KR20140099380A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
KR20140099380A
KR20140099380A KR1020130011836A KR20130011836A KR20140099380A KR 20140099380 A KR20140099380 A KR 20140099380A KR 1020130011836 A KR1020130011836 A KR 1020130011836A KR 20130011836 A KR20130011836 A KR 20130011836A KR 20140099380 A KR20140099380 A KR 20140099380A
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KR
South Korea
Prior art keywords
tube portion
spiral tube
refrigerant
shell
spiral
Prior art date
Application number
KR1020130011836A
Other languages
Korean (ko)
Inventor
이병휘
이주석
문정욱
김정규
Original Assignee
엘지전자 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.)
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Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to KR1020130011836A priority Critical patent/KR20140099380A/en
Priority to EP13193106.5A priority patent/EP2762820B1/en
Priority to ES13193106.5T priority patent/ES2574429T3/en
Priority to US14/089,951 priority patent/US9677819B2/en
Priority to EP14151438.0A priority patent/EP2762821B1/en
Publication of KR20140099380A publication Critical patent/KR20140099380A/en

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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • 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
    • F28F1/12—Tubular 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
    • F28F1/124—Tubular 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 being formed of pins
    • 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
    • F28D1/0472—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 helically or spirally coiled

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  • 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 of the present invention includes: a shell; an incurrent pipe for guiding heat source water into the shell; a first refrigerant tube having a first spiral tube portion; a second refrigerant tube having a second spiral tube portion which has a bigger radius than the first spiral tube portion; and an excurrent pipe where the heat source water, heat-exchanged with a refrigerant, is discharged. The first and second refrigerant tubes are arranged in a row, and the second spiral tube portion has a bigger pitch per turn than the first spiral tube portion, while having a smaller number of turns to make the first and second refrigerant tubes have the same flow passage length or minimize the flow passage length difference between the two, and to prevent a degradation of performance, which can occur when the flow passage lengths of the first and second refrigerant tubes are different.

Description

Heat exchanger

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger, and more particularly, to a heat exchanger in which a helical tube portion wound in a spiral shape is located inside a shell.

Generally, a heat exchanger is a device for moving heat between two fluids, and is widely used for cooling, heating, hot water supply, and the like.

The heat exchanger functions as a waste heat recovering heat exchanger for recovering the waste heat or as a cooler for cooling the hot fluid or as a condenser for condensing the vapor or as an evaporator for evaporating the coolant fluid .

Various types of heat exchangers may be used, including a tube through which the first fluid passes, a finned tube heat exchanger with the fin provided on the tube, a shell through which the first fluid passes, and a second fluid through which heat exchange with the first fluid passes A dual tube heat exchanger having an inner tube through which the first fluid passes and a second fluid that undergoes heat exchange with the first fluid and surrounds the inner tube and has an outer tube; And a plate heat exchanger in which the fluid passes through the heat transfer plate.

 The shell tubular heat exchanger in the heat exchanger can be formed in a spiral shape, and the spiral tube can heat exchange the first fluid and the second fluid inside the shell. The first fluid can flow into the shell and pass through the shell to heat or cool the second fluid, and the second fluid can exchange heat with the first fluid as it passes through the tube.

KR 10-0353334 B1 (2003.02.07)

The heat exchanger according to the related art includes a plurality of coils wound in a clockwise or counterclockwise direction up and down from the helical coil to the outermost coil winding and the innermost coil winding, There is a problem in that the structure is complicated because it is connected to each of the exhaust manifolds.

A shell according to the present invention for solving the above-mentioned problems; A water inlet tube for guiding the heat source water into the shell; A first refrigerant tube in which a first spiral tube portion is formed; A second refrigerant tube having a second spiral tube portion having a radius larger than a radius of the first spiral tube portion; The first refrigerant tube and the second refrigerant tube are connected in parallel, and the second spiral tube portion has a larger pitch between turns than the first spiral tube portion, and the number of turns is smaller than that of the first spiral tube portion .

The number of turns of the second spiral tube portion can be determined by the following Equation (1).

[Formula 1]

N2 = N1 x R1 / R2

Here, N2 is the number of turns of the second helical tube portion,

N1 is the number of turns of the first helical tube portion,

Wherein R1 is a radius of the first spiral tube,

And R2 is a radius of the second spiral tube portion.

The pitch between the turns of the second helical tube portion can be determined by the following Equation (2).

[Formula 2]

P2 = P1 X N1 / N2

Here, P2 is a pitch between the turns of the second helical tube portion,

And P1 is a pitch between the turns of the first spiral tube portion.

The pitch between the turns of the second spiral tube portion may be 1.3 to 1.5 times the pitch between the first spiral tube portions.

The second spiral tube portion may be disposed between the first spiral tube portion and the shell.

The first spiral tube portion and the second spiral tube portion may be vertically arranged inside the shell.

The vertical center axis of the first helical tube portion and the vertical center axis of the second helical tube portion may be matched.

The first upper extension portion extending from the uppermost turn of the first spiral tube portion may pass through a space formed by the first spiral tube portion.

The first upper extension may penetrate the lower plate of the shell.

And the second upper extension portion extending from the uppermost turn of the second spiral tube portion may pass through a space formed by the first spiral tube portion.

The second upper extension may penetrate the lower plate of the shell.

A pin may protrude from at least one of the first spiral tube portion and the second spiral tube portion.

The fin may have an inclination angle with the spiral tube portion in which the pin is protruded.

The inclination angle may be an acute angle.

The longitudinal direction of the fin may not coincide with the tangential direction of the projected spiral tube portion.

The water inlet pipe may disperse the heat source water into a plurality of positions in the shell.

The inlet pipe may have a plurality of outlets for dispersing the heat source water into the shell.

One of the plurality of outlets can guide the heat source water toward the first helical tube portion and the other can guide the heat source water toward the second helical tube portion.

The plurality of outlets can guide the heat source water toward the first spiral tube portion, and the large-diameter outlet can guide the heat source water toward the second spiral tube portion.

A plurality of the water inlet pipes may be spaced apart to guide the heat source water to a plurality of positions in the shell.

The present invention can be implemented with a simple structure that the first refrigerant tube and the second refrigerant tube have the same channel length or the difference in channel length can be minimized and the channel lengths of the first refrigerant tube and the second refrigerant tube are different There is an advantage that the performance degradation can be prevented.

1 is a view illustrating a configuration of an air conditioner to which a first embodiment of a heat exchanger according to the present invention is applied.
2 is a side view of a heat exchanger according to a first embodiment of the present invention,
FIG. 3 is a plan view showing a lower shell plate of the first embodiment of the heat exchanger according to the present invention, FIG.
4 is a longitudinal sectional view of the first embodiment of the heat exchanger according to the present invention,
5 is a plan view showing the inside of the first embodiment of the heat exchanger according to the present invention,
FIG. 6 is an exploded perspective view showing a plurality of refrigerant tubes of the first embodiment of the heat exchanger according to the present invention, FIG.
FIG. 7 is a side view showing the inside of the second embodiment of the heat exchanger according to the present invention,
8 is a plan view of the refrigerant tube of the second embodiment of the heat exchanger according to the present invention,
FIG. 9 is a longitudinal sectional view showing a configuration of a main portion of a heat exchanger according to a third embodiment of the present invention.

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

1 is a view illustrating a configuration of an air conditioner to which a first embodiment of a heat exchanger according to the present invention is applied.

The air conditioner shown in Fig. 1 may include a compressor 2, a first heat exchanger 4, an expansion mechanism 6, and a second heat exchanger 8. [ The first heat exchanger (4) can heat exchange the refrigerant with the heat source water. The heat source water can function as cooling water for absorbing the heat of the refrigerant or as heating water for heating the refrigerant. The air conditioner includes a compressor (2) in which a refrigerant is compressed, a first heat exchanger (4) in which the refrigerant undergoes heat exchange with the heat source water, an expansion mechanism (6) in which the refrigerant expands, and a second heat exchanger (8).

The refrigerant can pass through the compressor (2), the first heat exchanger (4), the expansion mechanism (6), and the second heat exchanger (8) in this order. That is, the refrigerant compressed in the compressor 2 can be recovered to the compressor 2 after sequentially passing through the first heat exchanger 4, the expansion mechanism 6, and the second heat exchanger 8. In this case, the first heat exchanger 4 can function as a condenser for condensing the refrigerant, the second heat exchanger 8 can function as an evaporator for evaporating the refrigerant, and the heat source number is compressed in the compressor 2 And may be cooling water that absorbs the heat of the refrigerant.

The refrigerant can pass through the compressor (2), the second heat exchanger (8), the expansion mechanism (6), and the first heat exchanger (4) in this order. That is, the refrigerant compressed in the compressor 2 can be recovered to the compressor 2 after sequentially passing through the second heat exchanger 8, the expansion mechanism 6, and the first heat exchanger 4. In this case, the second heat exchanger 8 may function as a condenser for condensing the refrigerant, the first heat exchanger 4 may function as an evaporator for evaporating the refrigerant, and the heat source water may flow through the first heat exchanger 4, The heat can be heated by the refrigerant passing through the heat exchanger.

The air conditioner includes a compressor (2) in which a refrigerant is compressed, a first heat exchanger (4) in which the refrigerant undergoes heat exchange with the heat source water, an expansion mechanism (6) in which the refrigerant expands, And a flow switching valve (not shown) which includes the compressor 8 and sends the refrigerant compressed in the compressor 2 to the first heat exchanger 4 or the second heat exchanger 8. The air conditioner is configured such that the refrigerant compressed in the compressor 2 sequentially passes through the flow path switching valve, the first heat exchanger 4, the expansion mechanism 6, the second heat exchanger 8 and the flow path switching valve And a first circulation circuit that is recovered to the compressor (2). The air conditioner is a system in which the refrigerant compressed in the compressor 2 is supplied to the first heat exchanger 4, the second heat exchanger 8, the expansion mechanism 6, the first heat exchanger 4, And the second circulation circuit which is recovered to the compressor 2 after passing through the second circulation circuit. The first circulation circuit can be a circuit in the cooling operation in which the room is cooled by the second heat exchanger 8. The first heat exchanger 4 can function as a condenser for condensing the refrigerant, The unit 8 can function as an evaporator for evaporating the refrigerant. The second circulation circuit can be a circuit in the heating operation in which the room is heated by the second heat exchanger 8 and the second heat exchanger 8 can function as a condenser for condensing the refrigerant, The unit (4) can function as an evaporator for evaporating the refrigerant.

 The heat source water can be composed of a heat source such as water or an antifreeze, and the refrigerant can be composed of any one of various refrigerants such as a freon refrigerant and a carbon dioxide refrigerant used in an air conditioner.

The compressor (2) may be composed of various compressors for compressing the refrigerant, and may be various compressors such as a rotary compressor, a scroll compressor, a screw compressor and the like. The compressor (2) may be connected to the first heat exchanger (4) and the compressor outlet flow path (3).

The first heat exchanger (4) may be constituted by a shell tubular heat exchanger. The first heat exchanger 4 may include a shell 20 through which a heat source such as water or an antifreeze passes, and a refrigerant tube 24 through which the refrigerant passes. The first heat exchanger (4) may be connected to the expansion mechanism (6) and the first heat exchanger expansion device connection flow path (5). The first heat exchanger 4 will be described later in detail.

The expansion mechanism (6) may be a capillary tube or an electronic expansion valve in which the refrigerant expands. The expansion mechanism (6) may be connected to the second heat exchanger (8) and the expansion mechanism second heat exchanger connecting flow path (7).

The second heat exchanger 8 may be constituted by a fin tube type heat exchanger or a coil type heat exchanger through which the refrigerant passes. The second heat exchanger 8 may include a refrigerant tube that exchanges heat with indoor air while passing the refrigerant. The second heat exchanger 8 may further include a fin which is a heat transfer member coupled with the refrigerant tube. The second heat exchanger (8) can be connected to the compressor (2) and the compressor suction passage (9).

The air conditioner may include a heat treatment unit (10) connected to the first heat exchanger (4). The heat treatment unit 10 may be configured as a cooler for cooling the heat source water when the first heat exchanger 4 functions as a condenser for condensing the refrigerant. The heat treatment unit 10 may be constituted by a heater for heating the heat source water when the first heat exchanger 4 functions as an evaporator for evaporating the refrigerant. When the heat treatment unit 10 is constituted by a cooler, the heat treatment unit 10 may include a cooling tower for cooling the heat source water. The heat treatment unit 10 can be connected to the first heat exchanger 4 and the water pipes 12 and 14. The first heat exchanger 4 can be connected to the heat treatment unit 10 and the water outlet pipe 12 and the heat source water of the first heat exchanger 4 can be connected to the heat treatment unit 10 through the water outlet pipe 12 . The first heat exchanger 4 may be connected to the heat treatment unit 10 and the inlet pipe 14 and the heat source water of the heat treatment unit 10 may be connected to the first heat exchanger 4 via the inlet pipe 14 . At least one of the heat treatment unit 10, the water outlet pipe 12 and the water inlet pipe 14 may be provided with a circulation mechanism such as a pump for circulating the heat source water to the heat treatment unit 10 and the first heat exchanger 4 .

The air conditioner may further include an indoor fan (16) for circulating air in the room to the second heat exchanger (8) and then discharging the air to the room again.

The compressor 2, the first heat exchanger 4, the expansion mechanism 6, the second heat exchanger 8, and the indoor fan 16 can be installed in one air conditioning unit, To the second heat exchanger (8), and then discharged back to the room through a duct or the like to cool or heat the room. The heat treatment unit 10 may be installed in addition to one air conditioning unit and may be connected to one air conditioning unit by water pipes 12 and 14. [

The compressor 2, the first heat exchanger 4, the expansion mechanism 6, the second heat exchanger 8 and the indoor fan 16 may be installed in a distributed manner in a plurality of air conditioning units I . The first heat exchanger 4 and the indoor fan 16 can be installed together in the indoor unit I and the compressor 2 and the first heat exchanger 4 can be installed together in the compression unit O Can be installed. The expansion mechanism (6) may be installed in at least one of the indoor unit (I) and the compression unit (O). The expansion mechanism (6) can be provided with one expansion mechanism in the indoor unit (I) or the compression unit (O). It is possible that a plurality of expansion mechanisms 6 may be provided, the first expansion mechanism may be installed in the indoor unit I, and the second expansion mechanism may be installed in the compression unit O. The first expansion mechanism may function as an outdoor expansion mechanism which is installed closer to the first heat exchanger (4) of the first heat exchanger (4) and the second heat exchanger (8). The second expansion mechanism can function as an indoor expansion mechanism that is installed closer to the first heat exchanger (4) and the second heat exchanger (8) of the second heat exchanger (8). The indoor unit (I) can be installed in a room to be cooled or heated. The compression unit (O) may be installed in a machine room, a basement or the like of a building or on the roof. The compression unit (O) can be connected to the heat treatment unit (10) by the water pipes (12) and (14).

Hereinafter, the first heat exchanger 4 will be referred to as a heat exchanger.

FIG. 2 is a side view of the first embodiment of the heat exchanger according to the present invention, FIG. 3 is a plan view of the lower shell plate of the first embodiment of the heat exchanger according to the present invention, FIG. 5 is an exploded perspective view illustrating a plurality of refrigerant tubes of the first embodiment of the heat exchanger according to the present invention, and FIG. 6 is a plan view of the interior of the first embodiment of the heat exchanger according to the present invention.

The heat exchanger (4) comprises a shell (20); A water inlet pipe (22) for guiding the heat source water into the shell (20); A plurality of refrigerant tubes (24) (26) through which the refrigerant passes; And a water outlet pipe 28 through which the heat source water heat-exchanged with the refrigerant flows out. The heat source water can be introduced into the shell 20 through the inlet pipe 22 and can be heat exchanged with the plurality of refrigerant tubes 24 and 26 inside the shell 20 and through the outlet pipe 28 Can be discharged outside the heat exchanger (4). The refrigerant can be heat-exchanged through the plurality of refrigerant tubes 24 and 26 with the heat source water inside the shell 20 while passing through the plurality of refrigerant tubes 24 and 26. The refrigerant can be evaporated while absorbing the heat of the heat source water when the temperature of the refrigerant is lower than the temperature of the heat source in the shell 20. The refrigerant can be condensed while heat is dissipated by the heat source water when the temperature of the refrigerant is higher than the heat source number inside the shell 20.

The shell 20 may have an empty space formed therein. The shell 20 can be arranged long up and down. The shell 20 may include a lower plate 31, a hollow shell 32 disposed on the upper side of the lower plate 31, and an upper plate 33 disposed on the upper side of the hollow shell 32. The hollow shell 32 may be formed in the shape of a hollow cylinder or a hollow polygonal cylinder. The hollow shell 32 may be formed with a lower flange 34 coupled to the lower plate 31 by a fastening member such as a bolt and a nut. The hollow shell 32 may have an upper flange 35 coupled to the upper plate 33 by a fastening member such as a bolt and a nut. The lower opening surface of the hollow shell 32 may be blocked by the lower plate 31 and the upper opening surface of the hollow shell 32 may be closed by the upper plate 33, .

The shell 20 may be provided with coolant tube through holes 36a, 36b, 37a, 37b through which the coolant tubes 24, 26 pass. The shell 20 may be provided with two refrigerant tube through holes per one refrigerant tube. When the heat exchanger 4 includes two refrigerant tubes 24 and 26, four refrigerant tube through holes 36a, 36b, 37a and 37b may be formed. The shell 20 may be provided with a water inlet pipe through hole 38 through which the water inlet pipe 22 passes. The shell (20) may be provided with a water pipe through-hole (39) through which the water pipe (28) penetrates. The heat exchanger 4 is constructed so that both the water inlet pipe 22, the plurality of refrigerant tubes 24 and 26 and the water outlet pipe 28 are connected to one of the lower plate 31 and the hollow shell 32 and the upper plate 33 As shown in FIG. The heat exchanger 4 may be formed with the refrigerant tube through holes 36a, 36b, 37a, 37b in the lower plate 31. [ The heat exchanger (4) can be formed with a water inlet pipe through hole (38) in the lower plate (31). The heat exchanger (4) can be formed with a water pipe through-hole (39) in the lower plate (31).

The water inlet pipe 22 may be positioned at one end outside the shell 20 and at the other end inside the shell 20. The other end of the water inlet pipe 22 positioned in the shell 20 may be positioned below at least one of the plurality of refrigerant tubes 24 and 26.

 The plurality of refrigerant tubes (24) and (26) may be connected in parallel with each other. A plurality of refrigerant tubes (24) (26) may be disposed through the shell (20). One end of the plurality of refrigerant tubes 24 and 26 located outside the shell 20 may be connected to the branch tube. The refrigerant tubes (24) and (26) may be connected to the joint pipe at the other end located outside the shell (20). The compressor outlet line 3 shown in FIG. 1 may be connected to the branch line, and the first heat exchanger expansion device connecting line 5 shown in FIG. 1 may be connected to the composite line. The refrigerant in the compressor outlet flow path 3 can be distributed to the plurality of refrigerant tubes 24 and 26 in the branch tube and the refrigerant having passed through the plurality of refrigerant tubes 24 and 26 is combined in the composite tube, Can be flowed to the heat exchanger expansion mechanism connection channel (5). The plurality of refrigerant tubes 24 and 26 may have a low heat exchange performance when the lengths of the refrigerant paths are different from each other, It is desirable that the difference be minimized.

 The plurality of refrigerant tubes (24) and (26) may include at least two refrigerant tubes through which the refrigerant passes, and each of the at least two refrigerant tubes may include a spiral tube portion in which a plurality of turns are spirally and continuously wound. The refrigerant tubes (24) and (26) may have different diameters (R1) and (R2) of the spiral tube portions. The spiral tube radius R1 of one of the plurality of refrigerant tubes 24 and 26 may be shorter than the spiral tube radius R2 of the other one of the refrigerant tubes 24 and 26. [ Each of the plurality of refrigerant tubes 24 and 26 may be installed such that the spiral tube portion is positioned between the vertical center axis Z of the shell 20 and the inner circumferential surface 21 of the shell 20. [ The plurality of refrigerant tubes 24 and 26 are arranged such that the spiral tube portion of the refrigerant tube 24 having the helical tube portion with a smaller radius R1 is connected to the vertical center axis Z of the shell 20 and the inner periphery of the shell 20 Can be installed closer to the vertical center axis Z of the shell 20 of the surface 21. The plurality of refrigerant tubes 24 and 26 are arranged such that the spiral tube portion of the refrigerant tube 26 having the helical tube portion with a larger radius R2 is connected to the vertical center axis Z of the shell 20, Can be installed closer to the inner circumferential surface (21) of the shell (20) of the surface (21). The spiral tube portion closer to the vertical center axis Z of the shell 20 may be an inner spiral tube portion with respect to the vertical center axis Z of the shell 20 and the inner circumferential surface 21 of the shell 20 may be an inner- May be an outer helix tube portion with respect to the vertical central axis Z of the shell 20. [ The outer helical tube portion can be located between the inner helical tube portion and the inner circumferential surface of the shell (20). The plurality of refrigerant tubes 24 and 26 may have a pitch between turns of the outer spiral tube portion longer than a pitch between turns of the inner spiral tube portion and a number of turns of the outer spiral tube portion may be smaller than the number of turns of the inner spiral tube portion, The length of the inner helical tube portion and the length of the outer helical tube portion may be the same or the difference in the length of the channel between the inner helical tube portion and the outer helical tube portion may be minimized. The plurality of refrigerant tubes (24) and (26) may have a longer pitch between turns and a smaller number of turns as the spiral portion closer to the inner circumferential surface (21) of the shell (20).

The plurality of refrigerant tubes 24 and 26 may have different numbers of turns and pitches between the turns of the refrigerant tubes in which the two refrigerant tubes are connected in parallel and connected in parallel. In the refrigerant tubes 24 and 26, three or four or more refrigerant tubes are connected in parallel and connected in parallel, the pitch and the number of turns of the helical tube portions may be different from each other. When three or more refrigerant tubes are installed, the pitch between turns of the refrigerant tube closest to the inner circumferential surface 21 of the shell 20 is largest and the number of turns is the smallest, and the vertical The pitch of the turn of the refrigerant tube nearest to the center axis Z is the smallest in the turn pitch and the number of turns can be the greatest.

The water outlet pipe 28 may be positioned at one end outside the shell 20 and at the other end inside the shell 20. The other end of the water outlet pipe 28 located inside the shell 20 may be located below the upper plate 33. The water outlet pipe 28 is capable of arranging one member through the shell 20, and it is possible for the two members to guide the outflow of the heat source water. The water outlet pipe 28 may be located in a space formed by a plurality of spiral tube portions located in the innermost portion of the refrigerant tubes 24 and 26. The water outlet pipe 28 may be connected to the water outlet pipe 12 shown in Fig. 1 at a portion 30 located outside the shell 20. [ The water outlet pipe 28 is provided with an inner water outlet pipe 29 located inside the shell 20 and an outer water outlet pipe 30 located outside the shell 20 when a plurality of members guide the water outlet of the heat source water . The upper end of the inner water pipe 29 may be separated from the upper plate 33 of the shell 20 and the lower end thereof may be coupled to the lower plate 31 of the shell 20. The outer water pipe 30 may be coupled to the water pipe through-hole 39 formed at the upper end of the lower plate 31 of the shell 20. The outer water pipe 30 may be smaller in diameter than the inner water pipe 29.

 Hereinafter, the plurality of refrigerant tubes 24 and 26 will be described as including the first refrigerant tube 24 and the second refrigerant tube 26. [

 The first refrigerant tube 24 has a first spiral tube portion 45 in which a plurality of turns 41, 42, 43 and 44 are spirally and continuously wound. The first spiral tube portion 45 may be vertically disposed inside the shell 20. The first spiral tube portion 45 can be continuous along the helical axis H1 with a plurality of turns 41, 42, 43 and 44 having the same distance as the vertical center axis X. [ The first spiral tube portion 45 may be formed with at least two intermediate turns 42 and 43 between the uppermost turn 41 and the lowermost turn 44. [ The first spiral tube portion 45 may be formed in a coil shape in its entirety and a space S may be formed inside the first spiral tube portion 45. The first spiral tube portion 45 may have one vertical central axis X. [ The first spiral tube portion 45 can be positioned such that the uppermost turn 41 can be positioned below the upper plate 33 and the lowermost turn 44 can be positioned above the lower plate 31, (Not shown).

A first upper extension tube portion 46 may extend on the uppermost turn 41 of the first helical tube portion 45 and a lower first extension tube portion 46 may be provided on the lowermost turn 44 of the first helical tube portion 45 47 can be extended.

 The first upper extension tube portion 46 may be formed such that its upper end is rounded at the uppermost turn 41 of the first spiral tube portion 45 and may have a vertical portion that is long in the up and down direction. The first upper extension tube portion 46 can penetrate the space S formed by the first spiral tube portion 45. The first upper extension tube portion 46 can penetrate the lower plate 31 of the shell 20.

The first lower extension pipe portion 47 may be formed such that its upper end is rounded at the lowermost turn 44 of the first spiral pipe portion 45 and may have a vertical portion that is long in the vertical direction. The first lower extension tube portion 47 can penetrate the lower plate 31 of the shell 20.

  The second refrigerant tube 26 has a second spiral tube portion 55 through which the refrigerant passes and a plurality of turns 51, 52, 53 and 54 are spirally wound in succession. The second helical tube portion 55 may be arranged vertically in the shell 20. The second helical tube portion 55 may be continuous with the plurality of turns 51, 52, 53 and 54 having the same distance from the vertical center axis Y along the helical axis H2. The second spiral tube portion 55 may be formed with at least two intermediate turns 52 and 53 between the uppermost turn 51 and the lowermost turn 54. [ The second helical tube portion 55 may be formed in a coil shape as a whole and the second helical tube portion 55 may be disposed between the first helical tube portion 45 and the shell 20. The second helical tubular portion 55 may be disposed between the first helical tubular portion 45 and the hollow shell 32. The pitch between the turns of the second spiral tube portion 55 is larger than that of the first spiral tube portion 55 and the number of turns of the second spiral tube portion 55 may be smaller. The gap between the turns of the second helical tube portion 55 may be larger than the gap between the turns of the first helical tube portion 55. The first spiral tube portion 45 may have no clearance or clearance between the turns and the second spiral tube portion 55 may be formed with a gap larger than the gap of the first spiral tube portion 45 between the turns have. The number of heat sources may be in contact with the turns of the first spiral tube portion 45 through the gap between the turns of the second spiral tube portion 55 to be heat-exchanged. The heat source is heat-exchanged with the lower portion of the turn 52 positioned on the upper side of two adjacent turns between the adjacent two turns of the second spiral tube portion 55 and exchanged with the upper portion of the turn 53 positioned on the lower side of the adjacent two turns, And can be heat-exchanged with the outer periphery of the turn of the first spiral tube portion 55 through the gap. The second spiral tube portion 55 may have one vertical center axis Y. [ The second spiral tube portion 55 may be installed so that the vertical center axis Y coincides with the vertical center axis X of the first spiral tube portion 55. The vertical center axis Y of the second helical tube portion 55 and the vertical center axis X of the first helical tube portion 55 can coincide with the vertical center axis Z of the shell 20. [ The second spiral tube portion 55 can be positioned such that the uppermost turn 51 is positioned below the upper plate 33 and the lowermost turn 54 is positioned above the lower plate 31, (Not shown).

The second upper extension tube portion 56 can be extended to the uppermost turn 51 of the second helical tube portion 55 and the second lower extension tube portion 56 can be extended to the lowermost turn 54 of the second helical tube portion 55 57 can be extended.

 The upper end portion of the second upper extension tube portion 56 may be rounded at the uppermost turn 51 of the second helical tube portion 55 and may have a vertical portion that is longer in the up and down direction. The second upper extension tube portion 56 can pass through the space S formed by the first spiral tube portion 55. The second upper extension tube portion 56 can penetrate the lower plate 31 of the shell 20.

The second lower extension pipe portion 57 may be formed such that its upper end is rounded at the lowermost turn 54 of the second spiral pipe portion 55 and may have a vertical portion that is long in the up and down direction. The second lower extension tube portion 57 can penetrate the lower plate 31 of the shell 20.

 The number of turns of the second spiral tube portion 55 can be determined by the following equation (1).

[Formula 1]

N2 = N1 x R1 / R2

Here, N2 is the number of turns of the second helical tube portion, N1 is the number of turns of the first helical tube portion, R1 is the radius of the first helical tube portion, and R2 is the radius of the second helical tube portion.

  The pitch between the turns of the second helical tube portion 55 can be determined by the following Equation 2.

[Formula 2]

P2 = P1 X N1 / N2

Here, P2 is the pitch between the turns of the second spiral tube portion, and P1 is the pitch between the turns of the first spiral tube portion.

  The pitch P2 between turns of the second helical tube portion 55 may be 1.3 to 1.5 times the pitch P1 between the turns of the first helical tube portion 45. [

For example, when the number of turns of the second spiral tube portion 55 is 11 and the number of turns of the first spiral tube portion 45 is 16, the pitch P2 between turns of the second spiral tube portion 55 is It can be approximately 1.454 times the pitch between turns. When the number of turns of the second spiral tube portion 55 is 12 and the number of turns of the first spiral tube portion 45 is 16, the pitch P2 between the turns of the second spiral tube portion 55 is equal to the pitch It can be approximately 1.333 times. When the number of turns of the second helical tube portion 55 is 12 and the number of turns of the first helical tube portion 45 is 17, the pitch P2 between turns of the second helical tube portion 55 is equal to the pitch between the turns of the first helical tube portion Can be approximately 1.416 times.

The heat exchanger (4) may include a shell support (60) for supporting the shell (20). The shell support 60 may include a support plate 62 on which the shell 20 is mounted and a plurality of support legs 64 and 66 for supporting the support plate 62. At least two support legs 64 (66) may be provided.

Hereinafter, the operation of the present invention will be described.

First, in operation of the air conditioner, the refrigerant can be dispersed and flowed into the first refrigerant tube 24 and the second refrigerant tube 26, and the heat source water flows through the inlet pipe 22 into the interior of the shell 20 Lt; / RTI > The number of heat sources may gradually flow from the inner lower portion of the shell 20 to the inner upper portion of the shell 20 and the first refrigerant tube 24 and the second refrigerant tube 26 ). ≪ / RTI > When the speed at which the inside of the shell 20 is received is small, the number of heat sources can be gradually elevated inside the shell 20, While being swirled in the spiral direction of the second spiral tube portion 55 while being guided by the second spiral tube portion 55. The heat source water flowing into the shell 20 flows into the gap between two adjacent turns of the second spiral tube portion 55 to be heat-exchanged with each of the two adjacent turns of the second spiral tube portion 55, And can be heat-exchanged with the outer circumferential portion of the turn of the spiral tube portion 44. The number of heat sources can be raised spirally along two adjacent turns of the second spiral tube portion 55 and the number of heat sources can be increased by the refrigerant passing through the second spiral tube portion 45 and the refrigerant passing through the first spiral tube portion 45 Lt; / RTI > The refrigerant passes through the first refrigerant tube (24) and the second refrigerant tube (26) and is allowed to pass through the independent refrigerant passage, and can be heat-exchanged with the heat source water. The refrigerant is in a state in which the length of the first spiral tube portion 45 and the length of the second spiral tube portion 55 are the same or the difference in the length of the channel is minimized when the refrigerant passes through the first spiral tube portion 45 and the second spiral tube portion 55 , The deterioration of the heat exchange performance, which occurs when the length of the channel length is large, can be minimized and heat exchange can be efficiently performed with the number of heat sources.

 FIG. 7 is a side view showing the inside of the second embodiment of the heat exchanger according to the present invention, and FIG. 8 is a plan view showing the refrigerant tube of the second embodiment of the heat exchanger according to the present invention.

The heat exchanger of the present embodiment can be formed with fins that can increase the heat transfer performance between the refrigerant and the heat source water in the refrigerant tube. The fins may be formed to protrude from the outer surface of the refrigerant tube. A plurality of pins (71) and (72) may be formed in the refrigerant tube. The plurality of fins 71 and 72 may be formed only in the portion of the refrigerant tube located inside the shell 20 and not in the portion located outside the shell 20. [ The pins 71 and 72 can be formed on each of the spiral tube portion and the extension tube portion, and can be formed only on the spiral tube portion, not on the extension tube portion. The plurality of fins 71 and 72 can be formed in each of the plurality of refrigerant tubes 24 and 26. The plurality of fins 71 and 72 can be formed in each of the plurality of refrigerant tubes 24 and 26 with respect to the vertical center axis of the shell 20 It is possible to form only the refrigerant tube located at the outermost position. 7 shows a configuration in which a plurality of fins 71 and 72 are formed only on the spiral tube portion of the second refrigerant tube 26 of the first refrigerant tube 24 and the second refrigerant tube 26. However, At least one of the first and second helical tube portions 26 and 26 may be formed with pins 71 and 72 and the plurality of pins 71 and 72 may be spaced apart from each other.

When the pins 71 and 72 are formed on the spiral tube portion, a plurality of the pins 71 and 72 may be formed apart from each other along the spiral tube portion. The pins 71 and 72 can be formed to protrude from the inner circumferential side and the outer circumferential side of the spiral tube portion, respectively. The pins 71 and 72 are not formed on the inner peripheral side of the spiral tube portion but can be formed to protrude only on the outer peripheral side of the spiral tube portion. The pins 71 and 72 are not formed on the outer peripheral side of the spiral tube portion but can be formed to protrude only on the inner peripheral side of the spiral tube portion. The pins 71 and 72 may be formed in a plate or corrugated shape. The pins 71 and 72 may be formed so as to have an inclination angle A with respect to the spiral tube portion. The pins 71 and 72 may be formed so that their longitudinal direction does not coincide with the tangential line C direction of the spiral tube portion. The tangent line C of the spiral tube section is a tangent line with respect to the longitudinal direction (i.e., spiral direction) of each tube section (i.e., turn) spirally wound and the tangent line C of the spiral tube section is such that each turn is spirally wound Due to the structure, it may have an acute angle of inclination with respect to the horizontal line D. On the other hand, the pins 71 and 72 may have a tangent line C and an inclination angle A of the spiral tube portion. Here, it is preferable that the inclination angle A between the tangent line C of the spiral tube portion and the pins 71 and 72 be an acute angle. The extension line B extending in the longitudinal direction at the pins 71 and 72 may have the tangent line C and the inclination angle A of the spiral tube portion. Here, it is preferable that the inclination angle A between the tangent line C of the spiral tube portion and the pins 71 and 72 be an acute angle. The larger the inclination angle A, the more the heat sources can be guided in the oblique direction, and the smaller the inclination angle A, the more the number of heat sources can be guided in the inclined direction close to the horizontal. When the inclination angle A of the fins 71 and 72 is equal to or as close as possible to the direction of the spiral circulation flow of the heat source water, the number of heat sources can be raised by spiral- And the inclination angle A of the pins 71 and 72 is preferably formed to be equal to the direction of the helical swirl flow of the heat source water.

FIG. 9 is a longitudinal sectional view showing a configuration of a main portion of a heat exchanger according to a third embodiment of the present invention.

Referring to FIG. 9, the water inlet pipe 22 'may be formed to disperse the heat source water into a plurality of positions in the shell 20. The number of heat sources can be dispersed to a plurality of positions in the shell 20 at the same time, and the heat source of the dispersed and inflowed heat sources can be maximally heat-transferred to the refrigerant tubes 24 and 26. The water inlet pipe 22 'is capable of dispersing the number of heat sources in a plurality of positions inside the shell 20, and a plurality of the water outlet pipes 22' can be spaced apart and dispersed in a plurality of positions in the shell 20.

The number of the inlet pipes 22 'may be one or more than one in the heat exchanger 4. When the inlet pipe 22 'is disposed in a single number in the heat exchanger 4, one inlet 22a and a plurality of outlets 22b and 22c may be formed. The inlet pipe 22 'can be connected to the inlet pipe 14 shown in FIG. 1 and has a plurality of internal oil passages for dispersing the heat source water into a plurality of outlets 22b and 22c And a plurality of outlets 22b, 22c can be positioned within the shell 20, respectively. One of the plurality of outlets 22b and 22c is arranged so as to guide the heat source water toward the first helical tube portion 45 of the first refrigerant tube 24, The other one 22c of the outlets 22b and 22c may be arranged to guide the heat source water toward the second spiral tube portion 55 of the second refrigerant tube 26. [ The diameter of the plurality of outlets 22b and 22c of the water inlet pipe 22 'may be different. In this case, the water inlet pipe 22 'can be arranged such that the large-diameter outlet 22c guides the heat source water toward the second spiral pipe section 55 of the second refrigerant tube 26, and the small-diameter outlet 22b May be arranged to guide the heat source water toward the first spiral tube portion 45 of the first refrigerant tube 24. The refrigerant passes through the first spiral pipe portion 45 and the second spiral pipe portion 55 and flows into the first spiral pipe portion 45 due to the difference in radius between the first spiral pipe portion 45 and the second spiral pipe portion 55, And the centrifugal force of the refrigerant passing through the second spiral tube portion 55 may be different from each other. The first helical tube portion 45 has a smaller turning radius of the refrigerant and a larger pressure loss than the second helical tube portion 55 and the first helical tube portion 45 and the second helical tube portion 55 ) May cause unevenness of the refrigerant flow rate, and the flow rate of the refrigerant in the second spiral tube portion 55 having a relatively small pressure loss may be large. When the small diameter outlet 22b guides the heat source water to the first helical tube portion 45 and the large diameter outlet 22c guides the heat source water to the second helical tube portion 55, 55, and the refrigerant can be heat-exchanged with the heat source water evenly at the first spiral pipe portion 45 and the second spiral pipe portion 55.

When a plurality of the inlet pipes 22 'are disposed in the single heat exchanger 4, the number of the heat sources may be dispersed into a plurality of inlet pipes and then introduced into a plurality of positions in the shell 20. The plurality of inlet pipes can be branched so that their respective inlets are connected to the inlet pipe 14 shown in FIG. 1 at the inlet pipe 14. The plurality of inlet pipes may have their respective outlets positioned within the shell 20. The plurality of inlet pipes may have the same or different diameters. The plurality of water inlet pipes may be arranged such that the water inlet pipe having a large diameter guides the heat source water toward the second helical pipe section 55 of the second refrigerant tube 26 when the diameters are different, The tube may be arranged so as to guide the heat source water toward the first spiral tube portion 45 of the first refrigerant tube 24. A larger amount of heat source water can be guided to the second spiral tube portion 55, as in the case where a plurality of outlets 22b, 22c are formed in the water inlet tube 22 ', even when the plurality of inlet tube diameters are different, The refrigerant can be heat-exchanged with the heat source water at the first spiral tube portion 45 and the second spiral tube portion 55.

In this embodiment, the other components and actions other than the water inlet pipe 22 'are the same as or similar to those of the first or second embodiment of the present invention, and thus the same reference numerals are used and a detailed description thereof will be omitted.

 1 is connected to the water outlet pipe 28 and the water outlet pipe 12 shown in FIG. 1 is connected to the water inlet pipe 22, So that the heat source of the inlet pipe 14 can be exchanged with the refrigerant tube after flowing into the shell 20 through the outlet pipe 28. The heat source heat exchanged with the refrigerant tube is discharged through the inlet pipe 22 It is possible to dispense to the piping 12, and various embodiments are possible within the technical scope to which the present invention belongs.

4: Heat exchanger 20: Shell
22: inlet pipe 24: first refrigerant tube
26: second refrigerant tube 28: water outlet pipe
41: uppermost turn 42: lowest-end turn
45: first spiral tube portion 46: first upper side tube portion
47: first lower extension pipe portion 51: uppermost turn
52: Lowermost turn 55: Second spiral tube
56: second upper extension tube portion 57: second lower extension tube portion
P1: pitch between turns of the first spiral tube P2: pitch between turns of the second spiral tube
X: Vertical center axis of first spiral tube part Y: Vertical center axis of second spiral tube part

Claims (20)

A shell;
A water inlet tube for guiding the heat source water into the shell;
A first refrigerant tube in which a first spiral tube portion is formed;
A second refrigerant tube having a second spiral tube portion having a radius larger than a radius of the first spiral tube portion;
And a water outlet pipe through which the heat source water heat-exchanged with the refrigerant flows out,
The first refrigerant tube and the second refrigerant tube are connected in parallel,
Wherein the second spiral tube portion has a pitch larger than the first spiral tube portion and has a smaller turn number. The method according to claim 1,
And the number of turns of the second spiral tube portion is determined by the following equation (1).
[Formula 1]
N2 = N1 x R1 / R2
Here, N2 is the number of turns of the second helical tube portion,
N1 is the number of turns of the first helical tube portion,
Wherein R1 is a radius of the first spiral tube,
And R2 is a radius of the second spiral tube portion. 3. The method of claim 2,
And the pitch between the turns of the second spiral tube portion is determined by the following Expression (2).
[Formula 2]
P2 = P1 X N1 / N2
Here, P2 is a pitch between the turns of the second helical tube portion,
And P1 is a pitch between the turns of the first spiral tube portion. 4. The method according to any one of claims 1 to 3,
And the pitch between the turns of the second spiral tube portion is 1.3 to 1.5 times the pitch between the first spiral tube portions. The method according to claim 1,
And the second spiral tube portion is disposed between the first spiral tube portion and the shell. The method according to claim 1,
Wherein the first spiral tube portion and the second spiral tube portion are vertically arranged in the shell. The method according to claim 1,
Wherein the vertical center axis of the first spiral tube portion and the vertical center axis of the second spiral tube portion coincide. The method according to claim 1,
And the first upper extension portion extending from the uppermost turn of the first spiral portion passes through a space formed by the first spiral portion. 9. The method of claim 8,
And the first upper extension portion passes through the lower plate of the shell. The method according to claim 1,
And the second upper extension portion extending from the uppermost turn of the second spiral tube portion passes through a space formed by the first spiral tube portion. 11. The method of claim 10,
And the second upper extension portion penetrates the lower plate of the shell. The method according to claim 1,
Wherein at least one of the first spiral tube portion and the second spiral tube portion has a pin protruding therefrom. 13. The method of claim 12,
Wherein the fin has an inclined angle with the spiral tube portion in which the fin protrudes. 14. The method of claim 13,
Wherein the inclination angle is an acute angle. 13. The method of claim 12,
Wherein the longitudinal direction of the fin does not coincide with the tangential direction of the spiral tube portion in which the pin protrudes. The method according to claim 1,
Wherein the water inlet pipe disperses the heat source water into a plurality of positions in the shell. The method according to claim 1,
Wherein the water inlet pipe has a plurality of outlets for dispersing the heat source water into the shell. 18. The method of claim 17,
One of the plurality of outlets guiding the heat source water toward the first spiral tube portion and the other guiding the heat source water toward the second spiral tube portion. 18. The method of claim 17,
The plurality of outlets guiding the heat source water toward the first spiral tube portion and the outlet having a large diameter guiding the heat source water toward the second spiral tube portion. The method according to claim 1,
Wherein a plurality of the water inlet pipes are spaced apart to guide the heat source water to a plurality of positions in the shell.
KR1020130011836A 2013-02-01 2013-02-01 Heat exchanger KR20140099380A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1020130011836A KR20140099380A (en) 2013-02-01 2013-02-01 Heat exchanger
EP13193106.5A EP2762820B1 (en) 2013-02-01 2013-11-15 Air conditioner and heat exchanger therefor
ES13193106.5T ES2574429T3 (en) 2013-02-01 2013-11-15 Air conditioning and heat exchanger for this one
US14/089,951 US9677819B2 (en) 2013-02-01 2013-11-26 Air conditioner and heat exchanger therefor
EP14151438.0A EP2762821B1 (en) 2013-02-01 2014-01-16 Air conditioner and heat exchanger therefor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020130011836A KR20140099380A (en) 2013-02-01 2013-02-01 Heat exchanger

Publications (1)

Publication Number Publication Date
KR20140099380A true KR20140099380A (en) 2014-08-12

Family

ID=51745723

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020130011836A KR20140099380A (en) 2013-02-01 2013-02-01 Heat exchanger

Country Status (1)

Country Link
KR (1) KR20140099380A (en)

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