DE102017201081A1 - Pipe for a heat exchanger - Google Patents

Abstract

There is provided a pipe for a heat exchanger, and more particularly, a pipe for a heat exchanger which forms a channel of a heat exchange medium and includes a plurality of inner holes having inner spaces separated in a width direction by a plurality of inner walls extending in a longitudinal direction in that a thickness is formed on outer walls of certain portions at both ends in the width direction of the pipe to be thicker than that of the remaining portions, thereby improving heat exchange performance and preventing corrosion.

Description

TECHNICAL AREA

The following disclosure relates to a tube for a heat exchanger and, more particularly, to a tube for a heat exchanger forming a channel for a heat exchange medium and having a plurality of inner holes having inner spaces separated in a width direction by a plurality of inner walls extending in a width direction Extend longitudinal direction in which a thickness of the outer walls are formed in certain areas at both ends in the width direction of the tube so that they are thicker than the remaining areas, whereby a heat exchanger performance is improved and corrosion is prevented.

BACKGROUND

A heat exchanger in a vehicle transfers heat from a high temperature fluid to a lower temperature fluid to heat or cool the fluid.

The heat transfer is carried out by conduction and Konvektionsphänomene. Conduction heat transfer is a phenomenon in which heat is transferred when a plurality of objects have different temperatures and come into contact with each other, which occurs in a portion of a temperature difference between the objects. Further, the heat transfer phenomenon is generated by convection by a gaseous or liquid fluid, and the fluid continuously contacts a heat transfer surface to exchange heat. Therefore, since a heat transfer amount is increased when fluid movement is active, heat transfer efficiency can be increased by forming a vortex in a flow path of the fluid.

The heat exchanger generally includes a pair of header tanks through which the heat exchange medium is introduced and discharged, and a pipe connecting the header tanks to allow the heat exchange medium to exchange heat while the heat exchange medium is flowing therein. 1 represents a typical heat exchanger of a fin type. The heat exchanger 10 includes: several tubes 40 having a heat exchange medium therein flowing and arranged in parallel in a row at regular intervals with a direction in which air blows; an inlet collection tank 20 containing the heat exchange medium which passes through an inlet to the plurality of tubes 40 is introduced, distributed; a discharge lamella 50 between the pipes 40 is inserted and a heat transfer surface with air between the pipes 40 flows, increases; and a drain collection tank 30 having the heat exchange medium contained in the tube 40 which is collected therein and discharges the collected heat exchange medium through an outlet.

There are various types of heat exchangers, such as a plate type or a pen tube type. In general, the heat exchanger of a fin type as described above is the most widely used one.

The heat transfer process of the heat exchanger of a fin tube type is as follows. A working fluid flows into one of the tanks 20 and in the distributor 30 and runs through a multi-stage pipe 40 , The multi-level pipe 40 , which receives heat from the working fluid, conducts the heat to the fins 50 between the pipes 40 are provided. At this time, while air from outside through the multiple fins 50 flows, the heat transfer is due to the convection phenomenon between the fins 50 and the introduced air.

As a patent for a heat exchanger of a fin tube type exists Korean Laid-Open Publication No. 10-2013-0016982 (Publication / Disclosure Date: 27.8.2014, Title: "Laminated Tube Heat Exchangers").

As in 1 As shown, the tube has a generally flat shape and an outer side thereof is soldered to a fin by a soldering system. At this time, in order to improve the performance of the heat exchanger, an inner duct of the pipe is formed in a square or circular shape, depending on the heat exchanger power requirements and an operating pressure of the system.

For a high-performance extrusion tube, it is necessary to increase a cross-sectional area over which a refrigerant can flow while an inner contact length of the refrigerant is increased. To achieve this, it is preferable to make the thickness of an inner wall and an outer wall thin.

However, it is preferable to make the thickness of the inner wall and the outer wall as thin as possible for their performance. However, since the thickness of the inner wall requires a pressure resistance performance together with an extrudability and a manufacturing performance, and the outer wall thickness, extrudability, manufacturing performance and corrosion resistance must be ensured, the pipe must be developed on the basis of a multilateral analysis.

[State of the art document]

[Patent Document]

• Korean Laid-Open Publication No. 10-2013-9016982 (Publication / publication date 27.8.2014, title: "finned tube heat exchanger")

PRESENTATION OF THE INVENTION

An embodiment of the present invention is directed to providing a tube for a heat exchanger that forms a heat exchange medium and includes a plurality of inner holes having inner spaces separated by a plurality of inner walls in a width direction and extending in a longitudinal direction in which a thickness of the outer walls of certain regions at both ends in the width direction of the tube is formed to be thicker than the remaining regions, thereby improving heat exchange performance and preventing corrosion.

In a general aspect is a tube 100 for a heat exchanger provided in plural and forming a passage for a heat exchange medium circulating in the heat exchanger and a plurality of inner holes 120 includes having internal spaces in a width direction through a plurality of inner walls 110 are separated, and extend in a longitudinal direction in which a thickness of outer walls lying at both ends in the width direction may be formed differently from that of the remaining portions.

The pipe 100 may be a first reinforcing section 132 in which a thickness of outer walls in regions lying on both surfaces in a thickness direction in the middle of regions lying in the widthwise direction at both ends is formed to be thicker than the remaining regions.

A thickness of the first reinforcing portion 132 may be in the interval of 0.2 to 0.25 mm and the thickness of the remaining portions may be in the interval of 0.18 to 0.23 mm.

The first reinforcement section 132 may be up to a length of 10 to 25% of a total length in the width direction of the tube at both ends 100 be educated.

When a width of the pipe is 100 N (8 mm ≦ N ≦ 20 mm), the number H _{num of} the inner holes 120 1.5 N ≤ H _num ≤ 3 N.

A thickness of the inner wall 110 can be at an interval of 0.1 to 0.15 mm and a width of the inner hole 120 may be in an interval of 0.25 to 0.5 mm.

One side or both sides of the tube 100 can the slat 200 that exist between adjacent pipes 100 in the thickness direction, contact, and may be flat in the width direction of the contact surface.

The pipe 100 and the slat 200 may be formed so that lengths of the contact surfaces are equal to each other.

A thickness T1 of surfaces lying at both ends in the width direction may be thicker than a thickness T2 of surfaces lying on both sides in the thickness direction.

The pipe 100 may be a second reinforcing section 140 in which the inner surfaces of surfaces lying at both ends in a width direction are formed protruding inward.

A protrusion height a2 of the second reinforcing portion 140 may be equal to or larger than distances a1 and a3 from each edge to both ends in the width direction of the second reinforcing portion 140 be.

The pipe 100 may be an extruded tube.

A hydraulic diameter may be in the interval of 0.4 to 0.65 mm.

An aspect ratio (cross-sectional area of inner hole / entire pipe surface) of a passage may be in an interval of 42 to 55%.

The pipe 100 can take a lead 150 which protrudes inwardly from inner surfaces from both sides in the thickness direction.

The lead 150 can also be on the inner wall 110 be educated.

BRIEF DESCRIPTION OF THE FIGURES

1 is a perspective view illustrating a typical heat exchanger.

2 FIG. 10 is a plan view illustrating a tube for a heat exchanger according to an exemplary embodiment of the present invention. FIG.

3 FIG. 11 is a plan view illustrating a pipe for a heat exchanger according to another exemplary embodiment of the present invention. FIG.

4 and 5 FIG. 16 is front elevational views illustrating a tube for a heat exchanger according to another exemplary embodiment of the present invention. FIG.

6 FIG. 12 is a plan view illustrating a state in which a fin is interposed between the tubes for a heat exchanger 3 is introduced.

7 FIG. 12 is a plan view illustrating a state in which a fin is interposed between the tubes for a heat exchanger 2 is introduced.

8th and 9 are enlarged plan views of a region in which a second reinforcing portion is formed, in the tube for a heat exchanger.

DETAILED DESCRIPTION OF THE EMBODIMENTS

Hereinafter, a tube for a heat exchanger according to exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

2 and 5 FIG. 11 is a plan view showing a tube for a heat exchanger according to various exemplary embodiments of the present invention; FIG. 6 FIG. 12 is a plan view illustrating a state in which a fin is interposed between the tubes for a heat exchanger 3 is inserted, 7 FIG. 12 is a plan view illustrating a state in which a fin is interposed between the tubes for a heat exchanger 2 is inserted and 8th and 9 FIG. 15 are enlarged views of a portion in which a second reinforcing portion is formed in the tube for a heat exchanger.

A pipe 100 for a heat exchanger according to an exemplary embodiment of the present invention is made by extrusion molding and is provided multiple times, so that a channel of a heat exchange medium circulating in the heat exchanger is formed and a plurality of inner holes 120 includes having internal spaces in a width direction through a plurality of inner walls 110 are separated and extend in a longitudinal direction and in particular a thickness of the outer walls of certain areas at both ends of the tube in the width direction of the tube is different from the remaining areas.

At this point, the tube includes 100 According to the exemplary embodiment of the present invention, a first reinforcing section 132 in that a thickness of outer walls of certain portions at both ends in the width direction is formed to be thicker than that of the remaining portions.

That is, as in 2 shown that the pipe 100 According to the exemplary embodiment of the present invention, a first reinforcing section 132 in which a thickness of the outer walls lying in both sides in a thickness direction is formed to be thicker at both ends in the width direction than portions of an outer wall thickness 131 an area that is located at a central part, in certain.

The area in which the first reinforcing section 132 is an area that most clearly comes in contact with the blowing wind, and is actually an area prone to corrosion due to corrosive matter entering in an airflow direction.

In the past, the outer wall was formed to be thicker over the entire area to prevent water loss due to such corrosion. In this case, a total weight of the pipe is increased and a cross-sectional area of the pipe in which a refrigerant can flow is reduced because the thickness of the outer wall is thick, thereby causing the problem in which a heat exchange performance decreases.

Therefore, according to the exemplary embodiment of the present invention, only the outer wall is 131 which is in the region most susceptible to corrosion, formed to be thick and the first reinforcing section 132 is formed at both ends in the width direction for simplification of the construction at the time of manufacturing.

That is, according to the exemplary embodiment of the present invention, the first reinforcing portion 132 is designed to prevent corrosion and the remaining areas are formed so that they have a minimum thickness of the outer wall 131 to ensure a heat exchanger performance. For this reason, through experiments, values for each part of the tube were established 100 optimized as described below.

The pipe 100 According to the exemplary embodiment of the present invention, a thickness Tr of the first reinforcing portion is designed 132 is in an interval of 0.2 to 0.25 mm, and a thickness To of the remaining portions is in an interval of 0.18 to 0.23 mm, and is based on the condition in which a thickness Tr of the first reinforcing portion 132 is formed to be thicker than the thickness To of the remaining areas.

As in 2 is the first reinforcing section 132 formed to a region in which about 3 inner holes 120 at both ends in the width direction of the pipe 100 lie, however, is the number of inner holes 120 not limited to it and can therefore be 2 or 4.

As described above, in the tube 100 To ensure the cross-sectional area over which the refrigerant flows, as well as to ensure the prevention effect of water leakage due to corrosion up to a certain level or beyond, it is preferable to have a length _having a width W _{hole of} the inner hole 120 and a thickness T _in the inner wall 110 corresponding to the area in which the first reinforcing section 132 is formed, and to obtain thicknesses of the two ends in the width direction of the tube at a certain level.

The following Table 1 shows the detailed example in which, when the width of the tube 12 is T, the thicknesses of both ends in the width direction, the thickness T _in the inner wall 110 , a width W _{hole of} the inner hole 120 and calculate the number A (descending) inner holes that depend on it. [Table 1] Width of the pipe Second reinforcement section Inner wall Width of the inner hole Number of inner holes 12T 0.4 0.10 0.30 28 0.6 0.15 0.50 16

Further, the following Table 2 shows an example of a length Lr of the first reinforcing section 132 and a ratio of the first reinforcing portion 132 to an entire width depending on the number of inner holes when the width of the tube 12 is T. [Table 2] Two inner holes + inner wall Three inner holes + inner wall length relationship length relationship 1.20 10.0 1.60 13.3 1.90 15.8 2.55 21.3

In consideration of the number of the inner holes, the thickness of the inner wall or the like as described above, the length Lr of the first reinforcing portion is 132 preferably at both ends each as much as a length of ten to 25% of the total length in the width direction of the tube 100 ,

However, the width of the tube is 100 generally designed to be 8 to 20mm.

According to the exemplary embodiment of the present invention, the overall size of the tube is maintained while the width of the tube 100 is maintained, however, the number of internal holes 120 increased and the thickness T _in the inner wall 110 is reduced, so that the pressure resistance performance can be achieved above a certain value.

More specifically, the relationship is the number of internal holes 120 that depends on the width of the pipe 100 depending on the following equation, when the pipe is 100 N mm, the number H _{num of} the inner holes may vary 120 1.5 N ≤ H _num ≤ 3 N.

At this point, the tube can 100 According to the exemplary embodiment of the present invention, the thickness T _in the inner wall 110 be formed so that it is 0.1 to 0.15 mm thin, and the width W _{hole of} the inner hole 120 may be in a range of 0.25 to 0.5 mm.

The following Table 3 shows an example of the number of inner holes 120 depending on the width of the tube 100 in the tube 100 having the above-described characteristics in which the number of internal holes 120 is not necessarily limited as in the following table, and therefore can be changed in the range of 1.5 N ≦ H _num ≦ 3 N without limitation.

At this point, it is preferable that a hydraulic diameter of the pipe 100 is equal to or less than 0.65 mm and a cross-sectional area (cross-sectional area of the inner hole / total pipe area) ratio of a passage is equal to or more than 42%.

The hydraulic diameter and passage area ratio are areas that can be difficult to reach through the existing pleated and extruded tubes and when the tube 100 According to the exemplary embodiment of the present invention, as a high-performance extrusion tube having the hydraulic diameter and the passage sectional area, and thus applied to a condenser, the heat exchange performance of the condenser and a coefficient of performance (COP) of the refrigeration cycle can be improved.

Here is the hydraulic diameter of the pipe 100 a hydraulic diameter Dh = 4 · Channel area / circumference for the channel divided by the inner wall 110 in the tube 100 out 2 in which the channel surface is the cross-sectional area of the inner hole of the tube 100 represents and the water contact length represents a circumferential length of the channel. [Table 3] 12 T-tube 16 T-tube Number of inner holes 23 30 Hydraulic diameter 0.54 0.58 Passage cross-sectional area ratio 48% 51%

In the above examples, if the width of the pipe 100 12 mm, the first reinforcement section can 132 be formed approximately from both ends to a region in which about three inner holes 120 and three inner walls 110 lie and if the width of the pipe 100 is changed, the area in which the first reinforcement section 132 is designed to be suitably adapted to meet the conditions described above.

As described above, the tube 100 According to the exemplary embodiment of the present invention, a predetermined number or more inner holes 120 on and minimizes the thickness of the inner wall 110 and the outer wall 131 a central part to sufficiently secure the cross-sectional area over which the refrigerant can flow, thereby improving the pressure resistance performance while maintaining the heat exchanging performance at a certain level or more at the same time.

As another example, as in 5 shown, the pipe can 100 projections 150 which protrude inward on an inner surface from both sides in the thickness direction. The lead 150 increases a contact area between the refrigerant and the pipe 100 , whereby the hydraulic diameter is increased and the heat exchange efficiency is improved.

At this point, the lead can 150 protruding on the inner surface from both sides in the thickness direction as in 5 shown, may be formed from the inner wall 110 stand out or may be trained several times.

Meanwhile, the lamella is 200 the heat exchanger between the pipes 100 is inserted, and thus the exchange between the heat exchange medium and the air is performed in the area which the pipe 100 contacted.

At this point, the heat transfer area increases because the contact area between the lamella 200 and the tube 100 increases and as a result, the larger the contact area between the lamella 200 and the tube 100 is, the better the heat exchanger performance.

For this purpose, the pipe 100 for a heat exchanger according to the exemplary embodiment of the present invention, be formed flat in the width direction of the surface containing the fin 200 contacted.

At this point, as in 7 shown, shows the tube 100 for a heat exchanger according to the exemplary embodiment of the present invention, a substantially rectangular cross section, in which it is preferred that each edge is minimally rounded so as to have a contact surface with tips of the fins 200 collapsing.

That is, given the length of the surfaces which the slats 200 Contact, the same ones are that the tube 100 a further increased heat transfer area and heat exchange performance compared to an existing pipe 100 has, which is rounded on the outside.

Further, as in 6 shown, the pipe can 100 for a heat exchanger of the present invention may be formed in a shape having circular roundings at both ends, but is not necessarily limited to a square or circular shape.

Furthermore, in the tube 100 a thickness T1 of the surfaces lying on both sides in the width direction may be equal to the thickness T2 of surfaces lying on both sides in the thickness direction, or as in FIG 8th shown, the thickness T1 of the surfaces which lie in the thickness direction on both sides, may be formed to be thicker than the thickness T2 of the surfaces lying on both sides in the thickness direction.

In particular, because the pipe 100 for a heat exchanger according to the present invention, the first reinforcing section 132 whose thickness of the outer walls at both ends in the width direction is formed to be thicker than the remaining portions even if the thickness T1 of the surface lying on both sides in the width direction is equal to the thickness T2 of the surfaces which is located on both sides in the thickness direction, is the tube 100 thicker than the existing pipe 100 whereby it has a certain degree of corrosion prevention function.

At this point is in the tube 100 the thickness T1 of the surfaces lying on both sides in the width direction is formed to be smaller than distances a1 and a3 of each of the outer edges to each of the inner edges.

8th Fig. 10 illustrates the example in which the thickness of the surfaces lying on both sides in the width direction is formed to be constantly thick, and 9 put the tube 100 that is a second reinforcing section 140 includes inner surfaces of the surfaces lying on both sides in the width direction, formed protruding inwardly.

At this point, it is preferable that a protruding height a2 of the second reinforcing portion 140 is equal to or greater than the distances a1 and a3, both ends of the second reinforcing portion 140 in the thickness direction of each edge of the pipe 100 and is designed so that it is at least 0.4 mm or more.

That's why the area that simply comes in contact with corrosive substances or foreign objects, while all the pipes 100 move, so formed that it is thicker than other areas, and therefore the pipe can 100 minimize the problem in which a water leak occurs due to the damage caused by corrosive substances or foreign objects, and contributes to an improvement in longevity.

To describe it again, according to the pipe 100 For a heat exchanger with the exemplary embodiments of the present invention, the thickness of the outer walls of certain areas at both ends of the width direction of the pipe 100 be designed to be thicker than the remaining area, whereby the longevity of the portion where the water loss is likely to occur due to the damage by corrosive substances or foreign objects is improved, and the remaining area may be formed to be thin is to secure the area of the area through which the coolant passes, whereby the heat exchange performance is kept at a predetermined level or higher.

In addition, according to the pipe 100 for a heat exchanger in accordance with the exemplary embodiments of the present invention, the thickness of the inner wall 110 and the number of inner holes 120 passing through the inner wall 110 can be optimized to meet the extrudability, manufacturing performance and pressure resistance performance.

In addition, according to the pipe 100 for a heat exchanger in accordance with the exemplary embodiments of the present invention, one or both sides of the tube come into contact with the fin 200 in the thickness direction and the surface from one end portion to the other end portion of the pipe 100 may be formed flat in the width direction of the contact surface to increase the heat transfer area further than that of the existing pipe 100 having outer curves, thereby improving the heat exchanger performance.

According to the pipe for a heat exchanger in accordance with the exemplary embodiments of the present invention, the thickness of the outer walls may be designed in certain regions at both ends in the width direction of the pipe to be thicker than the remaining area, thereby improving the durability of the section. where water loss due to damage by corrosive substances or foreign matters occurs is improved, and the remaining portions may be formed to be thin so as to secure the area of the area through which the coolant flows the heat exchanger performance is maintained at a certain level or beyond.

Moreover, according to the pipe for a heat exchanger in accordance with the exemplary embodiments of the present invention, the thickness of the inner wall and the number of inner holes formed by the inner wall can be optimized to the extrudability, the production performance and the pressure resistance performance to fulfill.

In addition, according to the tube for a heat exchanger according to the exemplary embodiments of the present invention, one or both sides of the tube come into contact with the fin in the thickness direction, and the surface from one end portion to the other end portion of the tube may be flat in the thickness direction Width direction of the contact surface may be formed to increase the heat transfer area further than in the existing tube having the outer rounding, whereby the heat exchange performance is improved.

The present invention is not limited to the above-mentioned embodiments but may be variously applied and variously modified by those skilled in the art to which this invention pertains without departing from the spirit of the present invention claimed in the claims. In particular, features of all embodiments and all claims can be combined with each other as long as they do not contradict each other.

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• KR 10-2013-0016982 [0007]
• KR 10-2013-9016982 [0011]

Claims (16)

A tube for a heat exchanger which is provided plural times to form a passage of a heat exchange medium circulating in the heat exchanger and includes a plurality of inner holes having inner spaces separated in a width direction by a plurality of inner walls and extending in a longitudinal direction wherein a thickness of outer walls of the regions lying at both ends in the width direction is different from that of the remaining regions. The pipe according to claim 1, wherein the pipe includes a first reinforcing portion in which a thickness of outer walls lying on both surfaces in a thickness direction between regions lying in the widthwise direction at both ends is formed to be thicker than the thickness the remaining areas. The pipe according to claim 2, wherein a thickness of the first reinforcing portion is in an interval of 0.2 to 0.25 mm, and the thickness of the remaining portions is in an interval of 0.18 to 0.23 mm. Pipe according to claim 2, wherein the first reinforcing section ( 132 ) at both ends each as long as 10 to 25% of an entire length in the width direction of the tube ( 100 ) is trained. The pipe according to claim 4, wherein when a width of the pipe is N (8 mm ≦ N ≦ 20 mm), the number H _{num of} the inner holes is 1.5 N ≦ H _num ≦ 3 N. The pipe according to claim 5, wherein a thickness of the inner wall is in an interval of 0.1 to 0.15 mm, and a width of the inner hole is in an interval of 0.25 to 0.5 mm. The pipe according to claim 2, wherein one side or both sides of the pipe contact a sipe interposed between the adjacent pipes in the thickness direction and formed flat in the width direction of the contact surface. Pipe according to claim 7, wherein the tube and the lamella are formed so that lengths of the contact surfaces are equal to each other. A pipe according to claim 7, wherein a thickness T1 of the surfaces lying at both ends in the width direction is thicker than a thickness T2 of surfaces lying on both sides in the thickness direction. The pipe according to claim 7, wherein the pipe includes a second reinforcing portion in which inner surfaces of surfaces lying at both ends in the width direction are formed inwardly projecting. The pipe according to claim 10, wherein a protruding height a2 of the second reinforcing portion is equal to or greater than distances a1 and a3 from each edge to both ends in the width direction of the second reinforcing portion. Pipe according to claim 7, wherein the pipe is an extruded pipe. A pipe according to claim 7, wherein a hydraulic diameter is in an interval of 0.4 to 0.65 mm. A pipe according to claim 7, wherein a cross section ratio (cross sectional area of an inner hole / entire pipe surface) of a passage is in a range of 42 to 55%. The pipe according to claim 1, wherein the pipe has a protrusion projecting inwardly on an inner surface from both sides in the thickness direction. The tube of claim 15, wherein the protrusion is further formed on the inner wall.

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