CN203605763U - Double-layer tubular heat exchanger and refrigeration circulating device - Google Patents
Double-layer tubular heat exchanger and refrigeration circulating device Download PDFInfo
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- CN203605763U CN203605763U CN201320613402.XU CN201320613402U CN203605763U CN 203605763 U CN203605763 U CN 203605763U CN 201320613402 U CN201320613402 U CN 201320613402U CN 203605763 U CN203605763 U CN 203605763U
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- tube
- heat transfer
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- transfer area
- heat exchanger
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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
- F28D7/10—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 arranged one within the other, e.g. concentrically
- F28D7/106—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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
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- 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
- F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular elements
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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
The utility model provides a double-layer tubular heat exchanger and a refrigeration circulating device. The refrigeration circulating device comprises an inner pipe (2), an outer pipe (1) and a heat transfer area expanding pipe (3), wherein first fluid flows through the inner pipe (2), the diameter of the outer pipe (1) is larger than that of the inner pipe (2), the outer pipe (1) covers the inner pipe (2), second fluid flows through the space between the outer pipe (1) and the inner pipe (2), the heat transfer area expanding pipe (3) is arranged in the space between the outer pipe (1) and the inner pipe (2), the length of an inner side contact portion (6) in contact with the outer wall of the inner pipe (2) is larger than the length of an outer side contact portion (7) in contact with the inner wall of the outer pipe (1) in the tubular circumference direction, in addition, convex-concave parts of a fin portion which cross-cuts the space in the tubular cross section and is located between the outer side contact portion (7) and the inner side contact portion (6) make contact with the outer wall of the inner pipe (2) and the inner wall of the outer pipe (1) in the oblique direction with the oblique angle smaller than 90 degrees, and the outer side contact portion (7) and the inner side contact portion (6) are welded in a brazing mode.
Description
Technical field
The utility model relates to combination to be had the pipe of different tube diameters and forms the double-tube type heat exchanger of two streams and use the refrigerating circulatory device of this double-tube type heat exchanger.
Background technology
As the example of the double-tube type heat exchanger of raising heat transfer property in the past, there is the double-tube type heat exchanger that a side's little diameter pipe (being denoted as below inner tube) is inserted to the side's that diameter is large pipe (being denoted as below outer tube) and form.And, following method has been proposed, using the inside of inner tube as the first stream, to be formed on two streams between pipe as the second stream, the heat transfer area enlarged tube that is configured as raised line shape is inserted to the second stream, make inner and outer tubes close contact, by the expansion effect of heat transfer area, improve heat transfer property (for example,, with reference to patent documentation 1).
[prior art document]
[patent documentation]
[patent documentation 1] TOHKEMY 2012-63067 communique (Fig. 1)
In above-mentioned patent documentation 1, a kind of double-tube type heat exchanger has been proposed, by inserting heat transfer area enlarged tube, expand heat transfer area and improve heat transfer property.But, do not mention about some concrete countermeasures that can improve to excellent in efficiency the heat transfer area enlarged tube of heat transfer property etc.
Utility model content
Therefore, the purpose of this utility model is double-tube type heat exchanger and the refrigerating circulatory device that obtains improving to excellent in efficiency heat transfer property.
The double-tube type heat exchanger of first method of the present utility model has: inner tube, and first fluid passes through therein, outer tube, diameter is larger and cover inner tube than inner tube, and second fluid is by the space between itself and described inner tube, heat transfer area enlarged tube, it is arranged in space, there is convex-concave shape, thereby, on pipe cross section, become Length Ratio on the pipe Zhou Fangxiang of inner side contact site of its part contacting with described outer wall of inner tube and become length on the pipe Zhou Fangxiang of outside contact site of its part contacting with described outer tube wall long, in addition, in described convex-concave shape, fin portion on pipe cross section between the inner side contact site in transversal space and described outside contact site contacts with described outer wall of inner tube and described outer tube wall from incline direction, described double-tube type heat exchanger carries out soldering to described outside contact site and described inner side contact site.
The double-tube type heat exchanger of second method of the present utility model is, in the double-tube type heat exchanger of first method, described fin portion has circular-arc on pipe cross section.
The double-tube type heat exchanger of Third Way of the present utility model is, in the double-tube type heat exchanger of first method or second method, described fin portion on pipe cross section for become the curved shape of convex in described inner tube side.
The double-tube type heat exchanger of cubic formula of the present utility model is, in the double-tube type heat exchanger of first method or second method, on pipe cross section, the described heat transfer area enlarged tube in the contact site of described inner side and described outer wall of inner tube angulation are less than the described heat transfer area enlarged tube in the contact site of described outside and described outer tube wall angulation.
The double-tube type heat exchanger of the 5th mode of the present utility model is, in the double-tube type heat exchanger of first method or second method, described outside contact site contacts in the mode that becomes a contact on pipe cross section, and described inner side contact site contacts in the mode that becomes line contact on pipe cross section.
The double-tube type heat exchanger of the 6th mode of the present utility model is, in the double-tube type heat exchanger of first method or second method, the external diameter of establishing the both ends of described outside contact site and the center angulation of described inner tube and outer tube and be θ 1, inner tube is d
io, outer tube internal diameter be d
oi, the convex form of described heat transfer area enlarged tube or the quantity of concave shape is n, in the situation that described convex form and described concave shape are all same shape, to meet θ 1> (360/n) { d
oi/ (d
io+ d
oi) mode form described heat transfer area enlarged tube.
The double-tube type heat exchanger of the 7th mode of the present utility model is that, in the double-tube type heat exchanger of first method or second method, the coating member being coated by scolder by surface forms described heat transfer area enlarged tube.
The refrigerating circulatory device of first method of the present utility model is that the double-tube type heat exchanger of use first method or second method, makes two kinds of cold-producing mediums carry out heat exchange.
The refrigerating circulatory device of second method of the present utility model is that, in the refrigerating circulatory device of first method, at least one party's described cold-producing medium is water or refrigerating medium.
The effect of utility model
According to the utility model, the long mode of length of the part contacting with the inwall of outer tube with the Length Ratio on the pipe Zhou Fangxiang of the part that contacts with the outer wall of inner tube, there is the heat transfer area enlarged tube contacting with outer tube and inner tube, so, during fabrication, the external force that puts on heat transfer area enlarged tube is disperseed, can suppress the loose contact with inner tube, and can realize the expansion of heat transfer area, improve heat transfer property.
Accompanying drawing explanation
Fig. 1 is the figure of the structure of the double-tube type heat exchanger for embodiment 1 of the present utility model is described.
Fig. 2 is the figure that represents the cross section of other directions of the double-tube type heat exchanger of embodiment 1 of the present utility model.
Fig. 3 is the figure that represents the cross section of the double-tube type heat exchanger of embodiment 3 of the present utility model.
Fig. 4 is the figure lifting for heat transfer area enlarged tube 3 is described.
Fig. 5 is the figure that represents the parameter that is set in double-tube type heat exchanger.
Fig. 6 is the figure that represents the soldering part of embodiment 4 of the present utility model.
Fig. 7 is the figure that has represented to use the refrigerating circulatory device of double-tube type heat exchanger of the present utility model.
The explanation of Reference numeral
1 outer tube, 2 inner tubes, 3 heat transfer area enlarged tube, 4 inside passages, 5 outside passages, 6 inner side contact sites, 7 outside contact sites, 8 compressors, 9 condensers, 10 expansion valves, 11 evaporimeters, 12 double-tube type heat exchangers, 13 flow rate regulating valves, 14 pumps, 15 scolders, 16 fin portions.
The specific embodiment
Fig. 1 is the figure of the structure of the double-tube type heat exchanger for embodiment 1 of the present utility model is described.In Fig. 1, show stream (especially inner tube 2) along cold-producing medium and dissect the cutaway view of double-tube type heat exchanger.Double-tube type heat exchanger is to be that the pipe that inner tube 2 is inserted the side that diameter is large is the inner side of outer tube 1 by a side's little diameter pipe.And the mode that the end of the heat exchanger of double-layer circular structure contacts (sidewall sections of sealing outer tube 1 covers inner tube 2) with the inner wall section (outer tube wall) of outer tube 1 and the outer wall section (outer wall of inner tube) of inner tube 2 forms.
Being inside passages 4 using the inside of inner tube 2 as the first stream, is outside passages 5 using the space being formed between inner tube 2 and outer tube 1 as the second stream.The outflow inflow entrance of the cold-producing medium of outside passages 5 forms through hole and is connected with connecting pipings on the wall of outer tube 1.And circulation has first fluid and second fluid respectively in inside passages 4 and outside passages 5.The first fluid that temperature difference is different and second fluid flow in each stream, can in double-tube type heat exchanger, carry out thus the heat exchange between fluid.
Fig. 2 is the figure that represents the cross section of other directions of the double-tube type heat exchanger of embodiment 1 of the present utility model.A-A ' line cross section (the pipe cross section of Fig. 2 presentation graphs 1.Cross section when pipe Zhou Fangxiang in the time observing from the mobile direction of fluid dissects).The double-tube type heat exchanger of present embodiment forms the further space segment that inserts outside passages 5 of heat transfer area enlarged tube 3 of the raised line shape shape with convex-concave.In heat transfer area enlarged tube 3, inwall in concave portion (heat transfer area enlarged tube inwall) contacts with outer wall of inner tube, and outer wall in convex portion (heat transfer area enlarged tube outer wall) contacts with outer tube wall.And sidewall is in the tiltedly space between transversal outside passages 5(inner tube 2 and outer tube 1 of pipe cross section updip), contact with outer wall of inner tube and outer tube wall from incline direction.
Here, in general, heat-shift Q, heat transfer area A, pyroconductivity K and the first fluid of heat exchange and the temperature difference dT of second fluid have the relation shown in formula (1).
[formula 1]
Q=A·K·dT...（1）
And formula for pyroconductivity K (2) represents.Here, α 1 is the pyroconductivity of first fluid, and d1 is the hydraulic diameter of inside passages 4, and α 2 is pyroconductivities of second fluid, and d2 is the hydraulic diameter of outside passages 5.In addition, λ is the pyroconductivity of inner tube 2, d
iothe external diameter of inner tube 2, d
iibe the internal diameter of inner tube 2, R is thermal resistance.
[formula 2]
K=πL/｛1/（α1·d1）+1/（α2·d2）+1n（d
io/d
ii）/2λ+R｝...（2）
Heat transfer area enlarged tube 3, by contacting with inner tube 2 and playing a role as fin, can expand the heat transfer area of heat exchange, can increase the heat-shift of first fluid and second fluid.
Here, the length on the pipe Zhou Fangxiang using the contact portion of outer wall of inner tube and heat transfer area enlarged tube inwall as inner side contact site 6(using the part contacting is as L1).In addition, the length on the pipe Zhou Fangxiang using the contact portion of outer tube wall and heat transfer area enlarged tube outer wall as outside contact site 7(using the part contacting is as L2).In addition, using the part playing a role as fin between inner side contact site 6 and outside contact site 7 (side wall surface in convex-concave shape) as fin portion 16.From increasing the viewpoint of heat transfer area of heat transfer area enlarged tube 3, on pipe cross section, about inner side contact site 6 and outside contact site 7, form double-tube type heat exchanger in the mode of some contact (some contact) respectively.By reducing contact portion, for example manage the increases such as heat transfer area in quantity, 1 fin portion 16 of the fin portion 16 on week, large thereby the heat transfer area of double-tube type heat exchanger entirety becomes.Here, about the point of following explanation, not the mathematical point that there is no area etc., guarantee the pipe point of the area of the degree of contact reliably each other but have.In addition, describe as a contact, but at double-tube type heat exchanger on the whole, contact portion becomes wire.
But about inner side contact site 6, while formation to become the mode of a contact, the thermal contact resistance in inner side contact site 6 increases.Therefore, the pyroconductivity K in above-mentioned formula (2) reduces, its result, and heat-shift Q reduces.In addition, while formation to become the mode of a contact, may produce the position of loose contact.When inner side contact site 6 adopts some contact, for example, while there is outer wall of inner tube and the discontiguous position of heat transfer area enlarged tube inwall, occur to conduct heat bad, can not effectively apply flexibly a large amount of heat transfer areas.
Therefore, in the double-tube type heat exchanger of embodiment 1, about outside contact site 7, form to become a mode for contact (length L 2 approaches 0), heat transfer area is expanded.In addition, on pipe cross section, about inner side contact site 6, form to there is the mode of contact length (in double-tube type heat exchanger entirety, contact portion becomes face).
Like this, according to the double-tube type heat exchanger of embodiment 1, about outside contact site 7, form in the mode that becomes a contact, heat transfer area is expanded, about inner side contact site 6, form in the mode with contact length, so can prevent the loose contact of outer wall of inner tube and heat transfer area enlarged tube inwall.Therefore, can can't harm heat transfer property and improve heat transfer property.
As shown in Figure 2, the double-tube type heat exchanger of above-mentioned embodiment 1, in the outside passages 5 being formed between outer tube 1 and inner tube 2, is provided with the have convex-concave shape heat transfer area enlarged tube 3 of shape of (raised line shape).Heat transfer area enlarged tube 3 is as illustrated in embodiment 1, and heat transfer area enlarged tube inwall contacts with outer wall of inner tube, and heat transfer area enlarged tube outer wall contacts with outer tube wall.And, become fin portion 16 transversal outside passages 5 on pipe cross section of sidewall.
Like this, in order to manufacture the double-tube type heat exchanger that outer tube 1, inner tube 2 and heat transfer area enlarged tube 3 are contacted, after heat transfer area enlarged tube 3 is inserted to outside passages 5, carry out the operation to inner tube 2 expanders, or carry out the operation to outer tube 1 draw.
Here,, with respect to outer tube 1 and inner tube 2, in the time that the part that becomes fin portion 16 of heat transfer area enlarged tube 3 is vertically formed, in the time carrying out expander or the draw, the power that puts on the part that becomes inner side contact site 6 or outside contact site 7 directly puts on fin portion 16.Therefore, may form the fin portion 16 with the form bending of non-anticipation.Therefore, the part that becomes fin portion 16 does not become vertically, in the time of expander or the draw, reduces the load that puts on the part that becomes fin portion 16.And fin portion 16 contacts from incline direction with respect to outer wall of inner tube and outer tube wall.Although be not particularly limited, but the in the situation that of 7 contacts of extraterrestrial side contacts portion as above-mentioned embodiment 1, as shown in Figure 2, the angle that the angle beta that the angle [alpha] that outer wall of inner tube contacts with heat transfer area enlarged tube inwall and heat transfer area enlarged tube outer wall contact with outer tube wall is less than 90 °.
Fig. 3 is the figure lifting for heat transfer area enlarged tube 3 is described.For example, in the time carrying out the operations such as expander, the draw, if desired above pressure puts on inner tube 2, heat transfer area enlarged tube 3, deforms at the inner side of heat transfer area enlarged tube 3 contact site 6, and the mid portion that originally should contact may lift.While lifting, exist for example thermal contact resistance to increase, damage the possibility of heat transfer property.
Therefore, for example, for preventing that this from lifting, fin portion 16 not only contacts from incline direction with respect to outer wall of inner tube and outer tube wall, about the heat transfer area enlarged tube 3 of inserting in the outside passages 5 of double-tube type heat exchanger, become the position (concave portion) of inner side contact site 6 and become outside the shape of the part that becomes fin portion 16 between the position (convex portion) of contact site 7 on pipe cross section, be circular-arc shape.By adopting such shape, while carrying out the draw of expander, outer tube 1 of inner tube 2, even if heat transfer area enlarged tube 3 is exceedingly pressed against inner tube 2, heat transfer area enlarged tube 3 is distortion agley also, thus, the load that puts on heat transfer area enlarged tube 3 disperses (buffering).Therefore, at inner side contact site 6, do not have irrational power to put on heat transfer area enlarged tube 3, can prevent from lifting.Therefore, can can't harm heat transfer property and improve heat transfer property.
Here,, about the direction that makes the part bending that becomes fin portion 16 by expander or the draw, the fin portion 16 forming preferably becomes convex towards inner tube 2 sides.Form by becoming convex towards inner tube 2 sides, fin portion 16 is to inner tube 2 side distortion, so the contact portion of fin portion 16 and inner tube 2 increases, inner side contact site 6 is elongated.Therefore, can carry out efficiently from the heat transfer of inner tube 2.In addition, for example, as shown in Figure 2, become angle [alpha] < angle beta, the gap smaller producing between heat transfer area enlarged tube 3 and inner tube 2.Therefore, for example, when contact site 6, scolder easily enters inside soldering.Therefore, can further carry out efficiently from the heat transfer of inner tube 2.In addition, in the contact portion of fin portion 16 and outer tube 1, the power compressing and angle beta become large amount and correspondingly die down, and can suppress the increase of outside contact site 7.
Here, in the present embodiment, the shape of heat transfer area enlarged tube 3 adopts circular-arc, but is not limited to circular-arc, as long as the shape more at least thering is sweep, just can bring into play the load that disperses to become in the part of fin portion 16, the effect of lifting that prevents inner side contact site 6.In addition, above explanation is not to set up similarly in the double-tube type heat exchanger of a contact at for example outside contact site 7, can bring into play same effect.
Fig. 4 is the figure that represents the double-tube type heat exchanger of embodiment 3 of the present utility model.Fig. 4 shows the pipe cross section same with A-A ' the line cross section of Fig. 1 of explanation in embodiment 1.In the double-tube type heat exchanger of present embodiment, the length L 2 of the outside contact site 7 of the length L 1 of the inner side contact site 6 of outer wall of inner tube and heat transfer area enlarged tube inwall and outer tube wall and heat transfer area enlarged tube outer wall becomes L1>L2.
For example, if the pass of L1 and L2 is L1<L2, in the time that superfluous external force puts on outer tube 1, inner tube 2 and heat transfer area enlarged tube 3, the end points of inner side contact site 6 becomes fulcrum, may deform.Therefore, as explained in Embodiment 2, in heat transfer area enlarged tube 3, the mid portion of inner side contact site 6 lifts from inner tube 2, may damage heat transfer property.
Therefore, by making L1>L2, for example as Embodiment 1, when observation tube cross section, even if side contacts portion 7 applies in the situation of external force the mode of outer tube 1 and heat transfer area enlarged tube 3 close contacts to have contact length outside, the power that puts on outside contact site 7 is also disperseed, and can prevent the distortion of pipe.
In addition, by making L1>L2, in order to make inner tube 2 and heat transfer area enlarged tube 3 close contacts, and make outer tube 1 and heat transfer area enlarged tube 3 close contacts and apply in the situation of external force, the external force that puts on inner side contact site 6 is roughly the same with the external force that puts on outside contact site 7, so applied in the situation of excessive external force, outside contact site 7 is first out of shape.Therefore,, in order to reduce thermal contact resistance, can prevent that most important inner side contact site 6 from lifting, and can can't harm heat transfer property and improve heat transfer property.
Below, in the double-tube type heat exchanger relevant to the embodiment 3 with such feature, study about the condition of the form parameter that becomes L1>L2.
Fig. 5 represents for the shape analysis of the double-tube type heat exchanger of embodiment 3 of the present utility model and the figure of the parameter of setting.The quantity of as shown in Figure 5, establishing the convex portion (concave portion) of heat transfer area enlarged tube 3 is that n, inner tube external diameter are d
io, outer tube diameter is d
oi.
In addition, θ 0 is the angle from the summit of the convex portion of heat transfer area enlarged tube 3 to the summit of next convex portion, and θ 1 is the angle that becomes the target that convex portion forms, and θ 2 is the angles that become the target that concave portion forms.And θ 1 ' is divided into θ 1 a part and gets the angle that wherein b part obtains (θ 1 '=b/a θ 1), θ 2 ' is divided into θ 2 a part and gets the angle that wherein b part obtains (θ 2 '=b/a θ 2).And establishing the length that inner tube 2 contacts with heat transfer area enlarged tube 3 is that the length that L1, outer tube 1 and heat transfer area enlarged tube 3 contact is L2.Here, the shape of the convex portion of heat transfer area enlarged tube 3 and the shape of concave portion are all same shapes.And geometrically, θ 0, θ 1, θ 2, θ 1 ', θ 2 ' represent with formula (3)～(6).
[formula 3]
θo=360/n...（3）
[formula 4]
θ2+θ1=θo=360/n...(4)
[formula 5]
θ1’=b/a·θ1...（5）
[formula 6]
θ2’=b/a·θ2...（6）
In addition, the length L 1 of inner side contact site 6 and the length L of outside contact site 72 can use respectively formula (7), formula (8) to represent.
[formula 7]
L1=π·2d
io·（θ1’/360）...（7）
[formula 8]
L2=π·2d
oi·（θ2’/360）...（8）
Based on formula (3)～(8), the condition that becomes L1>L2 can use formula (9) to represent.
[formula 9]
θ1>（360/n）·｛d
oi/（d
io+d
oi）｝...（9）
As mentioned above, according to the double-tube type heat exchanger of embodiment 3, the relation of the length L 2 of the outside contact site 7 of the length L 1 of the inner side contact site 6 of outer wall of inner tube and heat transfer area enlarged tube inwall and outer tube wall and heat transfer area enlarged tube outer wall becomes L1>L2, so can make the external force that puts on outside contact site 7 disperse.In addition, the external force that puts on inner side contact site 6 is roughly the same with the external force that puts on outside contact site 7, and thus, excessive external force is not only to put on inner side contact site 6 but dispersion, thus, can prevent lifting of inner side contact site 6.As mentioned above, can prevent the excessive deformation of each pipe.
Although do not specify in above-mentioned embodiment 1～3, but for make outer wall of inner tube and heat transfer area enlarged tube inwall contact and outer tube wall further reliable with contacting of heat transfer area enlarged tube outer wall, preferably each contact portion is carried out to soldering by scolder.
Fig. 6 is the figure that represents the soldering part of embodiment 4 of the present utility model.For example, after having assembled inner tube 2, outer tube 1 and heat transfer area enlarged tube 3, coated with solder 15 etc. are carried out soldering etc. and make scolder 15 meltings in stove, and contact site is carried out to soldering.For example, manage in the situation into aluminium etc., using the alloy of Al-Si class (aluminium-silicon class) that contains silicon in aluminium as scolder 15.
Here the in the situation that of being difficult to coated with solder 15 after assembling, also can use the coating member by scolder 15 coated (covering) heat transfer area enlarged tube 3 in advance.
In embodiment 5, describe about the example that has adopted the refrigerating circulatory device of the double-tube type heat exchanger of explanation in embodiment 1～4.Here, the structure of the refrigerating circulatory device to 4 kinds describes.
Fig. 7 is the figure that represents an example of the structure of the refrigerating circulatory device of embodiment 5.In the refrigerating circulatory device of present embodiment, connect compressor 8, condenser 9, expansion valve 10, evaporimeter 11 and double-tube type heat exchanger 12 by pipe arrangement and form refrigerant loop.
In addition, 10 pairs of cold-producing mediums of expansion valve (pressure-reducing valve, throttling arrangement) reduce pressure and make its expansion.Formed by flow control mechanisms such as such as electronic expansion valves, but for example also can be by the formations such as refrigerant flow regulating mechanism such as expansion valve, capillary (Capillary) with temperature sensing tube.Evaporimeter 11 makes cold-producing medium evaporation become the cold-producing medium (evaporation gasification) of gas (gaseous state) shape by the heat exchange of carrying out with air etc.
In addition, the double-tube type heat exchanger 12 in the refrigerating circulatory device of Fig. 7 (a) carries out the cold-producing medium of the HTHP flowing out from condenser 9 and the heat exchange of the cold-producing medium of the low-temp low-pressure that flows out from evaporimeter 11.By utilizing like this double-tube type heat exchanger 12, can improve the temperature of the cold-producing medium in condenser 9.Therefore, can improve the ability while heating, and can improve the value that COP(ability obtains divided by input).In addition, due to the cold-producing medium gasification that can make to flow out from evaporimeter 11, so can prevent that liquid refrigerant from returning to compressor 8.
Double-tube type heat exchanger 12 in the refrigerating circulatory device of Fig. 7 (b) carry out the cold-producing medium flow export place of condenser 9 high pressure liquid refrigerant and passed through the heat exchange between the two-phase system cryogen of middle pressure of flow rate regulating valve 13.And, make to carry out heat exchange and the refrigerant bypass of gas refrigerant that becomes middle pressure to the suction side pipe arrangement of compressor 8.
Like this, in the refrigerating circulatory device of Fig. 7 (b), make to pass through the cold-producing medium of condenser 9 by branch before expansion valve 10, utilized double-tube type heat exchanger 12 to make its bypass, thus, can reduce from expansion valve 10 refrigerant amount of side flow downstream.Therefore, the pressure loss can be reduced, COP can be improved.
Double-tube type heat exchanger 12 in the refrigerating circulatory device of Fig. 7 (c) carry out the cold-producing medium flow export place of condenser 9 high pressure liquid refrigerant and passed through the heat exchange between the two-phase system cryogen of middle pressure of flow rate regulating valve 13.And, make to carry out heat exchange and the cold-producing medium that becomes the gas refrigerant of middle pressure flows into the compression unit mid portion of (being expelled to) compressor 8.Here, the compressor 8 in the refrigerating circulatory device of Fig. 7 (c) is compressors of the multilevel hierarchy that can inject.
Like this, in the refrigerating circulatory device of Fig. 7 (c), make to pass through the cold-producing medium of condenser 9 by branch before expansion valve 10, utilized double-tube type heat exchanger 12 to make its bypass, thus, can reduce from expansion valve 10 refrigerant amount of side flow downstream.In addition, due to can be to the compression unit mid portion injection of the compressor of multilevel hierarchy 8, so can reduce discharge temperature etc. and the input power of compressor, can improve COP.
In the refrigerating circulatory device of Fig. 7 (d), using double-tube type heat exchanger 12 as condenser utilization.And the fluid that becomes the heat exchange object of cold-producing medium mobile in refrigerant loop adopts (following water describe) such as water, refrigerating mediums.
In Fig. 7 (d), pump 14 forms current and is sent into double-tube type heat exchanger 12.In double-tube type heat exchanger 12, by carrying out heat exchange with cold-producing medium, water is heated.Here using double-tube type heat exchanger 12 as condenser utilization, but also can be used as evaporimeter utilization.
Claims (9)
1. a double-tube type heat exchanger, is characterized in that, has:
Inner tube, first fluid passes through in the inside of described inner tube;
Outer tube, the diameter of described outer tube is larger and cover described inner tube than described inner tube, and second fluid is by the space between described outer tube and described inner tube;
Heat transfer area enlarged tube, described heat transfer area enlarged tube is arranged in described space, there is convex-concave shape, thereby, in pipe cross section, become Length Ratio on the pipe Zhou Fangxiang of inner side contact site of the part that described heat transfer area enlarged tube contacts with described outer wall of inner tube and become length on the pipe Zhou Fangxiang of outside contact site of the part that described heat transfer area enlarged tube contacts with described outer tube wall long, in addition, in described convex-concave shape, fin portion on pipe cross section between the described inner side contact site in transversal described space and described outside contact site contacts from incline direction with respect to described outer wall of inner tube and described outer tube wall,
Described outside contact site and described inner side contact site are carried out to soldering.
2. double-tube type heat exchanger as claimed in claim 1, is characterized in that, described fin portion has circular-arc on pipe cross section.
3. double-tube type heat exchanger as claimed in claim 1 or 2, is characterized in that, described fin portion on pipe cross section for become the curved shape of convex in described inner tube side.
4. double-tube type heat exchanger as claimed in claim 1 or 2, it is characterized in that, on pipe cross section, the described heat transfer area enlarged tube in the contact site of described inner side and described outer wall of inner tube angulation are less than the described heat transfer area enlarged tube in the contact site of described outside and described outer tube wall angulation.
5. double-tube type heat exchanger as claimed in claim 1 or 2, is characterized in that, described outside contact site contacts in the mode that becomes a contact on pipe cross section, and described inner side contact site contacts in the mode that becomes line contact on pipe cross section.
6. double-tube type heat exchanger as claimed in claim 1 or 2, is characterized in that, the external diameter of establishing the both ends of described outside contact site and the center angulation of described inner tube and outer tube and be θ 1, inner tube is d
io, outer tube internal diameter be d
oi, the convex form of described heat transfer area enlarged tube or the quantity of concave shape is n, in the situation that described convex form and described concave shape are all same shape, to meet θ 1> (360/n) { d
oi/ (d
io+ d
oi) mode form described heat transfer area enlarged tube.
7. double-tube type heat exchanger as claimed in claim 1 or 2, is characterized in that, the coating member being coated by scolder by surface forms described heat transfer area enlarged tube.
8. a refrigerating circulatory device, is characterized in that, right to use requires the double-tube type heat exchanger described in 1 or 2, makes two kinds of cold-producing mediums carry out heat exchange.
9. refrigerating circulatory device as claimed in claim 8, is characterized in that, at least one party's described cold-producing medium is water or refrigerating medium.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2012/075530 | 2012-10-02 | ||
| PCT/JP2012/075530 WO2014054117A1 (en) | 2012-10-02 | 2012-10-02 | Double-tube heat exchanger and refrigerating cycle device |
| PCT/JP2013/073688 WO2014054370A1 (en) | 2012-10-02 | 2013-09-03 | Double-tube heat exchanger and refrigerating cycle device |
| JPPCT/JP2013/073688 | 2013-09-03 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203605763U true CN203605763U (en) | 2014-05-21 |
Family
ID=50434478
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380051921.4A Active CN104704311B (en) | 2012-10-02 | 2013-09-03 | Double pipe exchanger and refrigerating circulatory device |
| CN201320613402.XU Expired - Lifetime CN203605763U (en) | 2012-10-02 | 2013-09-30 | Double-layer tubular heat exchanger and refrigeration circulating device |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380051921.4A Active CN104704311B (en) | 2012-10-02 | 2013-09-03 | Double pipe exchanger and refrigerating circulatory device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150241132A1 (en) |
| EP (1) | EP2916091B1 (en) |
| JP (1) | JP5944009B2 (en) |
| CN (2) | CN104704311B (en) |
| WO (2) | WO2014054117A1 (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6436529B2 (en) * | 2014-11-18 | 2018-12-12 | 株式会社アタゴ製作所 | Heat exchanger |
| JP6691538B2 (en) * | 2015-05-21 | 2020-04-28 | 日本碍子株式会社 | Heat exchange parts |
| EP3318822B1 (en) * | 2015-07-03 | 2020-11-25 | Mitsubishi Electric Corporation | Heat pump device |
| CN106032860A (en) * | 2015-09-02 | 2016-10-19 | 天津友大金属结构制造有限公司 | Heat exchange tube for remote transportation |
| JP6471867B2 (en) * | 2015-10-06 | 2019-02-20 | スズキ株式会社 | Waste heat recovery device |
| CN105843347B (en) * | 2016-04-22 | 2017-03-29 | 南京佳力图机房环境技术股份有限公司 | Bidirectional flow heat exchanger based on vibration induction |
| WO2018089130A1 (en) * | 2016-11-11 | 2018-05-17 | Stulz Air Technology Systems, Inc. | Dual mass cooling precision system |
| CN107166995A (en) * | 2017-06-17 | 2017-09-15 | 福建德兴节能科技有限公司 | High-performance heat exchanger and application thereof |
| JP6844791B2 (en) * | 2018-11-21 | 2021-03-17 | 株式会社ニチリン | Manufacturing method of double tube heat exchanger |
| CN109848499B (en) * | 2019-03-08 | 2021-05-14 | 西安远航真空钎焊技术有限公司 | Preparation method of complex heat exchanger core |
| JP7169923B2 (en) * | 2019-03-27 | 2022-11-11 | 日本碍子株式会社 | Heat exchanger |
| CN111750705B (en) * | 2019-03-28 | 2022-04-29 | 日本碍子株式会社 | Flow path structure of heat exchanger and heat exchanger |
| US11378307B2 (en) * | 2019-08-09 | 2022-07-05 | Enerpro | Hybrid condensing boiler with preheater |
| US20210278137A1 (en) * | 2020-03-03 | 2021-09-09 | Daikin Applied Americas, Inc. | System and Method for Manufacturing and Operating a Coaxial Tube Heat Exchanger |
| CN113081255A (en) * | 2021-04-30 | 2021-07-09 | 杭州佳量医疗科技有限公司 | Cooling sleeve and optical fiber conduit with same |
| CN114471439A (en) * | 2022-02-28 | 2022-05-13 | 茂名重力石化装备股份公司 | Series pipe reactor with static fit jacket |
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| US2372502A (en) * | 1942-02-14 | 1945-03-27 | Vapor Car Heating Co Inc | Inner tube radiation with internal metallic conduction |
| US2633338A (en) * | 1947-02-19 | 1953-03-31 | Continental Aviat & Engineerin | Heat exchanger |
| US2692763A (en) * | 1952-03-08 | 1954-10-26 | Air Preheater | Supporting spacer for annular corrugated fins |
| US2756032A (en) * | 1952-11-17 | 1956-07-24 | Heater | |
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| US4305457A (en) * | 1979-08-20 | 1981-12-15 | United Aircraft Products, Inc. | High density fin material |
| JPH045901Y2 (en) * | 1986-06-10 | 1992-02-19 | ||
| JPH064222Y2 (en) * | 1986-06-16 | 1994-02-02 | 神鋼メタルプロダクツ株式会社 | Heat exchanger |
| JPH04335993A (en) * | 1991-05-10 | 1992-11-24 | Toyo Radiator Co Ltd | Oil cooler |
| JP2000079462A (en) * | 1998-09-07 | 2000-03-21 | Maruyasu Industries Co Ltd | Heat exchanger |
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| DE10053000A1 (en) * | 2000-10-25 | 2002-05-08 | Eaton Fluid Power Gmbh | Air conditioning system with internal heat exchanger and heat exchanger tube for one |
| US20040182559A1 (en) * | 2001-03-22 | 2004-09-23 | Kent Scott Edward | Heat exchanger tube |
| DE10359806A1 (en) * | 2003-12-19 | 2005-07-14 | Modine Manufacturing Co., Racine | Heat exchanger with flat tubes and flat heat exchanger tube |
| CN2754040Y (en) * | 2004-08-27 | 2006-01-25 | 四川同一科技发展有限公司 | Dual-tube heat exchanger |
| US20060081362A1 (en) * | 2004-10-19 | 2006-04-20 | Homayoun Sanatgar | Finned tubular heat exchanger |
| JP4311373B2 (en) * | 2005-05-13 | 2009-08-12 | 三菱電機株式会社 | Heat exchanger for electric water heater |
| JP5743051B2 (en) | 2010-09-15 | 2015-07-01 | 三浦工業株式会社 | Heat exchanger and boiler water supply system |
-
2012
- 2012-10-02 WO PCT/JP2012/075530 patent/WO2014054117A1/en active Application Filing
-
2013
- 2013-09-03 CN CN201380051921.4A patent/CN104704311B/en active Active
- 2013-09-03 US US14/432,630 patent/US20150241132A1/en not_active Abandoned
- 2013-09-03 JP JP2014539645A patent/JP5944009B2/en active Active
- 2013-09-03 WO PCT/JP2013/073688 patent/WO2014054370A1/en active Application Filing
- 2013-09-03 EP EP13843545.8A patent/EP2916091B1/en active Active
- 2013-09-30 CN CN201320613402.XU patent/CN203605763U/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014054117A1 (en) | 2014-04-10 |
| WO2014054370A1 (en) | 2014-04-10 |
| EP2916091B1 (en) | 2019-10-23 |
| US20150241132A1 (en) | 2015-08-27 |
| JPWO2014054370A1 (en) | 2016-08-25 |
| CN104704311A (en) | 2015-06-10 |
| EP2916091A1 (en) | 2015-09-09 |
| EP2916091A4 (en) | 2016-08-10 |
| JP5944009B2 (en) | 2016-07-05 |
| CN104704311B (en) | 2017-03-01 |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140521 |