CN107532870B

CN107532870B - Heat exchanger and the refrigerating circulatory device for using it

Info

Publication number: CN107532870B
Application number: CN201680023056.6A
Authority: CN
Inventors: 小石原一贵; 町田和彦; 山冈由树; 青柳治
Original assignee: Panasonic Intellectual Property Management Co Ltd
Current assignee: Panasonic Intellectual Property Management Co Ltd
Priority date: 2015-04-28
Filing date: 2016-04-05
Publication date: 2019-08-30
Anticipated expiration: 2036-04-05
Also published as: EP3290854B1; WO2016174826A1; JPWO2016174826A1; CN107532870A; EP3290854A1; EP3290854A4; JP6687022B2

Abstract

Refrigerating circulatory device of the invention includes refrigerant circuit made of compressor, heat exchanger, decompressor and evaporator loop connecting at least；And control device, there is the defrosting operation mode for the frost melts for making evaporator, heat exchanger includes inner tube, the circulating water in inner tube；The insertion body being inserted into inner tube；With the outer tube for the periphery that inner tube is arranged in, refrigerant is flowed in outer tube, insertion body has axle portion and is formed in the twist tabs of the outer surface of axle portion, water flows in the helical flow path formed by the inner surface of inner tube, axle portion and twist tabs, the type of flow of refrigerant and water is opposite stream, and insertion body is made of resin.According to this structure, a kind of compact and good economy performance, quality parameter and the high heat exchanger of heat exchange performance and the refrigerating circulatory device with it are capable of providing.

Description

Heat exchanger and the refrigerating circulatory device for using it

Technical field

The present invention relates to the heat exchangers that heat exchange is carried out between fluid.

Background technique

In the prior art, as this heat exchanger, motion, which has, winds water pipe and the cohelix shape of refrigerant pipe Heat exchanger (referring for example to patent document 1).In addition, motion have on water pipe wind refrigerant pipe heat exchanger (such as Patent document 2).

It is mounted with the Teat pump boiler of this heat exchanger, the dress to boil water is mainly taken some time at night It sets, when heating operating, the flow velocity for flowing through the water of heat exchanger possessed by the water heater is smaller.

Therefore, the water flow for flowing through heat exchanger is laminar flow, so in order to improve the heat transfer property as heat exchanger, it is necessary to Water flow is confused to improve the heat transfer property in terms of water.

Figure 11 is the synoptic diagram (partial cross-sectional view) for the existing heat exchanger recorded in patent document 1.Figure 12 is to indicate The enlarged drawing in the section of the heat exchanger of Figure 11.

Heat exchanger 201 includes: water pipe 202；With 1 or more refrigerant pipe being arranged relative to 1 water pipe 202 203.Water pipe 202 is shaped generally as cylindrical shape by screw winding.Refrigerant pipe 203 is in the water for being shaped generally as cylindrical shape The periphery of pipe 202 screw winding at a specific interval.Moreover, more than at refrigerant pipe 203 at least one substantially throughout water pipe 202 Overall length engagement.The flow direction for flowing through the water of water pipe 202 is the flowing side with the refrigerant for the inside for flowing through refrigerant pipe 203 In the opposite direction.

By 202 spirally winding of water pipe as described above, centrifugal force works to the water for flowing through water pipe, vertical with pipe axis Section in generate the Secondary Flow as the arrow that Figure 12 is recorded.Here, to the water for flowing through helical flow path work from The size of mental and physical efforts can be indicated according to the interaction of power with following formula (1).

In formula (1), F indicates that centrifugal force, M (M=V × ρ) indicate quality, and V indicates volume, and ρ indicates density, and v indicates rotation Speed, r indicate radius of turn.

According to formula (1) it is found that big centrifugal force works the big fluid of temperature low-density, and towards spiral The outside of shape flow path.Therefore, the temperature difference of the water on heat-transfer area and refrigerant expands, and heat transfer is promoted.

Therefore, the temperature field in the section with mainstream vertical can be improved because of Secondary Flow water flow is laminar flow, so With by water pipe and refrigerant pipe engagement made of straight tube-like heat exchanger compared with can greatly improve heat transfer property.

Figure 13 is the skeleton diagram for the existing heat exchanger recorded in patent document 2.

Heat exchanger 301 includes: the water pipe 302 with straight line portion；Be arranged relative to 1 water pipe 302 1 or more Refrigerant pipe 303.Refrigerant pipe 303 is on water pipe 302, in the inside of water pipe 302 as heat transfer promotion mechanism insertion There is torsional band.

Like this, rotating flow is generated by being inserted into torsional band in water pipe, the flowing in terms of water is confused, to improve biography Hot property.

But in the structure of above patent document 1, due to being to be helically wound pipe to form heat exchanger, institute According to the material of pipe and caliber, wall thickness, it is possible to which water pipe becomes flat or bends.

Accordingly, it is considered to need to increase spiral shell in order not to occur to bend to the flat caused thinning wall thickness for needing to increase water pipe The curvature diameter D of coil.This leads to cost increase, and will increase the volume of heat exchanger.Moreover, having caused by centrifugal force The problem of heat transfer facilitation effect of Secondary Flow becomes smaller.

In addition, if the winding spacing of pipe is obtained it is larger if can reduce the risk of press-bending, but dead space can be become More interminable heat exchanger, it may have the problem of volume of heat exchanger unnecessarily becomes larger.

In addition, being improved near heat-transfer area in the structure of above patent document 2 with the rotating flow generated by torsional band Temperature Distribution, but the improvement of the Temperature Distribution on the central axis of farthest water pipe with a distance from heat-transfer area than heat-transfer area near It is small.

That is, will form heat transfer on the central axis of water pipe contributes small dead water region.In addition, if in order to reduce slough Domain and the caliber for reducing water pipe, then hydraulic pressure damage can become excessive, and the power of water delivery pump becomes larger.Have as a result, and is mounted with hot friendship The problem of day-to-day running costs of the equipment of parallel operation increase.

Existing technical literature

Patent document

Patent document 1: No. 4805179 bulletins of Japanese Patent Publication No.

Patent document 2: No. 4501446 bulletins of Japanese Patent Publication No.

Summary of the invention

The present invention solves above-mentioned problem of the prior art and completes, and its purpose is to provide a kind of compact and economy It gets well, the heat exchanger that quality parameter and heat exchange performance are high.

In order to achieve the above objectives, heat exchanger of the invention includes: inner tube, flows first fluid in the inner tube；It inserts Enter the insertion body into inner tube；With the outer tube for the periphery that inner tube is arranged in, second fluid is flowed in the outer tube.Insertion body includes The twist tabs of axle portion and the outer surface for being formed in axle portion.First fluid is by the inner surface of inner tube, axle portion and helical form It is flowed in the helical flow path that protruding portion is formed.

The helical flow path that first fluid is flowed as a result, can be by inner tube and with the insertion body of twist tabs Both parts are formed, so the formation of flow path does not need to wind inner tube.Therefore, inner tube press-bending or flat will not be made, it can The wall thickness of pipe is made into necessary minimum limit, so as to provide good economy performance light weight heat exchanger.

In addition, the curvature diameter of helical flow path can be set to it is smaller than the prior art, so being capable of providing Secondary Flow The big and compact heat exchanger of bring heat transfer facilitation effect.

Moreover, longest distance of the first fluid from heat-transfer area, by the diameter of axle of insertion body and the protruding portion of twist tabs Height determines.As a result, flow path cross sectional area can by change twist tabs spacing become water delivery pump can The hydraulic pressure of permission damages.Therefore, it is capable of providing the heat exchange performance that dead water region is greatly reduced within the scope of the limitation of hydraulic pressure damage High heat exchanger.

In accordance with the invention it is possible to provide a kind of compact and good economy performance, quality parameter and the high heat exchange of heat exchange performance Device.

Detailed description of the invention

Fig. 1 is the skeleton diagram of the heat exchanger of embodiments of the present invention 1.

Fig. 2A is the perspective view for indicating the flowing of the fluid of the outer tube of heat exchanger of embodiments of the present invention 1.

Fig. 2 B is the perspective view for indicating the flowing of the fluid of inner tube of the heat exchanger.

Fig. 3 is the enlarged drawing in the portion A of Fig. 1.

Fig. 4 is the figure for indicating the calculated result of the heet transfer rate in the helical form round tube.

Fig. 5 A is the outside drawing of the insertion body of the heat exchanger of embodiments of the present invention 2.

Fig. 5 B is the enlarged drawing in the portion B of Fig. 5 A.

Fig. 6 A is the sectional view of the heat exchanger of embodiments of the present invention 2.

Fig. 6 B is the portion the C enlarged drawing of Fig. 6 A.

Fig. 7 is the connector of the heat exchanger of embodiments of the present invention 2 and the perspective view of insertion body.

Fig. 8 makes the detailed sectional view of the heat exchanger of embodiments of the present invention 3.

Fig. 9 is the figure for indicating the relationship of the insertion body nose width and heat-exchange capacity.

Figure 10 is the schematic structural diagram of the refrigerating circulatory device of embodiments of the present invention 4.

Figure 11 is the skeleton diagram of existing heat exchanger.

Figure 12 is the enlarged drawing for indicating the section of heat exchanger of Figure 11.

Figure 13 is the skeleton diagram of existing another heat exchanger.

Specific embodiment

The heat exchanger of first invention includes: inner tube, flows first fluid in the inner tube；The insertion being inserted into inner tube Body；With the outer tube for the periphery that inner tube is arranged in, second fluid is flowed in the outer tube.Insertion body includes axle portion and is formed in axle portion Outer surface twist tabs.First fluid is in the spiral formed by the inner surface of inner tube, axle portion and twist tabs It is flowed in shape flow path.

The helical flow path that first fluid is flowed as a result, can be by inner tube and with the insertion body of twist tabs Both parts are formed, so will not make inner tube press-bending or flat, are capable of providing the wall thickness of pipe being made into necessary minimum limit Good economy performance and light weight heat exchanger.

Moreover, longest distance of the first fluid from heat-transfer area, by the diameter of axle of insertion body and the protruding portion of twist tabs Height determines therefore the hydraulic pressure damage that flow path cross sectional area can be designed to water delivery pump and can allow for is capable of providing and damages in hydraulic pressure Limitation within the scope of greatly reduce the heat exchange performance heat exchanger higher than the prior art of dead water region.

Especially in first invention, the coiling direction of outer tube is phase with the hand of spiral of twist tabs for second invention It is equidirectional, also, the type of flow of first fluid and second fluid is opposite stream.

First fluid and second fluid can carry out heat exchange with opposite flowing as a result, so being capable of providing heat exchange The high heat exchanger of energy.

Especially in first or second invention, outer tube is configured in the periphery of inner tube and the phase of helical flow path for third invention To portion.

It is able to carry out heat exchange in the substantially the entire area of heat exchanger, first fluid and second fluid as a result, so energy The higher heat exchanger of heat exchange performance is enough provided.

4th invention is especially in any invention in the invention of first~third, is had and is fixed inner tube, insertion body respectively Connector.

No matter state (longitudinal, horizontal, tilting) is arranged as a result, the insertion with twist tabs in inner tube The allocation position of body is fixed, so being capable of providing the heat exchanger that setting freedom degree improves.

Especially in any invention in the first~the 4th invention, twist tabs have to be connect with inner tube for 5th invention Multiple protrusions of touching, multiple protrusions arrange continuously in axial direction.

In the twist tabs other than protrusion and gap is generated between inner tube as a result, in addition to helical flow path, It is also formed with the flow path being axially connected to along heat exchanger.As a result, flowing can be stirred using Secondary Flow, and And increase the bypass amount for flowing through the first fluid in the gap in the big big flow of the centrifugal force for acting on first fluid.

Therefore, it is able to suppress the increase of the pressure loss in heat exchanger in big flow, conveys first fluid Delivery pump needed for power tail off, so the energy saving of equipment improves.

In addition, needing to increase the flow of first fluid so that first in the case where the inflow temperature of first fluid is high The outflow temperature of fluid will not be got higher extremely.In accordance with the invention it is possible to increase the flow that can be conveyed with the pump of same lift, institute Can ensure first fluid flowing out temperature limiting in the flow of defined temperature abundance below, the reliability of equipment is mentioned It is high.

6th invention is especially in any invention in the first~the 5th invention, when the nose width of twist tabs Meet the relationship of t1 < t2 when root width is t2 for t1.

Thereby, it is possible to expand first fluid that the helical flow path formed between inner tube and insertion body 2 is flowed to outside The heat transfer area that the second fluid of the internal flow of pipe is gone, so being capable of providing the high heat exchanger of heat exchange performance.

7th invention is a kind of refrigerating circulatory device comprising: at least by any in compressor, the first~the 6th invention Refrigerant circuit made of the heat exchanger of invention, decompressor and evaporator loop connecting；And control device, the refrigeration are followed Loop device has the defrosting operation mode for the frost melts for making evaporator, and insertion body is resin system.

By forming a part of the flow path of first fluid with the big resin of specific heat ratio metal, the amount of stored heat of heat exchanger Increase, more heats can be utilized from heat exchanger in defrosting.Therefore, defrosting operating can be terminated in the short time, improved The defrosting performance of equipment.

In the following, being described with reference to embodiments of the present invention.In addition, the present invention is not limited to these embodiments.

(embodiment 1)

Fig. 1 is the skeleton diagram (partial cross-sectional view) of the heat exchanger 11 of embodiments of the present invention 1.

The heat exchanger 11 of embodiments of the present invention 1 includes: inner tube 1；It is in a manner of being close to the outer surface of inner tube 1 The outer tube 3 of spirally winding；With the insertion body 2 for the inside for being inserted into inner tube 1.Insertion body 2 is by insertion body axle portion 21 and helical form Protruding portion 22 is constituted.

Moreover, the hand of spiral of the spiral helicine coiling direction of outer tube 3 and twist tabs 22 is the same direction, separately Outside, winding spacing is also identical.

For heat exchanger as constructed as above, it is acted be illustrated below.

Heat exchanger 11 is the water as first fluid and the carbon dioxide as second fluid via inner tube 1 and outer tube 3 Carry out the structure of heat exchange.

In heat exchanger 11, the flow path of water flowing is by the inner surface of inner tube 1, the outer surface of insertion body axle portion 21 and phase The helical flow path that adjacent twist tabs 22 are formed, by inner tube 1 and the 2 both parts shape of insertion body for being inserted into inner tube 1 At.

Therefore, there is no need to carry out bending process to form the water flow road, thus inner tube 1 will not become bend, it is flat, The wall thickness of inner tube 1 can be made into the minimum wall thickness (MINI W.) based on design philosophy (in view of wall thickness+etching extent of pressure resistance).As a result, can The heat exchanger of the light weight of good economy performance is enough provided.

Then, the heet transfer rate in the curvature diameter D and pipe of helical flow path is illustrated.

About the heet transfer rate in the region extended in the round tube bent as helix tube, in Japanese mechanical society heat transfer work It learns as follows in data modification the 5th edition.

Herein, Nu indicates that nusselt number, Pr indicate that Prandtl number, Re indicate Reynolds number.Moreover, D is helical flow path The curvature diameter of central axis, d are the equivalent diameters of pipe.Fig. 4 indicates to calculate reynolds number Re=2000, water temperature 40 with above-mentioned formula (3) Nusselt number Nu when changing (d/D) under conditions of DEG C.The longitudinal axis indicates that nusselt number Nu, horizontal axis indicate d/D.

According to above-mentioned formula (2), formula (3) and Fig. 4 it is found that under same Reynolds number, same Prandtl number, the equivalent diameter of pipe D is bigger or curvature diameter D is smaller, and the nusselt number in round tube is bigger.

That is, the heet transfer rate in pipe is got higher, so the heat transfer property of heat exchanger improves.It is filled in existing Teat pump boiler (d/D) of the heat exchanger similar with patent document 1 carried is 0.2 or less.In contrast, heat exchanger 11 of the invention Helical flow path is constituted with two components, so the curvature diameter D of the helical flow path of water flowing can be made bigger than the prior art Width reduces.Therefore, (d/D) becomes larger, and Secondary Flow bring mixing effect increases.Thereby, it is possible to provide heat transfer facilitation effect to improve And compact heat exchanger.

Fig. 2A and Fig. 2 B be indicate to flow through 11 fluid of the heat exchanger of embodiments of the present invention 1 flowing it is vertical Body figure.

Outer surface and adjacent spiral as the water of first fluid, in inner surface, insertion body axle portion 21 by inner tube 1 It is flowed in the helical flow path that shape protruding portion 22 is formed.The twist tabs 22 and coiling direction of insertion body 2, its spacing are same Step, carbon dioxide and work as the second fluid flowed in the inside for the outer tube 3 that the opposing part of helical flow path is wound Heat exchange is carried out for the water of first fluid.

Here, flowing water and the internal flow in outer tube 3 in helical flow path between inner tube 1 and insertion body 2 Carbon dioxide, flow direction are opposite, so as shown in Figure 2 A and 2 B, it can be throughout the substantially entire of heat exchanger 11 Region carries out heat exchange with opposite flowing, is capable of providing efficient heat exchanger.

Furthermore it is possible to be not winding outer tube 3 all sites all on the opposing part of helical flow path, if The equipment for loading it can be realized the range of heat exchanger effectiveness.In addition, the outer tube 3 with more for second fluid flowing, It is alternately wound around on the opposing part of helical flow path.

Fig. 3 is the sectional view of the heat exchanger 11 of embodiments of the present invention 1.The water flow of heat exchanger routes 1 He of inner tube 2 two components of insertion body are constituted, so the longest distance from water side heat-transfer area, can according to the diameter a of insertion body axle portion 21 and The protruding portion height th of twist tabs 22 is designed.

In addition, flow path cross sectional area S can be designed by the winding spacing P of the twist tabs 22 of change insertion body 2, To become the hydraulic pressure damage that conveys the water delivery pump of water in equipment and can allow for.Thereby, it is possible to damage to restrict in range substantially in hydraulic pressure Reduce dead water region.Here, the diameter a of the insertion body axle portion 21 and protruding portion height th of twist tabs 22, preferred design At in the range of following formula (4), heat exchange performance meets defined performance.

In addition, the flowing path section of the helical flow path as water flow road is formed as by interior in embodiments of the present invention 1 The rectangular section that inner surface, insertion body axle portion 21 and the twist tabs 22 of pipe 1 are formed is round situation phase with section Than being more prone to produce whirlpool, the effect of Secondary Flow becomes larger.

As described above, in present embodiment 1, by with inner tube 1 and the insertion body 2 with twist tabs 22 this two A component constitutes water flow road, is capable of forming spiral flow path without winding inner tube 1.Thereby, it is possible to provide the wall thickness for making inner tube 1 Necessary minimal light weight and the outstanding heat exchanger of economy.

In addition, can substantially reduce the curvature diameter D of helical flow path compared with prior art, thus be capable of providing it is compact and The high heat exchanger of heat transfer property.

Moreover, the longest distance of the heat-transfer area from water effluent road, it can be prominent with the diameter a and helical form of insertion body axle portion 21 The height th of the protruding portion in portion 22 is designed out, and flow path cross sectional area S can pass through the winding spacing of change twist tabs 22 P is in limitation to be designed so that hydraulic pressure damages.Thereby, it is possible to provide to greatly reduce stagnant water within the scope of the limitation of hydraulic pressure damage The high heat exchanger of the heat transfer property in region.

(embodiment 2)

Fig. 5 A and Fig. 5 B are the enlarged drawings of the twist tabs 22 of the insertion body 2 of the heat exchanger 11 of present embodiment 2. Fig. 6 A and Fig. 6 B are the sectional views of the heat exchanger of the embodiment.Fig. 7 is the connector of the heat exchanger of the embodiment and inserts Enter the perspective view of body.

Wherein, identical appended drawing reference is marked to component identical with embodiments of the present invention 1, omitted the description.

As shown in Figure 5 B, in the outer of the twist tabs 22 of the insertion body 2 for the heat exchanger 11 for constituting present embodiment 2 Surface is provided with continuously arranged protrusion 25 along the axial direction of the axial direction of heat exchanger 11, i.e. insertion body 2.In addition, as shown in fig. 7, The axial end of insertion body 2 is protrusion 23, and connector 4 has the recess portion 24 chimeric with the protrusion 23 of the end of insertion body 2.

Insertion body 2 is chimeric with the recess portion 24 of connector 4 by the protrusion 23 of the axial end of insertion body 2, twist tabs The protrusion 25 of 22 outer surface is fixed in a manner of contacting with inner tube 1.

In addition, the shape about insertion body 2 and the fitting portion of connector 4, is protrusion and recess portion in present embodiment 2, but It is also possible to other arbitrary shapes that can be fitted into.

For heat exchanger as constructed as above, it is acted be illustrated below.

In present embodiment, gap is generated between the twist tabs 22 in addition to protrusion 25 and inner tube 1, so removing The helical flow path recorded in embodiment 1 is also formed with the axial connection of the axial direction along heat exchanger 11, i.e. insertion body 2 Flow path (bypass flow path 50).

The heat exchanger 11 of present embodiment 2 is also same as embodiment 1, is being formed between inner tube 1 and insertion body 2 Helical flow path flowing the water as first fluid, the titanium dioxide with the internal flow in outer tube 3 as second fluid Carbon carries out heat exchange via inner tube 1 and outer tube 3 with opposite flowing.

Here, the water being heated is in heat exchanger 11 in the case where the inflow coolant-temperature gage for being flowed into heat exchanger 11 is high It is inside possible to boil, so increasing the flow for being transported to the water of heat exchanger 11, hot water temperature will be flowed out and be adjusted to defined Below temperature.

But the existing heat exchanger recorded in above patent document 1, it is to make pipe winding to form helical form stream Road, so flow path length is longer compared with flow path on straight line.Therefore, the hydraulic pressure damage of heat exchanger becomes larger when big flow, so depositing Become energy saving such problems that is excessive and damaging equipment in the pump power of the equipment of conveying water.

In addition, hot water temperature can not will be flowed out in the case where the hydraulic pressure of heat exchanger 11 damage is more than the conveying capacity of pump Temperature as defined in being limited in is hereinafter, in the presence of the reliability such problems for damaging equipment.

On the other hand, the heat exchanger 11 of present embodiment 2, on the basis of helical flow path, as shown in fig. 6, removing Have between the inner surface and twist tabs 22 of inner tube 1 except inner tube 1 and protrusion 25 axial direction along heat exchanger 11, That is the bypass flow path 50 of insertion body 2 being axially connected to.

Therefore, simultaneously, increasing the big flow Shi Re big in the centrifugal force for acting on water using Secondary Flow stirring water flow The bypass amount of flowing water in the coconnected flow path of axial direction of axial direction, that is, insertion body 2 of exchanger 11.

Therefore, compared to the existing heat exchanger recorded in above patent document 1, it is able to suppress pressure damage when big flow The increase of mistake, power needed for delivery pump tails off, so the energy saving of equipment improves.

In addition, being able to suppress the increase of hydraulic pressure damage, increase the flow that the pump of same lift can convey, so can be true It protects the flow for going out hot water temperature and being limited in defined temperature abundance below of the water of outflow, the reliability of equipment improves.

Moreover, connector 4 use it is chimeric with insertion body 2, by inner tube 1 from foreign side cover and be inserted into pin 5 grade fasteners come The position of fixed structure (referring to Fig.1), insertion body 2 and inner tube 1 is fixed.No matter setting state is (longitudinal, horizontal, oblique as a result, Set) how, it can ensure the axial direction i.e. axis of insertion body 2 between twist tabs 22 and inner tube 1 along heat exchanger 11 To the flow path of connection.

Therefore, the increase for inhibiting the pressure loss and the heat exchanger that freedom degree raising is set are capable of providing.

As described above, having in the outer surface of the twist tabs 22 of insertion body 2 along heat exchange in present embodiment 2 The protrusion 25 of the axially consecutive arrangement of device 11, in such a way that protrusion 25 is contacted with the inner surface of inner tube 1 with the fixed inner tube 1 of connector 4, Insertion body 2.As a result, in addition to helical flow path, be also upwardly formed flow path in the axis of heat exchanger 11, thus be capable of providing even if In the case where flowing through the water of heat exchanger 11 for big flow, it can also inhibit the increased heat exchanger 11 of hydraulic pressure damage.It loads as a result, There is the energy saving of the equipment of the heat exchanger 11 of present embodiment 2 to improve.

In addition, even if in the case where no protrusion 25, also by making connector 4 using chimeric with insertion body 2, by inner tube 1 The structure (referring to Fig. 5 A) for covering from foreign side and being fixed with fastener, no matter setting state (longitudinal horizontal, tilting), all It can ensure the axial direction i.e. stream of insertion body 2 being axially connected between twist tabs 22 and inner tube 1 along heat exchanger 11 Road (bypass flow path 50).As a result, by the way that appropriately distance will be set between twist tabs 22 and inner tube 1, it is capable of providing Inhibit the increase of hydraulic pressure damage and the heat exchanger 11 of freedom degree raising is set.

(embodiment 3)

Fig. 8 is the sectional view of the heat exchanger of present embodiment 3.Wherein, to identical with embodiments of the present invention 1,2 Component marks identical appended drawing reference, omits the description.

The heat exchanger of embodiments of the present invention 4, the nose width t1 of the twist tabs 22 of insertion body 2 and root The relationship of width t2 is t1 < t2.

For heat exchanger as constructed as above, it is acted record below.

The heat exchanger 11 of present embodiment 4 is also same as embodiment 1,2, is being formed between inner tube 1 and insertion body 2 Helical flow path flowing the water as first fluid, with two as second fluid as the internal flow in outer tube 3 Carbonoxide carries out heat exchange via inner tube 1 and outer tube 3 with opposite flowing.

Heat exchanger 11 is used as first fluid in the helical flow path flowing being formed between inner tube 1 and insertion body 2 Water, to the width L of the heat-transfer area of the carbon dioxide as second fluid of the internal flow in outer tube 3, as shown in figure 8, being The nose width t1 of twist tabs 22, i.e. P-t1 are subtracted from the pitch P of twist tabs 22.

In present embodiment, as shown in figure 8, the shape of the twist tabs 22 of insertion body 2 is configured to t1 < t2.By This, is able to maintain that water same as the fixed situation of the thickness of the twist tabs 22 as shown in Figure 3 as embodiment 1 Side flow path cross sectional area S, while the situation fixed compared to the thickness of twist tabs 22, can expand be formed in inner tube 1 with The water as first fluid of helical flow path flowing between insertion body 2 is used as second to the internal flow in outer tube 3 The width L of the heat-transfer area of the carbon dioxide of body.

That is, in the water as first fluid for the helical flow path flowing being formed between inner tube 1 and insertion body 2, Xiang The heat transfer area of the carbon dioxide as second fluid of the internal flow of outer tube 3 expands, so being capable of providing heat exchange performance Higher heat exchanger.

Fig. 9 indicates the length and water side flow path cross sectional area S for the helical flow path that will be formed between inner tube 1 and insertion body 2 It fixes, the relationship that i.e. water lateral pressure loses insertion body the protruding portion nose width t1 and heat-exchange capacity Q under equal conditions.

As can be seen from FIG. 9, the nose width t1 of twist tabs 22 is smaller, is being formed between inner tube 1 and insertion body 2 Helical flow path flowing the titanium dioxide as second fluid from the water as first fluid to the internal flow in outer tube 3 The heat transfer area of carbon expands.Heat-exchange capacity improves as a result,.

In addition, the root shape of twist tabs 22 in order to inhibit the Secondary Flow of root removing, reduce water lateral pressure Loss, can be R shape.Thereby, it is possible to reduce the friction loss of the water caused by being vortexed, so can be improved present embodiment The energy efficiency of heat exchanger and the equipment for loading it.

As described above, in present embodiment 3, the nose width t1 and root width of the twist tabs 22 of insertion body 2 The relationship of t2 is t1 < t2.It does not change water effluent travel permit part as a result, and (is formed in the helical flow path between inner tube 1 and insertion body 2 Length and water side flow path cross sectional area S), i.e. in water lateral pressure loss equal conditions under, can make be formed in inner tube 1 and insert The water as first fluid for entering the helical flow path flowing between body 2 is used as second fluid to the internal flow in outer tube 3 Carbon dioxide heat-transfer area length.As a result, heat transfer area can be expanded, so it is high to be capable of providing heat exchange performance Heat exchanger.

(embodiment 4)

Figure 10 is the structure chart of the refrigerating circulatory device of present embodiment 4.

Wherein, identical appended drawing reference is marked to component identical with embodiments of the present invention 1~3, omitted the description.

Figure 10 is the refrigerating circulatory device for being for example loaded into Teat pump boiler.Refrigerating circulatory device include: compressor 101, Radiator 102 as the heat exchanger 11 recorded in embodiments of the present invention 1~3, the dress of the decompression as electric expansion valve 103 and evaporator 104 are set, they are connected and circlewise constitutes refrigerant circuit 105.

Refrigerant circuit includes that the evaporator outlet temperature detection for the temperature for detecting the refrigerant flowed out from evaporator 104 is single Member 107, refrigerating circulatory device have control device 110 and defrosting operation mode.

Be sealed with the carbon dioxide as refrigerant in refrigerant circuit 105, when compressor 101 operates, high-pressure side with Supercriticality operating.

In addition, constituting radiator 102 (heat exchanger 11 recorded in embodiments of the present invention 1 or embodiment 2) Insertion body 2 with twist tabs 22 is the big resin system of specific heat ratio metal.

About refrigerating circulatory device formed as described above, illustrate its movement and effect below.

When compressor 101 operates, the refrigerant being discharged by high pressure compressed is sent to radiator 102, conveys with by water Pump 113 is radiated and entering the water at low temperature that water piping 111 is sent and carrying out heat exchange.Thus the water at low temperature after heating becomes high temperature Water is sent to storage hot water tank (not shown) and stores hot water as the hot water of high temperature by going out hot water piping 112.

The refrigerant flowed out from radiator 102 is sent to evaporation after being fed into the progress decompression expansion of decompressor 103 Device 104 carries out heat exchange with the air imported by blower 106, evaporates and gasify.Refrigerant after gasification is inhaled into compression Machine 101.

Then, the defrosting motion of Teat pump boiler is illustrated.

When with the low state of external air temperature carry out storage hot water operating when, evaporator 104 frost, the heat of evaporator 104 Exchange capacity can be greatly reduced.

Then, control device 110 defrosts to the frost for being attached to evaporator 104, carries out the heat exchange for making evaporator 104 The defrosting motion that ability is restored.Defrosting motion adheres to frost on evaporator 104, is detected by evaporator outlet temperature single The execution when temperature that member 107 detects is lower than defined temperature.Hereinafter, defrosting motion is specifically described.

Firstly, control device 110 stops the water delivery pump 113 for sending water to radiator 102 and blower 106, reduce decompression The flow path resistance of device 103.By the refrigerant of the compressed high temperature of compressor 101, by radiator 102 and decompressor 103, It is flowed into evaporator 104, after the heat possessed by refrigerant is defrosted, is inhaled into compressor 101.

Then, when the temperature detected by evaporator outlet temperature detection unit 107 is higher than defined temperature, defrosting fortune Rotation is made to terminate, and carries out heating operating.

In defrosting operating, in addition to the heat for the refrigerant being discharged from compressor 101, also effective use radiator 102 The heat of middle savings defrosts to evaporator 104.

Pass through the resin for keeping the insertion body 2 of a part of the flow path as radiator 102 big using specific heat ratio metal, heat dissipation The amount of stored heat of device 102 increases, and can utilize more heats from radiator 102 in defrosting.Thereby, it is possible to tie in the short time Beam defrosting operating, improves the defrosting performance of equipment.

In addition, the insertion body 2 with twist tabs 22 uses resin system (PPS) in embodiments of the present invention 4, But the big material of resin or specific heat other than PPS can also expect same function and effect.

In addition, the refrigerant flowed in outer tube 3 is used using carbon dioxide in embodiments of the present invention 1~3 Hydro carbons, HFC class (R410A etc.) refrigerant or their alternative refrigerant can also expect same function and effect.

In addition, each embodiment more than not only, the combination of above each embodiment is also in the scope of the present invention It is interior.

Industrial availability

As described above, heat exchanger of the invention, is capable of providing the compact and good economy performance of one kind, quality parameter and heat exchange The high heat exchanger of performance.Therefore, the present invention can be applied to be mounted with setting for the heat exchanger that heat exchange is carried out between fluid It is standby.

Description of symbols

1 inner tube

2 insertion bodies

3 outer tubes

4 connectors

5 locating snap rings (insertion pin)

11 heat exchangers

21 insertion body axle portions

22 twist tabs

23 protrusions

24 recess portions

25 protrusions

50 bypass flow paths

101 compressors

102 radiators

103 decompressors

104 evaporators

105 refrigerant circuits.

Claims

1. a kind of refrigerating circulatory device comprising:

At least by refrigerant circuit made of compressor, heat exchanger, decompressor and evaporator loop connecting；With

Control device,

Defrosting operation mode with the frost melts for making the evaporator,

The heat exchanger includes

Inner tube, the circulating water in said inner tube；

The insertion body being inserted into said inner tube；With

The outer tube of the periphery of said inner tube is set, flows refrigerant in the outer tube,

The insertion body has axle portion and is formed in the twist tabs of the outer surface of the axle portion,

The water flows in the helical flow path that inner surface, the axle portion and the twist tabs by said inner tube are formed It is dynamic,

The type of flow of the refrigerant and the water is opposite stream,

The insertion body is made of resin.

2. refrigerating circulatory device as described in claim 1, it is characterised in that:

In the heat exchanger, the hand of spiral of the coiling direction of the outer tube and the twist tabs is the same direction.

3. refrigerating circulatory device as claimed in claim 1 or 2, it is characterised in that:

In the heat exchanger, the outer tube configuration is in the periphery of said inner tube and the opposing part of the helical flow path.

4. refrigerating circulatory device as described in claim 1, it is characterised in that:

The heat exchanger has the connector for fixing said inner tube, the insertion body respectively.

5. refrigerating circulatory device as described in claim 1, it is characterised in that:

The twist tabs of the heat exchanger have the multiple protrusions contacted with said inner tube,

The multiple protrusion arranges continuously in axial direction.

6. refrigerating circulatory device as described in claim 1, it is characterised in that:

When the nose width of the twist tabs of the heat exchanger is that t1 meets t1 < t2 when root width is t2 Relationship.