CN101405558A - Fin-tube heat exchanger, fin for heat exchanger, and heat pump device - Google Patents

Abstract

The present invention provides a fin-tube heat exchanger 1, which includes a plurality of fins 3 arrayed spaced apart from and parallel to each other so as to form gaps for allowing a first fluid to flow therethrough, and a plurality of heat transfer tubes 2 penetrating the plurality of fins 3 and for allowing a second fluid to flow therethrough. The plurality of heat transfer tubes 2 includes first heat transfer tubes 2A and second heat transfer tubes 2B arranged in a predetermined row direction that intersects the flow direction of the first fluid. The fins 3 have protrusions 5 each disposed between a first heat transfer tube 2A and a second heat transfer tube 2B, for guiding the first fluid toward the first heat transfer tube 2A side and the second heat transfer tube 2B side. The equivalent diameter of the protrusion 5, as viewed in the axis direction of the heat transfer tubes 2, is equal to or greater than the outer diameter of the heat transfer tubes 2.

Description

Fin tube type heat exchanger, aluminum fin and heat pump assembly

Technical field

The present invention relates to fin tube type heat exchanger, aluminum fin and heat pump assembly.

Background technology

All the time, fin tube type heat exchanger is used to aircondition, fridge-freezer, dehumidifier, hot water machine etc.Fin tube type heat exchanger is opened predetermined distance a plurality of fins that are arranged in parallel and the heat-transfer pipe that connects these fins by sky and is constituted.

As everyone knows, to promote that the heat transfer or the reduction pressure loss etc. are purpose, the fin shape of fin tube type heat exchanger has been implemented further investigation.For example, in fin tube type heat exchanger, usually, the downwind side of heat-transfer pipe can become the low dead water region of localized heat conductivity.So known have to reduce dead water region to be purpose, to be provided with the fin tube type heat exchanger of projection on the surface of fin.

For example, disclose use is provided with the fin of many nicks on the surface fin tube type heat exchanger in the Japanese kokai publication hei 7-239196 communique.Specifically, the purport of putting down in writing in this communique is that as shown in figure 34, air is guided to the downwind side of heat-transfer pipe 101 by the many nicks 102 on the fin 103, thereby improves pyroconductivity.But, because each nick 102 is little, almost can not get air is induced to the effect of the downwind side of heat-transfer pipe 101, not too can expect the raising of pyroconductivity.

In Japanese kokai publication sho 63-294494 communique, disclose the fin tube type heat exchanger that is provided with the projection of triangle taper on the surface of fin.As shown in figure 35, in this fin tube type heat exchanger, the projection 111 of triangle taper is provided in the both sides of heat-transfer pipe 112.The purport of putting down in writing in the Japanese kokai publication sho 63-294494 communique is, air is induced to the downwind side of heat-transfer pipe 112 by these projections 111, rear at heat-transfer pipe 112, because of air current A becomes narrow air-flow C flow velocity is increased, therefore, rear at heat-transfer pipe 112 produces fierce turbulent flow, and consequently, dead water region becomes minimum (with reference to hurdle, the 17th row～lower-left, the 4th page of upper right hurdle the 1st row of Japanese kokai publication sho 63-294494 communique).

In the disclosed heat exchanger of Japanese kokai publication sho 63-294494 communique (with reference to Figure 35),, therefore, there is the pressure loss problem of increase and so on easily owing to be flowing in 111 quilt throttlings significantly of two projections of triangle taper.In addition, the disclosed heat exchanger of Japanese kokai publication sho 63-294494 communique is the heat exchanger that uses in the big regions of turbulent flow of air velocity, is the heat exchanger of the facilitation effect of turbulent flow being used as target.So, not necessarily can bring into play satisfactory performance at the laminar flow zone that air velocity is low.

In Japanese kokai publication hei 6-300474 communique, disclose the fin tube type heat exchanger that is provided with the projection of quadrangular pyramid shape on the surface of fin.As shown in figure 36, in this fin tube type heat exchanger, be formed with at the downwind side of heat-transfer pipe 121 and cut sheet 122, the teat 123 of quadrangular pyramid shape be provided between the adjacent heat-transfer pipe 121 and than heat-transfer pipe 121 by downwind side.The purport of putting down in writing in the Japanese kokai publication hei 6-300474 communique is, air is induced to by teat 123 and has cut sheet 122 sides, with the pyroconductivity (with reference to the 4th page of right hurdle the 30th row～the 36 row of Japanese kokai publication hei 6-300474 communique) of the downwind side that improves heat-transfer pipe 121.

In the disclosed heat exchanger of Japanese kokai publication hei 6-300474 communique (with reference to Figure 36), teat 123 is configured in than the position of heat-transfer pipe 121 center line 124 each other by downwind side.Therefore, the flow direction of air is changed by the downstream at the center than heat-transfer pipe 121.But, because teat 123 is smaller, so, be difficult to promptly change flowing of air.Thereby, be difficult to air is induced to fully the rear of heat-transfer pipe 121.

In addition, as shown in figure 37, in TOHKEMY 2002-90085 communique, disclose the fin tube type heat exchanger that uses the fin 105 that is formed with the portion of having cut 106.Such fin 105 is commonly referred to as the slit fin.Though slit fin 105 exists some unfavorable aspect the pressure loss, the effect of utilizing its pyroconductivity to increase in the leading edge part of the portion of having cut 106 is so-called leading edge effect, and the heat transfer property of heat exchanger is increased substantially.But, can be in the portion of having cut 106 of this slit fin 105 frosting and cause obstruction, cause the reduction significantly of rate of heat exchange, therefore, its applicable object is limited.Specifically, be difficult to be applicable to the evaporimeter that under atmosphere, makes the cold-producing medium evaporation than lower temperature.

But, be well known that, in fin tube type heat exchanger, in order to increase the heat output of cold-producing medium and fluid (for example air), when the speed by lifting fluid promotes pyroconductivity, the pressure loss of fluid during by heat exchanger also increases, and the power that the fin that fluid is flowed needs can become excessive.That is, the pyroconductivity and the pressure loss as the heat transfer property index has compromise relation.As the fin tube type heat exchanger of attempting the pyroconductivity and the pressure loss and depositing, the many uses of motion are flexed into plate-shaped fins the heat exchanger of undulatory wave-shaped fins.

For example, Figure 38 A and Figure 38 B represent the wave-shaped fins of Japanese kokai publication hei 1-90995 communique record.Wave-shaped fins 109 is alternately to occur with respect to the flow direction of the fluid of representing with arrow and the fin that forms with rib 109a and concave surface 109b.This wave-shaped fins 109 has the balance excellence of the heat transfer property and the pressure loss, and does not have the blockage problem that frosting causes, the advantage of restriction of no applicable object and so on.

In recent years, because of various problems such as tropical island effect problem, resource problem, earth environment problems, the expectation that the saving of the heat pump assembly that hot water machine or air conditioner are used can quantize is more and more urgent.In order to make heat pump assembly save energy more, the improvement of compressing mechanism and expansion mechanism is from needless to say, and the improvement of heat exchanger also is indispensable.Specifically be exactly heat exchanger heat transfer property excellence and the low fin tube type heat exchanger of the pressure loss that requires than using wave-shaped fins

Summary of the invention

The present invention develops in view of the above problems, and its purpose is to provide a kind of have excellent heat transfer property and the also little fin tube type heat exchanger of the pressure loss.Its another purpose provides a kind of heat pump assembly that possesses this fin tube type heat exchanger.Its again a purpose provide a kind of fin that can be applicable to this fin tube type heat exchanger.

That is, the invention provides a kind of fin tube type heat exchanger, it makes the first fluid and second fluid carry out heat exchange, wherein, possesses:

A plurality of fins, its space in order to be formed for first fluid is circulated, and the mutual empty standard width of a room in an old-style house is every being arranged in parallel;

A plurality of heat-transfer pipes, it connects a plurality of fins and is used to make second fluid flow,

A plurality of heat-transfer pipes comprise first heat-transfer pipe and second heat-transfer pipe of the column direction alignment arrangements of the regulation of intersecting along the flow direction with first fluid,

On column direction, first heat-transfer pipe and second heat-transfer pipe are adjacent mutually,

Fin has teat, and teat is formed between first heat-transfer pipe and second heat-transfer pipe, and with first fluid the lead first heat-transfer pipe side and the second heat-transfer pipe side,

From the diameter of equal value of the teat of axially seeing of heat-transfer pipe is more than the external diameter of heat-transfer pipe.

In addition, the invention provides the fin that a kind of above-mentioned fin tube type heat exchanger uses.

In addition, the invention provides a kind of heat pump assembly, it possesses:

Compressor, its compressed refrigerant;

Radiator, it makes by the refrigerant loses heat after the compressor compresses;

Expansion mechanism, it makes by the cold-producing medium behind the radiator heat-dissipation and expands;

Evaporimeter, it makes by the cold-producing medium evaporation after the expansion mechanism expansion,

At least one side of evaporimeter and radiator comprises above-mentioned fin tube type heat exchanger.

The fin tube type heat exchanger of the invention described above is formed with the big teat of surface area between first heat-transfer pipe and second heat-transfer pipe, can realize the expansion of the heat transfer area of fin, and, to suppress the target that develops into of temperature boundary layer and velocity boundary layer.By enlarging heat transfer area and suppressing development of boundary layer, can improve the heat transfer property of fin tube type heat exchanger.In addition, the diameter of equal value from the teat of axially seeing of heat-transfer pipe is more than the external diameter of heat-transfer pipe.In other words, with the teat orthographic projection to the plane parallel with a plurality of fins the time, the area that appears at the picture of the teat on this plane reaches more than the sectional area of heat-transfer pipe.According to this teat, the surface area of fin is played one's part to the full.In addition, the bigger teat of size between itself and first heat-transfer pipe flat site or the flat site between itself and second heat-transfer pipe, first fluid is played the effect of stronger raising flow velocity.Pyroconductivity improves if flow velocity improves then, and is therefore preferred.Especially can make that the lateral parts relative with teat fully helps heat transmission in the outer peripheral face (outer peripheral face that comprises the fin circle that surrounds heat-transfer pipe) of heat-transfer pipe.In addition, teat is induced to first fluid at the rear of heat-transfer pipe.Thus, can prevent that the rear of heat-transfer pipe from producing big dead water region, thereby improve the heat transfer property of fin tube type heat exchanger.

Description of drawings

Fig. 1 is the stereogram of fin tube type heat exchanger;

Fig. 2 is the vertical view of the fin of embodiment 1;

Fig. 3 is the III-III line sectional view of Fig. 2;

Fig. 4 is the figure suitable with Fig. 3 of variation;

Fig. 5 is the vertical view of fin of the embodiment 1 that flows of expression air;

Fig. 6 is the stereogram of the fin of embodiment 1;

Fig. 7 is the vertical view of simulation model;

Fig. 8 is the Performance Characteristics figure of the fin tube type heat exchanger of embodiment 1;

Fig. 9 is the sectional view that schematically shows the embodiment 1 of temperature boundary layer;

Figure 10 is the vertical view of the fin of embodiment 2;

Figure 11 is the stereogram of the fin of embodiment 2;

Figure 12 is the vertical view of the fin of embodiment 3;

Figure 13 is the vertical view of variation of the fin of expression embodiment 1;

Figure 14 is the vertical view of the fin of embodiment 4;

Figure 15 is the XV-XV line sectional view of Figure 14;

Figure 16 A is the schematic diagram of an example of the shape of expression teat;

Figure 16 B is another routine schematic diagram of the shape of expression teat;

Figure 17 A is the curve map of expression clothoid;

Figure 17 B is the sectional view that the teat of clothoid is described on the surface;

Figure 18 is to use the Action Specification figure of fin tube type heat exchanger of the fin of embodiment 4;

Figure 19 is the Action Specification figure of the fin tube type heat exchanger of comparative example;

Figure 20 is the vertical view of the fin of embodiment 5;

Figure 21 is the vertical view of the fin of embodiment 6;

Figure 22 is the vertical view of fin of the variation of relevant embodiment 6;

Figure 23 A is the vertical view of the fin of embodiment 7;

Figure 23 B is the D1-D1 sectional view of Figure 23 A;

Figure 24 A is the vertical view of fin of the variation of relevant embodiment 7;

Figure 24 B is the D2-D2 sectional view of Figure 24 A;

Figure 25 is the structure chart of heat pump assembly;

Figure 26 is the schematic diagram of application examples of the heat pump assembly of expression Figure 25;

Figure 27 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression embodiment 1;

Figure 27 B is the then contour map of the simulation result (velocity flow profile) of Figure 27 A of expression;

Figure 28 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression embodiment 2;

Figure 28 B is the then contour map of the simulation result (velocity flow profile) of Figure 28 A of expression;

Figure 29 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression embodiment 3;

Figure 29 B is the then contour map of the simulation result (velocity flow profile) of Figure 29 A of expression;

Figure 30 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression comparative example 1;

Figure 30 B is the then contour map of the simulation result (velocity flow profile) of Figure 30 A of expression;

Figure 31 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression embodiment 4;

Figure 31 B is the then contour map of the simulation result (velocity flow profile) of Figure 31 A of expression;

Figure 32 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression embodiment 5;

Figure 32 B is the then contour map of the simulation result (velocity flow profile) of Figure 32 A of expression;

Figure 33 A is the contour map of simulation result (nusselt number distribution) of the heat exchanger of expression comparative example 2;

Figure 33 B is the then contour map of the simulation result (velocity flow profile) of Figure 33 A of expression;

Figure 34 is the vertical view of the fin of existing fin tube type heat exchanger;

Figure 35 is the vertical view of the fin of existing fin tube type heat exchanger;

Figure 36 is the vertical view of the fin of existing fin tube type heat exchanger;

Figure 37 is the stereogram of slit fin;

Figure 38 A is the vertical view of wave-shaped fins;

Figure 38 B is the sectional view of wave-shaped fins.

The specific embodiment

(embodiment 1)

Below, with reference to accompanying drawing embodiments of the present invention are described.

Fig. 1 is the overall perspective view of the fin tube type heat exchanger of present embodiment.Fin tube type heat exchanger 1 possesses in order to be formed for making the space of first fluid circulation, and a plurality of fins 3 of arranging of spaced and parallel ground, a plurality of heat-transfer pipes 2 that connect these fins 3 in accordance with regulations.Heat exchanger 1 is the heat exchanger that makes the first fluid that flows along the interarea of fin 3 and carry out heat exchange at second fluid of the internal flow of heat-transfer pipe 2.In the present embodiment, air A flows along the interarea of fin 3, and cold-producing medium B is in the internal flow of heat-transfer pipe 2.The a plurality of heat-transfer pipes 2 that connect these fins 3 connect into one in the mode that cold-producing medium B flows in proper order.In addition, the kind and the state of the fluid that flows at the fluid of the internal flow of heat-transfer pipe 2 and along the interarea of fin 3 are not particularly limited.These fluids can be gas, also can be liquid.In addition, a plurality of heat-transfer pipes 2 also can not necessarily be connected to one.

Heat exchanger 1 with the column direction (Z direction) of the stacked direction (Y direction) of the flow direction (directions X) of air A and fin 3 and heat-transfer pipe 2 roughly the posture of quadrature be provided with.But, if can guarantee sufficient heat exchange amount, airflow direction also can tilt slightly from directions X.In addition, in this manual, defining the direction vertical with the interarea of fin 3 is that stacked direction (Y direction) is short transverse.

Fin 3 has the rectangular flat plate shape, arranges along the Y direction shown in Fig. 1.In the present embodiment, fin 3 is arranged with certain interval (spacing of fin).Spacing of fin for example is 1.0mm～1.5mm.But, spacing does not need and must fix, and the spacing difference also can.As shown in Figure 3, spacing FP represents with the distance between centers of the thickness direction of relevant adjacent two fins 3,3.The wall thickness that fin 3 can form with for example punch process is that the metallic plate of 0.08～0.2mm constitutes.Metallic plate for example is the flat board of aluminum.A plurality of through hole 3h (Fig. 2) form zigzag along the length direction of fin 3, and embedding in each of these through holes 3h has heat-transfer pipe 2.In addition, preferably the surface of fin 3 is implemented hydrophilies such as the coating processing of alumina treatment (ベ one マ イ ト processing) or hydrophilic coating, perhaps implement hydrophobicity and handle.

Fig. 2 is the vertical view of the fin that uses of the heat exchanger of Fig. 1.But, about heat-transfer pipe 2, what manifest among Fig. 2 is and the parallel cross section of the interarea of fin 3 interarea of the plane domain that does not form teat 5 (in detail).As shown in Figure 2, dispose front and back two biographies heat pipes 2 along the column direction parallel with the longitudinal direction of fin 3.Just, the straight line at the center of the through hole 3h of each row of binding is parallel with the leading edge 30p of fin 3.The heat-transfer pipe 2 of first row and the heat-transfer pipe 2 of secondary series depart from 1/2 amount of tube coupling distance in the Z direction.That is, heat-transfer pipe 2 is configured to zigzag.Belong to same row two heat-transfer pipes 2,2 in the heart beeline (=tube coupling apart from) can be set at 2 times～3 times of outer diameter D of this heat-transfer pipe 2 for example.The outer diameter D of heat-transfer pipe 2 for example is 1mm～20mm, and consistent with the opening diameter of the through hole 3h that forms on the fin 3.The fin circle 3a of heat-transfer pipe 2 and formation through hole 3h connects airtight and is entrenched togather with this fin circle 3a.This heat-transfer pipe 2 is the trough of belt pipes that are formed with groove by heat such as copper or copper alloy smooth tubes that very inner face that constitutes of the property led metal is level and smooth or inner face.

Be formed with the teat 5 of positive quadrangular pyramid shape on the surface of fin 3.Teat 5 is outstanding from the one side of fin 3, is configured in respectively between the heat-transfer pipe 2 of each row.In the present embodiment, teat 5 is disposed at the centre position between the adjacent heat-transfer pipe 2 of column direction.The area of the teat 5 when the Y direction is seen, just the area of the teat 5 the vertical view of Fig. 2 be set to the area of heat-transfer pipe 2 equal more than.That is, the diameter d of equal value of teat 5 is (according to π d ²The d of/4=S (area) definition) be more than the outer diameter D of heat-transfer pipe 2.Specifically, in the present embodiment, the length 1 of the bottom of teat 5 and the outer diameter D of heat-transfer pipe 2 equate that the diameter d of equal value of teat 5 is greater than the outer diameter D of heat-transfer pipe 2.In addition, symbol L represents the airflow direction length (directions X length) of teat 5.

The width of the Z direction of teat 5 is, the 8b of portion that partways along the flow direction of air A from upstream extremity 8a increases, and reduces from middle part 8b to downstream 8c.Teat 5 have the upper left side that is positioned at Fig. 2 the first inclined plane 6a, be positioned at the lower-left side the second inclined plane 6b, be positioned at the lower right side the 3rd inclined plane 6c, be positioned at the 4th inclined plane 6d of upper right side.The first inclined plane 6a and the second inclined plane 6b are separated by the crest line 7a that extends along directions X.The first inclined plane 6a is oblique to an adjacent side's heat-transfer pipe 2A (below be called first heat-transfer pipe) inclination, and the second inclined plane 6b is oblique to the opposing party's heat-transfer pipe 2B (below be called second heat-transfer pipe) inclination.The first inclined plane 6a and the 4th inclined plane 6d are separated by the crest line 7b that extends along the Z direction.In addition, the second inclined plane 6b and the 3rd inclined plane 6c are also separated by crest line 7b.

In this heat exchanger 1, teat 5 is configured in the comparison upstream side.Specifically, the upstream extremity 8a of teat 5 is positioned at the center C upstream side of each heat-transfer pipe 2.The middle part 8b of teat 5 is positioned at the downstream 2e upstream side of heat-transfer pipe 2.In other words, the upstream extremity 8a of teat 5 is positioned at center C line 9 upstream sides each other that link heat-transfer pipe 2, and the middle part 8b of teat 5 is positioned at downstream 2e line 10 upstream sides each other that link heat-transfer pipe 2.In addition, the downstream 8c of teat 5 is positioned at the downstream 2e downstream of heat-transfer pipe 2.

As shown in Figure 3, in the present embodiment, the height H of teat 5 is greater than spacing of fin FP.Therefore, the adjacent fin 3 of Y direction each other in, the part of the teat 5 of a side fin 3 enters the inboard of teat 5 of the opposing party's fin 3.But, the height H of teat 5 also can be equal with spacing of fin FP, also can be less than spacing of fin FP.The height H of teat 5 for example also can be 0.2 times～2 times of spacing of fin FP, also can be 0.5 times～2 times of spacing of fin FP.

But, as shown in Figure 4, if the height H of teat 5 less than spacing of fin FP, when upstream side is seen the downstream, will form the clearance G of extending along directions X straight 3 of adjacent fins.Therefore, consider that from the viewpoint that reduces the pressure loss height H of teat 5 is preferably less than spacing of fin FP.When considering reduction both sides' the balance of the raising of heat transfer property and the pressure loss, 1 times of then preferred more than 0.2 times of spacing of fin FP (preferred more than 0.25 times) of the height of teat 5 and less than.

Secondly, describe the air in this heat exchanger 1 is mobile.

(with reference to Fig. 6) as shown in Figure 5, the place ahead of fin 3 is flow through the air current A 1 of coming and is impacted teat 5.Then, a part of A2 of the air-flow after the impact is induced to the first heat-transfer pipe 2A side by the first inclined plane 6a, and other air current A 2 ' are induced to the second heat-transfer pipe 2B side by the second inclined plane 6b.Then, the air current A 2 of being induced by the first inclined plane 6a spreads to the rear of the first heat-transfer pipe 2A.In addition, other air current A 2 ' of being induced by the second inclined plane 6b spread to the rear of the second heat-transfer pipe 2B.Consequently, in the rear part of the first heat-transfer pipe 2A and the second heat-transfer pipe 2B of fin 3, the reduction of pyroconductivity is suppressed, and the area of dead water region reduces.

Then, the air current A 3 that has spread to the rear of the first heat-transfer pipe 2A is impacted secondary series teats 5, is induced to secondary series heat-transfer pipe 2C side by the second inclined plane 6b of this teat 5.Similarly, the air current A 3 ' that has spread to the rear of the second heat-transfer pipe 2B is impacted secondary series teat 5, is induced to above-mentioned heat-transfer pipe 2C side by the first inclined plane 6a of this teat 5.Then, by above-mentioned inclined plane 6a, the air current A 4 that 6b induces, A4 ' spreads to the rear of heat-transfer pipe 2C.Consequently, in the rear part of the heat-transfer pipe 2C of fin 3, the reduction of pyroconductivity also is suppressed, and the area of dead water region reduces.

Table 1 is that expression (is flexed into fin the fin of waveform to possessing existing wave-shaped fins.For example, with reference to the 1st and the 2nd figure of Japanese kokai publication hei 1-90995 communique) fin tube type heat exchanger and the simulation result that compares of the fin tube type heat exchanger (concrete shape is with reference to Fig. 7) of present embodiment.In this emulation, the thickness of establishing fin is 0.1mm, and spacing of fin is 1.5mm, and the external diameter of heat-transfer pipe is 7.0mm, and front wind speed Vair is 1m/s.In addition, the fin tube type heat exchanger of the expression of " the circular cone fin " in the table 1 embodiment 2 described later.

(table 1)

When heat exchanger was carried out performance evaluation, preferred pyroconductivity α was big, P is little for pressure loss Δ.That is the big side of α/Δ P.As shown in Table 1, in the heat exchanger of present embodiment, the airflow direction length L of teat 5 is long more, and α/Δ P is big more, and the height H of teat 5 is high more, and P is more little for α/Δ.That is, parameter L/H is big more, and α/Δ P is big more.So Fig. 8 represents to be transverse axis, to be the curve map of the longitudinal axis with the parameter alpha/Δ P ratio of fin (relatively existing) with parameter L/H.As shown in Figure 8, if L/H greater than 5.5, the value of α/Δ P just is higher than the heat exchanger of existing wave-shaped fins formula.Thereby preferred L/H is greater than 5.5.

As mentioned above, according to the fin tube type heat exchanger 1 of present embodiment, fin 3 is with at heat-transfer pipe 2A, and the teat 5 and the teat 5 that have the quadrangular pyramid shape between the 2B form the mode that air separates with another heat-transfer pipe 2B side to heat-transfer pipe 2A side.That is, on teat 5, be formed with to the first inclined plane 6a of a heat-transfer pipe 2A side induced air with to the second inclined plane 6b of another heat-transfer pipe 2B side induced air.And the upstream extremity 8a of teat 5 is positioned at each heat-transfer pipe 2A, the center C upstream side of 2B.Therefore, air begins to be induced to each heat-transfer pipe 2A, the center C upstream side of 2B, so, from beginning to change flow direction more for a long time.Consequently, air spreads to each heat-transfer pipe 2A, the rear of 2B easily.Thereby, can reduce dead water region according to present embodiment.

In addition, the part of wide cut is that middle part 8b is positioned at each heat-transfer pipe 2A on teat 5, the downstream 2e upstream side of 2B.Thus, air also spreads to each heat-transfer pipe 2A easily, the rear of 2B, thereby the minimizing of realization dead water region.

In addition, in the present embodiment, teat 5 is with air separation to heat-transfer pipe 2A side and another heat-transfer pipe 2B rear flank, and at teat 5 and each heat-transfer pipe 2A, the mobile of air is accelerated in the space between the 2B.Therefore, just because of the mobile of air is accelerated, the pyroconductivity of fin 3 improves.

In addition, the air after the acceleration impacts the teat 5 that is located at the downstream.Consequently, temperature boundary layer attenuation on the teat 5 in downstream.Therefore, can realize the raising of pyroconductivity of the teat 5 in downstream, and then the pyroconductivity of fin 3 integral body improves.

In addition, from the upstream extremity 8a 8b of portion that partways, the width of teat 5 increases, and to downstream 8c, the width of teat 5 reduces from middle part 8b.Therefore, (the first inclined plane 6a and the second inclined plane 6b) is induced to each heat-transfer pipe 2A with air in the part from upstream extremity 8a to middle part 8b, after the 2B side, the stream of air narrowed down.Thereby, according to the teat 5 of embodiment, can prevent that the pressure loss from too increasing.

In this heat exchanger 1, teat 5 is configured in the comparison upstream side.Therefore, as shown in Figure 9, from temperature boundary layer BL that the preceding genesis of fin 3 begins to develop before abundant development (before the temperature boundary layer BL thickening) just and teat 5 clash.Consequently, the temperature boundary layer attenuation of teat 5, the pyroconductivity of teat 5 increases.That is, according to this heat exchanger 1, teat 5 is configured in upstream side, can improve the pyroconductivity of teat 5 thus, in this, also can realize the raising of heat transfer property.

In addition, according to this heat exchanger 1, the diameter d of equal value of teat 5 is more than the outer diameter D of heat-transfer pipe 2, and teat 5 is compared the earth and forms.Therefore, can be with bigger scale change flow direction.Thereby, even less situation of the velocity ratio of air (for example not enough 2m/s of front wind speed) or especially little situation (for example not enough 1m/s of front wind speed) also can be induced to air the rear of heat-transfer pipe 2 well.According to this heat exchanger 1,, also can bring into play the good heat transfer performance for the air-flow of laminar condition.In addition, like this, form bigger teat 5, so, can between teat 5 and heat-transfer pipe 2, the air part be quickened significantly, thereby pyroconductivity is improved.

In addition, consider that preferred teat 5 shared occupied area in fin 3 integral body (but except heat-transfer pipe sectional area) acquires a certain degree from the viewpoint that increases teat 5.So, the occupied area of teat 5 also can for, more than the occupied area (30%) in for example aforesaid simulation model, and teat 5 can be configured in maximum between the heat-transfer pipe 3 (for example 75%) completely.In addition, better is, as shown in table 1, as long as occupied area is more than 43% and below 73%, the value of α/Δ P just can reach more than 1, therefore, is suitable like this.

In addition, in the present embodiment,, can on the first inclined plane 6a and the second inclined plane 6b, the flow direction of air be changed more sharp because teat 5 forms the quadrangular pyramid shape.Therefore, can be more effectively with the rear of air guide heat-transfer pipe 2.

In addition, in the present embodiment, when the surface integral body of fin and smooth situation compared, just because of teat 5, it is big that the surface area of fin 3 becomes.Thereby, by enlarging heat transfer area heat exchange amount is increased.In addition, the recruitment of heat transfer area is not particularly limited, and for example is 3～5%.

In addition, be used as at this heat exchanger 1 under the situation of the cooler (for example evaporimeter of freezing cycle device etc.) that cools off air, produce dewfall sometimes on the surface of fin 3.In addition, when this heat exchanger 1 is set on the off-premises station of cold district, produce frosting sometimes on the surface of fin 3.But according to this heat exchanger 1, the part surface beyond the teat 5 of fin 3 is smooth.Therefore, compare with so-called slit fin, the water droplet after dew or the defrosting is difficult to be trapped in the surface of fin 3, wanders apace easily.Thereby this heat exchanger 1 is also as the excellent effect of cooler performance.

In the present embodiment, teat 5 is outstanding from the one side of fin 3, but also can make a part of teat 5 outstanding from the one side of fin 3, and makes other teats 5 outstanding from the another side of fin 3.For example, also can make a plurality of teats 5 of arranging along column direction alternately outstanding to face side and inboard.

The airflow direction length of teat 5 is not particularly limited.For example, when the airflow direction length of fin 3 is 36mm, can be more than the 4.5mm with the length setting of teat 5 and not enough 36mm also.

In addition, the shape of teat 5 is not limited to the quadrangular pyramid shape.As long as can obtain that air A is induced to the effect of the first heat-transfer pipe 2A and the second heat-transfer pipe 2B and stop the significant effect shown in these specifications such as effect of generation of dead water region, the shape of teat 5 just can be pyramidal as other of triangle taper.

In addition, fin 43 as shown in figure 13 also can be used as embodiment 1 fin a variation and propose.The teat 45 of fin 43 shown in Figure 13 be the plane when seeing fin 43 viewed profile 45s be shown as the teat of rhombus.Teat 45 is preferably the quadrangular pyramid shape that is made of four inclined planes.Teat 45 in two diagonal of the profile 45s that is confirmed as rhombus, long-diagonal is parallel with directions X and short diagonal is parallel with the Z direction.Other structures of teat 45 are identical with the teat 5 of embodiment 1.

In addition, also can suitably adopt the teat of other shapes that illustrate in the following embodiment.

(embodiment 2)

As Figure 10 and shown in Figure 11, the teat 15 of the fin 13 of present embodiment forms coniform.In the present embodiment, on teat 15, there is not tangible crest line.But, suppose from upstream extremity 8a apicad the 11 imaginary line 7a that extend along directions X, by summit 11 during along imaginary line 7b that the Z direction is extended, between imaginary line 7a and imaginary line 7b, be formed with the second inclined plane 6b that air is induced to the first inclined plane 6a of the first heat-transfer pipe 2A side and air is induced to the second heat-transfer pipe 2B side.

In the present embodiment, the width of teat 15 also is to increase from the upstream extremity 8a 8b of portion that partways, and reduces to downstream 8c from middle part 8b.The upstream extremity 8a of teat 15 is positioned at each heat-transfer pipe 2A, the center C upstream side of 2B.The middle part 8b of teat 15 is positioned at each heat-transfer pipe 2A, the downstream 2e upstream side of 2B.The diameter d of teat 15 is more than the diameter D of heat-transfer pipe 2.

In addition, the height of teat 15 also can be greater than spacing of fin, also can be less than spacing of fin.In addition, the height of teat 15 also can equal spacing of fin.

Because other structures and embodiment 1 are same, omit its explanation.

In the present embodiment and embodiment 1 same, also can reduce the area of the dead water region at heat-transfer pipe 2 rears.Thereby, can realize the raising of heat-transfer character.In addition, according to present embodiment, the first inclined plane 6a and the second inclined plane 6b are curved surface, can be respectively to the first heat-transfer pipe 2A side and second more stable ground of the heat-transfer pipe 2B side induced air.

(embodiment 3)

As shown in figure 12, fin 23 its teats 25 of embodiment 3 form oval taper.At this, set ellipticity (ratio of major axis and minor axis) and be roughly 2.But, the ellipticity of teat 25 is not particularly limited.Ellipticity can and be below 2 greater than 1 also, also can be for more than 0.5 and less than 1.Teat 25 also can be the elongated oval taper of directions X, also can be the elongated oval taper of Z direction.

In the present embodiment, also can there be tangible crest line on the teat 25.But, same with embodiment 2, suppose from upstream extremity 8a apicad the 11 imaginary line 7a that extend along directions X, by summit 11 during along imaginary line 7b that the Z direction is extended, between imaginary line 7a and imaginary line 7b, be formed with the second inclined plane 6b that air is induced to the first inclined plane 6a of the first heat-transfer pipe 2A side and air is induced to the second heat-transfer pipe 2B side.

In the present embodiment, the width of teat 25 also is to increase from the upstream extremity 8a 8b of portion that partways, and reduces to downstream 8c from middle part 8b.The upstream extremity 8a of teat 25 is positioned at each heat-transfer pipe 2A, the center C upstream side of 2B.The middle part 8b of teat 25 is positioned at each heat-transfer pipe 2A, the downstream 2e upstream side of 2B.The diameter d of teat 25 is more than the diameter D of heat-transfer pipe 2.In addition, the height of teat 25 also can also can also can equate with spacing of fin less than spacing of fin greater than spacing of fin.

Because other structures and embodiment 1 are same, so omission is to their explanation.

In the present embodiment and embodiment 1 same, also can reduce the area of the dead water region at heat-transfer pipe 2 rears, realize the raising of heat-transfer character.In addition and embodiment 2 same, the first inclined plane 6a and the second inclined plane 6b are curved surface, can be respectively to the first heat-transfer pipe 2A side and second more stable ground of the heat-transfer pipe 2B side induced air.In addition, according to present embodiment,, can set the degree of inducing aptly with respect to the air of the first heat-transfer pipe 2A and the second heat-transfer pipe 2B by suitably changing the ellipticity of teat 25.Thereby, set the ellipticity of teat 25 aptly according to the service condition of heat exchanger 1, then can further realize the optimization or the optimization of heat-transfer character.

Then, the embodiment that teat is formed the fin of cima shape or oval mound shape describes.

(embodiment 4)

Figure 14 is the vertical view of the fin of embodiment 4.Be formed with teat 35 with oval mound shape on the surface of fin 30.Teat 35 is all outstanding to same direction from the one side of fin 30, and at the adjacent heat-transfer pipe of same row promptly between the first heat-transfer pipe 2A and the second heat-transfer pipe 2B.Just, heat-transfer pipe 2 and teat 35 alternately occur along column direction.With teat 35 orthographic projections to and the parallel imaginary plane of fin 30 in the time, the picture that reveals on this imaginary plane is ellipse.In addition, at the area of the picture of the teat 35 that reveals on this imaginary plane sectional area greater than the heat-transfer pipe 2 with radially the cutting off of length direction quadrature the time.In other words, from the short transverse vertical with interarea (Y direction) vertical view Figure 14 when fin 30 is seen on the plane, the profile 5s of teat 35 is oval, and its diameter d of equal value is (according to π d ²The d of/4=S (area) definition) greater than the outer diameter D of heat-transfer pipe 2.For example, form the major diameter d of oval-shaped profile 5s ₁Greater than the outer diameter D of heat-transfer pipe 2, regulate the size of teat 35, so that minor axis d ₂With respect to its major diameter d ₁Reach d ₂≤ d ₁≤ 2d ₂Scope in.In addition, the above-mentioned sectional area of heat-transfer pipe 2 is consistent with the aperture area that is formed at the through hole 3h on the fin 30 in order to dispose heat-transfer pipe 2.

In addition, as shown in figure 14, between the first heat-transfer pipe 2A and the second heat-transfer pipe 2B, only be formed with a teat 35.Just, alternately form teat 35 and through hole 3h along column direction.The complications that are configured to of teat 35 are passed zigzag between the through hole 3h.For example, as Japanese kokai publication hei 7-239196 communique is disclosed,,, be difficult to obtain the height of teat because of the problem in the processing forming between two adjacent heat-transfer pipes under the situation of many little teats.And this little teat is weak using of induced air A.In addition, highly inadequate teat is also low with respect to the increment rate of the heat transfer area of unprocessed flat board, and almost can not expect to suppress the effect of boundary layer development.With respect to this, the teat 35 according to present embodiment can obtain sufficient height H, and is therefore, stronger to the effect of heat-transfer pipe induced air A.In addition, can improve increment rate with comparalive ease with respect to the heat transfer area of undressed flat board, and, suppress the effect of boundary layer development and also strengthen, be enough to expect the raising of heat transfer property.

In addition, as described above, two row before and after heat-transfer pipe 2 is configured to zigzag promptly, lean on the prostatitis and the rank rear parallel with this prostatitis of the leading edge 30p of fin 30.Be disposed between two adjacent heat- transfer pipes 2,2 of rank rear, also be formed with another teat 35 that has and be formed at the identical shaped and same size of teat 35 between the two adjacent heat- transfer pipes 2,2 that are configured in the prostatitis.Thus, also can expect to improve the effect of pyroconductivity equally with the prostatitis at rank rear.

The position of teat 35 reaches to be determined towards being preferably as follows.As shown in figure 14, with the position of the upstream extremity 5f of teat 35 on the direction (directions X) of the interarea of fin 30 and column direction quadrature than heat-transfer pipe 2A, the upstream extremity 2f of 2B is by the leading edge 30p (outer rim of upstream side) of fin 30.Do like this, can promptly induce the air A of covering, help the raising of heat transfer property at the leading edge 30p of fin 30 to heat-transfer pipe 2.On the other hand, the downstream 5e of teat 35 is positioned at than heat-transfer pipe 2A, the center C 1 of 2B, and C2 is further from the leading edge 30p of fin 30.That is, be positioned at the downstream of the flow direction of air A.Do like this, just flow air A on the interarea of fin 30 can be induced to heat-transfer pipe 2A effectively, the rear of 2B, the situation that forms the dead water region that is unfavorable for that heat is transmitted can be inhibited.As present embodiment, the downstream 5e of preferred teat 35 is positioned at than heat-transfer pipe 2A, and the downstream 2e of 2B is by the downstream of the flow direction of air A.

In addition, with the minor axis of the ellipse mode parallel with the orientation (Z direction) of the first heat-transfer pipe 2A and the second heat-transfer pipe 2B determine profile 5s be oval-shaped teat 35 towards.That is to say that the flow direction of air A is parallel with long axis of ellipse.Do like this, air A can be induced to more swimmingly teat 35 about, thereby can reduce because of forming the increase degree of the pressure loss that teat 35 causes.Certainly, long axis of ellipse also can be set at the direction parallel with column direction.

In addition, teat 35 is formed at apart from the center C 1 of the first heat-transfer pipe 2A and the center C 2 of the second heat-transfer pipe 2B and is equidistant position.Promptly, be comprised in the line segment C1 C2 that to link the center C 2 of the center C 1 of the first heat-transfer pipe 2A and the second heat-transfer pipe 2B with beeline with the major axis of the oval-shaped picture in the plane of this teat 35 being carried out orthographic projection and carry out mode in the vertical binary imaginary plane MD, determine the position of teat 35 with respect to the first heat-transfer pipe 2A and the second heat-transfer pipe 2B.Do like this, the flat site both sides of air A between the flat site between the teat 35 and the first heat-transfer pipe 2A and the teat 35 and the second heat-transfer pipe 2B are flowed equably.That is to say, can help the first heat-transfer pipe 2A and the second heat-transfer pipe 2B both sides to carry out heat transmission comparably, Cao Zuo situation can make the heat transfer property maximization of fin tube type heat exchanger 1 like this.

As shown in figure 15, the distance between centers of establishing the relevant thickness direction of fin 30 is a spacing of fin when being FP, the height H of regulating teat 35 in the mode that satisfies (FP/4)≤H≤FP.Each fin 30 has the position of teat 35 to arrange in the mode of short transverse unanimity with shape.If the height H of teat 35 is less than spacing of fin FP, then when upstream side is seen the downstream, between an adjacent fin 30 and another fin 30, will form the clearance G of extending along directions X straight.Therefore, consider that from the viewpoint that reduces the pressure loss height H of teat 35 is preferably less than spacing of fin FP.On the other hand, from the viewpoint consideration that obtains heat transfer area, improves heat transfer property, preferably increase the height H of teat 35.Like this, the heat transfer property and the pressure loss have trade-off relation, but by regulate the height H of teat 35 in above-mentioned scope, both can do one's utmost to suppress the increase of the pressure loss, the effect of the heat transfer property that can be improved to greatest extent again.

In addition, the height H of teat 35 is towards its summit TP ₁Dull increasing.When this teat 35 is seen on the plane, summit TP ₁Consistent with the center of ellipse.According to such shape, air A is TP apicad ₁Flow swimmingly, therefore can suppress the increase of the pressure loss.

About the surface configuration of teat 35, can enumerate some preferred examples.The sectional view of fin 30 at first, shown in Figure 15 is represented that the interarea with the flat site of this fin 30 is vertical and is comprised the XY cross section of the major axis of teat 35.The XY cross section is parallel with the flow direction of air A and vertical with the interarea of fin 30 cross section still.Can in this XY cross section, describe the shape that the mode of curve is regulated teat 35 with surperficial 5p (outer peripheral face).This curve for example is a sine curve.In the concrete example shown in Figure 16 A, the surperficial 5p of teat 35 describes the sine curve with Y=Kcos (X) { K: constant ,-90 °≤X≤90 ° } expression in above-mentioned XY cross section.

In addition, shown in Figure 16 B, also can in the XY cross section, describe the sinusoidal mode shape of regulating teat 35 with surperficial 5p with Y=Kcos (X) { K: constant ,-180 °≤X≤180 ° } expression.That is, the surperficial 5p of teat 35 is connected with the interarea of the flat site of fin 30 continuously in corresponding-180 ° of positions with upstream extremity 5f.So long as such surface configuration, just can not reduce taking advantage of the flow velocity of the mode flow air A on teat 35, not only the height H of teat 35 can be obtained but also the increase of the pressure loss can be restrained.

As the degree of bending can be continuous another curve, clothoid is arranged, the surface configuration of teat 35 can adopt this clothoid.That is, teat 35 can be regulated its shape according to surperficial 5p describes clothoid in above-mentioned XY cross section mode.Figure 17 A represents clothoid.

Usually, the crooked situation of curve is represented with the circle of curvature.Crooked situation not have the leap and the curve of variation continuously from small to large or from big to small, and only is the linear of expressway.The example of this curve is optimum with " clothoid ".The radius r of the circle of curvature of clothoid and the distance on the curve (among Figure 17 A apart from initial point apart from s) are inversely proportional.That is, the curve by following polar equation (1) definition is a clothoid.

R=a ²/ s (a: constant) ... (1)

Though in the XY cross section, surperficial 5p describes clothoid,, single clothoid also is not suitable for the surperficial 5p of teat 35.Thereby, can will arrive summit TP from upstream extremity 5f among the surperficial 5p that in the XY cross section, manifests ₁Uplink interval be divided into a plurality of intervals, describe each of these divided intervals with clothoid, thereby regulate the shape of teat 35.Preferably regulate in section boundaries continually varying mode with the curvature radius of a circle.As long as from summit TP ₁The downlink interval and the uplink interval symmetry that arrive downstream 5e get final product.Do like this, in the XY cross section, whole clothoids of describing of surperficial 5p.

Perhaps, also can describe clothoid, remainder and describe the shape that the mode of other curves such as circular arc is regulated teat 35 with the part of surperficial 5p.For example, shown in the XY sectional view of Figure 17 B, make between the Lead-In Area of clothoid, that is to say up to the 5th section, from the position corresponding with upstream extremity 5f up to 1/2nd of height H corresponding positions.From the 5th section to the 10th section, just begin to comprise summit TP from the position corresponding with 1/2nd of height H ₁The first half describe with circular arc.As long as the flat site of fin 30 and the bottom of teat 35 gently are connected, just can be inhibited when air A hides upstream extremity 5f, in the rapid effect that reduces of this upstream extremity 5f flow velocity.In addition, the interval of the clothoid shown in Figure 17 B also can be other easement curves (curves that the curvature radius of a circle changes continuously), for example the sine curve or the cubic parabola that have illustrated of front.

Certainly, the curve that surperficial 5p describes in above-mentioned XY cross section does not contain flex point between upstream extremity 5f and summit TP1, is advantage during the shape of regulating teat 35 yet.(Figure 16 B) excellent performance when containing flex point, and (Figure 16 A) punching press easily when not containing flex point promptly have and make easy and so on advantage.For example, in above-mentioned XY cross section, the surperficial 5p of teat 35 also can be with arc representation from corresponding to the position of upstream extremity 5f via summit TP ₁Shape up to the whole interval of downstream 5e.

In addition, preferably with surperficial 5p vertical with the interarea of this fin 30 and comprise in the cross section of minor axis, just in the YZ cross section, describe the mode of easement curves such as sine curve or clothoid, regulate the shape of teat 35.More preferably with surperficial 5p vertical with the interarea of this fin 30 and comprise summit TP ₁Arbitrary section in describe the mode of easement curve, regulate the shape of teat 35.Do like this, just can be suppressed the effect that flow velocity reduces to greatest extent, and, can induce the air A of covering to heat-transfer pipe 2 more swimmingly at teat 35.

Like this, the shape of teat 35 can be depicted in upstream extremity 5f and summit TP with surperficial 5p vertical with the interarea of fin 30 and comprise in the cross section of oval minor axis or major axis ₁Between comprise the curve of flex point mode regulate.Do like this, can expect to be suppressed at the effect that the flow velocity on the teat 35 reduces.Also can be with surperficial 5p vertical with the interarea of fin 30 and comprise summit TP ₁Arbitrary section in describe to comprise the mode of the curve of flex point, the shape of regulating teat 35.

On the other hand, if surperficial 5p describes not contain the curve of flex point, just make fin 30 easily.That is, can be with surperficial 5p vertical with the interarea of fin 30 and comprise summit TP ₁Arbitrary section in describe not contain the mode of the curve of flex point, the shape of regulating teat 35.

Then, the effect to the fin tube type heat exchanger 1 of present embodiment describes.

As shown in figure 18, arrive on the interarea of air A fin 30 from be directed to of leading edge 30p of fin 30, just be directed to fin tube type heat exchanger 1 with the main surface parallel of fin 30 and with the direction of longitudinal direction quadrature.Because dispose heat-transfer pipe 2 in the mode that connects fin 30, so air A avoids heat-transfer pipe 2 and flows.In addition, owing on fin 30, be formed with teat 35, so air A has the tendency of avoiding teat 35 and flowing.In other words, teat 35 is to heat-transfer pipe 2 induced air A.Consequently, between teat 35 and heat-transfer pipe 2, form the air stream AF that flow velocity is enhanced.When flow velocity increased, pyroconductivity improved.Near the side of the heat-transfer pipe 2 that especially dots in Figure 18 pyroconductivity improves, and therefore, can make the heat of the cold-producing medium that flows in the heat-transfer pipe 2 move to air A effectively.Simultaneously, contact the leading edge effect that produces, the effect that is suppressed at the development of boundary layer of teat 35, air with the upstream extremity 5f of teat 35 to the mobile effect of bringing that reduces dead water region DS in the rear of heat-transfer pipe 2 based on air A, improve the heat transfer property of fin tube type heat exchanger 1.In addition, as mentioned above, teat 35 is adjusted to and suppresses the shape that the pressure loss increases as much as possible.Wait the result of the Computer Simulation carry out according to inventor, if be 1 o'clock with the pressure loss of the heat exchanger of existing wave-shaped fins, the pressure loss of present embodiment is 0.91, and is about little by 10%.

On the other hand, in order to compare, as shown in figure 19, can consider between the first heat-transfer pipe 2A and the second heat-transfer pipe 2B, to be formed with two teat 205a with oval mound shape, the fin 203 of 205b with the present invention.Each teat 205a, the diameter of equal value of 205b (being scaled the bowlder that area equates, its diameter of a circle) is less than the outer diameter D of heat-transfer pipe 2.One teat 205a forms the air stream AF that flow velocity is enhanced to the first heat-transfer pipe 2A induced air A between this teat 205a and the first heat-transfer pipe 2A ₁Similarly, another teat 205b forms the air stream AF that flow velocity is enhanced to the second heat-transfer pipe 2B induced air A between this teat 205b and the second heat-transfer pipe 2B ₂In addition, between a teat 205a and another teat 205b, also form the air stream AF that flow velocity is enhanced ₃

But, the air stream AF between teat 205a and the teat 205b ₃Be distant from heat-transfer pipe 2A, the air-flow of the position of 2B, therefore and heat-transfer pipe 2A, near the air current A F the 2B ₁, AF ₂Compare, little to the contribution degree of the raising of heat transfer property.So do, can think, be formed with a side of the teat 35 of large-size as the present invention, than forming two teat 205a, 205b is more effective.

(embodiment 5)

Fin tube type heat exchanger 1 can preferentially adopt the fin 31 shown in the vertical view of Figure 20.The configuration of heat-transfer pipe 2 and size etc. are identical with embodiment 4.Difference is to adopt the teat 51 with cima shape to substitute the teat 35 with oval mound shape.

As shown in figure 20, the teat 51 that is formed at fin 31 surfaces sees that on the plane profile 51s is for circular.That is to say that to the imaginary plane parallel with fin 31 time, the picture that reveals is for circular with teat 51 orthographic projections on this imaginary plane.In addition, the diameter of a circle d that describes of the profile 51s of teat 51 ₃Outer diameter D greater than heat-transfer pipe 2.

Towards not becoming problem, and can similarly determine with the situation on oval mound by the position as the teat 35 (Figure 14) with oval mound shape for teat 51 with cima shape.That is, teat 51 can form apart from the center C 1 of the first heat-transfer pipe 2A and center C 2 equidistant positions of the second heat-transfer pipe 2B.Specifically, can be with summit TP ₂The mode that overlaps in the vertical binary imaginary plane MD of line segment C1 C2 of the center C 2 of the center C 1 that will link the first heat-transfer pipe 2A with beeline and the second heat-transfer pipe 2B is determined the position of teat 51 with respect to the first heat-transfer pipe 2A and the second heat-transfer pipe 2B.In addition, the upstream extremity 51f of preferred teat 51 is positioned at the upstream extremity 2f upstream side of heat-transfer pipe 2, and downstream 51e is positioned at the downstream 2e downstream of heat-transfer pipe 2.Such design is identical with situation about having illustrated in embodiment 4.

In addition, height and surface configuration about teat 51, also and the situation of the teat 35 that in embodiment 4, has illustrated same, for example, can in the XY cross section, describe sine curve (Figure 16 A with surperficial 51p, Figure 16 B) or the mode of clothoid easement curves such as (Figure 17 B), regulate the shape of teat 51.In addition, can be with surperficial 51p at upstream extremity 51f and summit TP ₂Between describe to comprise the mode of the curve of flex point, the shape of regulating teat 51.Certainly, the curve described of surperficial 51p also can be at upstream extremity 51f and summit TP ₂Between do not contain flex point.

In addition, in embodiment 4 and embodiment 5 and embodiment 1 similarly, suppose upstream extremity 5f, imaginary line that 51f extends along directions X and the summit TP by teat 35,51 from teat 35,51 ₁, TP ₂During along imaginary line that the Z direction is extended, then between two imaginary lines, be formed with the air guiding to first inclined plane of the first heat-transfer pipe 2A side with second inclined plane of air guiding to the second heat-transfer pipe 2B side.

As Figure 14 and shown in Figure 20, the width of teat 35,51 is from upstream extremity 5f, the 51f 5b of portion that partways, and 51b increases, and from middle part 5b, 51b is to downstream 5e, 51e reduces.The upstream extremity 5f of teat 35,51,51f are positioned at each heat-transfer pipe 2A, the center C 1 of 2B, C2 upstream side.The middle part 5b of teat 35,51,51b are positioned at each heat-transfer pipe 2A, the downstream 2e upstream side of 2B.The diameter d of equal value of teat 35,51 is more than the diameter D of heat-transfer pipe 2.In addition, the height of teat 35,51 also can also can also can equal spacing of fin less than spacing of fin greater than spacing of fin.According to such structure, can obtain the effect same with embodiment 1.

(embodiment 6)

Fin tube type heat exchanger 1 can preferentially adopt the fin 32 shown in the vertical view of Figure 21.The configuration of heat-transfer pipe 2 and size etc. are identical with embodiment 4.Difference is at the teat 35 that is formed at the prostatitis and is formed between another teat 35 of rank rear, is formed with second teat 53 of surface area less than these teats 35,35.Strictly say, from the short transverse vertical (Y direction) vertical view Figure 21 when fin 32 is seen on the plane with interarea, the diameter d of second teat 53 ₄Outer diameter D less than heat-transfer pipe 2.In addition, the teat 35,35 of second teat 53 and prostatitis and rank rear is outstanding to equidirectional.

According to the fin 30 (Figure 14) of embodiment 4, producing between the teat 35 of the teat 35 in prostatitis and rank rear has some spaces.If form second teat 53 in this some space, just can enlarge heat transfer area.Especially, the zone that is formed with second teat 53 utilizes the effect of the teat 35 in prostatitis to become the passage of the air A that flow velocity is enhanced, and therefore, the air A that makes flow velocity be enhanced contacts with second teat 53 energetically, thus, can realize the further raising of heat transfer property.Second teat 53 so also can have the cima shape as present embodiment, also can have oval mound shape.

In addition, as shown in figure 22, the teat 35 that replaces oval mound, in the prostatitis and rank rear form the teat 51 of cima shape, 51, and between the teat 51 of the teat 51 in prostatitis and rank rear, form the fin 33 of surface area less than second teat 53 of these teats 51,51, based on reason same as described above, also be preferred.

(embodiment 7)

The teat 35,51,53 that has illustrated in the embodiment 4～6 is all to form to the outstanding mode of same direction.But as mentioning in the enforcement mode 1, this neither be necessary.Promptly, shown in Figure 23 A and Figure 23 B, can preferably adopt to mix to be formed with to the outstanding teat 35 of the first interarea 34j side (the table side of fin 34) with to the fin 34 of the outstanding teat 35 ' of the second interarea 34k side (inboard of fin 34) fin as fin tube type heat exchanger 1.

As mentioned above, mix ground and form the different teat 35 of projected direction, in the time of 35 ', have following effect.At first, when manufacturing is formed with the fin of all identical teat of projected direction, carry out following operation: the operation that metallic plate is cut into the size of regulation; Processing is used to dispose the operation of the through hole of heat-transfer pipe; On metallic plate, form the operation of teat by punch process.The projected direction of teat is limited under the unidirectional situation, and in the operation that forms teat, metallic plate deforms, and produces crooked on the fin that finally obtains.When producing this bending, in the assembling heat exchanger, spacing of fin becomes uneven sometimes, produces the position deviation of through hole, thereby makes heat-transfer pipe not insert swimmingly.

With respect to this, when manufacturing is formed with the fin 34 of the different teat of projected direction 35,35 ', be that the metallic plate as fin 34 is carried out punch process from the two sides.By carry out punch process from the two sides, can make distortion balance in table, thereby can prevent crooked generation.

In addition, teat 35,35 ' except making the projected direction difference, and size and position can be designed as having illustrated in the enforcement mode 4.These teat 35,35 ' preferred amounts are identical and alternately form along column direction.In this case, can obtain the high crooked effect that prevents.Certainly, also this structure and other all embodiments can be made up.

In addition, also can preferably adopt the fin of the fin 36 shown in Figure 24 A and Figure 24 B as fin tube type heat exchanger 1.Fin 36 is fins of having used fin 32 illustrated in fig. 21, is formed at the teat 35 in prostatitis and is formed at the projected direction of second teat 53 ' between the teat 35 of rank rear opposite with the projected direction of the teat 35,35 that front and back are big. Big teat 35,35 is all to form to the side-prominent mode of the first interarea 36j of fin 36, and the second little teat 53 ' is to form to the side-prominent mode of the second interarea 36k of fin 36.Do like this and also can fully be prevented crooked effect.

Embodiment 1～7 can be implemented freely to make up in the scope that does not break away from main idea of the present invention.For example, second teat 53 about middle explanations such as Figure 21 can be applicable to other all embodiments.

More than Shuo Ming fin tube type heat exchanger 1 can be applied to heat pump assembly that objects such as air or water are heated or cool off.As shown in figure 25, heat pump assembly 70 possesses: the compressor 71 of compressed refrigerant, make by the radiator 72 of the refrigerant loses heat after compressor 71 compression, make the expansion valve 73 that expands by the cold-producing medium after radiator 72 heat radiations, the evaporimeter 74 of the cold-producing medium evaporation after will expanding by expansion valve 73.Compressor 71, radiator 72, expansion valve 73, evaporimeter 74 are connected by pipe arrangement 75, form refrigerating circuit.Also can adopt positive-displacement expansion engine to replace expansion valve 73.Radiator 72 and evaporimeter 74 constitute as comprising the parts of fin tube type heat exchanger 1 of the present invention.

As shown in figure 26, above-mentioned heat pump assembly 70 can be applied to aircondition 80 or water heater 90.For example, the aircondition 80 of heat-pump-type possesses and should be disposed at indoor indoor unit 81 and form refrigerating circuit and should be disposed at outdoor outdoor unit 82 with this indoor unit 81.This aircondition 80 has the function of cooling and warming, and in when refrigeration with when heating, the loop direction of cold-producing medium is opposite.During refrigeration, 81 the heat exchanger that constitutes indoor unit becomes evaporimeter, and the heat exchanger that constitutes outdoor unit 82 becomes radiator.When heating, 81 the heat exchanger that constitutes indoor unit becomes radiator, and the heat exchanger that constitutes outdoor unit 82 becomes evaporimeter.Consider the frosting problem when heating, the heat exchanger of outdoor unit 82 usefulness preferably adopts fin tube type heat exchanger 1 of the present invention.When using heat-production functions, the heat exchanger that constitutes outdoor unit 82 is worked as the evaporimeter 74 of heat pump assembly 70, therefore, and especially in easy frosting in winter.But,, owing to be not formed with having cut as illustrating among Figure 37, therefore can not produce because of frosting and cause the problem that fin obstruction, rate of heat exchange reduce and so on significantly according to fin tube type heat exchanger 1 of the present invention.

In addition, as shown in figure 26, finned hot water machine 90 possesses heat pump unit 91 and hot-water storage jar unit 92.Heat pump unit 91 comprises the heat exchanger 73 of bearing the effect that water is heated and from the heat exchanger 74 of open air heat absorption.Latter's heat exchanger 74 can preferably adopt fin tube type heat exchanger 1 of the present invention.

Embodiment

Utilize Computer Simulation that the characteristic that has adopted fin tube type heat exchanger shown in Figure 20 is investigated.Specifically, the heat exchanger (embodiment 1～3) that has adopted the fin that is formed with the teat with cima shape is carried out Computer Simulation.In addition, the existing heat exchanger (comparative example 1) that has adopted wave-shaped fins is also carried out same Computer Simulation.Characteristic by the Computer Simulation investigation is flow velocity, nusselt number, pyroconductivity and the pressure loss of air.In addition, Off Le one エ Application ト ア ジ ア パ シ Off イ Star Network (FluentAsia Pacific) society's system " Fluent Ver.6 " is used in Computer Simulation, implements under the following conditions.

The condition that＜embodiment 1～3 and comparative example 1 are common 〉

Fin size: 16.94mm (flow direction of air) * 7.65mm (column direction)

Fin thickness: 0.1mm

Spacing of fin: 1.06mm

The external diameter of heat-transfer pipe: 5.0mm

The internal diameter of heat-transfer pipe: 4.0mm

Front wind speed Vair:1m/sec

The condition of＜embodiment 1 〉

The shape of teat: the cima that cos curve (90 °≤X≤90 °) forms

The diameter of teat: 6.0mm

The height of teat: 1.0mm

The condition of＜embodiment 2 〉

The shape of teat: the cima that cos curve (180 °≤X≤180 °) forms

The diameter of teat: 6.0mm

The height of teat: 1.0mm

The condition of＜embodiment 3 〉

The shape of teat: the cima that clothoid forms

The diameter of teat: 6.0mm

The height of teat: 1.0mm

The condition of＜comparative example 1 〉

Shape: waveform

The difference of height of rib and paddy: 1.0mm

The computer artificial result of embodiment 1～3 and comparative example 1 is shown in Figure 27～Figure 30 and table 2.Figure 27 is the result of embodiment 1, and Figure 28 is the result of embodiment 2, and Figure 29 is the result of embodiment 3, and Figure 30 is the result of comparative example 1.Among Figure 27～Figure 30, A figure expression nusselt number distributes, B figure expression velocity flow profile.Hollow arrow among the figure is represented the flow direction of air.

(table 2)

At first, by Figure 30 A as can be known, in the heat exchanger of the comparative example 1 that has adopted wave-shaped fins, the zone that nusselt number is big be defined to the leading edge of fin and heat-transfer pipe near.With respect to this, in the heat exchanger of embodiment 1～3, by Figure 27 A～Figure 29 A as can be known, the zone that nusselt number is big be not only the leading edge of fin and heat-transfer pipe near, and the surface of teat also enlarges.It is closely related that the pyroconductivity of the heat exchanger of such fact and so-called embodiment 1～3 is higher than result pyroconductivity, shown in the table 2 of the heat exchanger that has used wave-shaped fins.Nusselt number is and the proportional numerical value of pyroconductivity that the big more pyroconductivity that means of nusselt number is high more.

In addition, shown in Figure 30 B, in the heat exchanger of the comparative example 1 that has used wave-shaped fins, the big zone of flow velocity is distributed near the heat-transfer pipe in the mode of crossing over rib.Can think that such velocity flow profile has the effect that makes the side expansion downstream of the big zone of nusselt number.In this respect, the result with embodiment 1～3 is consistent.That is, by Figure 27 B～Figure 29 B as can be known, in the heat exchanger of embodiment 1～3, between heat-transfer pipe and teat, also be distributed with the big zone of flow velocity.In addition, on air is fully flowed through the rear this point of heat-transfer pipe, embodiment 1～3 and comparative example 1 basically identical.

In addition, each schemes the value of the velocity flow profile of B for the centre position between fin and fin.Under the situation that the spacing of fin of wave-shaped fins and fin of the present invention equates, it is significantly poor that velocity flow profile can not occur.But the factor that heat transfer property is improved mainly is that the boundary layer of fin surface is thin and heat-transfer pipe flow velocity on every side is bigger.On these two principal elements show that nusselt number distributes.

Like this, according to heat exchanger of the present invention, in the surface boundary layer attenuation of teat, in addition, the flow velocity between teat and the heat-transfer pipe increases, and thus, can realize the pyroconductivity than the heat exchanger excellence of having used wave-shaped fins.And as shown in table 2, the heat exchanger of embodiment 1～3 all has the pressure loss littler than the pressure loss of the existing heat exchanger that has used wave-shaped fins.

Secondly, under the following conditions, the heat exchanger (embodiment 4) that has used fin shown in Figure 14, the heat exchanger (embodiment 5) that has used fin shown in Figure 22 and the heat exchanger (comparative example 2) that used second wave-shaped fins have been carried out same Computer Simulation.

The condition that＜embodiment 4,5 and comparative example 2 are common 〉

Fin size: 27.0mm (air-flow direction) * 10.5mm (column direction)

Fin thickness: 0.1mm

Spacing of fin: 1.49mm

The external diameter of heat-transfer pipe: 7.0mm

The internal diameter of heat-transfer pipe: 5.8mm

Front wind speed Vair:1m/sec

The condition of＜embodiment 4 〉

The shape of teat: the oval mound that cos curve (90 °≤X≤90 °) forms

Teat towards: major axis is parallel with the flow direction of air

The major diameter of teat: 13.0mm

The minor axis of teat: 10.0mm

The height of teat: 0.765mm

The condition of＜embodiment 5 〉

The shape of first teat: the cima that cos curve (90 °≤X≤90 °) forms

The diameter of first teat: 10mm

The height of first teat: 0.765mm

The shape of second teat: the cima that cos curve (90 °≤X≤90 °) forms

The diameter of second teat: 5.7mm

The height of second teat: 0.765mm

The condition of＜comparative example 2 〉

Shape: waveform

The difference of height of rib and paddy: 1.49mm

The computer artificial result of embodiment 4,5 and comparative example 2 is shown in Figure 31～Figure 33 and table 3.Figure 31 is the result of embodiment 4, and Figure 32 is the result of embodiment 5, and Figure 33 is the result of comparative example 2.

(table 3)

By Figure 33 A, Figure 33 B we can say the heat exchanger of the comparative example 2 that has adopted the wave-shaped fins different with comparative example 1 size as can be known, demonstrates the identical tendency of heat exchanger of the comparative example 1 of making peace greatly.By Figure 31 A, Figure 31 B has used the heat exchanger of embodiment 4 of the fin that is shaped as oval mound of teat to demonstrate the tendency identical with the heat exchanger of embodiment 1～3 as can be known.As shown in table 3, with regard to the heat exchanger of embodiment 4, the heat exchanger of its pyroconductivity and comparative example 2 is roughly equal, and the pressure loss is better than the heat exchanger of comparative example 2.But can think,, pyroconductivity fully can be brought up to the degree equal with embodiment 1～3 by regulating the shape and size of teat.

On the other hand, according to the heat exchanger of embodiment 5, by Figure 32 A, Figure 32 B produces the big zone of flow velocity as can be known between teat in prostatitis (first teat) and the heat-transfer pipe, and, in the surperficial nusselt number increase of second teat.That is to say, can obtain making the effect of boundary layer attenuation on the surface of second teat.As shown in table 3, with regard to the heat exchanger of embodiment 5, the heat exchanger of its pyroconductivity and comparative example 2 is roughly equal, and the pressure loss is better than the heat exchanger of comparative example 2.But can think,, pyroconductivity fully can be brought up to the degree equal with embodiment 1～3 by regulating the shape and size of first teat and/or second teat.

Claims (33)

1, a kind of fin tube type heat exchanger, it makes the first fluid and second fluid carry out heat exchange, wherein, possesses:

A plurality of fins, its space in order to be formed for described first fluid is circulated, and the mutual empty standard width of a room in an old-style house is every being arranged in parallel;

A plurality of heat-transfer pipes, it connects described a plurality of fin and is used to make described second fluid flow,

Described a plurality of heat-transfer pipe comprises first heat-transfer pipe and second heat-transfer pipe of the column direction alignment arrangements of the regulation of intersecting along the flow direction with described first fluid,

On described column direction, described first heat-transfer pipe is adjacent mutually with described second heat-transfer pipe,

Described fin has teat, and described teat is formed between described first heat-transfer pipe and described second heat-transfer pipe, and with described first fluid lead described first heat-transfer pipe side and the described second heat-transfer pipe side,

From the diameter of equal value of the described teat of axially seeing of described heat-transfer pipe is more than the external diameter of described heat-transfer pipe.

2, fin tube type heat exchanger as claimed in claim 1, wherein,

The width of the described column direction of described teat, along the flow direction of described first fluid, the upstream extremity portion of the partwaying increase from described teat reduces to downstream from described middle part,

Between the described upstream extremity of described teat and described middle part, be formed with first inclined plane and second inclined plane, described first inclined plane to the described first heat-transfer pipe inclination tiltedly and with the described first fluid described first heat-transfer pipe side that leads, described second inclined plane to the described second heat-transfer pipe inclination tiltedly and with the described first fluid described second heat-transfer pipe side that leads

The described upstream extremity of described teat is positioned at the position of leaning on upstream side than the center of described first and second each heat-transfer pipe,

The described middle part of described teat is positioned at the position of leaning on upstream side than the downstream of described first and second each heat-transfer pipe.

3, fin tube type heat exchanger as claimed in claim 1, wherein,

Described heat-transfer pipe and described teat are arranged in zigzag respectively from axially seeing of described heat-transfer pipe.

4, fin tube type heat exchanger as claimed in claim 1, wherein,

Described teat forms pyramidal.

5, fin tube type heat exchanger as claimed in claim 4, wherein,

Described teat forms the quadrangular pyramid shape.

6, fin tube type heat exchanger as claimed in claim 1, wherein,

Described teat forms coniform or oval taper.

7, fin tube type heat exchanger as claimed in claim 1, wherein,

Described teat forms cima shape or oval mound shape.

8, fin tube type heat exchanger as claimed in claim 1, wherein,

Establishing length on the flow direction at described first fluid of described teat is L and the projecting height of establishing described teat when being H, and L/H is greater than 5.5.

9, fin tube type heat exchanger as claimed in claim 1, wherein,

The occupied area of the described teat on described each fin is more than 43% and below 73%.

10, fin tube type heat exchanger as claimed in claim 1, wherein,

Described teat is under the situation of orthographic projection to the plane parallel with described a plurality of fins, and the picture that shows on described plane is shown as circle or ellipse,

The area of the picture of the described teat that shows on described plane is greater than the sectional area of described heat-transfer pipe.

11, fin tube type heat exchanger as claimed in claim 1, wherein,

Between described first heat-transfer pipe and described second heat-transfer pipe, only be formed with a described teat.

12, fin tube type heat exchanger as claimed in claim 10, wherein,

On the flow direction of described first fluid, the upstream extremity of described teat is positioned at the position than the leading edge of the close described a plurality of fins of upstream extremity of described first heat-transfer pipe and described second heat-transfer pipe.

13, fin tube type heat exchanger as claimed in claim 10, wherein,

Described teat is shown as ellipse with the picture that shows on described plane, and minor axis that should ellipse and described first heat-transfer pipe and the described second heat-transfer pipe parallel mode of described column direction of arranging determine its towards.

14, fin tube type heat exchanger as claimed in claim 13, wherein,

Described teat is comprised in the line segment that will link the center of described first heat-transfer pipe and the center of described second heat-transfer pipe with beeline with long axis of ellipse and carries out mode in the vertical binary imaginary plane, determines the position with respect to described first heat-transfer pipe and described second heat-transfer pipe.

15, fin tube type heat exchanger as claimed in claim 13, wherein,

Described teat vertical with the interarea of described a plurality of fins and comprise the mode of describing curve in the cross section of the minor axis of described ellipse or major axis, is regulated its shape with the surface.

16, fin tube type heat exchanger as claimed in claim 15, wherein,

Described curve contains flex point between the upstream extremity of described teat and summit.

17, fin tube type heat exchanger as claimed in claim 15, wherein,

Described curve does not contain flex point between the upstream extremity of described teat and summit.

18, fin tube type heat exchanger as claimed in claim 13, wherein,

Described teat vertical with the interarea of described a plurality of fins and comprise in the cross section of the minor axis of described ellipse or major axis and describe sinusoidal mode, is regulated its shape with the surface.

19, fin tube type heat exchanger as claimed in claim 18, wherein,

Described surface is with identical with the sine curve of Y=Kcos (X) { K: constant ,-180 °≤X≤180 ° } expression.

20, fin tube type heat exchanger as claimed in claim 18, wherein,

Described surface is with identical with the sine curve of Y=Kcos (X) { K: constant ,-90 °≤X≤90 ° } expression.

21, fin tube type heat exchanger as claimed in claim 10, wherein,

Described teat is described the mode of clothoid with the surface in parallel with the flow direction of described first fluid and vertical with the interarea of described a plurality of fins cross section, regulate its shape.

22, fin tube type heat exchanger as claimed in claim 1, wherein,

At the height of establishing described teat is H and the parallel distance of establishing described a plurality of fins from being spacing of fin when being FP, regulates the height of described teat, to satisfy (FP/4)≤H≤FP.

23, fin tube type heat exchanger as claimed in claim 10, wherein,

Described teat is shown as circle with the picture that shows on described plane, and the surperficial mode of describing curve in the cross section vertical with the interarea of described a plurality of fins, regulates its shape.

24, fin tube type heat exchanger as claimed in claim 23, wherein,

Described curve contains flex point between the upstream extremity of described teat and summit.

25, fin tube type heat exchanger as claimed in claim 23, wherein,

Described curve does not contain flex point between the upstream extremity of described teat and summit.

26, fin tube type heat exchanger as claimed in claim 10, wherein,

Described teat is shown as circle with the picture that shows on described plane, and the surface in the cross section vertical, describe sinusoidal mode with the interarea of described a plurality of fins, regulate its shape.

27, fin tube type heat exchanger as claimed in claim 26, wherein,

Described surface is with identical with the sine curve of Y=Kcos (X) { K: constant ,-180 °≤X≤180 ° } expression.

28, fin tube type heat exchanger as claimed in claim 26, wherein,

Described surface is with identical with the sine curve of Y=Kcos (X) { K: constant ,-90 °≤X≤90 ° } expression.

29, fin tube type heat exchanger as claimed in claim 1, wherein,

Two row before and after described heat-transfer pipe is configured to zigzag, that is, and the prostatitis and the rank rear parallel of the leading edge of close described a plurality of fins with this prostatitis,

Be disposed between two adjacent described heat-transfer pipes of described rank rear, also be formed with another teat that has and be formed at the identical shaped and same size of described teat between the two adjacent described heat-transfer pipes that are configured in described prostatitis.

30, fin tube type heat exchanger as claimed in claim 29, wherein,

At the described teat that is formed at described prostatitis be formed between described another teat of described rank rear, be formed with the second little teat of these teats of surface area ratio.

31, a kind of fin, it is used for the described fin tube type heat exchanger of claim 1.

32, a kind of heat pump assembly, it possesses:

Compressor, its compressed refrigerant;

Radiator, it makes by the refrigerant loses heat after the described compressor compresses;

Expansion mechanism, it makes by the cold-producing medium behind the described radiator heat-dissipation and expands;

Evaporimeter, it makes by the cold-producing medium evaporation after the described expansion mechanism expansion,

At least one side of described evaporimeter and described radiator comprises the described fin tube type heat exchanger of claim 1.

33, heat pump assembly as claimed in claim 32, wherein,

At least described evaporimeter comprises the described fin tube type heat exchanger of claim 1.

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