KR20170088605A - Exchanger - Google Patents

Exchanger Download PDF

Info

Publication number
KR20170088605A
KR20170088605A KR1020160008688A KR20160008688A KR20170088605A KR 20170088605 A KR20170088605 A KR 20170088605A KR 1020160008688 A KR1020160008688 A KR 1020160008688A KR 20160008688 A KR20160008688 A KR 20160008688A KR 20170088605 A KR20170088605 A KR 20170088605A
Authority
KR
South Korea
Prior art keywords
tube
louver
heat exchanger
width direction
thickness
Prior art date
Application number
KR1020160008688A
Other languages
Korean (ko)
Other versions
KR101977797B1 (en
Inventor
송준영
심호창
이선미
임홍영
Original Assignee
한온시스템 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to KR1020160008688A priority Critical patent/KR101977797B1/en
Publication of KR20170088605A publication Critical patent/KR20170088605A/en
Application granted granted Critical
Publication of KR101977797B1 publication Critical patent/KR101977797B1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128Fins with openings, e.g. louvered fins
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325Fins with openings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007Auxiliary supports for elements
    • F28F9/013Auxiliary supports for elements for tubes or tube-assemblies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/0202Header boxes having their inner space divided by partitions
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00Fins
    • F28F2215/08Fins with openings, e.g. louvers

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The present invention relates to a heat exchanger and, more specifically, relates to a heat exchanger which comprises: a tube having a plurality of inside holes of which an internal space is separated by a partition; and a pin having a plurality of louvers interposed between the tubes, and inclined at a predetermined angle for air to pass therethrough, wherein the louvers are arranged to correspond to the inside holes of the tube. Therefore, heat transmission performance between the tube and the louvers can be improved.

Description

Heat Exchanger {Exchanger}

The present invention relates to a heat exchanger, and more particularly to a heat exchanger including a tube including a plurality of inner holes into which an inner space is divided by a partition wall, a plurality of louvers interposed between the tubes, And a fin formed by arranging the louvers so as to correspond to the inner holes of the tubes, thereby improving the heat transfer performance between the tubes and the pin louvers.

In recent years, interest in environment and energy has increased in the automobile industry, and studies for improving fuel efficiency have been made. In particular, since it is necessary to satisfy the various regulations such as the pedestrian protection law and various consumer's desires, , Research and development for miniaturization and high performance are being carried out steadily.

The fin for the heat exchanger is a major component of the heat exchanger interposed between the adjacent tubes to increase the area of contact with the air to increase the heat exchange efficiency. Researches and developments have been continued to maximize the heat dissipation performance of such heat exchanger fins.

At this time, the fin is stacked up and down, and is used as a waveform. In order to maximize the heat exchange efficiency, air flows between the upper and lower layers of the fins to increase the heat exchanging area. In order to increase the heat exchange area, louvers in the form of scales are formed on the fins.

As a related art, a louver fin for a heat exchanger has been disclosed in Korean Patent No. 1225597 (entitled Louver Fin for Heat Exchanger).

A conventional louver fin for a vehicle heat exchanger is shown in Fig. In the heat exchanger for exchanging the inside circulating fluid and the outside air such as the evaporator, the condenser or the radiator of the automobile air conditioner, the tubes 120 are arranged between the tubes forming the circulating fluid passage, as shown in FIG. 1 (a) A louver fin 110 for a heat exchanger having a waveform structure for increasing the heat exchange efficiency between the two fluids is provided.

The louver fin 110 is in contact with the tube 120 through which the circulating fluid flows and performs heat exchange with the tube 120 and heat exchange with the air in contact with the surface of the tube 120 so that the heat exchange rate between the circulating fluid in the tube 120 and the air As the thermal conductivity is high and the specific surface area (specific surface area) is large, the heat exchange rate is increased.

Therefore, the louver fins 110 are generally made of a metal material having a high thermal conductivity and easy to be molded, such as aluminum, and in particular, as shown in Fig. 1 (b) It is manufactured in a thin plate structure with a waveform that can be maximized.

1 (b) and 1 (c), the incised portion is bent obliquely with respect to the direction of the air flow, Shaped louvers 113 for inducing air to be introduced into the louver fins 110 and passing the oblique faces 111 through the cut openings 112 are formed at regular intervals along the air flow direction .

In other words, the louver pins are formed to allow the air to escape through the louvers, so that the heat transfer efficiency is much higher than that of the louver-free fins because turbulence is generated in the air flow.

The heat exchange between the fin and the air is caused by the convective heat transfer. In the case of the convective heat transfer, the heat transfer is much better when the turbulence flow than by the laminar flow.

In more detail, a boundary layer is formed as shown in FIG. 2 in a portion where a fluid and a solid generally meet and flow starts. At the interface between the fluid and the solid, that is, at the surface of the solid, the flow velocity of the fluid is always zero. The slope of the flow velocity gradually increases from the solid surface to the vertical direction. Theoretically, Position, the fluid flows at a flow rate when there is no solid.

At this time, as shown in Fig. 2, it is the boundary layer which goes up from the solid surface in the vertical direction to the points near the original flow rate.

In this boundary layer, heat transfer occurs due to diffusion rather than convection, that is, conduction of the fluid. In the fluid, heat transfer due to convection occurs much better than heat transfer by conduction. Therefore, in order to increase heat transfer efficiency, do. The louver fin is a structure provided to prevent the formation of such a boundary layer.

3 is an analysis of the heat distribution of the air passing through the louver fins of the condenser. In this case, the air is gradually heated through the louver fins located at the inlet side from the louver fins located at the inlet side in the flow direction Able to know.

As described above, the louver fins have a certain angle and are inclined from forward to backward in the direction of air flow. The air starts heat transfer through contact with the louvers at the front of the louver fins, To the surface of the louver. In this case, the heat transfer coefficient increases due to the turbulence of air, but the turbulence is not sufficiently generated in the flow toward the rear end of the louver, and the boundary layer development can not be sufficiently suppressed, so that the heat exchange efficiency at the rear end of the louver becomes lower than the front end.

In other words, the heat exchange efficiency in the louver fin as shown in Fig. 3 can be seen that the front end of the louver is best when viewed from each louver.

For reference, there are two types of heat exchange in the heat exchange between refrigerant and air.

Q total = Q1 (refrigerant → tube → air) + Q2 (refrigerant → tube → pin → air)

At this time, the heat transfer efficiency in Q2 is much higher than Q1, and in Q2 heat transfer, the majority of the heat exchange occurs in the louver of the pin.

However, as described above, simply forming a louver on the pin can not sufficiently increase the heat exchange efficiency. In order to actually obtain the effect of increasing the heat exchange efficiency, it is necessary to suggest a way to optimize the arrangement structure of the louver and the tube by considering the heat transfer characteristic such as Q2 and the heat exchange efficiency characteristic in the louver fin.

Korean Registered Patent No. 1225597 (Registered on Apr. 17, 201, entitled: Louver Fin for Heat Exchanger)

SUMMARY OF THE INVENTION The present invention has been conceived to solve the problems as described above, and it is an object of the present invention to provide a tube having a plurality of inner holes in which an inner space is separated by a partition wall, A plurality of louvers for passing air therethrough are formed and the louvers are formed so as to correspond to the inner holes of the tubes, thereby improving the heat transfer performance between the tubes and the pin louvers.

The heat exchanger of the present invention comprises a pair of header tanks spaced apart from each other by a predetermined distance; A tube having both ends fixed to the header tank to form a flow path of the heat exchange medium and having a plurality of inner holes 220 separated from each other in the width direction by a plurality of partition walls 210 extending in the longitudinal direction, And a plurality of louvers 110 interposed between the tubes 200 so as to allow air to pass through the louvers 110. The louvers 110 are installed in the inner holes 220 of the tube 200, A pin 100 disposed to correspond to the pin 100; And the second electrode is formed.

The heat exchanger may have a louver 110 pitch Lp of the fin 100 and a thickness of one partition wall 210 when the a number of the louvers 110 correspond to n inner holes 220, T web , and the width T hole of the inner hole 220 can satisfy the following expression (1).

nT web + nT hole = aLp (1)

In addition, the heat exchanger may be formed so that one side inner surface in the width direction of the inner hole 220 and one side edge of the louver 110 are located on the same line.

In addition, the tube 200 is formed such that one side or both sides of the tube 200 are in contact with the fin 100 interposed between the neighboring tubes 200, and the side from the one side to the other side in the width direction of the contacting side is flat .

The tubes 200 and the pins 100 may be formed to have the same length of contact surfaces.

In addition, the thickness (T1) of the tube 200 located on both sides in the width direction of the tube 200 may be thicker than the thickness T2 of the surface located on both sides in the thickness direction.

In addition, the tube 200 may include a rigid beam-guiding portion 230 whose inner surfaces protrude inward from the surfaces located on both sides in the width direction.

The tube 200 may be formed such that the projection height a2 of the rigid beam guiding portion 230 is greater than or equal to the distances a1 and a3 extending from the respective corners to both ends of the rigid beam guiding portion 230 in the thickness direction have.

In addition, the tube 200 may be formed in a round shape at both ends in the width direction.

In addition, the tube 200 may be formed such that the thickness A of both side surfaces in the width direction is larger than the thickness B of both side surfaces in the thickness direction.

The heat exchanger of the present invention includes a tube including a plurality of inner holes in which an inner space is separated by a partition wall, a plurality of louvers interposed between the tubes to be sloped at a predetermined angle to pass air therethrough, The heat transfer performance between the tube and the pin louver is improved by including the fin disposed to correspond to the inner hole of the tube.

That is, the heat exchanger of the present invention is disposed such that the front end portion of the louver having the best heat exchange efficiency is located inside the inner hole of the tube, which is a region where the refrigerant actually flows, thereby improving heat exchange efficiency.

In the heat exchanger of the present invention, one side or both sides of the tube are contacted in the thickness direction of the tube and the tubes interposed between adjacent tubes, and the surface from one side to the other side in the width direction of the contacting side is flat, The heat transfer area is increased compared with a tube having an outer round in the past, and heat exchange performance can be improved.

1 is a view showing a louver fin of a conventional heat exchanger;
2 is a conceptual illustration of a boundary layer in a louver fin.
Fig. 3 is an analysis of the heat distribution of the louver fins. Fig.
Figures 4 to 6 are partial cross-sectional views schematically showing the arrangement of tubes and fins in the heat exchanger of the present invention.
7 is a cross-sectional view of a tube in a heat exchanger according to the present invention.
8 is a cross-sectional view of yet another embodiment of a tube in a heat exchanger according to the present invention.
9 is a cross-sectional view of yet another embodiment of a tube in a heat exchanger according to the present invention.

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

The heat exchanger of the present invention is largely formed by including a header tank (not shown), a tube 200, and a fin 100.

The header tank is a pair of header tanks spaced apart from each other by a predetermined distance in the longitudinal direction or the height direction of the heat exchanger, and the header tank is formed such that the refrigerant is introduced or discharged.

The tube 200 is fixed at its both ends to the header tank to form a flow path of the heat exchange medium. The tube 200 has a plurality of inner holes 220 ).

At this time, the heat exchange medium flowing inside the tube 200 may be a coolant or a coolant depending on the type of the heat exchanger.

Particularly, the heat exchanger of the present invention includes a plurality of louvers 110 provided at predetermined angles to pass air therethrough, the fin 100 being interposed between the tubes 200 to increase the heat transfer area, And the louver 110 is disposed to correspond to the inner hole 220 of the tube 200.

The reason for this is that the air starts to transfer heat through the contact with the louver 110 at the front of the louver 110 pin 100 and passes over the surface of the louver 110 to the rear end of the louver 110, The heat transfer efficiency at the rear end of the louver 110 becomes lower than the front end portion because the turbulence in the flow can not sufficiently be generated toward the rear end of the louver 110 and the boundary layer development can not be sufficiently suppressed, The efficiency is due to the best front end of the louver 110 when viewed from each louver 110.

That is, in the heat exchanger of the present invention, the front end portion of the louver 110 having the best heat exchange efficiency is arranged in the inner hole 220, which is a space between the partition walls 210 of the tube 200 in which the heat exchange medium actually flows, .

FIGS. 4-6 illustrate various embodiments in which the louver 110 is disposed to correspond to the inner hole 220 of the tube 200.

The heat exchanger of the present invention may have a louver 110 pitch Lp of the fin 100 and a plurality of louvers 110 of the fin 100 when the a louvers 110 are arranged to correspond to the n inner holes 220, 210) T web of one thickness and the width T hole of the inner hole 220 can satisfy the following equation (1).

nT web + nT hole = aLp (1)

4, in the heat exchanger in which one louver 110 is arranged to correspond to one inner hole 220, the width of the inner hole 220 of the tube 200 and the thickness of one partition wall 210 Is equal to the pitch of the louver 110 and satisfies the following expression (2).

T web + T hole = Lp (Equation 2)

At this time, the pin 100 is positioned on the left side of the inner hole 220 corresponding to the front end of the louver 110, and the rear end is positioned on the left inner side of the adjacent inner hole 220.

That is, the fin 100 is disposed in the inner hole 220 of the tube 200 with a good heat exchange efficiency and the rear end of the tube 200 having a relatively low heat exchange efficiency is formed with the partition 210 of the tube 200 Area.

In the embodiment shown in FIG. 5, one louver 110 corresponds to the two inner holes 220, and the following equation (3) is satisfied.

2T web + 2T hole = Lp (Equation 3)

At this time, the pin 100 is located on the same line as the left inner surface of the inner hole 220 located at the front in the air flow direction among the inner holes 220 corresponding to the front end of the louver 110, The first inner hole 220 and the inner hole 220 adjacent to the first inner hole 220.

In the embodiment shown in FIG. 6, two louvers 110 are arranged so as to correspond to one inner hole 220, and the following equation (4) is satisfied.

T web + T hole = 2Lp (Equation 4)

At this time, the front end of the louver 110 located at the front portion in the air flow direction is positioned on the same line as the left inner surface of the corresponding inner hole 220, and the rear end of the second louver 110 And is positioned on the same line as the left inner surface of the adjacent inner hole 220.

The number n of the inner holes 220 and the number a of the louvers 110 are one or more, and the maximum value thereof is not limited to 2 as shown in FIGS.

The heat exchanger of the present invention is arranged such that the front end portion of the louver 110 having the best heat exchange efficiency is located inside the inner hole 220 of the tube 200 which is a region where the refrigerant actually flows, There is an advantage that the heat transfer performance between the louvers 110 of the pin 100 is improved.

Meanwhile, the fin 100 is interposed between the tubes 200 to perform heat exchange between the heat exchange medium and the air due to heat conduction due to conduction generated in a region contacting the tube 200.

At this time, the heat transfer area increases as the contact area of the fin 100 and the tube 200 increases, so that the heat exchange performance is as great as the contact area of the fin 100 and the tube 200 is maximized.

To this end, the heat exchanger tube 200 of the present invention may be formed flat from one end to the other end in the width direction of the surface contacting the fin 100. At this time, it is preferable that the heat exchanger tube 200 of the present invention has a substantially rectangular cross-section, and that the corners of the heat exchanger tube 200 are provided in a minimum round to make the contact areas with the ends of the fin 100 coincide with each other.

That is, since the tubes 200 are formed to have the same lengths of the surfaces contacting the pins 100, the heat transfer area can be increased and the heat exchange performance can be improved compared to the tubes 200 having the outer rounds conventionally There are advantages.

The tube 200 may have the same thickness T1 on both sides in the width direction and the thickness T2 on both sides in the thickness direction, May be formed to be thicker than the thickness T2 of the surface located on both sides in the thickness direction.

At this time, the tube 200 is formed so that the thickness T1 of the surface located on both sides in the width direction is smaller than the distances a1 and a3 reaching the inner side edges from the outer side edges.

FIG. 7 shows an example in which the thicknesses of the surfaces located on both sides in the width direction are formed to have a uniform thickness. FIG. 8 shows a tube 200 including a rigid beam- ).

The protrusion height a2 of the stiffening steel portion 230 is formed to be equal to or larger than the distances a1 and a3 extending from the corners of the tube 200 to both ends of the stiffening steel portion 230 in the thickness direction, And is formed to be at least 0.4 mm or more.

In addition, as shown in FIG. 9, both ends of the tube 200 may be formed in a round shape in the width direction. At this time, it is preferable that the thickness (A) of both sides of the tube (200) in the width direction is formed thicker than the thickness (B) of both sides in the thickness direction.

Accordingly, the entire area of the tube 200, which is likely to be in contact with corrosive substances or foreign matter during traveling, is formed to be thicker than other regions, so that the problem of leakage due to damage due to corrosion or foreign matter can be minimized, It is possible to contribute to improvement.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. It goes without saying that various modifications can be made.

100: pin
110: Louver
200: tube
210: partition wall 220: inner hole
230: Stiffness steel section

Claims (10)

A pair of header tanks spaced apart from each other by a predetermined distance;
A tube having both ends fixed to the header tank to form a flow path of the heat exchange medium and having a plurality of inner holes 220 separated from each other in the width direction by a plurality of partition walls 210 extending in the longitudinal direction, 200); And
A plurality of louvers 110 interposed between the tubes 200 and sloping at a predetermined angle to allow air to pass therethrough are formed and the louvers 110 are arranged to correspond to the inner holes 220 of the tubes 200 A pin (100) formed on the base (100); Wherein the heat exchanger is formed to include the heat exchanger.
The method according to claim 1,
The heat exchanger
when a number of the louvers 110 correspond to the n inner holes 220,
Wherein the louver 110 pitch Lp of the fin 100, the thickness T web of one partition wall 210, and the width T hole of the inner hole 220 satisfy the following expression (1) heat transmitter.
nT web + nT hole = aLp (1)
3. The method of claim 2,
The heat exchanger
Is formed so that one side inner surface in the width direction of the inner hole (220) and one side edge of the louver (110) are located on the same line.
The method according to claim 1,
The tube (200)
Wherein one side or both side surfaces are in contact with the fin (100) interposed between the neighboring tubes (200), and a flat surface is formed from one side end to the other side in the width direction of the contacting surface. .
5. The method of claim 4,
The tube (200) and the pin (100)
And the lengths of the contacting surfaces are equal to each other.
5. The method of claim 4,
The tube (200)
Characterized in that the thickness (T1) of the faces located on both sides in the width direction is thicker than the thickness (T2) of the faces located on both sides in the thickness direction.
5. The method of claim 4,
The tube (200)
And a stiffening steel portion (230) having inner surfaces of the surfaces located on both sides in the width direction protruding inward.
8. The method of claim 7,
The tube (200)
Wherein the projecting height a2 of the rigid beam guiding steel portion 230 is formed to be equal to or greater than the distances a1 and a3 reaching the both ends of the rigid beam guiding steel portion 230 in the thickness direction at each corner.
The method according to claim 1,
The tube (200)
And both ends are formed in a round shape in the width direction.
10. The method of claim 9,
The tube (200)
(A) of both side faces in the width direction is formed thicker than the thickness (B) of both side faces in the thickness direction.
KR1020160008688A 2016-01-25 2016-01-25 Exchanger KR101977797B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020160008688A KR101977797B1 (en) 2016-01-25 2016-01-25 Exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020160008688A KR101977797B1 (en) 2016-01-25 2016-01-25 Exchanger

Publications (2)

Publication Number Publication Date
KR20170088605A true KR20170088605A (en) 2017-08-02
KR101977797B1 KR101977797B1 (en) 2019-05-14

Family

ID=59652013

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020160008688A KR101977797B1 (en) 2016-01-25 2016-01-25 Exchanger

Country Status (1)

Country Link
KR (1) KR101977797B1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR19980048652A (en) * 1996-12-18 1998-09-15 구자홍 Heat exchanger for evaporator
JP2005055108A (en) * 2003-08-06 2005-03-03 Matsushita Electric Ind Co Ltd Heat exchanger
JP2010038477A (en) * 2008-08-07 2010-02-18 Tokyo Radiator Mfg Co Ltd Porous tube for heat exchange
KR101225597B1 (en) 2006-09-04 2013-01-24 한라공조주식회사 A Louver Fin for a Heat-Exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR19980048652A (en) * 1996-12-18 1998-09-15 구자홍 Heat exchanger for evaporator
JP2005055108A (en) * 2003-08-06 2005-03-03 Matsushita Electric Ind Co Ltd Heat exchanger
KR101225597B1 (en) 2006-09-04 2013-01-24 한라공조주식회사 A Louver Fin for a Heat-Exchanger
JP2010038477A (en) * 2008-08-07 2010-02-18 Tokyo Radiator Mfg Co Ltd Porous tube for heat exchange

Also Published As

Publication number Publication date
KR101977797B1 (en) 2019-05-14

Similar Documents

Publication Publication Date Title
US9689628B2 (en) Oil cooler with inner fin
EP3040670A1 (en) Heat exchanger, in particular a condenser or a gas cooler
US20230003467A1 (en) Heat exchanger and corrugated fin
CN107709917B (en) Inner fin of heat exchanger
US20080000627A1 (en) Heat exchanger
JPWO2016043340A1 (en) Corrugated fin for heat exchanger
CN112368535B (en) Heat exchanger
JP2015078819A (en) Inner fin
KR20110072005A (en) The heat exchanger
US11506457B2 (en) Header plateless type heat exchanger
KR101977797B1 (en) Exchanger
JP7229986B2 (en) heat exchanger tank structure
WO2019229180A1 (en) A core of a heat exchanger comprising corrugated fins
JP2010255864A (en) Flat tube and heat exchanger
JP2016205718A (en) Heat exchanger
JP5772608B2 (en) Heat exchanger
KR20170044965A (en) A tube of heat exchanger
JP2009236470A (en) Heat exchanger
JP2019219139A (en) Corrugated fin for heat exchanger
CN113557403B (en) Heat exchanger
KR101160665B1 (en) Heat exchanger
KR102350040B1 (en) A tube of heat exchanger and heat exchanger with the same
KR20110080899A (en) Fin for heat exchanger
WO2021161680A1 (en) Heat exchanger bracket
JP2011158130A (en) Heat exchanger

Legal Events

Date Code Title Description
A201 Request for examination
E902 Notification of reason for refusal
E701 Decision to grant or registration of patent right
GRNT Written decision to grant