tube 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 larger cross-sectional area than 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, an inflow coupling protrusion protruding to an outside of the 1 st header tank, and an outflow coupling protrusion, the shunt tube includes an inflow channel protrusion and an outflow channel protrusion, the inflow channel protrusion is inserted into and coupled to an inside of the inflow coupling protrusion, and the outflow channel protrusion is inserted into an inside of the outflow coupling protrusion.

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

Preferably, the inflow passage projection portion and the outflow passage projection portion include coupling projections, the inflow coupling projection portion and the outflow coupling projection portion include coupling groove portions, and the coupling projections are inserted into the coupling groove portions to be coupled.

Preferably, an insertion groove is provided 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 portion 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 manifold plate is inclined with respect to the center portion, and the inclination has a bilateral symmetry.

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

Preferably, the 1 st end plate and the 2 nd end plate each have a plurality of 1 st fixing protrusions and a plurality of 2 nd fixing protrusions at both side ends thereof, the 1 st inclined portion is provided on a side surface of the 1 st fixing protrusion, and the 2 nd inclined portion is provided on a side surface of the 2 nd fixing protrusion.

Preferably, the 1 st inclined portion disposed on one side of the 1 st end plate is disposed on the 1 st fixing protrusion in the same direction as the 1 st fixing protrusion, and the 1 st inclined portion disposed on the other side is disposed on 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, a plurality of tube coupling holes are provided in the 1 st header plate, and embossments are provided between the plurality of tube coupling holes.

Preferably, the 1 st tank is provided with an embossing opposing the embossing formed in the 1 st header plate.

Preferably, a baffle plate forming a flow path is arranged between the embossments arranged vertically opposite to each other.

Effects of the invention

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

In addition, the effect of preventing leakage or improving the coupling force is obtained, whereby the quality can be improved.

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

The various and advantageous advantages and effects of the present invention are not limited to the above, and can be more easily understood in the course of the description of the specific embodiments of the present invention.

Drawings

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

Fig. 2 is a view showing a joint structure of the 1 st header tank which is a constituent element 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 constituent element of fig. 1.

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

Fig. 7 is a combined perspective view of the header tank 1 and the end plate among the constituent 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, which is a structural element of fig. 7.

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

Fig. 12 is a perspective view of the shunt (manifold) which is a component of fig. 1.

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

Fig. 14 is a view showing the combination of the shunt tube and the end cap, which are components of fig. 1.

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

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

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

Fig. 18 is a diagram showing the structure of the baffle plate, which is a structural 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 cross-sectional view of the tube, which is 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 plate, which is a structural element of fig. 1.

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

Detailed Description

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

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

The terms (including technical and scientific terms) used in the embodiments of the present invention are not particularly limited, and may be interpreted as meanings that are generally understood by those skilled in the art, and the meanings that are generally used, such as terms defined in a dictionary, are interpreted in consideration of the meanings of the related art.

The term used in the embodiments of the present invention is used for the description of the embodiments, and the present invention is not limited thereto.

In the present specification, unless otherwise mentioned, singular terms include plural cases, and in the case of being described as "at least one (or one or more) of a and (sum) B, C," one or more of all combinations of A, B, C may be included.

In the description of the components of the embodiment of the present invention, the terms 1, 2, A, B, (a), and (b) 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, etc. of the constituent elements.

In addition, the description that a certain component is "connected", "coupled" or "connected" to another component includes not only a case where the component is directly connected, coupled or connected to another component, but also a case where the component is "connected", "coupled" or "connected" to another component by another different component between the component and the other component.

In addition, in the case described as "upper (upper) or lower (lower)" formed or arranged in each of the structural elements, the upper (upper) or lower (lower) includes not only the case where two structural elements are in direct contact with each other but also the case where one or more other different structural elements are formed or arranged between two structural elements. In addition, when expressed as "upper (upper) or lower (lower)", not only the upper direction with respect to one component but also the lower direction may be included.

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

In fig. 1 to 26, only the main features are explicitly shown for the conceptual understanding of the present invention, and as a result, various modifications of the illustrated embodiments are conceivable, and the scope of the present invention is not limited to the specific shapes shown.

Referring to fig. 1, a heat exchanger of an embodiment of the present invention includes: the 1 st header tank 100 and the 2 nd header tank 200, which are disposed at a distance from each other in the height direction; and a core 900 that is disposed between the 1 st header tank 100 and the 2 nd header tank 200 and includes a pipe 910 and fins (fin) 930.

The 1 st header tank 100 and the 2 nd header tank 200 are partitioned into the 1 st flow path and the 2 nd flow path by partition walls. The 1 st header tank 100 and the 2 nd header tank 200 are provided with baffles 300 therein 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 to allow the inflow and outflow of the refrigerant.

The 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.

The 1 st and 2 nd end plates 600 and 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 1 st header tank 100, which is a structural element of fig. 1, fig. 3 is a diagram showing a structure of the partition wall, which is a structural element of fig. 1, and fig. 4 and 5 are diagrams showing a structure of the header, which is a structural element 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.

The 1 st header plate 110 is formed by bending both side end portions and inclining toward the center portion. As an example, the 1 st manifold plate 110 has a laterally symmetrical structure with respect to the center portion. The 1 st manifold plate 110 may have an inclination angle of 4 to 6 degrees, preferably 5 degrees, and has a laterally symmetrical structure with respect to the 1 st partition 150. In the 1 st header plate 110 having such an inclination, condensed water flows along the inclination and is discharged.

A 2 nd cap fixing hole 111 for fixing the end cap 400 is formed at one side end portion of the 1 st header plate 110. As an example, the 2 nd cap fixing holes 111 are provided on both sides with respect to the 1 st partition 150, respectively.

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

The 1 st partition 150 is connected to the 1 st header plate 110 and is formed so as to protrude by a predetermined height. The 1 st partition 150 divides the 1 st header tank 100 into 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 150.

The pipe coupling hole 113 is formed in a direction perpendicular to the 1 st partition 150, and the pipe 910 is inserted into the pipe coupling hole 113 to achieve coupling. 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 symmetrically with respect to the 1 st partition 150 and are formed in the same shape for uniform movement of the refrigerant and ease of production.

Further, embossments 115 are arranged between the tube coupling holes 113. As one 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 and 2 nd passages formed by the 1 st partition wall 150 to move the refrigerant.

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

In fig. 6, the heat dissipation performance in the case of using only the conventional main communication hole 151 and the heat dissipation performance in the case of using the auxiliary communication hole 153 are compared.

The effect of the auxiliary communication hole 153 was tested based on the heat radiation performance in the case of using the conventional main communication hole 151.

Referring to 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 dissipation performance is reduced 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 dissipation performance is reduced to 98.8%.

Referring to experimental data #3, when the auxiliary communication hole 153 has an area of 10.8% based on the area of the main communication hole 151, the heat dissipation performance is reduced to 98.7%.

Referring to 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 dissipation performance is increased to 100.8%.

Referring to 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 dissipation performance is increased to 101.7%.

Referring to the above experimental data #1 to #5, it was confirmed that the heat radiation performance was changed according to the area of the auxiliary communication hole 153 arranged to be spaced apart from the main communication hole 151 arranged in the partition wall for passing the refrigerant. The heat radiation performance is not improved simply by providing the auxiliary communication holes 153, but the performance is improved only in a certain area range with respect to the main communication holes 151.

In the present invention, the shape of the auxiliary communication hole 153 is illustrated as a circle, which is just an example, and can be modified into various shapes to be implemented.

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 of a required level or more is concentrated on the auxiliary communication hole 153, and the refrigerant distribution is poor, whereby it is possible to confirm that the heat radiation performance is degraded.

In the present invention, when the area ratio of the auxiliary communication holes 153 to the main communication holes 151 is 3 to 7%, the distribution of the refrigerant passing through the communication holes 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 end portions are bent, and a recess 131 into which the partition wall is inserted is provided in one region in the center.

The recessed portion 131 is provided along the longitudinal direction of the 1 st header tank 100, and is bonded to the 1 st partition 150 by being in close contact therewith. The recess 131 and the 1 st partition 150 are closely bonded to each other to define a flow path defined by the 1 st partition 150, but the present invention is not limited thereto, and may be bonded by brazing. In addition, the concave portions 131 are arranged in a structure in which valleys and ridges are repeated, whereby the effective availability of a defined space can be increased.

The 1 st case 130 is provided with embossments 135 disposed opposite to embossments 115 formed in the 1 st header plate 110. Embossing 135 can supplement the rigidity of case 1 130.

The 1 st case 130 has a 1 st end cap fixing hole 133 for coupling with the end cap 400 on one side thereof.

The 1 st header plate 110 and the 1 st tank 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 where 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 the conventional header tank, the header plate has a planar structure, and the header tank is arranged so that the height of the header tank and the height of the region where the header plate and the tank are welded are in a ratio of 1:0.15 to 1:0.16.

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

The 1 st header tank 100 forms a flow path having various paths by the baffle 300. Conventionally, the baffle 300 is inserted into a groove formed in the case.

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

In order to solve the durability problem, the present invention is assembled by removing the conventional groove and changing the entire structure to an embossed structure and inserting the baffle 300 into the embossment, thereby improving the durability as compared with the conventional one.

Fig. 7 is a combined perspective view of the 1 st header tank 100 and the 1 st 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 400 which is a component of fig. 7, fig. 11 is a side view of fig. 10, fig. 12 is a perspective view of the shunt 500 which is a component of fig. 1, fig. 13 is an exploded view of fig. 12, fig. 14 is a view showing a combination of the shunt 500 and the end cap 400 which is a component of fig. 1, and fig. 15 is a sectional view showing a combination 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 the shunt tube 500 to allow inflow and outflow of the refrigerant.

The head cap 400 includes a head cap 410, an inflow port 431 through which the head cap 410 flows into the inside of the 1 st header tank 100, and an outflow port 451 through which the refrigerant flows out of the inside of the 1 st header tank 100.

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

The end cap plate 410 is provided with a plurality of fixing portions for fixing with the 1 st header tank 100. As an example, the 1 st fixing portion 411 is provided on the surface of the end cover plate 410 that contacts the 1 st case 130, and the pair of 2 nd fixing portions 413 is provided on the surface of the end cover plate 410 that contacts 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 to be fixed. The 1 st fixing portion 411 is formed across the 1 st flow path and the 2 nd flow path divided by the partition wall, and includes an confusion preventing portion 412 for preventing confusion of the insertion direction on one side. As one example, the confusion preventing unit 412 is formed to have a step to prevent erroneous assembly at the time of assembly.

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

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

The surface of the end plate 410 in contact with the 1 st header plate 110 is formed with the same inclination as the inclination surface formed in the 1 st header plate 110.

Further, the end cap plate 410 is provided with adhesion coupling portions 416 on both sides thereof. The close contact bonding portion 416 performs a 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 bonded. The close contact bonding portion 416 is formed in the same shape as the step area generated by bonding the 1 st tank 130 and the 1 st header plate 110.

An inflow port 431 for the movement of the refrigerant is formed in the center of the inflow coupling protrusion 430, and is coupled to the inflow channel 510 provided in the shunt tube 500 so as to protrude 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 outflow port 451 through which the refrigerant flows out is formed in the center of the outflow coupling projection 450, and is coupled to the outflow channel 530 provided in the shunt tube 500, so as to project outward when coupled to the 1 st header tank 100.

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

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 inner side of the inflow coupling protrusion 430 to be coupled, and the outflow channel protrusion 531 is inserted into the outflow coupling protrusion 450 to be coupled. 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 areas different from each other. The inflow channel 510 may have a smaller area than the outflow channel 530. The cross-sections 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 138mm ² In this case, the inflow channel 510 may have a length of 28 to 38mm ² Is a part of the area of the substrate.

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 inflow refrigerant smoothly flows.

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. The following description will be focused on the coupling structure of the inflow coupling protrusion 430 and the inflow channel 510.

The inflow channel protruding portion 511 is inserted into the inner side of the inflow coupling protruding portion 430 to be coupled. 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 channel protruding portion 511 is set to be in the range of 3.8 to 4.2mm, thereby securing assembly strength and maximizing space efficiency.

The end of the inner side surface of the inflow coupling protrusion 430 is provided with a curved surface or inclined. This can facilitate the coupling of the inflow channel protruding portion 511.

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

In the case where the coupling protrusion 512 is provided at the end of the inflow channel protrusion 511, the coupling protrusion 512 is supported by the inner sidewall of the inflow coupling protrusion 430. In addition, in the case where 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 side surface of the inflow coupling protrusion 430. The coupling groove 433 is formed in a shape corresponding to the coupling protrusion 512, and may be deformed into various shapes.

Fig. 16 is a view showing a structure in which the throttle 800 is coupled to the header tank 200 of fig. 1 at the 2 nd, and fig. 17 is a sectional view of the throttle 800 which is a constituent element of fig. 16.

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

The basic structure of the throttle 800 is a 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 portion 416 for sealing the outside.

An orifice 810 is disposed in a central region of the orifice 800 to regulate the flow of the refrigerant. The restriction 800 prevents the refrigerant from moving toward the end, increasing the refrigerant distribution efficiency. The throttle 800 is disposed at a position spaced apart from the end of the flow path (based on the flow of the flow path) of the 2 nd header tank 200. As an example, the throttle 800 is disposed at a distance of 55 to 70mm from one side of the 2 nd header tank 200.

The orifice 810 may be formed with a size of 10 to 20% with respect to the entire area of the orifice 800. The shape of the orifice 810 is not limited, and is preferably arranged at the center of the area of the orifice 800.

The 3 rd fixing portion 820 and the 4 th fixing portion 830 for fixing the throttle 800 are provided in the throttle 800.

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

The 4 th fixing portion 830 is inserted into the 2 nd orifice 231 formed in the 2 nd case 230, and the 2 nd orifice 231 is disposed in the 2 nd case 230 so as to span the space divided by the 2 nd partition wall 250.

* The 4 th fixing portion 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 portion 830 is formed in a hook structure.

The throttle 800 is applied with a bilateral symmetry structure and can be shared 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 a baffle 300, which is a structural element of fig. 1.

Referring to fig. 18, a baffle 300 is provided inside the 1 st header tank 100 or the 2 nd header tank 200 to regulate the flow of refrigerant. The baffle 300 is formed in a plate shape blocking the flow of the refrigerant in the length direction of the 1 st header tank 100 or the 2 nd header tank 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, into which the 1 st partition wall 150 is inserted, and a recess portion insertion portion 310 that is in close contact with and engages with the recess portion 131 formed in the 1 st housing 130 is disposed on the opposite side of the 1 st partition wall insertion groove 320.

The baffle 300 has a structure that is closely coupled to the inner 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 view 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 on one side of the core 900 composed of the pipe 910 and the fin 930. The 1 st endplate 600 is disposed on the opposite side of the side to which the shunt 500 is coupled.

The 1 st end plate 600 has a plurality of 1 st fixing projections 610 at both side ends thereof, the 1 st fixing projections 610 are inserted into 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 projections 610.

The arrangement of the 1 st fixing protrusion 610 and the 1 st inclined portion 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 portion 620 coupled to the 2 nd header tank 200.

As an example, the 1 st fixing protrusion 610 coupled to the 1 st header tank 100 is provided with the 1 st inclined portion 620 on the same side. The 1 st inclined portion 620 is arranged to have the same inclination as the 1 st header plate 110. Further, the 1 st fixing protrusion 610 coupled to the 2 nd header tank 200 is provided with the 1 st inclined portion 620 at the opposite side to each other. Thereby performing the function of a stopper while preventing erroneous assembly when assembling the 1 st endplate 600.

The 1 st fixing protrusion 610 is vertically coupled with the 1 st header plate 110. At this time, the position of the 1 st fixing protrusion 610 is disposed outside the end cap plate 410, whereby leakage due to poor welding occurring at the time of brazing can be prevented.

The 1 st end plate 600 increases the supporting force by using a plurality of bent structures. The bending structure is formed as a bending structure or a structure with a region trapped therein.

The 1 st end plate 600 includes a 1 st outer bent portion 640 at each of the 1 st center bent portion 630 and both side ends of the 1 st center bent portion 630, and at least one 1 st additional bent portion between the 1 st center bent portion 630 and the 1 st outer bent portion 640.

The 1 st central curved portion 630 may have a lower height than the 1 st outer curved portions 640. The 1 st outer bending part 640 is provided at both sides of the 1 st center bending part 630 and can be bent at an angle of 90 degrees.

As an example, in the case where 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 endplate 700 supports the core 900 on the opposite side of the 1 st endplate 600. In order to secure a space for coupling the shunt 500, the 2 nd endplate 700 has a structure in which one region of the center 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 structure as the 1 st end plate 600.

The 2 nd endplate 700 includes 2 nd outer bends 740 provided on both sides of the 2 nd central bend 730 and the 2 nd central bend 730, respectively.

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

As an example, the 2 nd central bending portion 730 may have a height h of 13.0-13.5 mm ₂₁ And may include a planar area d of 10mm or more ₂₁ 。

In addition, the height h of the 2 nd outside bend 740 ₂₂ Can be greater than the height h of the 2 nd central bend 730 ₂₁ Low. As one example, the 2 nd outer bend 740 may have a height of 2.5 mm.

Fig. 23 is a cross-sectional view of the 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, a tube 910, which is a structural element of the core, 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 opposite to 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 the thickness h of the tubes 910 is reduced in the present invention ₃ While increasing the number of tubes 910. Thus, the area for exchanging heat by the refrigerant increases, and the efficiency of the heat exchanger is improved. The width of the tube and the height of the tube may have a ratio of 1:0.08 to 0.085.

As one example, the height h of tube 910 ₃ May have a height of 1.75 to 1.85 mm.

The tube 910 has a plurality of flow holes 913 disposed therein. In the present invention, the tube 910 is reduced in height, thereby increasing the number of flow holes 913. The number of holes is increased as compared to the structure of the conventional tube 910, thereby increasing the resistance of the fluid and thus improving the heat exchange performance.

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

Thickness t of upper wall 911 and lower wall 912 of tube 910 ₃₁ May be 0.22mm, the thickness t of the partition wall 914 ₃₂ May be 0.15mm. This saves costs compared with the conventional pipe structure.

The outermost walls 915 disposed on both sides of the tube 910 may be thicker than 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 1.9-2.1 times the thickness of the dividing wall 914. In the case where the thickness of the partition wall 914 is 0.15mm, the thickness of the outermost wall 915 may be 0.3mm.

Both side ends of the tube 910 may be provided with stops 916. This is to adjust the depth of insertion of the pipe 910 into the pipe coupling hole 113, and to facilitate insertion, the end portion may have an inclined or curved structure.

Referring to fig. 25, the baffle 300 is disposed between the embossments 115, 135 oppositely disposed in 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 plate. In such a structure, embossing is difficult to form in the portion where the baffle plate is inserted, and there is a problem that rigidity becomes weak in the region where embossing is not formed.

In order to solve such a problem, the present invention provides the embossing 115, 135 to supplement rigidity to the entire 1 st header plate 110 and 1 st tank 130, and fixes the embossing 115 and the embossing 135 with the baffle 300 interposed therebetween.

As an example, the barrier 300 is disposed by being in close contact with the inner side of the embossments 115, 135 by surface contact.

In this way, the conventional coupling groove is omitted, and the position of the baffle 300 can be adjusted as needed, so that the number and positions of various channels can be formed.

Fig. 26 is a diagram showing a structure of a 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 150, and the 2 nd header tank 200 has a 2-row structure by the 2 nd partition 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 column of the 1 st header tank 100 moves downward and then moves upward in the 1 st column of the 2 nd header tank 200. Then, the refrigerant moves from the 1 st row to the 2 nd row of the 1 st header tank 100, descends along the 2 nd row of the 2 nd header tank 200 after moving to the 2 nd row, ascends, passes through the 2 nd row of the 1 st header tank 100, and flows out.

At this time, the 2 nd header tank 200 is divided into 4 areas by the baffle plate disposed in the 1 st header tank 100, and the throttle 800 may be disposed in each of the 1 st and 2 nd columns of the 2 nd header tank 200.

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

In this case, the throttle 800 may be disposed at the central portions of the 2 nd and 4 th regions.

As an example, in the case where the heat exchanger has a 33-column structure (N), the baffle 300 is disposed in a region dividing 15 columns (N1) and 18 columns (N2) with reference to the inflow side of the refrigerant. At this time, the throttle bodies arranged in the 2 nd region are arranged so as to divide 9 rows (N21) and 9 rows (N22), and the throttle bodies arranged in the 4 th region are arranged at positions to divide 7 rows (N11) and 8 rows (N12).

In the case where the heat exchanger has a 37-column structure (N), the baffle 300 is disposed in a region that divides 18 columns (N1) and 19 columns (N2) with reference to the inflow side of the refrigerant. At this time, the throttle arranged in the 2 nd region is arranged in the region dividing 10 columns (N21) and 9 columns (N22), and the throttle arranged in the 4 th region is arranged in the region dividing 9 columns (N11) and 9 columns (N12).

The embodiments of the present invention have been described above in detail with reference to the accompanying drawings.

The above description is merely illustrative of the technical idea of the present invention, and various modifications, alterations and substitutions can be made by those skilled in the art without departing from the essential characteristics of the present invention. Accordingly, the embodiments and drawings disclosed in the present invention are not limited to the technical idea of the present invention, but are described to illustrate 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 following claims, and all technical ideas within the same scope as the scope of the present invention are included in the scope of the claims.

(symbol description) 100: header 1, 110: 1 st header plate, 111: end cap 2 fixing hole, 113: tube coupling holes, 115, 135: embossing, 130: 1 st box, 131: recessed portion, 133: end cap 1 fixing hole, 150: 1 st partition, 151: main communication hole, 153: auxiliary communication hole, 200: header tank 2, 210: header plate 2, 211: 1 st orifice, 230: 2 nd box, 231: 2 nd orifice, 250: partition 2, 300: baffle, 400: end cap, 410: end cover plate, 411: 1 st fixing portion, 412: confusion prevention unit, 413: 2 nd fixing portion, 415: insertion slot, 416: cling to the joint, 430: inflow coupling projection, 431: inflow port, 433: coupling groove portion, 450: outflow binding protrusion 451: outflow port, 500: shunt tube, 510: inflow channel, 511: inflow channel protruding portion, 512: coupling protrusion, 530: outflow channel, 531: outflow channel protruding part, 600: end plate 1, 610: 1 st fixing protrusion, 620: 1 st incline portion, 630: 1 st center bend, 640: 1 st outer bend, 700: end plate 2, 710: 2 nd fixing projection, 720: 2 nd inclined portion, 730: center bend 2, 740: 2 nd outer bend, 800: throttling element, 810: orifice, 820: 3 rd fixing portion, 830: 4 th fixing portion 831: 4 th fixed slot, 900: core, 910: tube, 911: upper wall, 912: lower wall, 913: flow holes, 914: dividing wall, 915: outermost wall, 916: stop, 930: and (5) a fin.

Claims

1. A heat exchanger, comprising: a 1 st header tank and a 2 nd header tank disposed at a distance from each other in the height direction; and a core part which is arranged between the 1 st header tank and the 2 nd header tank and is provided with a plurality of tubes and fins,

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

a shunt tube having an inflow channel and an outflow channel, which are provided with different sizes, is connected to the outside of the 1 st header tank,

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

an end cap is connected to the end of the 1 st header tank,

the end cap includes an end cap plate,

the end cap plate is provided with a 1 st fixing part for fixing with the 1 st header tank,

the first fixing part 1 has a confusion preventing part for preventing confusion of the inserting direction, the confusion preventing part is formed in a step manner,

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

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

the 1 st partition is inserted into the insertion groove,

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,

the end cover plate has a pair of 2 nd fixing portions on a surface thereof contacting the 1 st header plate.

2. A heat exchanger according to claim 1 wherein,

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

3. A heat exchanger according to claim 1 wherein,

the shunt tube is provided with an inflow channel protruding part and an outflow channel protruding part,

the inflow channel protruding portion is inserted into the inner side of the inflow coupling protruding portion and coupled thereto, and the outflow channel protruding portion is inserted into the inner side of the outflow coupling protruding portion.

4. A heat exchanger according to claim 3 wherein,

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

5. A heat exchanger according to claim 3 wherein,

the inflow channel protruding portion and the outflow channel protruding portion are provided with coupling protrusions,

the inflow coupling protrusion and the outflow coupling protrusion are provided with coupling groove portions,

the coupling protrusion is inserted into the coupling groove to be coupled.

6. A heat exchanger according to claim 1 wherein,

the 1 st manifold plate is inclined with respect to the center portion, and the inclination has a bilateral symmetry.

7. The heat exchanger of claim 6, wherein the heat exchanger is configured to heat the heat exchanger,

the ratio of the maximum height of the 1 st header tank to the height of the region where the 1 st header plate and the 1 st tank are welded is 1:0.115 to 0.125.

8. The heat exchanger of claim 6, wherein the heat exchanger is configured to heat the heat exchanger,

the end portions of the 1 st end plate and the 2 nd end plate are respectively provided with a plurality of 1 st fixing protrusions and a plurality of 2 nd fixing protrusions,

the 1 st inclined portion is provided on the side surface of the 1 st fixing projection, and the 2 nd inclined portion is provided on the side surface of the 2 nd fixing projection.

9. The heat exchanger of claim 8, wherein the heat exchanger is configured to heat the heat exchanger,

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

10. The heat exchanger of claim 6, wherein the heat exchanger is configured to heat the heat exchanger,

the tilt is formed at 4 to 6 degrees.

11. A heat exchanger according to claim 1 wherein,

the 1 st header plate has a plurality of tube coupling holes, and the embossing is arranged between the plurality of tube coupling holes.

12. The heat exchanger of claim 11, wherein the heat exchanger is configured to heat the heat exchanger,

the 1 st tank is provided with an embossed pattern opposed to the embossed pattern formed in the 1 st header plate.

13. The heat exchanger of claim 12, wherein the heat exchanger is configured to heat the heat exchanger,

a baffle plate forming a flow path is arranged between the embossments arranged in a vertically opposite manner.