CN105008839A - Double-pipe heat exchanger and refrigeration cycle device - Google Patents
Double-pipe heat exchanger and refrigeration cycle device Download PDFInfo
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- CN105008839A CN105008839A CN201280077614.9A CN201280077614A CN105008839A CN 105008839 A CN105008839 A CN 105008839A CN 201280077614 A CN201280077614 A CN 201280077614A CN 105008839 A CN105008839 A CN 105008839A
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- tube
- transfer area
- heat transfer
- area enlarged
- double
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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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
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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
- 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
- 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
- F28F1/14—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 extending longitudinally
- F28F1/20—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 extending longitudinally the means being attachable to the element
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
- F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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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
- 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
- F25B39/00—Evaporators; Condensers
-
- 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)
- Chemical & Material Sciences (AREA)
- Crystallography & Structural Chemistry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Provided are a double-pipe heat exchanger and the like with which the heat exchange performance can be increased when a two-phase flow flows in a second flow path. This double-pipe heat exchanger (1) is equipped with an expanded-heat-transfer-area pipe (11) having protrusions and recesses in the radial direction. The inner surface of the portion of the expanded-heat-transfer-area pipe (11) in contact with the inner surface of an outer pipe (3), and the portion of the inner surface of the outer pipe that defines a second flow path (23) in conjunction with the outer surface of the expanded-heat-transfer-area pipe, are areas in which grooves are not formed, that is, are grooveless surfaces. In addition, a candidate groove formation area is provided, with this area comprising the portion of the expanded-heat-transfer-area pipe when the area in which grooves are not formed is excluded from the portion of the inner surface that defines the second flow path in conjunction with the outer surface of an inner pipe, and the portion of the outer surface of the expanded-heat-transfer-area pipe that defines the second flow path in conjunction with the inner surface of the outer pipe, and the portion of the outer surface of the inner pipe (5) that defines the second flow path in conjunction with the inner surface of the expanded-heat-transfer-area pipe. Grooves extending in the direction of flow are formed in all or a part of the candidate groove formation area.
Description
Technical field
The present invention relates to combination there is the pipe of different tube diameters and form the double-tube type heat exchanger of two streams and employ the refrigerating circulatory device of double-tube type heat exchanger.
Background technology
Double-tube type heat exchanger is that pipe (hereinafter referred to as interior pipe) little for diameter is inserted the large pipe of diameter (hereinafter referred to as outer tube), using the inside of interior pipe as first flow path, using the outside of interior pipe and the part of the inner side of outer tube as the second stream, carry out heat exchange between the second fluid in the first fluid in first flow path and the second stream.
In addition, in this double-tube type heat exchanger, as the research improving heat transfer property, such as, there is the structure disclosed in patent document 1.Namely, following method is proposed: the second stream interpolation of the ring-type between the outside of pipe in cylindrical shape and the inner side of the outer tube of cylindrical shape enters the heat transfer area enlarged tube that cross section is many flaps, improves heat transfer property by the expansion effect of heat transfer area in patent document 1.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2012-063067 publication
Summary of the invention
The problem that invention will solve
The research to expanding heat transfer area is only disclosed in above-mentioned patent document 1.At this, the present inventor is conceived to suitably conduct heat when making two phase refrigerant carry out heat exchange.
The present invention completes in view of this situation, and object is that provide a kind of has the double-tube type heat exchanger etc. that can improve heat exchange performance when two phase flow in the second stream.
For solving the means of problem
To achieve these goals, double-tube type heat exchanger of the present invention possesses: outer tube, interior pipe, described interior pipe is inserted into the inner side of described outer tube, between this outer tube, form annular section, and forms first flow path in inner side, and heat transfer area enlarged tube, it is concavo-convex that described heat transfer area enlarged tube has relative to radial direction, is configured in the inner side of described outer tube and the outside of described interior pipe, forms the second stream at described annular section, the part of with the outer surface of described heat transfer area enlarged tube together with delimiting described second stream of inner surface in the inner surface of described outer tube of the part of this heat transfer area enlarged tube of touching with the inner surface of described outer tube in the inner surface of described heat transfer area enlarged tube is set to respectively and does not form groove scope, this does not form groove scope is without groove face, form groove candidate scope to form by with lower part, namely described in delimiting together with the outer surface of described interior pipe in the part of described second stream the inner surface of described heat transfer area enlarged tube eliminates, groove scope is not formed and the part obtained, the part of delimiting described second stream together with the inner surface of described outer tube in the outer surface of described heat transfer area enlarged tube, and the part of delimiting described second stream together with the inner surface of described heat transfer area enlarged tube in the outer surface of described interior pipe, at least partially or whole described formation groove candidate scope be formed along flow direction extend groove.
The effect of invention
According to the present invention, when having two phase flow in the second stream, heat exchange performance can be improved.
Accompanying drawing explanation
Fig. 1 is the in-built figure representing the double-tube type heat exchanger of embodiments of the present invention 1 in the direction orthogonal with tubular axis.
Fig. 2 is the sectional view of the double-tube type heat exchanger of the II-II line of Fig. 1.
Fig. 3 is the figure of the second stream represented enlargedly in Fig. 2.
Fig. 4 is the part about Fig. 3, in order to be described by the figure that outer tube, heat transfer area enlarged tube and interior pipe represent separated from each other.
Fig. 5 is the figure of the embodiment 1 representing the refrigerating circulatory device employing double-tube type heat exchanger.
Fig. 6 is the figure of the embodiment 2 representing the refrigerating circulatory device employing double-tube type heat exchanger.
Fig. 7 is the figure of the embodiment 3 representing the refrigerating circulatory device employing double-tube type heat exchanger.
Fig. 8 is the figure of the embodiment 4 representing the refrigerating circulatory device employing double-tube type heat exchanger.
Fig. 9 be about embodiment 2 with the figure of Fig. 3 same form.
Figure 10 be about embodiment 3 with the figure of Fig. 3 same form.
Detailed description of the invention
Below, with reference to the accompanying drawings embodiments of the present invention are described.In the drawings, same Reference numeral represents same or corresponding part.
Embodiment 1
Fig. 1 is the in-built figure representing the double-tube type heat exchanger of embodiments of the present invention 1 in the direction orthogonal with tubular axis.Fig. 2 is the sectional view of the double-tube type heat exchanger of the II-II line of Fig. 1.In addition, preferentially guarantee the clear property of figure, eliminate the diagram of heat transfer area enlarged tube described later in FIG.Double-tube type heat exchanger 1 have the relatively large pipe of diameter and outer tube 3 inner concentric insert the relatively little pipe of diameter namely in the dual tube construction of pipe 5.The inner space of interior pipe 5 plays the function of first flow path 7.On the other hand, in the outside of interior pipe 5 and the inner side of outer tube 3 and annular section 9 contain heat transfer area enlarged tube 11.
Heat transfer area enlarged tube 11 has as about relative concavo-convex multiple protuberances 13 of radial direction and multiple recess 15.As shown in the cross section of Fig. 2, multiple protuberance 13 is radially arranged to give prominence to towards the radial outside of heat transfer area enlarged tube 11.In addition, multiple protuberance 13 is to be configured in circumferencial direction roughly at equal intervals.On the other hand, multiple recess 15 lays respectively between the circumferencial direction of corresponding a pair protuberance 13.These recesses 15 are also to be positioned at circumferencial direction roughly at equal intervals.Therefore, see on the whole in heat transfer area enlarged tube 11, multiple protuberance 13 and multiple recess 15 are alternately positioned at circumferencial direction.
In the present invention, the convex form of the protuberance seen in the cross section of the Fig. 2 about heat transfer area enlarged tube and the concave shape of recess can consider various forms, and as an example, as follows in present embodiment 1.Heat transfer area enlarged tube 11 comprises contiguity portion, multiple outside 17, contiguity portion, multiple inner side 19 and multiple continuous portion 21.As shown in Figure 2, the outer surface 17a in contiguity portion, outside 17 and the inner surface 3b of outer tube 3 of heat transfer area enlarged tube 11 touch, and especially in this example, outer surface 17a contacts with inner surface 3b face.That is, the outer surface 17a in the contiguity portion, outside 17 of heat transfer area enlarged tube 11 has bend roughly the same with the inner surface 3b of outer tube 3.Equally, the inner surface 19b in contiguity portion, inner side 19 and the outer surface 5a of interior pipe 5 of heat transfer area enlarged tube 11 touch, and especially in this example, inner surface 19b contacts with outer surface 5a face.That is, the inner surface 19b in the contiguity portion, inner side 19 of heat transfer area enlarged tube 11 has bend roughly the same with the outer surface 5a of interior pipe 5.In addition, this identical case of bending can obtain under the free state that outer tube 3, interior pipe 5, heat transfer area enlarged tube 11 are respective, also can obtain under the state finished along with the assembling procedure applying certain power outside the central side or radial direction of double-tube type heat exchanger 1.
Continuous portion 21 lays respectively between adjacent contiguity portion, outside 17 and contiguity portion, inner side 19.In the present embodiment, contiguity portion 17, multiple outside is to be positioned at circumferencial direction at equal intervals, and contiguity portion, multiple inner side 19 is also to be positioned at circumferencial direction at equal intervals.If see whole heat transfer area enlarged tube 11, then in a circumferential direction, repeatedly contiguity portion 17, outside, continuously portion 21, contiguity portion, inner side 19, the continuously order in portion 21 collocation form.In addition, the border that protuberance 13 and recess 15 are clear and definite, protuberance 13 is made up of the part outside the close radial direction in contiguity portion, outside 17 and continuous portion 21, and recess 15 is made up of the part inside the close radial direction in contiguity portion, inner side 19 and continuous portion 21.
The inner side of the protuberance 13 in above-mentioned annular section 9 and the outside of recess 15 play the function of the second stream 23.That is, in annular section 9, the second stream 23 delimited by heat transfer area enlarged tube 11.
More particularly, the second stream 23 comprises the part of two kinds of forms, and the part of the first form delimited by inner surface 17b, the corresponding inner surface 21b in a pair continuous portion 21 and outer surface 5a of interior pipe 5 in contiguity portion, outside 17.In addition, the part of the second form delimited by outer surface 19a, the corresponding outer surface 21a in a pair continuous portion 21 and inner surface 3b of outer tube 3 in contiguity portion, inner side 19.The part of the first form is alternately arranged in a circumferential direction with the part of the second form.
In such a configuration, first fluid circulates in first flow path 7, and second fluid circulates at the second stream 23.First fluid is different from the temperature of second fluid, via the heat conduction of interior pipe 5 and heat transfer area enlarged tube 11, between first fluid and second fluid, carries out heat exchange.
Generally, at heat-shift Q, heat transfer area A, coefficient of overall heat transmission K, there is the relation shown in formula (1) between first fluid and the temperature difference dT of second fluid.
[several 1]
Q＝A·K·dT (1)
In addition, coefficient of overall heat transmission K can represent with formula (2).
[several 2]
In addition, the meaning of each symbol is as follows.α 1: the coefficient of overall heat transmission of fluid 1, d1: the hydraulic diameter of stream 1, α 2: the coefficient of overall heat transmission of fluid 2, d2: the hydraulic diameter of stream 2, λ: the thermal conductivity of interior pipe, dio: the external diameter of interior pipe, doi: the internal diameter of interior pipe, R: thermal resistance.
Above-mentioned heat transfer area enlarged tube 11 plays the effect of fin by contacting with interior pipe 5, therefore, it is possible to expand heat transfer area, can increase the heat-shift of first fluid and second fluid.
At this, with reference to figure 3 and Fig. 4, the flow regime of cold-producing medium when having biphase gas and liquid flow to flow in the second stream 23 is described.Fig. 3 is the figure with Fig. 2 same form, and the part that to be the figure representing the second stream enlargedly, Fig. 4 be about Fig. 3, in order to be described by the figure that outer tube, heat transfer area enlarged tube and interior pipe represent separated from each other.At this, generally, the liquid refrigerant that the coefficient of overall heat transmission in two phase flow is high and tube wall touch, and the gas refrigerant that the coefficient of overall heat transmission is low flows at the position away from tube wall.That is, liquid refrigerant concentrates on the wall shown in Reference numeral 3b, 5a, 17b, 19a, 21a, 21b shown in Fig. 3.
Therefore, in the present invention, what be set as follows does not form groove scope and forms groove candidate scope, does not form groove scope for without groove face, at least partially or whole formation groove candidate scope be formed with groove along flow direction extension.Present embodiment 1 is the example of the situation of groove that defines in whole formation groove candidate scope wherein.
The details not forming groove scope and formation groove candidate scope is described.Specifically, the inner surface (the inner surface 17b in contiguity portion, outside 17) of the part of the heat transfer area enlarged tube 11 of touching with the inner surface 3b of outer tube 3 in the inner surface of heat transfer area enlarged tube 11 does not form groove scope.Further, the part of delimiting the second stream 23 together with the outer surface of heat transfer area enlarged tube 11 in the inner surface 3b of outer tube 3 is also do not form groove scope.Do not form groove scope at these and do not form groove 25 described later.
In addition, form groove candidate scope to form by with lower part: eliminate from delimiting together with the outer surface 5a of interior pipe 5 in the part of the second stream 23 inner surface of heat transfer area enlarged tube 11 and above-mentioned do not form groove scope (the inner surface 17b in contiguity portion, outside 17) and the part (the inner surface 21b in continuous portion 21) that obtains, the part (the outer surface 21a in continuous portion 21 and the outer surface 19a in contiguity portion, inner side 19) of delimiting the second stream 23 together with the inner surface 3b of outer tube 3 in the outer surface of heat transfer area enlarged tube 11, and the part of delimiting the second stream 23 together with the inner surface of heat transfer area enlarged tube 11 in the outer surface 5a of interior pipe 5.
In present embodiment 1, as mentioned above, do not form groove not forming groove scope, and form groove in whole formation groove candidate scope, more particularly, as follows.Groove 25 is formed: delimit the part of the outer surface 5a of pipe 5 in the second stream 23, the outer surface 19a in the contiguity portion, inner side 19 of heat transfer area enlarged tube 11 and the outer surface 21a in continuous portion 21 and inner surface 21b with contiguity portion, outside 17 together with a pair continuous portion 21 in following part.In addition, outside touched the inner surface 17b in portion 17 and be set to without groove face with the part that contiguity portion, inner side 19 delimit the inner surface 3b of the outer tube 3 of the second stream 23 together with a pair continuous portion 21.In addition, be not particularly limited as the present invention, but in present embodiment 1, the outer surface 17a in the contiguity portion, outside 17 of heat transfer area enlarged tube 11 and the part of the inner surface 3b of outer tube 3 of touching with this outer surface 17a are set to without groove face, further, inner side is touched portion 19 inner surface 19b and in touching with this inner surface 19b the part of the outer surface 5a of pipe 5 be set to without groove face.
In order to make cold-producing medium flow swimmingly to flow direction, form groove 25 with the form extended along flow direction.In addition, the groove in Fig. 3 and Fig. 4 is schematically drawn, and in addition, in fig. 2, preferably guarantees the clear property of figure, eliminates the diagram of groove.
In addition, can consider to be shaped heat transfer area enlarged tube 11 by punch forming, drawing processing, therefore, in order to simplify processing, when punch forming, drawing adds grooving 25 simultaneously in man-hour.In addition, by the heat transfer area enlarged tube 11 defining groove 25 is inserted annular section 9 between outer tube 3 and interior pipe 5 and to outer tube 3 carry out the draw or internally pipe 5 carry out expander, heat transfer area enlarged tube 11 is supported by outer tube 3 and interior pipe 5.
Or as the method making interior pipe 5 and outer tube 3 touch with heat transfer area enlarged tube 11 more reliably, the form of carrying out soldering to engage to each contact surface is also suitable.Specifically, after heat transfer area enlarged tube 11 is installed on outer tube 3 and interior pipe 5, to contact surface coating brazing material, by furnace brazing etc., brazing material melts can be made, soldering carried out to contact surface.In addition, apply the inconvenient situation of brazing material after heat transfer area enlarged tube 11 is installed on interior pipe 5 and outer tube 3 under, also soldering can be carried out by the clad material being coated with brazing material is in advance used in heat transfer area enlarged tube 11.
According to the double-tube type heat exchanger 1 formed as described above, the advantage of following excellence can be obtained.Even if the outer surface 19a in the specified part of the outer surface 5a of interior pipe 5 and contiguity portion, inner side 19 in the part of delimitation second stream 23 be also from first flow path 7 extremely close to part, be as the highest part of the availability of heat-transfer area.In addition, continuous portion 21 is between the part and the part of the second form of above-mentioned first form of the second stream 23, the inner surface in continuous portion 21 and outer surface, play the effect of fin making continuous portion 21 and between the part and the part of the second form of the first form, (internal relations of the second stream 23) carries out between second fluid heat exchange time be effective heat-transfer area.Therefore, form groove 25 as described above, the specified part that liquid refrigerant can be made to be gathered in the outer surface 5a of the interior pipe 5 near first flow path 7 energetically and the outer surface 19a in contiguity portion, inner side 19 touch with interior pipe 5 and continuous portion 21 inner surface and outer surface.In addition, meanwhile, by being set in advance as without groove face as the specified part of inner surface 3b of the low outer tube 3 of heat-transfer area availability and the inner surface 17b in contiguity portion, outside 17 away from first flow path 7, relatively, compared with the specified part of outer surface 5a, outer surface 19a, liquid refrigerant is not easily assembled, and as its counteractive effect, auxiliary liquid cold-producing medium is gathered in the specified part of outer surface 5a, outer surface 19a and the inner surface in portion 21 and outer surface continuously.Namely, the high liquid refrigerant of the coefficient of overall heat transmission also by the inner surface 17b in the specified part that is supplied in a large number as the inner surface 3b of the low outer tube 3 of heat-transfer area availability and contiguity portion, outside 17, thus correspondingly suppress liquid refrigerant to as the high outer surface 5a of heat-transfer area availability specified part, outer surface 19a and the inner surface in portion 21 and the quantity delivered of outer surface reduce continuously.Like this, according to the present embodiment, even if when having biphase gas and liquid flow to flow in the second stream, by effectively utilizing heat-transfer area, also heat exchange performance can be improved.
In addition, in present embodiment 1, the outer surface 17a in the contiguity portion, outside 17 of heat transfer area enlarged tube 11 and the part of the inner surface 3b of outer tube 3 of touching with this outer surface 17a are without groove face, equally, the inner surface 19b in contiguity portion 19, inner side and in touching with this inner surface 19b the part of the outer surface 5a of pipe 5 be without groove face, thus can interior pipe 5 and outer tube 3 be kept high with the adhesion of heat transfer area enlarged tube 11, moreover, especially because interior pipe 5 is high with the adhesion of heat transfer area enlarged tube 11, the efficiency of the heat conduction undertaken by heat transfer area enlarged tube 11 can be improved, the existence of heat transfer area enlarged tube 11 can be utilized efficiently.
Below, with reference to figure 5 to Fig. 8, the embodiment of the refrigerating circulatory device applying above-mentioned double-tube type heat exchanger 1 is described.
As refrigerating circulatory device embodiment 1, Fig. 5 shown in refrigerating circulatory device 101 there is compressor 103, condenser 105, expansion valve 107, evaporimeter 109 and above-mentioned double-tube type heat exchanger 1 as loop main composition key element.In double-tube type heat exchanger 1, export the high pressure liquid refrigerant (second fluid) of the entrance of expansion valve 107 (flow into before) and come to carry out heat exchange between low-pressure refrigerant gas (first fluid) that flash-pot 109 exports (before flowing into the entrance of compressor 103) carrying out condenser 105.Like this, by utilizing double-tube type heat exchanger 1, the inlet temperature of condenser 105 rises, therefore, it is possible to the ability improved when heating improve COP (value that ability obtains divided by input), maybe can prevent liquid refrigerant from turning back to compressor.
Below, as refrigerating circulatory device embodiment 2, Fig. 6 shown in refrigerating circulatory device 201 there is compressor 103, condenser 105, first expansion valve 207a, the second expansion valve 207b, evaporimeter 109 and above-mentioned double-tube type heat exchanger 1 as loop main composition key element.Expansion valve 207a is the same with the situation of embodiment 1 with evaporimeter 109 for compressor 103, condenser 105, first, constitutes basic refrigeration cycle.Bypass 211 is also provided with at refrigerating circulatory device 201, this bypass 211 is connected between the entrance exporting to the first expansion valve 207a from condenser 105 at the first tie point 213a, is connected between the entrance exporting to compressor 103 from evaporimeter 109 at the second tie point 213b.Second expansion valve 207b is arranged on bypass 211.
In double-tube type heat exchanger 1, export the high pressure liquid refrigerant (first fluid) of (before arriving the first tie point 213a) and calm the anger between liquid two phase refrigerant (second fluid) in exporting from the second expansion valve 207b of bypass 211 and carry out heat exchange carrying out condenser 105.The medium pressure gas cold-producing medium carried out in double-tube type heat exchanger 1 after heat exchange is inhaled into compressor 103.Like this, by utilizing double-tube type heat exchanger, can reduce than the first expansion valve 207a circulating mass of refrigerant downstream, therefore, it is possible to reduce the pressure loss, can COP be improved.
Below, as refrigerating circulatory device embodiment 3, Fig. 7 shown in refrigerating circulatory device 301 there is compressor 303, condenser 105, first expansion valve 207a, the second expansion valve 207b, evaporimeter 109 and above-mentioned double-tube type heat exchanger 1 as loop main composition key element.Expansion valve 207a is the same with the situation of embodiment 1 with evaporimeter 109 for compressor 303, condenser 105, first, constitutes basic refrigeration cycle.
In double-tube type heat exchanger 1, export the high pressure liquid refrigerant (first fluid) of (before arriving the first tie point 213a) and calm the anger between liquid two phase refrigerant (second fluid) in exporting from the second expansion valve 207b of bypass 211 and carry out heat exchange carrying out condenser 105.Then, make to have carried out in double-tube type heat exchanger 1 in the middle of the medium pressure gas refrigerant bypass after heat exchange to the compression unit of compressor 303.Like this, by utilizing double-tube type heat exchanger, can reduce than the first expansion valve 207a circulating mass of refrigerant downstream, and compression section can be carried out with multistage, therefore, it is possible to reduce the input of compressor, can COP be improved.
Further, the condenser of double-tube type heat exchanger 1 as basic refrigeration cycle itself uses by the refrigerating circulatory device 401 shown in Fig. 8.Refrigerating circulatory device 401 is that the cold-producing medium (second fluid) of the condenser made in double-tube type heat exchanger 1 under the usual condition of refrigeration cycle is carried out heat exchange with the fluid such as water, refrigerating medium (first fluid) carried by pump 415 and provides the example of the device of hot water.
Embodiment 2
Below, embodiments of the present invention 2 are described.Fig. 9 is relevant to present embodiment 2 with figure that is Fig. 3 same form.Present embodiment 2 is except the part of following explanation, and the embodiment 1 all with above-mentioned is the same, in addition, can be implemented too by the refrigerating circulatory device of pie graph 5 to Fig. 8.
Double-tube type heat exchanger 51 is the examples defining the groove 25 extended along flow direction in formation groove candidate scope at least partially.Namely, in present embodiment 2, only formed groove candidate scope namely in the afore mentioned rules portion of outer surface 5a of pipe 5, the inner surface in continuous portion 21 as shown in Figure 9 in the inner surface in the outer surface 19a in contiguity portion, inner side 19 and continuous portion 21 and outer surface and outer surface define groove 25.In such present embodiment 2, also the same with embodiment 1, liquid refrigerant can be made to be gathered in inner surface as the high continuous portion 21 of heat-transfer area availability and outer surface efficiently, even if when having biphase gas and liquid flow to flow in the second stream, by effectively utilizing heat-transfer area, also heat exchange performance can be improved.
Embodiment 3
Below, embodiments of the present invention 3 are described.Figure 10 be about present embodiment 3 with the figure of Fig. 3 same form.The embodiment 1 of present embodiment 3 all with above-mentioned except the part of following explanation is the same, in addition, equally also can be implemented by the refrigerating circulatory device of pie graph 5 to Fig. 8.
Double-tube type heat exchanger 61 is also the example defining the groove 25 extended along flow direction within the scope of formation groove candidate at least partially.In present embodiment 3, only formed groove candidate scope namely in the afore mentioned rules portion of outer surface 5a of pipe 5, in the inner surface in the outer surface 19a in contiguity portion, inner side 19 and continuous portion 21 and outer surface as shown in Figure 10 in the afore mentioned rules portion of outer surface 5a of pipe 5 and the outer surface 19a in contiguity portion, inner side 19 define groove 25.In such present embodiment 3, also the same with embodiment 1, when having biphase gas and liquid flow to flow in the second stream, by effectively utilizing heat-transfer area, also can heat exchange performance be improved.
Above, with reference to preferred embodiment illustrating content of the present invention, but certainly, as those skilled in the art, according to basic fundamental thought of the present invention and instruction, various changing form can be adopted.
Such as, in above-mentioned embodiment 1, also can change over and also form groove 25 at the outer surface 17a in the contiguity portion, outside 17 of heat transfer area enlarged tube 11.By such change, relative to the whole outer surface of heat transfer area enlarged tube 11, groove 25 is set as unified processing, the simplification of manufacture can be realized by the uniformity of processing.In addition, even if carried out such change, the outer surface 17a in the contiguity portion, outside 17 of the heat transfer area enlarged tube 11 of touching with outer tube 3, the importance as heat-transfer area is low, to utilize the viewpoint of heat-transfer area, also can't reduce validity of the present invention.That is, the easiness of producing can be improved while suitably keeping effective usability of the heat-transfer area in the present invention.
Description of reference numerals
1,51,61 double-tube type heat exchangers, 3 outer tubes, pipe in 5,7 first flow path, 9 annular sections, 11 heat transfer area enlarged tube, 23 second streams, 25 grooves, 101,201,301,401 refrigerating circulatory devices.
Claims (7)
1. a double-tube type heat exchanger, is characterized in that, possesses:
Outer tube;
Interior pipe, described interior pipe is inserted into the inner side of described outer tube, between this outer tube, form annular section, and forms first flow path in inner side; And
Heat transfer area enlarged tube, it is concavo-convex that described heat transfer area enlarged tube has relative to radial direction, is configured in the inner side of described outer tube and the outside of described interior pipe, forms the second stream at described annular section,
The part of with the outer surface of described heat transfer area enlarged tube together with delimiting described second stream of inner surface in the inner surface of described outer tube of the part of this heat transfer area enlarged tube of touching with the inner surface of described outer tube in the inner surface of described heat transfer area enlarged tube is set to respectively and does not form groove scope, this does not form groove scope is without groove face
Form groove candidate scope to form by with lower part, namely from not forming groove scope described in delimiting together with the outer surface of described interior pipe in the part of described second stream the inner surface of described heat transfer area enlarged tube eliminates and the part of delimiting described second stream together with the inner surface of described heat transfer area enlarged tube in the outer surface of the part of delimiting described second stream together with the inner surface of described outer tube in the outer surface of the part obtained, described heat transfer area enlarged tube and described interior pipe
At least partially or whole described formation groove candidate scope be formed along flow direction extend groove.
2. double-tube type heat exchanger according to claim 1, is characterized in that,
The part of touching with the outer surface of described interior pipe in the part of touching with the inner surface of described heat transfer area enlarged tube in the outer surface of the part of touching with the inner surface of described outer tube in the outer surface of the part of touching with the outer surface of described heat transfer area enlarged tube in the inner surface of described outer tube, described heat transfer area enlarged tube, described interior pipe and the inner surface of described heat transfer area enlarged tube is without groove face respectively.
3. double-tube type heat exchanger according to claim 1 and 2, is characterized in that,
After described heat transfer area enlarged tube defines described groove, this heat transfer area enlarged tube is inserted the described annular section between described outer tube and described interior pipe, the draw is carried out to described outer tube or expander is carried out to described interior pipe, thus this heat transfer area enlarged tube is by this outer tube and this interior piping support.
4. double-tube type heat exchanger according to any one of claim 1 to 3, is characterized in that,
Soldering is carried out to described interior pipe and described outer tube and described heat transfer area enlarged tube.
5. double-tube type heat exchanger according to claim 4, is characterized in that,
Described heat transfer area enlarged tube is the clad material of brazing material at surface application.
6. a refrigerating circulatory device, is characterized in that,
There is the double-tube type heat exchanger any one of claim 1 to 5,
In described double-tube type heat exchanger, cold-producing medium carries out heat exchange each other.
7. a refrigerating circulatory device, is characterized in that,
There is the double-tube type heat exchanger any one of claim 1 to 5,
Heat exchange is carried out between cold-producing medium and water or refrigerating medium in described double-tube type heat exchanger.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2012/082080 WO2014091558A1 (en) | 2012-12-11 | 2012-12-11 | Double-pipe heat exchanger and refrigeration cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105008839A true CN105008839A (en) | 2015-10-28 |
| CN105008839B CN105008839B (en) | 2017-04-05 |
Family
ID=50933884
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280077614.9A Active CN105008839B (en) | 2012-12-11 | 2012-12-11 | Double-tube type heat exchanger and refrigerating circulatory device |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20150323263A1 (en) |
| JP (1) | JP6029686B2 (en) |
| CN (1) | CN105008839B (en) |
| WO (1) | WO2014091558A1 (en) |
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| CN106965549A (en) * | 2017-01-18 | 2017-07-21 | 徐志强 | Ultrahigh speed hot-rolling |
| CN112008349A (en) * | 2019-05-28 | 2020-12-01 | 马勒国际有限公司 | Method for producing a heat exchanger assembly and heat exchanger assembly |
| CN113309637A (en) * | 2020-02-07 | 2021-08-27 | 中西商事株式会社 | Double tube structure, support, and method for forming double tube structure |
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| WO2017159542A1 (en) * | 2016-03-14 | 2017-09-21 | カルソニックカンセイ株式会社 | Double pipe |
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| CN108204750A (en) * | 2018-02-11 | 2018-06-26 | 佛山科学技术学院 | A kind of concave surface heat exchanger tube double pipe heat exchanger that interlocks |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2014091558A9 (en) | 2015-08-27 |
| WO2014091558A1 (en) | 2014-06-19 |
| US20150323263A1 (en) | 2015-11-12 |
| CN105008839B (en) | 2017-04-05 |
| JP6029686B2 (en) | 2016-11-24 |
| JPWO2014091558A1 (en) | 2017-01-05 |
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