KR101427430B1 - Heat exchanger for vehicle - Google Patents

Abstract

The present invention relates to a heat exchanger for a vehicle having an improved heat exchange ratio of a heat exchanger by fitting a ratio of an internal heat exchange area and an external heat exchange area of the heat exchanger core to each other and arranged in parallel in the air flow direction, A core comprising a plurality of tubes flowing and a pin interposed between adjacent tubes; (A _in ) of the core and an inner heat exchange area (A _in ) of the core (113), the inner heat exchanging area (A _in ) of the core being located above and below the core and communicating with the tube, (A _out / A _in ) of the outer heat exchanging area (A _out ) of the outer heat exchanger is 1.70 to 2.23.

Heat exchanger, heat exchange area ratio, heat radiation performance

Description

[0001] Heat exchanger for vehicle [

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicular heat exchanger, and more particularly, to a vehicular heat exchanger in which a heat exchange rate of a heat exchanger is improved by adapting a ratio of an internal heat exchange area and an external heat exchange area of a core of the heat exchanger.

Usually, the heat exchanger is provided with a passage through which a heat exchange medium such as cooling water or a refrigerant can flow, thereby enabling the medium to perform heat exchange with the outside air while flowing through the passage. The vehicle usually has a radiator for cooling the engine, a heater core for air conditioning in the vehicle interior, and a heat exchanger such as an evaporator. The heat exchanger has been developed in various ways according to the kind of the refrigerant used as the heat exchange medium and the internal pressure generated in the heat exchanger.

1 is a schematic perspective view showing an example of a conventional vehicle heat exchanger.

Referring to the drawings, a vehicle heat exchanger 11 is formed by laminating a plate 12 having a concave-convex portion of a predetermined shape, and a radiating fin 14 is disposed therebetween. The plate 12 may be formed as an uneven surface having a predetermined shape on an entirely flat aluminum plate material so that a channel of the heat exchange medium may be formed therein when the pair of plates are brazed in mutually facing states .

At the upper and lower ends of the plate 12, fluid passages 15 formed by deforming the plate are formed. An inflow pipe 16 for connecting the supply pipe of the heat exchange medium to the fluid passages 15 and an outflow pipe 17 for connecting the outflow pipe are disposed.

The heat exchanger 11 formed as described above is configured to circulate the air between the plates 12 until the heat exchange medium supplied through the inlet pipe 16 circulates through the flow path between the plates 12 and flows out through the outflow pipe 17 And the heat dissipation fins 14 serve to assist the heat exchange operation.

The heat exchanger 11 shown in Fig. 1 has a core width W, a core height h, and a thickness t. At this time, the air flows in the direction indicated by A.

Since the heat exchange of the vehicle heat exchanger is sequentially performed by the path of air → heat exchanger → heat exchange medium (coolant), the amount of heat exchange between the air and the heat exchanger and the heat exchange amount between the heat exchanger and the heat exchange medium Are the same.

The amount of heat exchange between the air and the heat exchange medium and the heat exchanger, that is, the heat exchange amount in the heat exchanger is referred to as the heat radiation amount of the heat exchanger.

The heat radiation amount Q of the heat exchanger is calculated as shown in Equation (1).

[Equation 1]

Q = U _Refrigerant A _Refrigerant ΔT _Refrigerant = U _Air A _Air ΔT _Air

(Q: heat release amount, U _refrigerant: overall heat transfer coefficient of the refrigerant, A _refrigerant: refrigerant-side heat transfer area, ΔT _refrigerant: inlet and outlet of the coolant temperature difference, U _air: overall heat transfer coefficient of the air, A _air: air-side heat transfer area, ΔT _air: Air inlet / outlet temperature difference)

As can be seen from the above equation, since the heat radiation amount of the heat exchanger is proportional to the heat exchange area A _refrigerant and the _air A, it is preferable to increase the A _refrigerant and the A _air to increase the heat radiation amount of the heat exchanger.

However, the vehicle heat exchanger is limited mounting space, and as shown in FIG. 2, the refrigerant-side heat transfer area (A _refrigerant) of the internal heat transfer area (A _in) and the air-side heat transfer area (A _air) of the outer heat exchange surface area (A _out is in inverse proportion to the structure, there is a limit in increasing the internal heat exchange area (A _in ) and the external heat exchange area (A _out ) uniformly to improve the heat radiation performance.

Accordingly, when designing the heat exchanger in consideration of the space in which the vehicle is mounted, heat exchange efficiency of the heat exchanger is lowered.

It is an object of the present invention to provide a heat exchanger for a vehicle having improved heat transfer performance by improving the relationship between the inner heat exchange surface area and the external heat exchange area.

According to an aspect of the present invention, there is provided an air conditioning system comprising: a core including a plurality of tubes arranged in parallel to each other in parallel to an air flow direction and having a heat exchange medium flowing therein; And a main tank which is located above and below the core and communicates with the tube and has an inlet pipe and an outlet pipe through which a heat exchange medium flows in and out, and the inside of the core 113 determined by the following equation (2) A ratio A _out / A _{in of the} heat exchange area A _in and an outer heat exchange area A _out of the core 113 is 1.70 to 2.23.

&Quot; (2) "

Internal heat exchange area (A _in ) = number of tubes × 4 × tube flow area × core height (H _core ) / hydraulic diameter of _tube (Dh _tube )

An external heat transfer area (A _out) = fin height (H _fin) × pinpok (W _fin) × core height (H _core) × number of pins / fin pitch (P _fin) of

Here, the hydraulic diameter (Dh _tube ) of the _tube = 4 占 퐉 area / reception length, where the channel area means the channel cross-sectional area of the tube, and the reception length means the circumferential length of the channel.

Preferably, the internal heat exchange area (A _in ) is 1.35 cm 2 to 1.6 cm 2, and the external heat exchange area (A _out ) is 2.6 cm 2 to 3.0 cm 2.

The pin 111 has 31 to 34 pins and the pin 112 has 32 to 35 pins. The pin width is 35 mm. The core has an H _core of 233 mm and a hydraulic diameter Dh _tube . The height of the _fin (H _fin ) is preferably 5.6 mm to 7.0 mm, and the FPDM is preferably 64 to 84 mm.

According to the present invention as described above, it is possible to provide a vehicle heat exchanger having a limited space for installation and a high heat dissipation performance by setting the ratio of the internal heat exchange area and the external heat exchange area to 1.70 to 2.23.

Further, the present invention has an advantage that the design of the heat exchanger having improved heat dissipation performance can be facilitated by providing the optimum ratio of the internal heat exchange area and the external heat exchange area for the heat dissipation performance and the specification of the tube and the fin.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. Prior to this, terms and words used in the present specification and claims should not be construed as limited to ordinary or dictionary terms, and the inventor should appropriately interpret the concepts of the terms appropriately It should be interpreted in accordance with the meaning and concept consistent with the technical idea of the present invention based on the principle that it can be defined.

Therefore, the embodiments described in the present specification and the configurations shown in the drawings are merely the most preferred embodiments of the present invention and are not intended to represent all of the technical ideas of the present invention. Therefore, various equivalents It should be understood that water and variations may be present.

FIG. 3 is a perspective view of a vehicle heat exchanger according to an embodiment of the present invention, FIG. 4 is a partially cutaway perspective view showing a tube and a pin of a vehicle heat exchanger shown in FIG. Sectional view, and Fig. 6 is a graph relating heat dissipation performance of the vehicle heat exchanger shown in Fig.

3 and 4, the vehicle heat exchanger according to the embodiment of the present invention includes a core 113 composed of a tube 111 and a fin 112, and a main tank 114.

31 to 34 of the tubes 111 are arranged in parallel in the air flow direction, and the refrigerant flows into the tubes.

And a pin 112 is formed between the tube and the neighboring tube. In this embodiment, the pin 112 is a Louver fin, and 32 to 35 pins are formed.

Wherein the tube has a height (H _tube ) of 1.4 mm to 3.0 mm, a _fin width (W _fin ) of 35 mm, a fin pitch (P _fin ) of 0.74 mm, (W _core ) is 273 mm to 280 mm, and the core (H _core ) is 233 mm.

The main tank 114 is positioned to communicate with upper and lower sides of the tube, and an outflow conduit 117 and an inlet conduit 118 are formed at one side.

The refrigerant flows into the main tank 114 through the inlet pipe 118, circulates through the tube through the tube, exchanges heat with the heat exchanger, and then flows out to the outside through the outlet pipe 117.

On the other hand, the air introduced into the core 113 passes through the core 113 and exchanges heat with the tube 111 and the fin 112.

In this case, the heat exchange area of the heat exchanger is an internal heat exchange area (A _in ) which is a refrigerant heat exchange area and an external heat exchange area (A _out ) which is an air side heat exchange area, and the heat radiation performance of the heat exchanger is determined according to these areas .

The relationship between the internal heat exchange area and the external heat exchange area and the heat radiation amount of the heat exchanger according to the embodiment of the present invention will be described below.

First, the internal heat exchange area (A _in ) and the external heat exchange area (A _out ) of the heat exchanger of this embodiment are calculated as shown in Equation (2).

&Quot; (2) "

Internal heat exchange area (A _in ) = number of tubes × 4 × tube flow area × core height (H _core ) / hydraulic diameter of _tube (Dh _tube )

An external heat transfer area (A _out) = fin height (H _fin) × pinpok (W _fin) × core height (H _core) × number of pins / fin pitch (P _fin) of

Here, the hydraulic diameter (Dh _tube ) of the _tube is calculated as follows.

Hydraulic diameter of the _tube (Dh _tube ) = 4 占 퐉 area / reception length

Here, the channel area refers to the cross-sectional area of the channel 120 of the tube, which is visible in the sectional view of the tube shown in FIG. 5, and the reception length is equal to the circumferential length of the channel 120 shown in FIG.

Meanwhile, since the heat radiation amount of the heat exchanger is calculated by Equation (1), the heat radiation performance of the heat exchanger depends on the internal heat exchange area (A _{in )} and the external heat exchange area (A _out ). Since the internal heat exchange area A _in is inversely proportional to the external heat exchange area A _out and the air and refrigerant have different heat transfer coefficients, the area ratio of the internal heat exchange area and external heat exchange area A _out / A _in ) can be appropriately determined to achieve the maximum heat dissipation performance.

In this embodiment, the ratio (A _out / A _in ) of the internal heat exchange area (A _in ) of the core (13) to the external heat exchange area (A _out ) of the core of the heat exchanger for achieving the maximum heat radiation performance is 1.70 To 2.23.

6 is a graph showing the change in the amount of heat radiation according to the ratio of the internal heat exchange area and the external heat exchange area, and FIG. 6 is a graph showing changes in the amount of heat radiation according to the ratio of the internal heat exchange area and the external heat exchange area It is a graph.

[Table 1]

No Internal heat exchange area External heat exchange area Outside / inside Amount of heat radiation [㎠] [㎠] One 1.49 2.83 1.90 4643 2 1.37 2.91 2.12 4642 3 1.26 2.67 2.12 4639 4 1.37 2.91 2.12 4659

In this experimental example, the tube height (H _tube ) was 1.4 to 3.0 mm, the hydraulic diameter (Dh _tube ) was 0.97 to 1.63 mm, the _fin height (H _fin ) was 5.6 mm to 7.0 mm, FPDM Meter) is 64-84. Here, the FPDM means the number of the mountains of the pin or the number of the fins which enter within 10 cm as shown in FIG.

As shown in Table 1 and FIG. 6, the number of tubes of the heat exchanger of this experimental example was 31 to 34, the flow area was 21.9 to 23.7 mm 2, the hydraulic diameter (Dh _tube ) was 1.26 to 1.49, _{Wherein the fin} width (W _fin ) is 35 mm, the fin pitch (P _fin ) is 0.74 mm, the number of fins is 32 to 35, the internal heat exchange area is 1.35 cm 2 to 1.6 cm 2, To 3.0 cm < 2 >

The maximum heat dissipation performance (Max) when the internal heat exchange area and the external heat exchange area ratio of the heat exchanger of the present experimental example is approximately 2.0 and the maximum heat dissipation amount (Max) when the internal heat exchange area and the external heat exchange area ratio is 1.70 to 2.23 ) Of 99.5% (0.995Max) or more.

That is, according to the present invention, it is possible to stably provide a heat exchanger satisfying the condition that the heat radiation amount is 99.5% of the maximum heat radiation amount, by setting the area ratio of the internal heat exchange area and the external heat exchange area of the heat exchanger to 1.70 to 2.23.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments. It will be understood that various modifications and changes may be made without departing from the scope of the appended claims.

1 is a perspective view showing an example of a conventional vehicle heat exchanger,

2 is a graph showing a relationship between an internal heat exchange area and an external heat exchange area of a general vehicle heat exchanger,

3 is a perspective view of a vehicle heat exchanger according to an embodiment of the present invention,

FIG. 4 is a partially cutaway perspective view showing the tube and the pin of the vehicle heat exchanger shown in FIG. 3,

5 is a sectional view of the tube of the vehicle heat exchanger shown in Fig. 3,

6 is a graph relating heat dissipation performance of the vehicle heat exchanger shown in Fig.

BRIEF DESCRIPTION OF THE DRAWINGS FIG.

111: tube 112: pin

113: core 114: main tank

117: Outflow conduit 118: Inflow conduit

Claims (3)

A core (113) arranged in parallel to the air flow direction and including a plurality of tubes (111) through which the heat exchange medium flows, and pins (112) interposed between the adjacent tubes (111); And a main tank (114) located above and below the core (113) and communicating with the tube (111) and having a flow channel (117) and an inlet channel (118) In the group, (A _out / A _in ) of the internal heat exchange area (A _in ) of the core (113) and the external heat exchange area (A _out ) of the core (113) determined by the following formula (2) is 1.70 to 2.23 And the second heat exchanger is a heat exchanger. Internal heat exchange area (A _in ) = number of tubes × 4 × tube flow area × core height (H _core ) / hydraulic diameter of _tube (Dh _tube ) An external heat transfer area (A _out) = fin height (H _fin) × pinpok (W _fin) × core height (H _core) × number of pins / fin pitch (P _fin) of Here, the hydraulic diameter (Dh _tube ) of the _tube = 4 × flow area / reception length, and the flow area refers to the cross-sectional area of the flow path of the tube, and the reception length means the circumferential length of the flow path. The method according to claim 1, Wherein the internal heat exchange area (A _in ) is 1.35 cm 2 to 1.6 cm 2, and the external heat exchange area (A _out ) is 2.6 cm 2 to 3.0 cm 2. The method according to claim 1, The tube 111 is 31 to 34, wherein the pin (112) is 32 to 35, wherein the pin is 35㎜ width, height (H _core) of the core is 233mm, the hydraulic diameter (Dh _tube) is 0.97 mm to 1.63 mm, the height of the fin (Hfin) is 5.6 mm to 7.0 mm, and the FPDM is 64 to 84.

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