CN105008839B - Double-tube type heat exchanger and refrigerating circulatory device - Google Patents
Double-tube type heat exchanger and refrigerating circulatory device Download PDFInfo
- Publication number
- CN105008839B CN105008839B CN201280077614.9A CN201280077614A CN105008839B CN 105008839 B CN105008839 B CN 105008839B CN 201280077614 A CN201280077614 A CN 201280077614A CN 105008839 B CN105008839 B CN 105008839B
- Authority
- CN
- China
- Prior art keywords
- tube
- transfer area
- heat transfer
- area enlarged
- double
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- 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
The present invention provide it is a kind of have two phase flow in second flow path in the case of can improve double-tube type heat exchanger of heat exchange performance etc..In double-tube type heat exchanger (1), possess with the concavo-convex heat transfer area enlarged tube (11) relative to radial direction, the part that second flow path (23) delimited together with the outer surface of heat transfer area enlarged tube in the inner surface of part and the inner surface of outer tube of the heat transfer area enlarged tube that the inner surface in the inner surface of the heat transfer area enlarged tube (11) with outer tube (3) is touched is set to as not forming groove scope without groove face.On the other hand, setting forms groove candidate's scope by what following part constituted, the part that second flow path delimited together with the inner surface of heat transfer area enlarged tube in the outer surface for not forming obtained from groove scope part, the part that second flow path delimited together with the inner surface of outer tube in the outer surface of heat transfer area enlarged tube and inner tube (5) is eliminated in the part that second flow path delimited together with the outer surface of inner tube i.e. from the inner surface of heat transfer area enlarged tube, the groove that extends is formed along flow direction in a part or the whole groove candidate scope that formed.
Description
Technical field
The present invention relates to combine the double-tube type heat exchanger that two streams are formed with the pipe of different tube diameters and
The refrigerating circulatory device of double-tube type heat exchanger is used.
Background technology
Double-tube type heat exchanger is that diameter little pipe (hereinafter referred to as inner tube) is inserted the big pipe of diameter (hereinafter referred to as
For outer tube), using the inside of inner tube as first flow path, using the outside of inner tube and the inner side of outer tube part as second flow path,
Heat exchange is carried out between the second fluid in the first fluid and second flow path in first flow path.
In addition, in the double-tube type heat exchanger, as the research for improving heat transfer property, such as there is patent documentation 1
Disclosed structure.That is, following method is proposed in patent documentation 1：Positioned at the outside of cylindric inner tube and cylinder
The second flow path of the ring-type between the inner side of the outer tube of shape is inserted into the heat transfer area enlarged tube that cross section is many flaps, by passing
The expansion effect of hot area is improving heat transfer property.
Prior art literature
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 2012-063067 publications
The content of the invention
Invention problem to be solved
The research to expanding heat transfer area is only disclosed in above-mentioned patent documentation 1.Here, the present inventor is conceived to
Two phase refrigerant is made to carry out suitably being conducted heat during heat exchange.
The present invention be in view of this situation and complete, it is therefore intended that provide one kind have two phase flow in second flow path
In the case of can improve double-tube type heat exchanger of heat exchange performance etc..
Means for solving the problems
To achieve these goals, double-tube type heat exchanger of the invention possesses：Outer tube；Inner tube, said inner tube are inserted
Enter the inner side of the outer tube, annular section is formed between the outer tube, and first flow path is formed in inner side；And heat-transfer area
Product enlarged tube, the heat transfer area enlarged tube with the inner side for relative to the concavo-convex of radial direction, being configured in the outer tube and it is described in
The outside of pipe, forms second flow path in the annular section；Will be outer with described in the inner surface of the heat transfer area enlarged tube
Pipe inner surface contiguity the heat transfer area enlarged tube the inner surface of part and the inner surface of the outer tube in the biography
The outer surface of hot area enlarged tube delimited the part of the second flow path together and is set to not form groove scope, and this does not form groove
Scope is, without groove face, to form groove candidate scope and be made up of following part, i.e., from the inner surface of the heat transfer area enlarged tube
Described formation obtained from groove scope is eliminated in the part that the second flow path delimited together with the outer surface of said inner tube
Partly, the portion that the second flow path delimited together with the inner surface of the outer tube in the outer surface of the heat transfer area enlarged tube
Point, and the outer surface of said inner tube in delimit the second flow path together with the inner surface of the heat transfer area enlarged tube
Part, is formed with the groove along flow direction extension at least a portion or the whole groove candidate's scope that formed.
The effect of invention
According to the present invention, in the case of having two phase flow in second flow path, it is possible to increase heat exchange performance.
Description of the drawings
Fig. 1 is to represent the inside of the double-tube type heat exchanger of embodiments of the present invention 1 in the direction orthogonal with pipe axle
The figure of construction.
Fig. 2 is the sectional view of the double-tube type heat exchanger of the II-II lines of Fig. 1.
Fig. 3 be enlargedly represent Fig. 2 in second flow path figure.
Fig. 4 is the part with regard to Fig. 3, is mutually divided outer tube, heat transfer area enlarged tube and inner tube to illustrate
The figure of liftoff expression.
Fig. 5 is the figure of the embodiment 1 for representing the refrigerating circulatory device for having used double-tube type heat exchanger.
Fig. 6 is the figure of the embodiment 2 for representing the refrigerating circulatory device for having used double-tube type heat exchanger.
Fig. 7 is the figure of the embodiment 3 for representing the refrigerating circulatory device for having used double-tube type heat exchanger.
Fig. 8 is the figure of the embodiment 4 for representing the refrigerating circulatory device for having used double-tube type heat exchanger.
Fig. 9 is the figure with Fig. 3 same forms with regard to embodiment 2.
Figure 10 is the figure with Fig. 3 same forms with regard to embodiment 3.
Specific embodiment
Hereinafter, with reference to the accompanying drawings embodiments of the present invention are illustrated.In figure, same reference represent it is same or
Corresponding part.
Embodiment 1
Fig. 1 is to represent the inside of the double-tube type heat exchanger of embodiments of the present invention 1 in the direction orthogonal with pipe axle
The figure of construction.Fig. 2 is the sectional view of the double-tube type heat exchanger of the II-II lines of Fig. 1.Additionally, preferentially guarantee the clear property of figure,
The diagram of heat transfer area enlarged tube described later is eliminated in FIG.Double-tube type heat exchanger 1 is with the relatively large circle of diameter
Pipe be the inner concentric of outer tube 3 insert the relatively small pipe of the diameter i.e. dual tube construction of inner tube 5.The inner side of inner tube 5 is empty
Between play first flow path 7 function.On the other hand, in the outside of inner tube 5 and the inner side of outer tube 3 is that annular section 9 contains biography
Hot area enlarged tube 11.
Heat transfer area enlarged tube 11 has as the relative concavo-convex multiple convex portions 13 with regard to radial direction and multiple recesses 15.
As shown in the cross section of Fig. 2, multiple convex portions 13 are radially arranged towards the radial outside of heat transfer area enlarged tube 11 and dash forward
Go out.In addition, multiple convex portions 13 are being substantially configured in circumferencial direction at equal intervals.On the other hand, multiple recesses 15 are located at correspondence respectively
A pair of convex portions 13 circumferencial direction between.These recesses 15 are also with substantially at equal intervals positioned at circumferencial direction.Therefore, in heat-transfer area
Product enlarged tube 11 sees that multiple convex portions 13 and multiple recesses 15 are alternately positioned in circumferencial direction on the whole.
In the present invention, the convex form of the convex portion seen in the cross section of the Fig. 2 with regard to heat transfer area enlarged tube and recessed
The concave shape in portion can consider various forms, and as an example, it is as follows in present embodiment 1.Heat transfer area expands
Big pipe 11 includes multiple outside contiguity portions 17, multiple inner side contiguity portions 19 and multiple continuous portions 21.As shown in Fig. 2 heat-transfer area
The outer surface 17a in the outside contiguity portion 17 of product enlarged tube 11 is touched with the inner surface 3b of outer tube 3, especially in this example, appearance
Face 17a is contacted with inner surface 3b faces.That is, the outer surface 17a in the outside contiguity portion 17 of heat transfer area enlarged tube 11 with outer tube 3
The roughly the same bendings of inner surface 3b.Equally, the inner surface 19b and inner tube in the inner side contiguity portion 19 of heat transfer area enlarged tube 11
5 outer surface 5a contiguity, especially in this example, inner surface 19b is contacted with outer surface 5a faces.That is, heat transfer area enlarged tube 11
Inner side contiguity portion 19 inner surface 19b with the bending roughly the same with the outer surface 5a of inner tube 5.Additionally, the identical is curved
Curved state can be obtained under outer tube 3, inner tube 5,11 respective free state of heat transfer area enlarged tube, it is also possible to along with from
Apply on the outside of the central side or radial direction of double-tube type heat exchanger 1 certain power assembling procedure finish in the state of obtain
.
Continuous portion 21 is located between adjacent outside contiguity portion 17 and inner side contiguity portion 19 respectively.In the present embodiment,
To be located at circumferencial direction at equal intervals, multiple inner side contiguity portions 19 are also with equal intervals positioned at circumferencial direction in multiple outside contiguity portions 17.
If seeing whole heat transfer area enlarged tube 11, in a circumferential direction, repeatedly outside contiguity portion 17, continuous portion 21, inner side it is close
The collocation form of socket part 19, the order in continuous portion 21.Additionally, convex portion 13 and recess 15 do not have a clear and definite border, convex portion 13 by
Part on the outside of the close radial direction in outside contiguity portion 17 and continuous portion 21 is constituted, and recess 15 is by inner side contiguity portion 19 and continuously
Part on the inside of the close radial direction in portion 21 is constituted.
The inner side of the convex portion 13 in above-mentioned annular section 9 and the outside of recess 15 play the function of second flow path 23.That is,
Second flow path 23 delimited by heat transfer area enlarged tube 11 in annular section 9.
More specifically, second flow path 23 includes the part of two kinds of forms, and the part of the first form is by outside contiguity portion 17
Inner surface 17b, the inner surface 21b in corresponding a pair continuous portions 21 and inner tube 5 outer surface 5a delimit.In addition, the second shape
The part of formula is by outer surface 19a, the outer surface 21a in corresponding a pair continuous portions 21 and outer tube 3 in inner side contiguity portion 19
Surface 3b delimited.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 in second flow path 23.The
One fluid is different from the temperature of second fluid, via the heat conduction of inner tube 5 and heat transfer area enlarged tube 11, in first fluid and second
Heat exchange is carried out between fluid.
Typically, deposit between heat-shift Q, heat transfer area A, coefficient of overall heat transmission K, first fluid and temperature difference dT of second fluid
In the relation shown in formula (1).
[number 1]
Q=AKdT (1)
In addition, coefficient of overall heat transmission K can be represented with formula (2).
[number 2]
Additionally, the meaning of each symbol is as follows.α1：The coefficient of overall heat transmission of fluid 1, d1：The hydraulic diameter of stream 1, α 2：Fluid 2
The coefficient of overall heat transmission, d2：The hydraulic diameter of stream 2, λ：The thermal conductivity of inner tube, dio：The external diameter of inner tube, doi：The internal diameter of inner tube, R：Heat
Resistance.
Above-mentioned heat transfer area enlarged tube 11 plays the effect of fin by contacting with inner tube 5, therefore, it is possible to expand
Heat transfer area, by increasing capacitance it is possible to increase the heat-shift of first fluid and second fluid.
Here, with reference to Fig. 3 and Fig. 4 to have in second flow path 23 biphase gas and liquid flow flow in the case of cold-producing medium stream
Dynamic state is illustrated.Fig. 3 is the figure with Fig. 2 same forms, is the figure for enlargedly representing second flow path, and Fig. 4 is with regard to Fig. 3
Part, figure outer tube, heat transfer area enlarged tube and inner tube represented separated from each other in order to illustrate.Here, it is general,
The high liquid refrigerant of the coefficient of overall heat transmission in two phase flow is touched with tube wall, and the low gas refrigerant of the coefficient of overall heat transmission is at the position away from tube wall
Flowing.That is, liquid refrigerant concentrates on reference 3b, 5a shown in Fig. 3, the wall shown in 17b, 19a, 21a, 21b.
Therefore, in the present invention, what setting was following does not form groove scope and forms groove candidate's scope, and not forming groove scope is
Without groove face, the groove along flow direction extension is formed with least a portion or the whole groove candidate's scope that formed.Present embodiment 1
It is the example of the situation that groove is defined in whole formation groove candidate's scope therein.
Illustrate to not forming groove scope and forming the details of groove candidate's scope.Specifically, heat transfer area expands
Inner surface (the outside of the part of the heat transfer area enlarged tube 11 touched with the inner surface 3b of outer tube 3 in the inner surface of big pipe 11
The inner surface 17b in contiguity portion 17) it is not form groove scope.Also, in the inner surface 3b of outer tube 3 with heat transfer area enlarged tube 11
Outer surface to delimit the part of second flow path 23 together be also not form groove scope.Do not formed after groove scope do not formed at these
The groove 25 stated.
In addition, form groove candidate scope being made up of following part：From the inner surface of heat transfer area enlarged tube 11 with it is interior
The outer surface 5a of pipe 5 delimited together to eliminate in the part of second flow path 23 and above-mentioned formed groove scope (outside contiguity portion 17
Inner surface 17b) obtained from part (the inner surface 21b in continuous portion 21), in the outer surface of heat transfer area enlarged tube 11 with
The inner surface 3b of outer tube 3 delimit together second flow path 23 part (the outer surface 21a in continuous portion 21 and inner side contiguity portion 19 it is outer
Surface 19a), and the outer surface 5a of inner tube 5 in second flow path 23 delimited together with the inner surface of heat transfer area enlarged tube 11
Part.
In present embodiment 1, as described above, groove is not formed groove scope is not formed, and form groove candidate's model whole
Enclose to form groove, it is more specifically, as follows.Groove 25 is formed in following part：With outside contiguity portion 17 and a pair continuous portions
The part of outer surface 5a of 21 inner tubes 5 for delimiting second flow path 23 together, the inner side contiguity portion 19 of heat transfer area enlarged tube 11
Outer surface 19a and the outer surface 21a and inner surface 21b in continuous portion 21.In addition, by the inner surface 17b in outside contiguity portion 17 with
And the part of the inner surface 3b of the outer tube 3 of delimitation second flow path 23 is set to nothing together with inner side contiguity portion 19 and a pair continuous portions 21
Groove face.Additionally, be not particularly limited as the present invention, but in present embodiment 1, will be the outside of heat transfer area enlarged tube 11 close
The part of the inner surface 3b of the outer surface 17a of socket part 17 and the outer tube 3 touched with outer surface 17a is set to without groove face, also, will
The part of the outer surface 5a of the inner surface 19b in inner side contiguity portion 19 and the inner tube 5 touched with inner surface 19b is set to without groove face.
In order that cold-producing medium swimmingly flows to flow direction, groove 25 is formed in the form of extending along flow direction.This
Outward, the groove in Fig. 3 and Fig. 4 is schematically drawn, in addition, in fig. 2, preferably ensuring that the clear property of figure, eliminates groove
Diagram.
Furthermore, it is possible to consider by punch forming, drawing processing to shape heat transfer area enlarged tube 11, therefore, for letter
Change processing, while grooving 25 when in punch forming, drawing processing.In addition, by the heat transfer area for defining groove 25 is expanded
Big pipe 11 inserts the annular section 9 between outer tube 3 and inner tube 5 and carries out the draw to outer tube 3 or carry out expander to inner tube 5, conducts heat
Area enlarged tube 11 is supported by outer tube 3 and inner tube 5.
Or, as inner tube 5 and outer tube 3 and the method for the contiguity of heat transfer area enlarged tube 11 is more reliably made, each is connect
The form that contacting surface carries out soldering to engage is also suitable.Specifically, can be outside heat transfer area enlarged tube 11 be installed on
After pipe 3 and inner tube 5, brazing material is applied to contact surface, by furnace brazing etc., make brazing material melts, contact surface is entered
Row soldering.In addition, the inconvenient feelings of brazing material are applied after heat transfer area enlarged tube 11 to be installed on inner tube 5 and outer tube 3
Under condition, it is also possible to carry out pricker by the clad material for being pre-coated with brazing material is used in heat transfer area enlarged tube 11
Weldering.
According to double-tube type heat exchanger 1 constructed as disclosed above, following excellent advantage can be obtained.Inner tube 5
Even if the specified part of outer surface 5a and the outer surface 19a in inner side contiguity portion 19 delimit second flow path 23 part in be also from
The extremely near part of first flow path 7, is the effective degree highest part as heat-transfer area.In addition, continuous portion 21 is located at second flow path
Between the 23 above-mentioned part of the first form and the part of the second form, the inner surface and outer surface in continuous portion 21 make continuously
Portion 21 plays the effect of fin and (closes the inside of second flow path 23 between the part of the first form and the part of the second form
System) carry out being effective heat-transfer area during the heat exchange between second fluid.Therefore, groove 25 is formed as described above, can
Make liquid refrigerant be energetically gathered near first flow path 7 inner tube 5 outer surface 5a specified part and with inner tube 5 contiguity
The outer surface 19a and 21 inner surface of continuous portion and outer surface in inner side contiguity portion 19.In addition, at the same time, by will be far from
One stream 7 and as the low outer tube 3 of heat-transfer area effective degree inner surface 3b specified part and the inner surface in outside contiguity portion 17
17b is set in advance as without groove face, and relatively, compared with the specified part, outer surface 19a with outer surface 5a, liquid refrigerant is difficult to gather
Collection, used as its counteractive effect, auxiliary liquid cold-producing medium is gathered in the specified part of outer surface 5a, outer surface 19a and continuous
The inner surface and outer surface in portion 21.That is, the high liquid refrigerant of the coefficient of overall heat transmission is also by large supply to low as heat-transfer area effective degree
Outer tube 3 inner surface 3b specified part and the inner surface 17b in outside contiguity portion 17, so as to correspondingly suppress liquid refrigerant to
The inner surface and outer surface of specified part, outer surface 19a and continuous portion 21 as the high outer surface 5a of heat-transfer area effective degree
Quantity delivered is reduced.So, according to present embodiment, even if in second flow path, have biphase gas and liquid flow to flow in the case of, passing through
Effectively utilize heat-transfer area, it is also possible to improve heat exchange performance.
In addition, in present embodiment 1, the outer surface 17a in the outside contiguity portion 17 of heat transfer area enlarged tube 11 and
Part with the inner surface 3b of the outer tube 3 of outer surface 17a contiguity is without groove face, equally, the inner surface 19b in inner side contiguity portion 19
And the part of the outer surface 5a of the inner tube 5 touched with inner surface 19b is without groove face such that it is able to by inner tube 5 and outer tube 3 and biography
The adhesion of hot area enlarged tube 11 is kept as height, moreover, is particularly due to inner tube 5 close with heat transfer area enlarged tube 11
Connecing property is high, it is possible to increase the efficiency of the heat conduction carried out by heat transfer area enlarged tube 11, efficiently can be expanded using heat transfer area
The presence of pipe 11.
Hereinafter, with reference to Fig. 5 to Fig. 8 to applying the enforcement of the refrigerating circulatory device of above-mentioned double-tube type heat exchanger 1
Example is illustrated.
Used as the embodiment 1 of refrigerating circulatory device, the refrigerating circulatory device 101 shown in Fig. 5 has compressor 103, condensation
Device 105, expansion valve 107, vaporizer 109 and above-mentioned double-tube type heat exchanger 1 are used as loop main composition key element.Double
In layer tubing heat exchanger 1, carrying out condenser 105 and exporting the highly pressurised liquid refrigeration of the entrance of expansion valve 107 (flow into before)
Agent (second fluid) exports the low-pressure refrigerant gas (first of (before flowing into the entrance of compressor 103) with flash-pot 109 is carried out
Fluid) between carry out heat exchange.So, by using double-tube type heat exchanger 1, the inlet temperature of condenser 105 rises, because
This can improve ability when heating and improve COP (ability is divided by value obtained from input), or be prevented from liquid refrigerant
Return to compressor.
Hereinafter, as the embodiment 2 of refrigerating circulatory device, the refrigerating circulatory device 201 shown in Fig. 6 have compressor 103,
Condenser 105, the first expansion valve 207a, the second expansion valve 207b, vaporizer 109 and above-mentioned double-tube type heat exchanger 1
As loop main composition key element.Compressor 103, condenser 105, the first expansion valve 207a and vaporizer 109 and embodiment 1
Situation is the same, constitutes basic refrigeration cycle.Bypass 211 is also provided with refrigerating circulatory device 201, the bypass
211 are connected between the entrance for exporting to the first expansion valve 207a of condenser 105 in the first junction point 213a, connect second
Contact 213b is connected between the entrance for exporting to compressor 103 of vaporizer 109.Second expansion valve 207b is arranged on bypass
Road 211.
In double-tube type heat exchanger 1, carrying out condenser 105 and exporting the height of (reach in the first junction point 213a before)
The middle pressure gas-liquid two-phase cold-producing medium that hydraulic fluid cryogen (first fluid) is exported with the second expansion valve 207b from bypass 211
Heat exchange is carried out between (second fluid).The medium pressure gas refrigeration after heat exchange has been carried out in double-tube type heat exchanger 1
Agent is inhaled into compressor 103.So, by using double-tube type heat exchanger, can reduce than the first expansion valve 207a on the lower
The circulating mass of refrigerant of trip, therefore, it is possible to reduce the pressure loss, it is possible to increase COP.
Hereinafter, as the embodiment 3 of refrigerating circulatory device, the refrigerating circulatory device 301 shown in Fig. 7 have compressor 303,
Condenser 105, the first expansion valve 207a, the second expansion valve 207b, vaporizer 109 and above-mentioned double-tube type heat exchanger 1
As loop main composition key element.Compressor 303, condenser 105, the first expansion valve 207a and vaporizer 109 and embodiment 1
Situation is the same, constitutes basic refrigeration cycle.
In double-tube type heat exchanger 1, carrying out condenser 105 and exporting the height of (reach in the first junction point 213a before)
The middle pressure gas-liquid two-phase cold-producing medium that hydraulic fluid cryogen (first fluid) is exported with the second expansion valve 207b from bypass 211
Heat exchange is carried out between (second fluid).Then, calm the anger in making to have carried out in double-tube type heat exchanger 1 after heat exchange
Cryogen is bypassed in the middle of the compression unit of compressor 303.So, by using double-tube type heat exchanger, ratio can be reduced
First expansion valve 207a circulating mass of refrigerant downstream, and operation can be compressed with multistage, therefore, it is possible to reduce pressure
The input of contracting machine, it is possible to increase COP.
Also, the refrigerating circulatory device 401 shown in Fig. 8 is returned double-tube type heat exchanger 1 as basic kind of refrigeration cycle
The condenser on road itself is used.Refrigerating circulatory device 401 is refrigeration cycle is made in double-tube type heat exchanger 1 usual
The fluids (first fluid) such as the cold-producing medium (second fluid) of the condenser under situation and the water, refrigerating medium conveyed by pump 415 are entered
Row heat exchange and the example of the device of hot water is provided.
Embodiment 2
Hereinafter, embodiments of the present invention 2 are illustrated.Fig. 9 is related to present embodiment 2 with Fig. 3 phase similar shapes
The figure of formula.Present embodiment 2 in addition to the part of following explanation, all as above-mentioned embodiment 1, in addition, similarly
Can be implemented by the refrigerating circulatory device of composition Fig. 5 to Fig. 8.
Double-tube type heat exchanger 51 is to define along flow direction to prolong at least one of formation groove candidate's scope
The example of the groove 25 stretched.That is, in present embodiment 2, the above-mentioned rule that groove candidate's scope is the outer surface 5a of inner tube 5 are being formed only
Determine the continuous portion as shown in Figure 9 in the inner surface and outer surface in portion, the outer surface 19a in inner side contiguity portion 19 and continuous portion 21
21 inner surface and outer surface define groove 25.In such present embodiment 2, also as embodiment 1, liquid can be made
Cryogen is efficiently gathered in inner surface and outer surface as the high continuous portion 21 of heat-transfer area effective degree, even if in second
In the case of having biphase gas and liquid flow to flow in road, by effectively utilizing heat-transfer area, it is also possible to improve heat exchange performance.
Embodiment 3
Hereinafter, embodiments of the present invention 3 are illustrated.Figure 10 is with regard to present embodiment 3 and Fig. 3 same forms
Figure.Present embodiment 3 in addition to the part of following explanation all as above-mentioned embodiment 1, in addition, equally also can
Implemented by constituting the refrigerating circulatory device of Fig. 5 to Fig. 8.
Double-tube type heat exchanger 61 is also to define along flowing side in the range of at least one of formation groove candidate
To the example of the groove 25 for extending.In present embodiment 3, only formed groove candidate's scope be inner tube 5 outer surface 5a it is above-mentioned
It is as shown in Figure 10 interior in the inner surface and outer surface of specified part, the outer surface 19a in inner side contiguity portion 19 and continuous portion 21
The above-mentioned specified part of the outer surface 5a of pipe 5 and the outer surface 19a in inner side contiguity portion 19 define groove 25.In such this embodiment party
In formula 3, also as embodiment 1, in second flow path, have biphase gas and liquid flow to flow in the case of, by effectively utilizing biography
Hot face, it is also possible to improve heat exchange performance.
More than, reference is preferred embodiment illustrated to present disclosure, but certainly, as ability
Field technique personnel, can be with basic fundamental thought of the invention and instruction, using various changes form.
For example, in above-mentioned embodiment 1, it is also possible to change in the outside contiguity portion 17 of heat transfer area enlarged tube 11
Outer surface 17a also form groove 25.By so change, relative to the whole outer surface of heat transfer area enlarged tube 11, as system
One processing and groove 25 is set, can pass through processing uniformity realize manufacture simplification.Even if in addition, having carried out such changing
Become, the outer surface 17a with the outside contiguity portion 17 of the heat transfer area enlarged tube 11 of the contiguity of outer tube 3, as the importance of heat-transfer area
It is low, from the viewpoint of using heat-transfer area, can't also reduce effectiveness of the invention.That is, this can suitably kept
The easiness of production is improved while the effectively utilizes of the heat-transfer area in bright.
Description of reference numerals
1st, 51,61 double-tube type heat exchanger, 3 outer tubes, 5 inner tubes, 7 first flow path, 9 annular sections, 11 heat transfer areas expand
It is big to manage, 23 second flow paths, 25 grooves, 101,201,301,401 refrigerating circulatory devices.
Claims (7)
1. a kind of double-tube type heat exchanger, it is characterised in that possess：
Outer tube；
Inner tube, said inner tube are inserted into the inner side of the outer tube, and annular section is formed between the outer tube, and in inner side shape
Into first flow path；And
Heat transfer area enlarged tube, the heat transfer area enlarged tube are configured in the interior of the outer tube with relative to the concavo-convex of radial direction
Side and the outside of said inner tube, form second flow path in the annular section,
By the heat transfer area enlarged tube touched with the inner surface of the outer tube in the inner surface of the heat transfer area enlarged tube
The inner surface of part and the inner surface of the outer tube in delimit together with the outer surface of the heat transfer area enlarged tube it is described
The part of second flow path is set to not form groove scope, this do not formed groove scope be without groove face,
Form groove candidate scope to be made up of following part, i.e., from the inner surface of the heat transfer area enlarged tube and said inner tube
Outer surface delimit together to eliminate in the part of the second flow path and described form part, the biography obtained from groove scope
The part that the second flow path delimited together with the inner surface of the outer tube in the outer surface of hot area enlarged tube and described
The part that the second flow path delimited together with the inner surface of the heat transfer area enlarged tube in the outer surface of inner tube,
The groove along flow direction extension is formed with least a portion or the whole groove candidate's scope that formed.
2. double-tube type heat exchanger according to claim 1, it is characterised in that
The part touched with the outer surface of the heat transfer area enlarged tube in the inner surface of the outer tube, the heat transfer area are expanded
In the part touched with the inner surface of the outer tube, the outer surface of said inner tube in the outer surface of big pipe with the heat-transfer area
The appearance with said inner tube in the part of inner surface contiguity of product enlarged tube and the inner surface of the heat transfer area enlarged tube
The part of face contiguity is without groove face respectively.
3. double-tube type heat exchanger according to claim 1, it is characterised in that
After the heat transfer area enlarged tube defines the groove, by the heat transfer area enlarged tube insert described outer tube with it is described
The annular section between inner tube, carries out the draw or carries out expander to said inner tube, so as to the heat transfer area to the outer tube
Enlarged tube is by the outer tube and the interior piping support.
4. double-tube type heat exchanger according to claim 1, it is characterised in that
Soldering is carried out to said inner tube and the outer tube and the heat transfer area enlarged tube.
5. double-tube type heat exchanger according to claim 4, it is characterised in that
The heat transfer area enlarged tube is to be coated with the clad material of brazing material on surface.
6. a kind of refrigerating circulatory device, it is characterised in that
Double-tube type heat exchanger with any one of claim 1 to 5,
In the double-tube type heat exchanger, cold-producing medium carries out heat exchange each other.
7. a kind of refrigerating circulatory device, it is characterised in that
Double-tube type heat exchanger with any one of claim 1 to 5,
Heat exchange is carried out in the double-tube type heat exchanger between cold-producing medium and water or refrigerating medium.
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 CN105008839A (en) | 2015-10-28 |
| CN105008839B true 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) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20160001389A (en) * | 2014-06-27 | 2016-01-06 | 삼성전자주식회사 | Refrigerator and method for controlling the same |
| JP6657613B2 (en) * | 2015-06-18 | 2020-03-04 | ダイキン工業株式会社 | Air conditioner |
| WO2017159542A1 (en) * | 2016-03-14 | 2017-09-21 | カルソニックカンセイ株式会社 | Double pipe |
| US10399117B2 (en) | 2016-04-12 | 2019-09-03 | United Technologies Corporation | Method of making light weight component with internal metallic foam and polymer reinforcement |
| US10323325B2 (en) | 2016-04-12 | 2019-06-18 | United Technologies Corporation | Light weight housing for internal component and method of making |
| US10335850B2 (en) | 2016-04-12 | 2019-07-02 | United Technologies Corporation | Light weight housing for internal component and method of making |
| US10302017B2 (en) | 2016-04-12 | 2019-05-28 | United Technologies Corporation | Light weight component with acoustic attenuation and method of making |
| US10619949B2 (en) * | 2016-04-12 | 2020-04-14 | United Technologies Corporation | Light weight housing for internal component with integrated thermal management features and method of making |
| US10724131B2 (en) | 2016-04-12 | 2020-07-28 | United Technologies Corporation | Light weight component and method of making |
| US20170356692A1 (en) * | 2016-06-08 | 2017-12-14 | Savannah River Nuclear Solutions, Llc | Finned Heat Exchanger |
| CN106965549A (en) * | 2017-01-18 | 2017-07-21 | 徐志强 | Ultrahigh speed hot-rolling |
| 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 |
| EP3731610B1 (en) * | 2019-04-23 | 2023-11-15 | ABB Schweiz AG | Heat exchanging arrangement and subsea electronic system |
| DE102019207830A1 (en) * | 2019-05-28 | 2020-12-03 | Mahle International Gmbh | Manufacturing method for manufacturing a heat exchanger arrangement and heat exchanger arrangement for cooling and / or heating a heat exchanger fluid |
| JP7055826B2 (en) * | 2020-02-07 | 2022-04-18 | 中西商事株式会社 | Double tube structure, support and method of forming double tube structure |
| CA3124555A1 (en) | 2020-08-21 | 2022-02-21 | Yutaka Giken Co., Ltd. | Double pipe and method for manufacturing same |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2347133Y (en) * | 1998-10-20 | 1999-11-03 | 无锡市灵通机械厂 | High-efficiency heat exchange tube with inner fins |
| CN1378638A (en) * | 1999-07-22 | 2002-11-06 | 施皮罗研究公司 | Method for manufacturing double-walled heat exchanging tube with leak detection and said heat exchanging tube |
| CN2537923Y (en) * | 2002-04-28 | 2003-02-26 | 重庆市江北区兴海机电有限责任公司 | Composite metal tube for water heater |
| JP2006207936A (en) * | 2005-01-28 | 2006-08-10 | Matsushita Electric Ind Co Ltd | Heat exchanger |
| CN2876678Y (en) * | 2006-02-22 | 2007-03-07 | 苏权兴 | Heat exchanger for heat pump water heater |
| CN101469920A (en) * | 2007-12-28 | 2009-07-01 | 昭和电工株式会社 | Double-wall-tube heat exchanger |
| CN201449184U (en) * | 2009-04-23 | 2010-05-05 | 中山市高申节能电器有限公司 | Condensed double pipe heat exchanger |
| CN201628427U (en) * | 2009-09-07 | 2010-11-10 | 上海汽车空调配件有限公司 | Composite pipe structure for air-conditioner pipeline |
| CN102636052A (en) * | 2012-05-11 | 2012-08-15 | 江苏亚太轻合金科技股份有限公司 | High-efficiency heat exchange coaxial pipe |
| CN102650480A (en) * | 2011-02-22 | 2012-08-29 | 富士电机零售设备系统株式会社 | Heat exchanger |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3831247A (en) * | 1971-11-22 | 1974-08-27 | United Aircraft Prod | Method of metallurgically bonding a internally finned heat exchange structure |
| JPH064221Y2 (en) * | 1987-05-21 | 1994-02-02 | 三菱電機株式会社 | Heat exchanger |
| JPH0482571U (en) * | 1990-11-26 | 1992-07-17 | ||
| JP2000002492A (en) * | 1998-06-17 | 2000-01-07 | Zexel Corp | Heat exchanger |
| DE10392626T5 (en) * | 2002-05-10 | 2005-06-30 | Usui Kokusai Sangyo Kaisha, Ltd. | Heat pipe and heat exchanger with such a heat pipe |
| JP2004093037A (en) * | 2002-08-30 | 2004-03-25 | Toyo Radiator Co Ltd | Double-pipe heat exchanger |
| JP3811123B2 (en) * | 2002-12-10 | 2006-08-16 | 松下電器産業株式会社 | Double tube heat exchanger |
| JP4983279B2 (en) * | 2007-02-01 | 2012-07-25 | パナソニック株式会社 | Manufacturing method of heat exchanger |
| JP5333041B2 (en) * | 2009-08-21 | 2013-11-06 | ダイキン工業株式会社 | Heat exchanger and refrigeration apparatus provided with the same |
| JP2011112331A (en) * | 2009-11-30 | 2011-06-09 | T Rad Co Ltd | Heat exchanger for exhaust gas |
-
2012
- 2012-12-11 JP JP2014551768A patent/JP6029686B2/en active Active
- 2012-12-11 US US14/648,343 patent/US20150323263A1/en not_active Abandoned
- 2012-12-11 WO PCT/JP2012/082080 patent/WO2014091558A1/en active Application Filing
- 2012-12-11 CN CN201280077614.9A patent/CN105008839B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2347133Y (en) * | 1998-10-20 | 1999-11-03 | 无锡市灵通机械厂 | High-efficiency heat exchange tube with inner fins |
| CN1378638A (en) * | 1999-07-22 | 2002-11-06 | 施皮罗研究公司 | Method for manufacturing double-walled heat exchanging tube with leak detection and said heat exchanging tube |
| CN2537923Y (en) * | 2002-04-28 | 2003-02-26 | 重庆市江北区兴海机电有限责任公司 | Composite metal tube for water heater |
| JP2006207936A (en) * | 2005-01-28 | 2006-08-10 | Matsushita Electric Ind Co Ltd | Heat exchanger |
| CN2876678Y (en) * | 2006-02-22 | 2007-03-07 | 苏权兴 | Heat exchanger for heat pump water heater |
| CN101469920A (en) * | 2007-12-28 | 2009-07-01 | 昭和电工株式会社 | Double-wall-tube heat exchanger |
| CN201449184U (en) * | 2009-04-23 | 2010-05-05 | 中山市高申节能电器有限公司 | Condensed double pipe heat exchanger |
| CN201628427U (en) * | 2009-09-07 | 2010-11-10 | 上海汽车空调配件有限公司 | Composite pipe structure for air-conditioner pipeline |
| CN102650480A (en) * | 2011-02-22 | 2012-08-29 | 富士电机零售设备系统株式会社 | Heat exchanger |
| JP2012189312A (en) * | 2011-02-22 | 2012-10-04 | Fuji Electric Retail Systems Co Ltd | Heat exchanger |
| CN102636052A (en) * | 2012-05-11 | 2012-08-15 | 江苏亚太轻合金科技股份有限公司 | High-efficiency heat exchange coaxial pipe |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2014091558A1 (en) | 2017-01-05 |
| CN105008839A (en) | 2015-10-28 |
| WO2014091558A1 (en) | 2014-06-19 |
| US20150323263A1 (en) | 2015-11-12 |
| WO2014091558A9 (en) | 2015-08-27 |
| JP6029686B2 (en) | 2016-11-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105008839B (en) | Double-tube type heat exchanger and refrigerating circulatory device | |
| CN100491866C (en) | Multistage-cascaded compression type heat pump set under large temperature difference | |
| CN209910459U (en) | Heat exchange double-layer sleeve | |
| CN104704311B (en) | Double pipe exchanger and refrigerating circulatory device | |
| CN101226031A (en) | Winding type spiral pipe heat exchanger | |
| JP2018071967A (en) | Evaporator and method of conditioning air | |
| CN105865064A (en) | Refrigerator refrigeration circulation system | |
| CN2926937Y (en) | Heat exchanger of wind-cooling hot-pump set | |
| CN102022933A (en) | Wound pipe heat exchanger | |
| CN202361699U (en) | Micro-channel heat exchanger with enlarged elongated inner volume | |
| CN104040281B (en) | Air conditioner | |
| CN105910346A (en) | Shell-and-tube condenser | |
| CN106091742A (en) | Become caliber heat-exchange device and pipe-line system | |
| CN103277944B (en) | Dry-type evaporator | |
| CN201935605U (en) | Spiral coil heat exchanger | |
| CN102980332B (en) | Heat recovery shell and tube condenser | |
| CN207395245U (en) | A kind of Teat pump boiler condenser and the Teat pump boiler with the condenser | |
| CN205690752U (en) | A kind of shell and tube condenser | |
| CN102967086B (en) | Plate-type evaporator and refrigeration system | |
| CN206001738U (en) | Cascade type heat pump unit | |
| CN205655723U (en) | A shell and tube type heat exchanger for carbon dioxide heat pump system | |
| CN203561064U (en) | Water tank heat exchanger and heat-pump water heater | |
| CN103353191A (en) | Heat exchanger, evaporator and manufacturing method of heat exchange components | |
| CN211601199U (en) | Evaporator and engine | |
| CN206875764U (en) | Condenser assembly and air-conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |