US20070151713A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- US20070151713A1 US20070151713A1 US11/646,334 US64633406A US2007151713A1 US 20070151713 A1 US20070151713 A1 US 20070151713A1 US 64633406 A US64633406 A US 64633406A US 2007151713 A1 US2007151713 A1 US 2007151713A1
- Authority
- US
- United States
- Prior art keywords
- tube
- refrigerant
- heat exchanger
- agitating member
- exchanger according
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
Definitions
- the present invention relates to a heat exchanger, and more particularly, to a refrigerant tube structure of a heat exchanger that improves heat exchange efficiency by increasing a contact area between a liquid refrigerant flowing through a refrigerant tube and an inner periphery of the refrigerant tube.
- a fin-tube type heat exchanger used in an air conditioner or the like includes a refrigerant tube having the shape of a meander line which is curved a plurality of times, and a plurality of heat exchange fins inserted into the refrigerant tube in a direction that the heat exchange fins are intersected with the refrigerant tube.
- the related art fin-tube type heat exchanger acts as an evaporator or a condenser in such a way that a refrigerant exchanges heat with external air while the refrigerant flowing through the refrigerant tube. Specifically, a heat exchange area between the refrigerant and the external air is increased by means of the heat exchange fins which are inserted into the refrigerant tube and arranged close to each other. Thus, a heat exchange is effectively performed.
- grooves are formed on an inner periphery of the refrigerant tube of the fin-tube type heat exchanger for improving heat exchange efficiency.
- the grooves are spirally formed such that they are connected in a longitudinal direction of the refrigerant tube.
- the contact area between the liquid refrigerant and the refrigerant tube is increased, and thus the heat exchange efficiency is improved.
- the contact area between the vapor refrigerant and the refrigerant tube is increased so that the heat exchanger having the grooves is advantageous in improving the heat exchange efficiency.
- the liquid refrigerant flows at an outlet portion of the refrigerant tube.
- the heat exchanger is used as the condenser, the liquid refrigerant flows at an inlet portion of the refrigerant tube.
- Such a refrigerant flows along a bottom surface of the refrigerant tube due to gravity.
- the related art heat exchanger having the above-described refrigerant tube when used as an evaporator, the liquid refrigerant flows into the inlet of the evaporator. Therefore, the contact area between the refrigerant and the inner periphery of refrigerant tube is decreased at the inlet of the evaporator, and thus the heat exchange efficiency of the heat exchanger is degraded. That is, there is a drawback that the refrigerant is not completely vaporized because the degree of superheat of the evaporator is lowered.
- the heat exchanger when used as a condenser, the liquid flows through the outlet of the condenser. Accordingly, the contact area between the liquid refrigerant and the inner periphery of the refrigerant tube is decreased at the outlet of the condenser, and thus the heat exchange efficiency of the heat exchanger is degraded. That is, there is a drawback that the refrigerant is not completely liquidized because the degree of supercooling of the condenser is lowered.
- the present invention is directed to a heat exchanger that substantially obviates one or more problems due to limitations and disadvantages of the related art.
- An object of the present invention is to provide a heat exchanger that improves heat exchange efficiency by increasing a contact area between a refrigerant and an inner periphery of a refrigerant tube at an inlet of the refrigerant when the heat exchanger is used as an evaporator.
- Another object of the present invention is to provide a heat exchanger that improves heat exchange efficiency by increasing a contact area between a refrigerant and an inner periphery of a refrigerant tube at an outlet of the refrigerant when the heat exchanger is used as a condenser.
- a heat exchanger including: a tube through which a refrigerant flows; a fin disposed on an outer periphery of the tube; and an agitating member inserted into the tube, and agitating the refrigerant.
- a heat exchanger including: a tube; a fin contacting the tube to be thermally in contact with an external air; and an agitating member spiraled a plurality of times for increasing a contact area between a liquid refrigerant and an inner periphery of the tube, the agitating member being provided inside the tube.
- the heat exchanger according to the present invention When the heat exchanger according to the present invention is used as an evaporator, a contact area between a liquid refrigerant and an inner periphery of the refrigerant tube at an inlet of the evaporator is increased. Thus, it is possible to increase heat exchange efficiency.
- the heat exchanger according to the present invention when used as condenser, a contact area between a liquid refrigerant and an inner periphery of the refrigerant tube at an outlet of the condenser is increased. Thus, it is possible to increase heat exchange efficiency.
- FIG. 1 is a perspective view of a heat exchanger according to the preset invention
- FIG. 2 is a sectional view of a refrigerant tube according to a refrigerant tube
- FIG. 3 is an exploded perspective view illustrating a connection of the refrigerant tube according to the present invention.
- FIG. 4 is a partially sectional perspective view taken along line I-I of FIG. 3 ;
- FIG. 5 is a graph of experimental data illustrating a performance comparison result of a related art heat exchanger and the heat exchanger according to the present invention.
- FIG. 1 is a perspective view of a heat exchanger 1 according to the present invention.
- the heat exchanger 1 includes a refrigerant tube 10 through which a refrigerant flows, heat exchange fins 20 penetrated by the refrigerant tube 10 and arranged at regular distances, and an agitating member 30 inserted into the refrigerant tube 10 .
- the heat exchange fin 20 is formed from a thin plate with high thermal conductivity and is attached on an outer periphery of the tube 10 , thereby increasing a heat exchange area between the refrigerant and an air current S and thermal conductivity.
- FIG. 2 is a sectional view of the refrigerant tube 10 according to a refrigerant tube.
- a plurality of protrusions 13 are formed on an inner periphery of the refrigerant tube 10 in spiral shape.
- the protrusions 13 are formed such that they scrape along the inner periphery of the refrigerant tube 10 in a spiral direction. These protrusions 13 play a role in improving heat transfer capability by increasing a contact area with the refrigerant tube 10 when the refrigerant flows through the refrigerant tube 10 .
- the agitating member 30 having a helical shape is inserted into the refrigerant tube 10 . Specifically, the agitating member 30 changes the flow of the refrigerant flowing through the refrigerant tube 10 so that the contact area between the refrigerant and the inner periphery of the refrigerant tube 10 is increased.
- the flow of the refrigerant flowing through the refrigerant tube 10 is changed into turbulent flow from laminar flow, which increases the contact area between the refrigerant and the refrigerant tube 10 .
- FIG. 3 is an exploded perspective view illustrating a connection of the refrigerant tube 10 according to the present invention
- FIG. 4 is a partially sectional perspective view taken along line I-I of FIG. 3 .
- the refrigerant tubes 10 of the heat exchanger 1 according to the present invention is prepared such that a plurality of U-shaped pipes are mutually connected to each other by a return band 11 .
- the agitating member 30 is inserted into an end of the refrigerant tube 10 .
- the agitating member has a length extending from one end of the refrigerant tube 10 to the other end from which a curvature starts. Therefore, turbulence phenomenon does not occur due to the flow of the refrigerant in a state that the agitating member 30 is inserted into the refrigerant tube 10 .
- the agitating member 30 is shaped such that a rim-shaped member with a predetermined width and thickness T is spirally wound.
- the spirally shaped agitating member 30 is formed in the shape of a spring having a predetermined inner diameter D 1 and a predetermined outer diameter D 2 .
- the inner diameter D 1 of the agitating member 30 be 25-40% of an inner diameter D 3 of the refrigerant tube 10 in consideration of flow resistance of the refrigerant and the contact area between the liquid refrigerant and the inner periphery of the refrigerant tube 10 .
- the outer diameter D 2 of the agitating member 30 be 95% or less of the inner diameter D 3 of the refrigerant tube 10 .
- a distance P between pitches of the agitating member 30 be greater than the inner diameter D 3 of the refrigerant tube 10 at least.
- the agitating member 30 having the above shape is inserted into an inside portion of the refrigerant tube 30 through which the liquid refrigerant flows.
- a vapor refrigerant can contact the inner periphery of the refrigerant tube 10 with ease but the liquid refrigerant is generally in contact with a bottom portion of the refrigerant tube 10 due to its own viscosity and gravity.
- the liquid refrigerant flowing through the refrigerant tube 10 contacts the inner periphery of the refrigerant tube 10 to increase a heat exchange area.
- a binary phase refrigerant that has undergone an expansion procedure flows into an inlet of the evaporator. Since the amount of liquid refrigerant is more than the amount of vapor refrigerant at the inlet of the evaporator, it is preferable that the agitating member 30 be provided to the inlet of the evaporator.
- the heat exchanger 1 when used as a condenser, a vapor refrigerant with high pressure and temperature that has passed through a compressor flows into an inlet of the condenser, and a liquid refrigerant with high temperature flows into an outlet of the condenser through condensation procedure. Accordingly, it is preferable that the agitating member 30 be provided to the outlet of the condenser.
- FIG. 5 is a graph of experimental data illustrating a performance comparison result of a related art heat exchanger and the heat exchanger according to the present invention.
- a low temperature liquid refrigerant flows into the inlet of the evaporator, and is heat-exchanged with an external air while it flowing through the refrigerant tube 10 so that the low temperature liquid refrigerant is changed into a low temperature vapor refrigerant.
- the liquid refrigerant flowing through the refrigerant tube 10 absorbs the heat of the air current S transferred through the fin 20 . Therefore, the low temperature liquid refrigerant is changed into the vapor refrigerant and the vapor refrigerant then flows out through the outlet of the evaporator. The heat of the air current S is transferred to the refrigerant, and thus the air becomes cool.
- the heat of evaporation of the evaporator employing the inventive refrigerant tube 10 having the agitating member 30 is increased to 101.7% assuming that the heat of evaporation of the related art heat exchanger be 100%. That is, when the heat exchanger 1 having the refrigerant tube structure according to the present invention is used as the evaporator, it was understood from FIG. 5 that the heat exchanger absorbs more heat, i.e., about 1.7%, from the air current S in comparison with the related art evaporator, and thus its heat exchanging capability is improved.
- a high temperature vapor refrigerant flows into an inlet of a condenser, and is changed into a high temperature liquid refrigerant while it flowing through the refrigerant tube 10 . That is, after the heat of the vapor refrigerant is released into the air current S through the fins 20 so that the vapor refrigerant is changed into the liquid refrigerant, the liquid refrigerant flows out through the outlet of the condenser.
- the heat of condensation of the condenser employing the inventive refrigerant tube 10 is increased to 102.7% assuming that the heat of condensation of the related art heat exchanger be 100%. That is, when the heat exchanger having the refrigerant tube structure according to the present invention is used as the condenser, it was understood that the heat exchanger release more heat, i.e., about 2.7%, into the air current S in comparison with the related art evaporator, and thus its heat exchanging capability is improved.
- the amount of heat exchange of the refrigerant with the external air can be increased by inserting the agitating member 30 into the refrigerant tube 10 , because the agitating member 30 increases the contact area with the inner periphery of the refrigerant tube by changing the flow of the refrigerant.
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
A heat exchanger is provided. The heat exchanger includes a tube through which a refrigerant flows, a fin disposed on an outer periphery of the tube, and an agitating member inserted into the tube, and agitating the refrigerant.
Description
- 1. Field of the Invention
- The present invention relates to a heat exchanger, and more particularly, to a refrigerant tube structure of a heat exchanger that improves heat exchange efficiency by increasing a contact area between a liquid refrigerant flowing through a refrigerant tube and an inner periphery of the refrigerant tube.
- 2. Description of the Related Art
- In general, a fin-tube type heat exchanger used in an air conditioner or the like includes a refrigerant tube having the shape of a meander line which is curved a plurality of times, and a plurality of heat exchange fins inserted into the refrigerant tube in a direction that the heat exchange fins are intersected with the refrigerant tube.
- The related art fin-tube type heat exchanger acts as an evaporator or a condenser in such a way that a refrigerant exchanges heat with external air while the refrigerant flowing through the refrigerant tube. Specifically, a heat exchange area between the refrigerant and the external air is increased by means of the heat exchange fins which are inserted into the refrigerant tube and arranged close to each other. Thus, a heat exchange is effectively performed.
- In addition, grooves are formed on an inner periphery of the refrigerant tube of the fin-tube type heat exchanger for improving heat exchange efficiency. Here, the grooves are spirally formed such that they are connected in a longitudinal direction of the refrigerant tube.
- In virtue of the grooves, when the heat exchanger is used as an evaporator, the contact area between the liquid refrigerant and the refrigerant tube is increased, and thus the heat exchange efficiency is improved. Besides, when the heat exchanger is used as a condenser, the contact area between the vapor refrigerant and the refrigerant tube is increased so that the heat exchanger having the grooves is advantageous in improving the heat exchange efficiency.
- Meanwhile, when the heat exchanger having the related art refrigerant tube is used as the evaporator, the liquid refrigerant flows at an outlet portion of the refrigerant tube. When the heat exchanger is used as the condenser, the liquid refrigerant flows at an inlet portion of the refrigerant tube. Such a refrigerant flows along a bottom surface of the refrigerant tube due to gravity.
- Specifically, when the related art heat exchanger having the above-described refrigerant tube is used as an evaporator, the liquid refrigerant flows into the inlet of the evaporator. Therefore, the contact area between the refrigerant and the inner periphery of refrigerant tube is decreased at the inlet of the evaporator, and thus the heat exchange efficiency of the heat exchanger is degraded. That is, there is a drawback that the refrigerant is not completely vaporized because the degree of superheat of the evaporator is lowered.
- Moreover, when the heat exchanger is used as a condenser, the liquid flows through the outlet of the condenser. Accordingly, the contact area between the liquid refrigerant and the inner periphery of the refrigerant tube is decreased at the outlet of the condenser, and thus the heat exchange efficiency of the heat exchanger is degraded. That is, there is a drawback that the refrigerant is not completely liquidized because the degree of supercooling of the condenser is lowered.
- Accordingly, the present invention is directed to a heat exchanger that substantially obviates one or more problems due to limitations and disadvantages of the related art.
- An object of the present invention is to provide a heat exchanger that improves heat exchange efficiency by increasing a contact area between a refrigerant and an inner periphery of a refrigerant tube at an inlet of the refrigerant when the heat exchanger is used as an evaporator.
- Another object of the present invention is to provide a heat exchanger that improves heat exchange efficiency by increasing a contact area between a refrigerant and an inner periphery of a refrigerant tube at an outlet of the refrigerant when the heat exchanger is used as a condenser.
- Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention may be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.
- To achieve these objects and other advantages and in accordance with the purpose of the invention, as embodied and broadly described herein, there is provided a heat exchanger, including: a tube through which a refrigerant flows; a fin disposed on an outer periphery of the tube; and an agitating member inserted into the tube, and agitating the refrigerant.
- In another aspect of the present invention, there is provided a heat exchanger, including: a tube; a fin contacting the tube to be thermally in contact with an external air; and an agitating member spiraled a plurality of times for increasing a contact area between a liquid refrigerant and an inner periphery of the tube, the agitating member being provided inside the tube.
- When the heat exchanger according to the present invention is used as an evaporator, a contact area between a liquid refrigerant and an inner periphery of the refrigerant tube at an inlet of the evaporator is increased. Thus, it is possible to increase heat exchange efficiency.
- In addition, when the heat exchanger according to the present invention is used as condenser, a contact area between a liquid refrigerant and an inner periphery of the refrigerant tube at an outlet of the condenser is increased. Thus, it is possible to increase heat exchange efficiency.
- It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are intended to provide further explanation of the invention as claimed.
- The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the principle of the invention. In the drawings:
-
FIG. 1 is a perspective view of a heat exchanger according to the preset invention; -
FIG. 2 is a sectional view of a refrigerant tube according to a refrigerant tube; -
FIG. 3 is an exploded perspective view illustrating a connection of the refrigerant tube according to the present invention; -
FIG. 4 is a partially sectional perspective view taken along line I-I ofFIG. 3 ; and -
FIG. 5 is a graph of experimental data illustrating a performance comparison result of a related art heat exchanger and the heat exchanger according to the present invention. - Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
-
FIG. 1 is a perspective view of aheat exchanger 1 according to the present invention. - Referring to
FIG. 1 , theheat exchanger 1 according to the present invention includes arefrigerant tube 10 through which a refrigerant flows, heat exchange fins 20 penetrated by therefrigerant tube 10 and arranged at regular distances, and anagitating member 30 inserted into therefrigerant tube 10. - Specifically, the
heat exchange fin 20 is formed from a thin plate with high thermal conductivity and is attached on an outer periphery of thetube 10, thereby increasing a heat exchange area between the refrigerant and an air current S and thermal conductivity. -
FIG. 2 is a sectional view of therefrigerant tube 10 according to a refrigerant tube. - Referring to
FIG. 2 , a plurality ofprotrusions 13 are formed on an inner periphery of therefrigerant tube 10 in spiral shape. - In detail, the
protrusions 13 are formed such that they scrape along the inner periphery of therefrigerant tube 10 in a spiral direction. Theseprotrusions 13 play a role in improving heat transfer capability by increasing a contact area with therefrigerant tube 10 when the refrigerant flows through therefrigerant tube 10. - The
agitating member 30 having a helical shape is inserted into therefrigerant tube 10. Specifically, theagitating member 30 changes the flow of the refrigerant flowing through therefrigerant tube 10 so that the contact area between the refrigerant and the inner periphery of therefrigerant tube 10 is increased. - That is, the flow of the refrigerant flowing through the
refrigerant tube 10 is changed into turbulent flow from laminar flow, which increases the contact area between the refrigerant and therefrigerant tube 10. -
FIG. 3 is an exploded perspective view illustrating a connection of therefrigerant tube 10 according to the present invention, andFIG. 4 is a partially sectional perspective view taken along line I-I ofFIG. 3 . - Referring to
FIG. 3 , therefrigerant tubes 10 of theheat exchanger 1 according to the present invention is prepared such that a plurality of U-shaped pipes are mutually connected to each other by areturn band 11. Theagitating member 30 is inserted into an end of therefrigerant tube 10. - Here, the agitating member has a length extending from one end of the
refrigerant tube 10 to the other end from which a curvature starts. Therefore, turbulence phenomenon does not occur due to the flow of the refrigerant in a state that theagitating member 30 is inserted into therefrigerant tube 10. - Referring to
FIG. 4 , theagitating member 30 according to the present invention is shaped such that a rim-shaped member with a predetermined width and thickness T is spirally wound. - In detail, the spirally shaped
agitating member 30 is formed in the shape of a spring having a predetermined inner diameter D1 and a predetermined outer diameter D2. - In more detail, it is preferable that the inner diameter D1 of the
agitating member 30 be 25-40% of an inner diameter D3 of therefrigerant tube 10 in consideration of flow resistance of the refrigerant and the contact area between the liquid refrigerant and the inner periphery of therefrigerant tube 10. - In other words, when the diameter D1 of the agitating
member 30 is less than 25% of the inner diameter D3 of therefrigerant tube 10, the contact area between the liquid refrigerant and therefrigerant tube 10 is increased and a flow resistance of the refrigerant is increased as well. Therefore, the heat exchange capability of theheat exchanger 1 is degraded. - On the contrary, when the inner diameter D1 of the agitating
member 30 is greater than 40% of the inner diameter D3 of therefrigerant tube 10, the flow resistance of the refrigerant is decreased and the contact area between the liquid refrigerant and therefrigerant tube 10 is also decreased, which causes the heat exchange capability of theheat exchanger 1 to be degraded. - In addition, in consideration of a contact area between the
protrusions 13 formed in therefrigerant tube 10 and the flow resistance of the refrigerant, it is preferable that the outer diameter D2 of the agitatingmember 30 be 95% or less of the inner diameter D3 of therefrigerant tube 10. - That is, when a diameter D2 of the agitating
member 30 is greater than 95% of the diameter D3 of therefrigerant tube 10, the contact area between the refrigerant and theprotrusion 13 is increased but the flow resistance of the refrigerant is also increased, whereby the heat exchange capability of thethermal exchanger 1 is degraded. - In addition, to reduce the flow resistance of the refrigerant, it is preferable that a distance P between pitches of the agitating
member 30 be greater than the inner diameter D3 of therefrigerant tube 10 at least. - Preferably, the agitating
member 30 having the above shape is inserted into an inside portion of therefrigerant tube 30 through which the liquid refrigerant flows. - In other words, a vapor refrigerant can contact the inner periphery of the
refrigerant tube 10 with ease but the liquid refrigerant is generally in contact with a bottom portion of therefrigerant tube 10 due to its own viscosity and gravity. Thus, it is preferable that the liquid refrigerant flowing through therefrigerant tube 10 contacts the inner periphery of therefrigerant tube 10 to increase a heat exchange area. - Specifically, when the
heat exchanger 1 is used as an evaporator, a binary phase refrigerant that has undergone an expansion procedure flows into an inlet of the evaporator. Since the amount of liquid refrigerant is more than the amount of vapor refrigerant at the inlet of the evaporator, it is preferable that the agitatingmember 30 be provided to the inlet of the evaporator. - Contrariwise, when the
heat exchanger 1 is used as a condenser, a vapor refrigerant with high pressure and temperature that has passed through a compressor flows into an inlet of the condenser, and a liquid refrigerant with high temperature flows into an outlet of the condenser through condensation procedure. Accordingly, it is preferable that the agitatingmember 30 be provided to the outlet of the condenser. - Thereinafter, the performance of the
heat exchanger 1 having the above-mentioned structure will be described with reference to a graph showing experimental data. -
FIG. 5 is a graph of experimental data illustrating a performance comparison result of a related art heat exchanger and the heat exchanger according to the present invention. - Referring to
FIG. 5 , when theheat exchanger 1 is used as an evaporator, a low temperature liquid refrigerant flows into the inlet of the evaporator, and is heat-exchanged with an external air while it flowing through therefrigerant tube 10 so that the low temperature liquid refrigerant is changed into a low temperature vapor refrigerant. In detail, the liquid refrigerant flowing through therefrigerant tube 10 absorbs the heat of the air current S transferred through thefin 20. Therefore, the low temperature liquid refrigerant is changed into the vapor refrigerant and the vapor refrigerant then flows out through the outlet of the evaporator. The heat of the air current S is transferred to the refrigerant, and thus the air becomes cool. - Meanwhile, it was confirmed that the heat of evaporation of the evaporator employing the
inventive refrigerant tube 10 having the agitatingmember 30 is increased to 101.7% assuming that the heat of evaporation of the related art heat exchanger be 100%. That is, when theheat exchanger 1 having the refrigerant tube structure according to the present invention is used as the evaporator, it was understood fromFIG. 5 that the heat exchanger absorbs more heat, i.e., about 1.7%, from the air current S in comparison with the related art evaporator, and thus its heat exchanging capability is improved. - In addition, when the
heat exchanger 1 is used as a condenser, a high temperature vapor refrigerant flows into an inlet of a condenser, and is changed into a high temperature liquid refrigerant while it flowing through therefrigerant tube 10. That is, after the heat of the vapor refrigerant is released into the air current S through thefins 20 so that the vapor refrigerant is changed into the liquid refrigerant, the liquid refrigerant flows out through the outlet of the condenser. - Furthermore, it was confirmed from
FIG. 5 that the heat of condensation of the condenser employing theinventive refrigerant tube 10 is increased to 102.7% assuming that the heat of condensation of the related art heat exchanger be 100%. That is, when the heat exchanger having the refrigerant tube structure according to the present invention is used as the condenser, it was understood that the heat exchanger release more heat, i.e., about 2.7%, into the air current S in comparison with the related art evaporator, and thus its heat exchanging capability is improved. - As described above, according to the present invention, the amount of heat exchange of the refrigerant with the external air can be increased by inserting the agitating
member 30 into therefrigerant tube 10, because the agitatingmember 30 increases the contact area with the inner periphery of the refrigerant tube by changing the flow of the refrigerant. - It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention. Thus, it is intended that the present invention covers the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.
Claims (12)
1. A heat exchanger comprising:
a tube through which a refrigerant flows;
a fin disposed on an outer periphery of the tube; and
an agitating member inserted into the tube, and agitating the refrigerant.
2. The heat exchanger according to claim 1 , wherein the agitating member has a helical shape.
3. The heat exchanger according to claim 1 , wherein the agitating member is disposed in a section where a liquid refrigerant flows.
4. The heat exchanger according to claim 1 , wherein a distance between pitches of the agitating member is greater than an inner diameter of the tube.
5. The heat exchanger according to claim 1 , wherein a plurality of protrusions are formed on an inner periphery of the tube.
6. The heat exchanger according to claim 1 , wherein the agitating member is provided in a linear section of the tube.
7. A heat exchanger comprising:
a tube;
a fin contacting the tube to be thermally in contact with an external air; and
an agitating member spiraled a plurality of times for increasing a contact area between a liquid refrigerant and an inner periphery of the tube, the agitating member being provided inside the tube.
8. The heat exchanger according to claim 7 , wherein the agitating member is curved in a direction different from a flow direction of a refrigerant.
9. The heat exchanger according to claim 7 , wherein an outer diameter of the agitating member is 95% or less of an inner diameter of the tube.
10. The heat exchanger according to claim 7 , wherein an inner diameter of the agitating member is 25%˜40% of an inner diameter of the tube.
11. The heat exchanger according to claim 7 , wherein the agitating member is provided to an outlet of the tube when a refrigerant passing through a compressor flows into the tube.
12. The heat exchanger according to claim 7 , wherein the agitating member is provided to an inlet of the tube when the refrigerant undergoing an expansion procedure flows into the tube
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2005-0136227 | 2005-12-31 | ||
KR20050136227 | 2005-12-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070151713A1 true US20070151713A1 (en) | 2007-07-05 |
Family
ID=38213715
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/646,334 Abandoned US20070151713A1 (en) | 2005-12-31 | 2006-12-28 | Heat exchanger |
Country Status (2)
Country | Link |
---|---|
US (1) | US20070151713A1 (en) |
CN (1) | CN1991290B (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090084129A1 (en) * | 2007-08-31 | 2009-04-02 | Dong Hwi Kim | Heat exchanger and refrigeration cycle apparatus having the same |
US20100057064A1 (en) * | 2008-09-03 | 2010-03-04 | Baust John M | Medical Device for the Transport of Subcooled Cryogenic Fluid through a Linear Heat Exchanger |
US20120060545A1 (en) * | 2010-12-02 | 2012-03-15 | General Electric Company | Condenser assembly for multiple refrigeration systems |
JP2015224804A (en) * | 2014-05-26 | 2015-12-14 | 株式会社ノーリツ | Heat exchanger |
US20160076828A1 (en) * | 2014-09-12 | 2016-03-17 | Trane International Inc. | Turbulators in enhanced tubes |
DE102015115261A1 (en) * | 2015-09-10 | 2016-08-25 | Semikron Elektronik Gmbh & Co. Kg | Cooling device with a liquid heat sink |
WO2019055390A1 (en) * | 2017-09-13 | 2019-03-21 | Carrier Corporation | Helical insert for shell and tube heat exchanger background |
WO2021177603A1 (en) * | 2020-03-05 | 2021-09-10 | 효성중공업 주식회사 | Heat dissipating device using turbulent flow |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2300579A (en) * | 1936-09-03 | 1942-11-03 | Servel Inc | Refrigeration |
US2676001A (en) * | 1950-09-05 | 1954-04-20 | Rudy Mfg Company | Plate type heat exchange unit providing edge radiation |
US2930208A (en) * | 1958-03-14 | 1960-03-29 | Westinghouse Electric Corp | Dehumidification apparatus |
US4044797A (en) * | 1974-11-25 | 1977-08-30 | Hitachi, Ltd. | Heat transfer pipe |
US4269265A (en) * | 1979-11-29 | 1981-05-26 | Modine Manufacturing Company | Tubular heat exchanger with turbulator |
US4367791A (en) * | 1978-01-27 | 1983-01-11 | Kobe Steel, Ltd. | Heat transfer tubing for natural gas evaporator |
US4545428A (en) * | 1979-05-16 | 1985-10-08 | Daikin Kogyo Co., Ltd. | Heat exchanger for air conditioning system |
US5398752A (en) * | 1993-08-19 | 1995-03-21 | Abbott; Roy W. | Strip fin and tube heat exchanger |
US5497824A (en) * | 1990-01-18 | 1996-03-12 | Rouf; Mohammad A. | Method of improved heat transfer |
US6119769A (en) * | 1998-08-05 | 2000-09-19 | Visteon Global Technologies, Inc. | Heat transfer device |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0875384A (en) * | 1994-07-01 | 1996-03-19 | Hitachi Ltd | Heat transfer tube for non-azeotrope refrigerant, heat exchanger using the same tube, assembling method and refrigerating air conditioner using the same exchanger |
CN2397454Y (en) * | 1999-05-24 | 2000-09-20 | 上海得灵电器实业有限公司 | High efficient condenser for air conditioner |
-
2006
- 2006-12-28 US US11/646,334 patent/US20070151713A1/en not_active Abandoned
- 2006-12-31 CN CN2006101732750A patent/CN1991290B/en not_active Expired - Fee Related
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2300579A (en) * | 1936-09-03 | 1942-11-03 | Servel Inc | Refrigeration |
US2676001A (en) * | 1950-09-05 | 1954-04-20 | Rudy Mfg Company | Plate type heat exchange unit providing edge radiation |
US2930208A (en) * | 1958-03-14 | 1960-03-29 | Westinghouse Electric Corp | Dehumidification apparatus |
US4044797A (en) * | 1974-11-25 | 1977-08-30 | Hitachi, Ltd. | Heat transfer pipe |
US4367791A (en) * | 1978-01-27 | 1983-01-11 | Kobe Steel, Ltd. | Heat transfer tubing for natural gas evaporator |
US4545428A (en) * | 1979-05-16 | 1985-10-08 | Daikin Kogyo Co., Ltd. | Heat exchanger for air conditioning system |
US4269265A (en) * | 1979-11-29 | 1981-05-26 | Modine Manufacturing Company | Tubular heat exchanger with turbulator |
US5497824A (en) * | 1990-01-18 | 1996-03-12 | Rouf; Mohammad A. | Method of improved heat transfer |
US5398752A (en) * | 1993-08-19 | 1995-03-21 | Abbott; Roy W. | Strip fin and tube heat exchanger |
US6119769A (en) * | 1998-08-05 | 2000-09-19 | Visteon Global Technologies, Inc. | Heat transfer device |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090084129A1 (en) * | 2007-08-31 | 2009-04-02 | Dong Hwi Kim | Heat exchanger and refrigeration cycle apparatus having the same |
US20100057064A1 (en) * | 2008-09-03 | 2010-03-04 | Baust John M | Medical Device for the Transport of Subcooled Cryogenic Fluid through a Linear Heat Exchanger |
US10182859B2 (en) * | 2008-09-03 | 2019-01-22 | Endocare, Inc. | Medical device for the transport of subcooled cryogenic fluid through a linear heat exchanger |
US20120060545A1 (en) * | 2010-12-02 | 2012-03-15 | General Electric Company | Condenser assembly for multiple refrigeration systems |
JP2015224804A (en) * | 2014-05-26 | 2015-12-14 | 株式会社ノーリツ | Heat exchanger |
US20160076828A1 (en) * | 2014-09-12 | 2016-03-17 | Trane International Inc. | Turbulators in enhanced tubes |
US10480872B2 (en) * | 2014-09-12 | 2019-11-19 | Trane International Inc. | Turbulators in enhanced tubes |
DE102015115261A1 (en) * | 2015-09-10 | 2016-08-25 | Semikron Elektronik Gmbh & Co. Kg | Cooling device with a liquid heat sink |
WO2019055390A1 (en) * | 2017-09-13 | 2019-03-21 | Carrier Corporation | Helical insert for shell and tube heat exchanger background |
WO2021177603A1 (en) * | 2020-03-05 | 2021-09-10 | 효성중공업 주식회사 | Heat dissipating device using turbulent flow |
US11953273B2 (en) | 2020-03-05 | 2024-04-09 | Hyosung Heavy Industries Corporation | Heat dissipating device using turbulent flow |
Also Published As
Publication number | Publication date |
---|---|
CN1991290A (en) | 2007-07-04 |
CN1991290B (en) | 2011-04-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20070151713A1 (en) | Heat exchanger | |
US6390183B2 (en) | Heat exchanger | |
US6932153B2 (en) | Heat exchanger | |
EP2455687B1 (en) | Outdoor heat exchanger and heat pump having the same | |
US20120292000A1 (en) | Turbulators for heat exchanger tubes | |
JP2008202896A (en) | Heat exchanger | |
KR102048356B1 (en) | Refrigerant pipe, and fin type heat exchanger and air conditioner comprising the same | |
EP3191784B1 (en) | Turbulators in enhanced tubes | |
US11236946B2 (en) | Microchannel heat exchanger | |
JPH11257800A (en) | Heat exchanger and air conditioner with exchanger | |
EP2796822B1 (en) | Air conditioner | |
US20040035563A1 (en) | Heat exchanger | |
JP2009145010A (en) | Fin-less heat exchanger for air conditioner | |
JPWO2018185824A1 (en) | Heat exchanger and refrigeration cycle equipment | |
CN111556950A (en) | Heat exchanger for refrigerator | |
CN117157500A (en) | Heat exchanger | |
JP2017133814A (en) | Heat exchanger | |
KR20120054346A (en) | Refrigerant tube and heat exchanger including the same | |
KR100575278B1 (en) | A tube for heat exchange with a capillary-type heat pipe | |
JP4983878B2 (en) | Heat exchanger, refrigerator equipped with this heat exchanger, and air conditioner | |
JP5020159B2 (en) | Heat exchanger, refrigerator and air conditioner | |
JPH10325644A (en) | Heat exchanger and refrigerating cycle device | |
KR100619151B1 (en) | Condenser enhanced heat transfer performance | |
US10480872B2 (en) | Turbulators in enhanced tubes | |
KR100314186B1 (en) | Tri-tube type heat exchanger for Evaporator |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: LG ELECTRONICS INC., KOREA, REPUBLIC OF Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LEE, HAN CHOON;JANG, DONG YEON;LEE, SANG YEUL;AND OTHERS;REEL/FRAME:018751/0393 Effective date: 20061228 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |