CN104704311B - Double pipe exchanger and refrigerating circulatory device - Google Patents
Double pipe exchanger and refrigerating circulatory device Download PDFInfo
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- CN104704311B CN104704311B CN201380051921.4A CN201380051921A CN104704311B CN 104704311 B CN104704311 B CN 104704311B CN 201380051921 A CN201380051921 A CN 201380051921A CN 104704311 B CN104704311 B CN 104704311B
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- Prior art keywords
- tube
- heat transfer
- transfer area
- inner tube
- contact
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
-
- 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
Abstract
The present invention provides a kind of double pipe exchanger, there is the inner tube (2) that first fluid internally passes through, the outer tube (1) that inner tube (2) and space between inner tube (2) for the second fluid are passed through is covered with the diameter bigger than inner tube (2), with heat transfer area enlarged tube (3), described heat transfer area enlarged tube (3) arranges in space, there is convex-concave profile, described convex-concave profile as with the pipe circumferential direction in the interior side contacts portion (6) of the part of the wall contacts of inner tube (2) on length be used for long with the length in the pipe circumferential direction in the contact outside portion (7) of the part of the contact internal walls of outer tube (1), in addition, on pipe cross section, crosscutting space and the fin part between contact outside portion (7) and interior side contacts portion (6) are from incline direction and the outer wall of inner tube (2) and the contact internal walls of outer tube (1).
Description
Technical field
The present invention relates to the double hose being combined and form two streams the pipe with different tube diameter changes
Hot device and the refrigerating circulatory device using this double pipe exchanger.
Background technology
As the example of the double pipe exchanger that improve conventional heat transfer property, have by pipe little for diameter (below
It is designated as inner tube) insert the structure being formed in the big pipe (being designated as outer tube below) of diameter.And it is proposed that following method：Will
The inside of inner tube as first flow path, will be formed in stream between two pipes as second flow path, will be shaped to ridge shape
Heat transfer area enlarged tube insertion second flow path is simultaneously in close contact with inner and outer tubes, is improved by the expansion effect of heat transfer area
Heat transfer property (referring for example to patent documentation 1).
Prior art literature
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 2012-63067 publication (Fig. 1)
Content of the invention
Invention technical problem to be solved
It is proposed that expanding heat transfer area thus improving by inserting heat transfer area enlarged tube in above-mentioned patent documentation 1
The double pipe exchanger of heat transfer property.But, do not relate to efficiently improve the heat transfer area enlarged tube of heat transfer property
Specific scheme etc..
Therefore, it is an object of the invention to obtaining a kind of double pipe exchanger and system that can efficiently improve heat transfer property
SAPMAC method device.
Means for solving the problem
The double pipe exchanger of the present invention has：Inner tube, first fluid passes through in the inside of said inner tube；Outer tube, described
Outer tube covers inner tube with the diameter bigger than this inner tube, and second fluid passes through the space between outer tube and inner tube；Heat transfer area expands
Big pipe, described heat transfer area enlarged tube is arranged on described space, and in pipe cross section, heat transfer area enlarged tube is in interior side contacts portion
It is less than in contact outside portion and described outer tube wall angulation, described interior side contacts with said inner tube outer wall angulation
Portion is the contact portion of described heat transfer area enlarged tube and described outer tube outer wall, and described contact outside portion is that described heat transfer area expands
Big pipe and the contact portion of described outer tube wall, described heat transfer area enlarged tube has convex-concave profile on pipe cross section, in pipe
On cross section crosscutting space and the fin part between interior side contacts portion and contact outside portion from incline direction and outer wall of inner tube and
Outer tube wall contacts.
The effect of invention
According to the present invention, due to have with the length in the pipe circumferential direction of the part of the wall contacts of inner tube than with outer tube
The heat transfer area enlarged tube contacting with outer tube and inner tube of the length length of the part of contact internal walls, therefore, it is possible to make during fabrication
It is applied to the external force dispersion of heat transfer area enlarged tube, on the basis of enabling in particular to the loose contact between suppression and inner tube, scheme
Ask the expansion of heat transfer area, improve heat transfer property.
Brief description
Fig. 1 is the figure of the structure of the double pipe exchanger that embodiments of the present invention 1 are described.
Fig. 2 is the figure in the section of the other direction of the double pipe exchanger representing embodiments of the present invention 1.
Fig. 3 is the figure in the section of the double pipe exchanger representing embodiments of the present invention 3.
Fig. 4 is the figure of the projection for heat transfer area enlarged tube 3 is described.
Fig. 5 is the figure representing the parameter being set in double pipe exchanger.
Fig. 6 is the figure of the brazed portion representing embodiments of the present invention 4.
Fig. 7 is the figure of the refrigerating circulatory device representing the double pipe exchanger employing the present invention.
Specific embodiment
Embodiment 1
Fig. 1 is the figure of the structure of the double pipe exchanger that embodiments of the present invention 1 are described.In FIG, represent along system
The flowing (especially along inner tube 2) of cryogen is cutting off the sectional view of double pipe exchanger.The structure of double pipe exchanger is：Will be straight
The little pipe in footpath is that inner tube 2 inserts the inner side that the big pipe of diameter is outer tube 1.And, the end of the heat exchanger of dual round structure
It is configured to：The inner wall section (outer tube wall) of outer tube 1 contacts the (side of closing outer tube 1 with the outer wall section (outer wall of inner tube) of inner tube 2
Wall part covers inner tube 2).
The inside of inner tube 2 is inside passages 4 as first flow path, the space that will be formed between inner tube 2 and outer tube 1 is made
It is outside passages 5 for second flow path.The flow export of the cold-producing medium of outside passages 5 and inflow entrance form insertion in the wall of outer tube 1
Hole is simultaneously connected to connecting pipings.And, first fluid and second fluid flow respectively in inside passages 4 and outside passages 5.Logical
Cross the first fluid making different temperatures and second fluid respectively flows through each stream such that it is able to be flowed in double pipe exchanger
Heat exchange between body.
Fig. 2 is the figure in the section of the other direction of the double pipe exchanger representing embodiments of the present invention 1.Fig. 2 represents
A-A ＇ section (the pipe cross section of Fig. 1.Section when cutting off in the pipe circumferential direction from terms of the direction of flow of fluid when).This reality
The structure applying the double pipe exchanger of mode is：It is formed into the heat transfer area enlarged tube having irregular ridge shape shape further
The space segment of 3 insertion outside passages 5.In heat transfer area enlarged tube 3, in recess office, inwall is (in heat transfer area enlarged tube
Wall) contact with outer wall of inner tube, in protuberance office, outer wall (heat transfer area expansion pipe outer wall) is contacted with outer tube wall.And, in pipe
On cross section, the crosscutting outside passages 5 (space between inner tube 2 and outer tube 1) in sidewall slope ground, and from incline direction with inner tube
Wall contacts with outer tube wall.
Therefore, generally, in heat-shift Q, the first fluid of heat transfer area A, pyroconductivity K and heat exchange and second fluid
Between temperature difference dT between, there is the relation as shown in formula (1).
[formula 1]
Q=A K dT ... (1)
And, pyroconductivity K is represented with formula (2).Here, α 1 is the pyroconductivity of first fluid, d1 is inside passages 4
Hydraulic diameter, α 2 is the pyroconductivity of second fluid, and d2 is the hydraulic diameter of outside passages 5.In addition, λ is the conduction of heat of inner tube 2
Rate, dio is the external diameter of inner tube 2, and dii is the internal diameter of inner tube 2, and R is thermal resistance.
[formula 2]
K=π L/ { 1/ (α 1 d1)+1/ (α 2 d2)
+1n(dio/dii)/2λ+R …(2)
Heat transfer area enlarged tube 3 is used as fin and plays a role by being contacted with inner tube 2, can expand the heat transfer of heat exchange
Area, can increase the heat-shift between first fluid and second fluid.
Here, using the part of outer wall of inner tube and heat transfer area enlarged tube contact internal walls as interior side contacts portion 6 (by contact
Length in partial pipe circumferential direction is as L1).In addition, the part of outer tube wall and heat transfer area enlarged tube wall contacts is made
For contact outside portion 7 (using the length in the pipe circumferential direction of the part of contact as L2).In addition, will be in interior side contacts portion 6 with outward
The part (the side wall of concaveconvex shape) playing a role as fin between side joint contact portion 7 is as fin part 16.From expanding by passing
Hot area enlarged tube 3 and from the point of view of this viewpoint of heat transfer area of producing, on pipe cross section, double pipe exchanger is formed as in
Side joint contact portion 6 contacts (point contact) respectively on one point with contact outside portion 7.By reducing contact portion, the such as wing on pipe week
The quantity in piece portion 16, heat transfer area of a fin part 16 etc. can increase, and the overall heat transfer area of double pipe exchanger becomes big.?
Here, with regard to point described below, it is not the point in the mathematical meaning do not have area etc., but has and guarantee between pipe
The area of this degree of reliable contact point.In addition, though illustrate as a contact, but in double pipe exchanger
In entirety, contact portion then becomes wire.
But, with regard to interior side contacts portion 6, the thermal contact resistance if formed as a contact then interior side contacts portion 6 increases.Cause
This, pyroconductivity K in above-mentioned formula (2) declines, and its result is that heat-shift Q declines.In addition, if be formed as a contact then depositing
Probability in the position producing loose contact.When interior side contacts portion 6 is formed as contact, if there is such as inner tube outside
Wall expands, with heat transfer area, the place that inside pipe wall is not in contact with, then generation heat transfer is bad, and a lot of heat transfer areas can not be had
Effect ground utilizes.
Therefore, in the double pipe exchanger of embodiment 1, contact outside portion 7 is formed as a contact (makes length L2 connect
Nearly 0), to expand heat transfer area.In addition, on pipe cross section, interior side contacts portion 6 is formed as with contact length (two-tube
In formula heat exchanger entirety, contact portion forms face).
So, the double pipe exchanger according to embodiment 1, contact outside portion 7 is formed as a contact to expand heat transfer
Area, and interior side contacts portion 6 is formed as with contact length, therefore, it is possible to prevent in outer wall of inner tube and heat transfer area enlarged tube
Loose contact between wall.Therefore, it is possible to not damage heat transfer property, but improve heat transfer property.
Embodiment 2
The double pipe exchanger of above-mentioned embodiment 1 is as shown in Fig. 2 in the outside being formed between outer tube 1 and inner tube 2
There is in stream 5 the heat transfer area enlarged tube 3 of the shape of concavo-convex (ridge shape).Heat transfer area enlarged tube 3 is as in embodiment 1
As illustrating, heat transfer area is expanded inside pipe wall and is contacted with outer wall of inner tube, and heat transfer area is expanded pipe outer wall and connect with outer tube wall
Touch.And, as side wall fin part 16 on pipe cross section crosscutting outside passages 5.
Like this, in order to manufacture the double pipe exchanger making outer tube 1, inner tube 2 contact with heat transfer area enlarged tube 3, be
After heat transfer area enlarged tube 3 is inserted outside passages 5, enter to be about to the operation of inner tube 2 expander, or the work by outer tube 1 draw
Sequence.If here, the part of the fin part 16 as heat transfer area enlarged tube 3 is formed as hang down with respect to outer tube 1 and inner tube 2
Directly, then, when carrying out expander or the draw, the power being applied to the part as interior side contacts portion 6 or contact outside portion 7 directly applies
To fin part 16.Therefore, it is possible to formed with it is not expected that shape and the fin part 16 that bends.Therefore, make as fin
The part out of plumb in portion 16, makes the load being applied to the part as fin part 16 in expander or the draw reduce.And, make wing
Piece portion 16 is contacted with outer wall of inner tube and outer tube wall from incline direction.For example, make contact outside as above-mentioned embodiment 1
In the case that portion 7 becomes contact, as shown in Fig. 2 make outer wall of inner tube and heat transfer area enlarged tube contact internal walls angle [alpha] and
The angle beta that heat transfer area expansion pipe outer wall is contacted with outer tube wall becomes the angle less than 90 °, but this structure is not especially
Limit.
Fig. 3 is the figure of the projection for heat transfer area enlarged tube 3 is described.For example, when carrying out the operations such as expander, the draw,
If applied beyond required pressure it is likely that in heat transfer area enlarged tube 3 in inner tube 2, heat transfer area enlarged tube 3
Side joint contact portion 6 is deformed, and the mid portion that should contact occurs raised.In the event of raised, then exist and for example contact
Thermal resistance increases, the probability of infringement heat transfer property.
Thus, for example, in order to prevent this projection, not only making fin part 16 from incline direction and outer wall of inner tube and outer tube wall
Contact, and for the heat transfer area enlarged tube 3 in the outside passages 5 of insertion double pipe exchanger, make as fin part 16
Partial shape forms arc-shaped on pipe cross section, and described fin part 16 is in the position (recess divides) becoming interior side contacts portion 6
And become between the position (male portion) in contact outside portion 7.By being formed as such shape, carrying out the expander of inner tube 2, outer
During the draw of pipe 1, even if heat transfer area enlarged tube 3 is exceedingly pressed on inner tube 2, the side being bent by area enlarged tube 3
Formula deforms, and the load being applied to heat transfer area enlarged tube 3 opens (buffering).Therefore, in interior side contacts portion 6, in heat transfer area
Excessive power will not be applied in enlarged tube 3, be prevented from projection.Therefore, it is possible to not damage heat transfer property, but improve conductivity of heat
Energy.
Here, the direction bending because of expander or the draw with regard to the part as fin part 16, the fin preferably being formed
Portion 16 becomes the shape protruded towards inner tube 2 side.The shape convex by being formed towards inner tube 2 side, fin part 16 is to inner tube 2 side
Deformation, therefore fin part 16 are increased with the contact portion of inner tube 2, and interior side contacts portion 6 is elongated.Therefore, it is possible to efficiently carry out coming
Heat transfer from inner tube 2.In addition, for example, as shown in Fig. 2 angle [alpha] ＜ angle beta, result from heat transfer area enlarged tube 3 and inner tube 2 it
Between gap diminish.Thus, for example, when carrying out soldering to interior side contacts portion 6, solder is easily accessible.Therefore, it is possible to more increase
Effect ground carries out the heat transfer from inner tube 2.In addition, the degree big with angle beta change is correspondingly, in fin part 16 contact with outer tube 1
Partial pressing force dies down, and can suppress the increase in contact outside portion 7.
Therefore, in the present embodiment, make heat transfer area enlarged tube 3 is shaped as arc-shaped, but is not limited to arc-shaped,
As long as in the shape to a little less place with sweep it becomes possible to play the load of the part as fin part 16
Effect with the projection preventing interior side contacts portion 6.In addition, above explanation is not the double of a contact in such as contact outside portion 7
Similarly set up in pipe heat exchanger, same effect can be played.
Embodiment 3
Fig. 4 is the figure of the double pipe exchanger representing embodiments of the present invention 3.Fig. 4 represents and says in embodiment 1
The same pipe cross section in the A-A ＇ section of clear Fig. 1.In the double pipe exchanger of present embodiment, make L1 ＞ L2, described
L1 is the length that outer wall of inner tube and heat transfer area expand the interior side contacts portion 6 between inside pipe wall, and described L2 is outer tube wall and biography
Hot area expands the length in the contact outside portion 7 between pipe outer wall.
For example, if the relation between L1 and L2 is L1 ＜ L2, apply in outer tube 1, inner tube 2 and heat transfer area enlarged tube 3
During excessive external force, there is a possibility that the end points in interior side contacts portion 6 becomes fulcrum and is deformed.Therefore, as in embodiment party
As illustrating in formula 2, in heat transfer area enlarged tube 3, the mid portion that there is interior side contacts portion 6 is from inner tube 2 projection
The probability of infringement heat transfer property.
Therefore, by making L1 ＞ L2, thus for example as Embodiment 1, even if making in observing tube in applying external force
In the case that during cross section, contact outside portion 7 is had contact length and so that outer tube 1 is in close contact with heat transfer area enlarged tube 3, apply
The power being added in contact outside portion 7 scatter, and is prevented from the deformation of pipe.
In addition, by making L1 ＞ L2, thus applying external force and so that inner tube 2 and heat transfer area enlarged tube 3 is in close contact simultaneously
In the case of so that outer tube 1 is in close contact with heat transfer area enlarged tube 3, it is applied to the external force in interior side contacts portion 6 and is applied to outside
The external force of contact site 7 is roughly the same, and therefore in the case of being applied with excessive external force, contact outside portion 7 first deforms.Therefore,
It is prevented from, for the projection reducing thermal contact resistance most important interior side contacts portion 6, heat transfer property can not being damaged, but improve
Heat transfer property.
Next, inquiring into the shape making L1 ＞ L2 in the double pipe exchanger of the embodiment 3 having the feature that
The condition of parameter.
Fig. 5 has been expressed as the shape analysis of the double pipe exchanger of embodiments of the present invention 3 and the parameter that sets
Figure.As shown in figure 5, using the quantity of the male portion (recess divides) of heat transfer area enlarged tube 3 as n, using inner tube external diameter as dio,
Using outer tube diameter as doi.
In addition, θ 0 is the summit starting from the summit of a male portion of heat transfer area enlarged tube 3 to next male portion
Till angle, θ 1 be as male portion formed benchmark angle, θ 2 is the angle of the benchmark dividing formation as recess.And
And, θ 1 ＇ is θ 1 to be divided into a part and takes the angle (θ 1 ＇=b/a θ 1) of b part therein, and θ 2 ＇ is θ 2 to be divided into a part and takes
The angle (θ 2 ＇=b/a θ 2) of b part therein.Additionally, the length contacting inner tube 2 with heat transfer area enlarged tube 3 is as L1,
The length that outer tube 1 is contacted with heat transfer area enlarged tube 3 is as L2.Here, making the shape of the male portion of heat transfer area enlarged tube 3
The shape divided with recess is entirely same shape.And, from geometric angle, represent θ 0, θ 1, θ 2, θ with formula (3)～(6)
1 ＇, θ 2 ＇.
[formula 3]
θ o=360/n ... (3)
[formula 4]
θ 2+ θ 1=θ o=360/n ... (4)
[formula 5]
θ 1 '=b/a θ 1 ... (5)
[formula 6]
θ 2 '=b/a θ 2 ... (6)
In addition, length L2 in length L1 in interior side contacts portion 6 and contact outside portion 7 is able to be come with formula (7), formula (8)
Represent.
[formula 7]
L1=π 2dio (θ 2 '/360) ... (7)
[formula 8]
L2=π 2doi (θ 1 '/360) ... (8)
According to formula (3)～(8), the condition of L1 ＞ L2 can be represented with formula (9).
[formula 9]
θ 1 ＞ (360/n) { doi/ (dio+doi) } ... (9)
As described above, according to the double pipe exchanger of embodiment 3, the relation due to making L1 and L2 becomes L1 ＞ L2, because
This can make to be applied to the external force dispersion in contact outside portion 7, and described L1 is outer wall of inner tube and heat transfer area expands between inside pipe wall
Interior side contacts portion 6 length, described L2 is the length in the contact outside portion 7 that outer tube wall and heat transfer area expand between pipe outer wall
Degree.Further, since the external force being applied to interior side contacts portion 6 is roughly the same with the external force being applied to contact outside portion 7, therefore excessively
External force will not be only applied to interior side contacts portion 6, but scatter such that it is able to prevent the projection in interior side contacts portion 6.According to
Upper reason, is prevented from the excessive deformation of each pipe.
Embodiment 4
Above-mentioned embodiment 1～3 is not particularly shown, but in order that outer wall of inner tube and heat transfer area enlarged tube
Contact between contact between inwall and outer tube wall and heat transfer area expansion pipe outer wall is more reliable, preferably contacts at each
Part carries out the soldering using solder 15.
Fig. 6 is the figure of the brazed portion representing embodiments of the present invention 4.For example, by inner tube 2, outer tube 1 and heat-transfer area
After long-pending enlarged tube 3 assembling, solder 15 is coated, carries out furnace brazing etc. to make solder 15 melt, and contact site is entered
Row soldering.For example, in the case that pipe is aluminum etc., using the Al-Si system containing silicon (aluminum-silicon systems) alloy in aluminum as solder
15.
Here, it is also possible to solder 15 covering (covering) will be used in advance in the case of being difficult to after assembling be coated with solder 15
Clad material is used for heat transfer area enlarged tube 3.
Embodiment 5
In embodiment 5, to the kind of refrigeration cycle employing the double pipe exchanger illustrating in embodiment 1～4
The example of device illustrates.Here, illustrating to the structure of four kinds of refrigerating circulatory devices.
Fig. 7 is the figure of of the structure of the refrigerating circulatory device representing embodiment 5.Follow in the refrigeration of present embodiment
In loop device, compressor 8, condenser 9, expansion valve 10, vaporizer 11 and double pipe exchanger 12 are connected with pipe arrangement to constitute
Refrigerant loop.
Cold-producing medium is sucked by compressor 8, is collapsed into the state of High Temperature High Pressure and discharges.Here, for example can use as follows
The compressor of type is constituting：Described compressor controls rotating speed by frequency changer circuit etc., and can adjust the output of cold-producing medium.Make
For heat exchanger condenser 9 for example from aerator (not shown) be supplied to come air and cold-producing medium between carry out heat exchange,
Cold-producing medium is made to condense the cold-producing medium (condensation liquefaction) becoming liquid.
In addition, expansion valve (air relief valve, throttling arrangement) 10 makes cold-producing medium reduce pressure and expands.By such as electronic expansion valve etc.
Flow control mechanism is constituting it is also possible to by for example having the cold-producing medium streams such as expansion valve, the capillary tube (capillary) of temperature-sensing pipe
Measure governor motion etc. to constitute.Vaporizer 11 makes cold-producing medium evaporate by the heat exchange between air etc. becomes gas (gas)
The cold-producing medium (evaporation gasification) of shape.
In addition, the double pipe exchanger 12 of the refrigerating circulatory device of Fig. 7 (a) carries out the High Temperature High Pressure flowing out from condenser 9
Cold-producing medium and from vaporizer 11 flow out low-temp low-pressure cold-producing medium between heat exchange.By according to so utilizing double hose
Heat exchanger 12 is such that it is able to improve the temperature of the cold-producing medium in condenser 9.Therefore, it is possible to improve heating capacity when heating, can
Improve COP (removing the value of heating capacity gained with input power).In addition, the refrigerant vapor that can will flow out from vaporizer 11, because
This is prevented from liquid refrigerant and returns to compressor 8.
The double pipe exchanger 12 of the refrigerating circulatory device of Fig. 7 (b) carries out the high pressure liquid of the refrigerant outflow port of condenser 9
Heat exchange between cryogen and the middle pressure two-phase system cryogen having passed through flow adjustment man's cap used in ancient times 13.And, make to carry out heat exchange simultaneously
The cold-producing medium becoming medium pressure gas cold-producing medium flows to the suction side line of compressor 8 from bypass.
Like this in the refrigerating circulatory device of Fig. 7 (b), make to have passed through the cold-producing medium of condenser 9 by expansion valve 10
Before branch and using double pipe exchanger 12 from bypass circulation, thereby, it is possible to reduce from expansion valve 10 downstream side flowing
Refrigerant amount.Therefore, it is possible to reduce the pressure loss, it is possible to increase COP.
The double pipe exchanger 12 of the refrigerating circulatory device of Fig. 7 (c) carries out the high pressure liquid of the refrigerant outflow port of condenser 9
Heat exchange between cryogen and the middle pressure two-phase system cryogen having passed through flow adjustment man's cap used in ancient times 13.And, make to carry out heat exchange simultaneously
The cold-producing medium becoming medium pressure gas cold-producing medium flows into the compression unit mid portion that (injection) arrives compressor 8.Here, the system of Fig. 7 (c)
The compressor 8 of SAPMAC method device is the compressor of the multilevel hierarchy that can be sprayed.
Like this in the refrigerating circulatory device of Fig. 7 (c), make to have passed through the cold-producing medium of condenser 9 by expansion valve 10
Branch before, using double pipe exchanger 12 from bypass circulation, thereby, it is possible to reduce the system from expansion valve 10 downstream side flowing
Cryogen amount.Further, since can be to the compression unit mid portion injection of the compressor 8 of multilevel hierarchy, therefore, it is possible to reduce compression
Discharge temperature of machine etc. and input power, it is possible to increase COP.
In the refrigerating circulatory device of Fig. 7 (d), double pipe exchanger 12 is used as condenser.And, as with
In refrigerant loop, the fluid of the object that the cold-producing medium of flowing carries out heat exchange is that water, refrigerating medium etc. (below, are carried out taking water as a example
Illustrate).
In Fig. 7 (d), pump 14 forms current and sends into double pipe exchanger 12.In double pipe exchanger 12, water passes through
Heat exchange and cold-producing medium between and be heated.Here, double pipe exchanger 12 to be used but it is also possible to make as condenser
To use for vaporizer.
The explanation of reference
1 outer tube
2 inner tubes
3 heat transfer area enlarged tube
4 inside passages
5 outside passages
6 interior side contacts portions
7 contact outside portions
8 compressors
9 condensers
10 expansion valves
11 vaporizers
12 double pipe exchanger
13 flow adjustment man's caps used in ancient times
14 pumps
15 solders
16 fin part
Claims (8)
1. a kind of double pipe exchanger is it is characterised in that have：
Inner tube, first fluid passes through in the inside of said inner tube；
Outer tube, described outer tube covers said inner tube with the diameter bigger than said inner tube, and second fluid passes through described outer tube and institute
State the space between inner tube；And
Heat transfer area enlarged tube, described heat transfer area enlarged tube is arranged in described space, on pipe cross section, interior side contacts portion
Pipe circumferential direction on length longer than the length in the pipe circumferential direction in contact outside portion, described interior side contacts portion is described heat-transfer area
Long-pending enlarged tube and the contact portion of said inner tube outer wall, described contact outside portion is described heat transfer area enlarged tube and described outer tube
The contact portion of inwall, and, described heat transfer area enlarged tube on described pipe cross section crosscutting described space positioned at described
Fin part between interior side contacts portion and described contact outside portion is with respect to said inner tube outer wall and described outer tube wall from inclination
Direction contacts, and described heat transfer area enlarged tube has convex-concave profile,
Described fin part is the curved shape protruding to said inner tube side on described pipe cross section, at described interior side contacts portion
Described heat transfer area enlarged tube and said inner tube outer wall angulation, expand than the described heat transfer area at described contact outside portion
Big pipe is little with described outer tube wall angulation.
2. double pipe exchanger as claimed in claim 1 is it is characterised in that described fin part has circular arc on pipe cross section
Shape.
3. double pipe exchanger as claimed in claim 1 or 2 is it is characterised in that described contact outside portion is with pipe cross section
On become the mode of contact and contact, described interior side contacts portion is contacted in the way of becoming linear contact lay on pipe cross section.
4. double pipe exchanger as claimed in claim 1 or 2 is it is characterised in that by the both ends in described contact outside portion
With the center angulation of said inner tube and outer tube as θ 1, using the external diameter of inner tube as dio, using the internal diameter of outer tube as
Doi, using the quantity of the convex form of described heat transfer area enlarged tube or concave shape as n, and described convex form and described concave shape
In the case of being entirely same shape,
To meet θ 1<(360/n) mode of { doi/ (dio+doi) }, forms described heat transfer area enlarged tube.
5. double pipe exchanger as claimed in claim 1 or 2 is it is characterised in that to described contact outside portion and described inner side
Contact site carries out soldering.
6. double pipe exchanger as claimed in claim 5 is it is characterised in that with covering clad material shape on surface by solder
Become described heat transfer area enlarged tube.
7. a kind of refrigerating circulatory device is it is characterised in that use the double hose heat exchange as any one of claim 1～6
Device, and heat exchange is carried out to two kinds of cold-producing mediums.
8. refrigerating circulatory device as claimed in claim 7 is it is characterised in that the described cold-producing medium of at least one party is water or refrigerating
Agent.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2012/075530 | 2012-10-02 | ||
| PCT/JP2012/075530 WO2014054117A1 (en) | 2012-10-02 | 2012-10-02 | Double-tube heat exchanger and refrigerating cycle device |
| PCT/JP2013/073688 WO2014054370A1 (en) | 2012-10-02 | 2013-09-03 | Double-tube heat exchanger and refrigerating cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104704311A CN104704311A (en) | 2015-06-10 |
| CN104704311B true CN104704311B (en) | 2017-03-01 |
Family
ID=50434478
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380051921.4A Active CN104704311B (en) | 2012-10-02 | 2013-09-03 | Double pipe exchanger and refrigerating circulatory device |
| CN201320613402.XU Expired - Lifetime CN203605763U (en) | 2012-10-02 | 2013-09-30 | Double-layer tubular heat exchanger and refrigeration circulating device |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320613402.XU Expired - Lifetime CN203605763U (en) | 2012-10-02 | 2013-09-30 | Double-layer tubular heat exchanger and refrigeration circulating device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150241132A1 (en) |
| EP (1) | EP2916091B1 (en) |
| JP (1) | JP5944009B2 (en) |
| CN (2) | CN104704311B (en) |
| WO (2) | WO2014054117A1 (en) |
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|---|---|---|---|---|
| JP6436529B2 (en) * | 2014-11-18 | 2018-12-12 | 株式会社アタゴ製作所 | Heat exchanger |
| DE112016002290T5 (en) * | 2015-05-21 | 2018-03-01 | Ngk Insulators, Ltd. | Heat exchange component |
| CN107636404B (en) * | 2015-07-03 | 2020-03-27 | 三菱电机株式会社 | Heat pump device |
| CN106032860A (en) * | 2015-09-02 | 2016-10-19 | 天津友大金属结构制造有限公司 | Heat exchange tube for remote transportation |
| JP6471867B2 (en) * | 2015-10-06 | 2019-02-20 | スズキ株式会社 | Waste heat recovery device |
| CN105843347B (en) * | 2016-04-22 | 2017-03-29 | 南京佳力图机房环境技术股份有限公司 | Bidirectional flow heat exchanger based on vibration induction |
| WO2018089130A1 (en) * | 2016-11-11 | 2018-05-17 | Stulz Air Technology Systems, Inc. | Dual mass cooling precision system |
| CN107166995A (en) * | 2017-06-17 | 2017-09-15 | 福建德兴节能科技有限公司 | High-performance heat exchanger and application thereof |
| JP6844791B2 (en) * | 2018-11-21 | 2021-03-17 | 株式会社ニチリン | Manufacturing method of double tube heat exchanger |
| CN109848499B (en) * | 2019-03-08 | 2021-05-14 | 西安远航真空钎焊技术有限公司 | Preparation method of complex heat exchanger core |
| JP7169923B2 (en) * | 2019-03-27 | 2022-11-11 | 日本碍子株式会社 | Heat exchanger |
| CN111750705B (en) * | 2019-03-28 | 2022-04-29 | 日本碍子株式会社 | Flow path structure of heat exchanger and heat exchanger |
| US11378307B2 (en) * | 2019-08-09 | 2022-07-05 | Enerpro | Hybrid condensing boiler with preheater |
| CA3170432A1 (en) * | 2020-03-03 | 2021-09-10 | Daikin Applied Americas, Inc. | System and method for manufacturing and operating a coaxial tube heat exchanger |
| CN113081255A (en) * | 2021-04-30 | 2021-07-09 | 杭州佳量医疗科技有限公司 | Cooling sleeve and optical fiber conduit with same |
| CN114471439A (en) * | 2022-02-28 | 2022-05-13 | 茂名重力石化装备股份公司 | Series pipe reactor with static fit jacket |
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- 2013-09-03 JP JP2014539645A patent/JP5944009B2/en active Active
- 2013-09-03 EP EP13843545.8A patent/EP2916091B1/en active Active
- 2013-09-03 CN CN201380051921.4A patent/CN104704311B/en active Active
- 2013-09-03 WO PCT/JP2013/073688 patent/WO2014054370A1/en active Application Filing
- 2013-09-30 CN CN201320613402.XU patent/CN203605763U/en not_active Expired - Lifetime
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| US2692763A (en) * | 1952-03-08 | 1954-10-26 | Air Preheater | Supporting spacer for annular corrugated fins |
| US2756032A (en) * | 1952-11-17 | 1956-07-24 | Heater | |
| JPH045901Y2 (en) * | 1986-06-10 | 1992-02-19 | ||
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Also Published As
| Publication number | Publication date |
|---|---|
| JP5944009B2 (en) | 2016-07-05 |
| JPWO2014054370A1 (en) | 2016-08-25 |
| CN203605763U (en) | 2014-05-21 |
| EP2916091A4 (en) | 2016-08-10 |
| CN104704311A (en) | 2015-06-10 |
| EP2916091B1 (en) | 2019-10-23 |
| US20150241132A1 (en) | 2015-08-27 |
| EP2916091A1 (en) | 2015-09-09 |
| WO2014054370A1 (en) | 2014-04-10 |
| WO2014054117A1 (en) | 2014-04-10 |
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