CN102032819A - Heat exchanger and apparatus for storing articles using same - Google Patents

Abstract

The invention discloses a heat exchanger comprising a plurality of plate fins which are in parallel arrangement and allow air flow among them; a refrigerant pipe which penetrates the plate fins at a slightly right angle, is provided with a fluid to flow therein, and is configured in grid shape relative to the air flow. In addition, the plate fins are separated into rows with respect to the refrigerant pipe. In such a completely independent plate-fin type heat exchanger, through holes of heat conduction are disposed to block the rim from the refrigerant pipe to the plate fins and are parallel to the flowing direction of the air flow. The construction of the invention can not only increase properties of the heat exchanger, but also give efficient defrosting.

Description

Heat exchanger and use the article stowage arrangement of this heat exchanger

Technical field

The article stowage arrangements such as freezer that the present invention relates to a kind of fully independently fin tube type heat exchanger and be equipped with this heat exchanger.

Background technology

Recent years, based on effectively utilizing earth resource, the viewpoints such as power consumption of control household appliances are in the employed heat exchanger of refrigeration plant, to miniaturization and high efficiency and raising frosting resistance and defrosting efficiency, the requirement that improves aspects such as dust tightness further increases.

Generally speaking, in freezer etc., utilize boundary layer leading edge effect to be easy to realize high heat exchange performance, therefore, adopt the fully independently heat exchanger of fin tube type of a kind of what is called that connects one or two refrigerant pipe on by row a slice plate wing separately.The relevant look-ahead technique documentation ﹠ info of this invention for example has Japanese kokai publication sho 60-2409876 communique (following conduct " patent documentation 1 ").

A kind of heat exchanger that can obtain the so-called helical fin tubular type of boundary layer leading edge effect equally, is also arranged.The relevant look-ahead technique documentation ﹠ info of this invention for example has TOHKEMY 2004-12119 communique (following conduct " patent documentation 2 ").

Figure 25 is the stereogram of the existing fully independently fin tube type heat exchanger put down in writing in above-mentioned patent documentation 1.As shown in figure 25, fully independently fin tube type heat exchanger 401 adopts a refrigerant pipe 403 is connected by row plate wing 402 separately, and these refrigerant pipe 403 bending machining are formed the creep structure of shape of snake.

Therefore, the ora terminalis area of the plate wing 402 that intersects with the air-flow of arrow 404 directions is many, and therefore, boundary layer leading edge effect is obvious, can improve the performance of heat exchanger 401.

Figure 26 is the front elevation of the existing helical fin tubular type heat exchanger put down in writing in above-mentioned patent documentation 2.As shown in figure 26, a kind of fin 413 with band shape of helical fin tubular type heat exchanger 411 general employings is coiled on the refrigerant pipe 412, the structure of the shape of then refrigerant pipe 412 bending machining formation snake being creeped.

Therefore, observe, be wound onto the circle that fin 413 on the refrigerant pipe 412 presents path from the direction of principal axis of refrigerant pipe 412, and, the bending diameter of refrigerant pipe 412 also can be dwindled.Not only can form small-sized like this and shape flexibly, and can save the space is set.

In addition, owing to the fin 413 that is wound onto on the refrigerant pipe 412 forms circle, therefore, can guarantee the enough intervals between fin 413 adjacent on row or the section direction, also can prevent the dust accumulation, dust tightness is good.

But the plate wing 402 of disclosed fully independently fin tube type heat exchanger 410 is rectangles in the above-mentioned patent documentation 1, and the distance of periphery and refrigerant pipe 403 and different.

So, heat exchanger 401 is being used as under the situation of refrigerator, because of boundary layer leading edge effect, in a large amount of frostings of fin section such as ora terminalis.

And this frosting begins to take place from weather side, according to the ventilation cell of the mutual plate wing 402 of blocking every mode spread.Therefore, become blocked state between the plate wing 402, ventilate and hindered, so be difficult to obtain the heat exchange action of downwind side.

Therefore, though few in the downwind side frosting, can obtain heat exchange action,, also have the such problem of running that must defrost.

This defrosting running is to utilize Defrost heater to wait heating and cooling agent pipe 403, and be used to from the heat-transfer effect and the cold-producing medium in the refrigerant pipe 403 of refrigerant pipe 403 convection effects (below, this convection effects is called " thermal siphon effect ") come heating plate wing 402, thus melt the operation of frosting.But, as mentioned above, be the peripheral distance at center and different with the refrigerant pipe 403 of plate wing 402, therefore, in the defrosting running, uneven phenomenon takes place easily to melt.So, carrying out once more under the situation of cooling operation, will exist and can't bring into play refrigerating capacity, power consumption increases, and the frequency of the running that defrosts increases such problem.

In addition, though by prolonging defrosting time, can carry out above-mentioned defrost operation effectively,, along with the running of Defrost heater prolongs, the power consumption that refrigeration plants such as Defrost heater also occurred increases such problem.And break period of cooling operation prolongs, and the temperature that cooled object occurred raises, the quality of storage article such problem that might be damaged.

The close refrigerant pipe 412 of the ora terminalis of the fin 413 of the heat exchanger 411 of disclosed helical fin tubular type in above-mentioned patent documentation 2, and the distance between the ora terminalis of fin 413 and the refrigerant pipe 412 is the same substantially.Therefore; though the defrosting effect from the heat-transfer effect of refrigerant pipe 413 and thermal siphon effect is obvious, because the interval between fin 413 adjacent on column direction and the section direction is big; therefore, appearing at refrigerant pipe 413 through regular meeting is the such problem of the unusual frosting in position at center.In addition, compare with fin tube type heat exchanger, its fin surface is long-pending little, therefore, is difficult to realize high performance, therefore, is not suitable for use in the such problem of cooler with regard to existence.

Summary of the invention

The present invention is with solving above-mentioned existing technical task, and its purpose is, a kind of heat exchange performance and defrost performance that not only improves when being used as cooler is provided, and can significantly reduce the heat exchanger of the power consumption of refrigeration plant.

Heat exchanger of the present invention comprises: a plurality of be arranged in parallel and air communication is crossed therebetween rectangular slab wing; Connect described plate wing and fluid refrigerant pipe in internal flow, described refrigerant pipe is the clathrate setting with respect to described air-flow, described plate wing with respect to described refrigerant pipe by row separately, in the heat exchanger of this fully independently fin tube type, setting is used for interdicting from the heat conducting through hole of described refrigerant pipe to the ora terminalis parallel with the flow direction of air-flow on the part of described plate wing.

According to this structure, can suppress through hole to the frosting between the plate wing end.And, even, near under the state that stops up, also can between plate wing end, ventilate between the plate wing at through hole in the frosting of refrigerant pipe periphery.In addition, not only can carry out with direction of ventilation on the heat exchange of back segment plate wing, continue to utilize heat exchange action, and can suppress the defrosting running.

Heat exchanger of the present invention comprises: a plurality of be arranged in parallel and air communication is crossed therebetween plate wing; Connect described plate wing and fluid refrigerant pipe in internal flow, described refrigerant pipe is the clathrate setting with respect to air-flow, described plate wing with respect to described refrigerant pipe by row separately, in the heat exchanger of this fully independently fin tube type, the ora terminalis of the described plate wing that intersects with described air-flow forms, with described air-flow meet at right angles the line that intersects be standard shaft and with the different waveform shape of the distance of described standard shaft.

According to this structure, not only can bring into play the boundary layer leading edge effect of fin and the turbulent flow facilitation effect of air-flow, and can improve the heat conduction efficiency of air end.Therefore, can improve the performance of heat exchanger, reduce the power consumption of the refrigeration plant that has carried this heat exchanger.In addition, can also improve the power consumption of refrigeration plant when reducing defrosting from the heat-transfer effect of refrigerant pipe and the defrost performance of thermal siphon effect.

Article stowage arrangement of the present invention comprises: the article storeroom that is formed by insulated space; Compressor, condenser, decompressor and evaporimeter are linked the freeze cycle that forms ring-type by pipe arrangement; The cooling flow of described evaporimeter is sent into air blast in the described article storeroom, and in this stowage arrangement, described evaporimeter is described heat exchanger.

According to this structure, not only can improve refrigeration performance, and can reduce the power consumption of article stowage arrangement.

Description of drawings

Fig. 1 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 1.

Fig. 2 is the profile along the 2A-2A line of Fig. 1 of the heat exchanger in the embodiments of the present invention 1.

Fig. 3 is the enlarged drawing that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 1.

Fig. 4 is the profile along the 4A-4A line of Fig. 3 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 1.

Fig. 5 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 2.

Fig. 6 is the profile along the 6A-6A line of Fig. 5 of the heat exchanger in the embodiments of the present invention 2.

Fig. 7 is the enlarged drawing that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 2.

Fig. 8 is the profile along the 8A-8A line of Fig. 7 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 2.

Fig. 9 is the schematic diagram of the structure of the article stowage arrangement in the expression embodiments of the present invention 3.

Figure 10 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 4.

Figure 11 is the profile along the 11A-11A line of Figure 10 of the heat exchanger in the embodiments of the present invention 4.

Figure 12 is the enlarged drawing that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 4.

Figure 13 is the profile along the 13A-13A line of Figure 12 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 4.

Figure 14 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 5.

Figure 15 is the profile along the 15A-15A line of Figure 14 of the heat exchanger in the embodiments of the present invention 5.

Figure 16 is the enlarged drawing that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 5.

Figure 17 is the profile along the 17A-17A line of Figure 16 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 5.

Figure 18 is the profile along the 18A-18A line of Figure 16 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 5.

Figure 19 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 6.

Figure 20 is the profile along the 20A-20A line of Figure 19 of the heat exchanger in the embodiments of the present invention 6.

Figure 21 is the enlarged drawing that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 6.

Figure 22 is the profile along the 22A-22A line of Figure 21 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 6.

Figure 23 is the profile along the 23A-23A line of Figure 21 that constitutes the plate wing of the heat exchanger in the embodiments of the present invention 6.

Figure 24 is the schematic diagram of the structure of the article stowage arrangement in the expression embodiments of the present invention 7.

Figure 25 is the stereogram of existing fully independently fin tube type heat exchanger.

Figure 26 is the front elevation of existing helical fin tubular type heat exchanger.

The specific embodiment

Below, with reference to accompanying drawing an embodiment of the invention are described.In following accompanying drawing, for identical member, mark identical symbol, therefore, omit its explanation sometimes.In addition, the present invention is not limited to this embodiment.

(embodiment 1)

Fig. 1 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 1.Fig. 2 is the profile along the 2A-2A line of Fig. 1 of the heat exchanger in this embodiment 1.Fig. 3 is the enlarged drawing that constitutes the plate wing of the heat exchanger in this embodiment 1.Fig. 4 is the profile along the 4A-4A line of Fig. 3 that constitutes the plate wing of the heat exchanger in this embodiment 1.

In Fig. 1 to Fig. 4, fully independently fin tube type heat exchanger 1 is by being that the refrigerant pipe 2 made of raw material and a plurality of plate wings 3 of adopting identical materials to make constitute with the high aluminium of pyroconductivity, copper.

Plate wing 3 forms the identical shape and the rectangle of same size, for example forms rectangle, and is separated configuration along the airflow direction shown in the arrow X.On this plate wing 3, be provided with: the hole 3a that refrigerant pipe 2 connects wherein; The fin cannula portion 3b (with reference to Fig. 4) that around the 3a of this hole, gives prominence to along direction of principal axis; And along the through hole 3c that extends with the slightly parallel direction of the minor face 3e of plate wing 3.

The hole 3a of through hole 3c is set at the position of the summary of plate wing 3 near the below as shown in Figure 3, and forms in the distance side farthest with refrigerant pipe 2, is used for interdicting the heat conduction from refrigerant pipe 2, and it also can be slot-shaped or blind shaped.In addition, being not limited to rectilinear form, also can be slightly crooked shape.

The arrangement that plate wing 3 is reversed is up and down alternately adopted in the configuration of cutting apart of the airflow direction in the plate wing 3.

Like this, refrigerant pipe 2 is continuous and nonoverlapping cancellate configuration on airflow direction at the configuration relation on the airflow direction, and through hole 3c also is configured in along the staggered up and down position of airflow direction.Adopt the heat exchanger 1 of this structure to assemble, therefore, omit its explanation according to well-known process sequence.

Below, the situation the when heat exchanger 1 with above-mentioned structure is used as cooler describes.

At first, according to cooling operation, air-flow flows along the direction shown in the arrow X, and begins heat exchange after plate wing 3 contacts.At this moment, by the edge 3d acquisition boundary layer leading edge effect of plate wing 3, heat exchange action obtains promoting, thereby can obtain good refrigeration.

In present embodiment 1, because refrigerant pipe 2 is the clathrate setting with respect to air-flow, therefore, shown in arrow Y, the refrigerant pipe 2 that the air-flow that runs into refrigerant pipe 2 is had a circular cross section separately contacts with the refrigerant pipe 2 of leeward continuously, therefore, can carry out more effective heat exchange.

Then, if proceed cooling operation, so, and will frosting on whole heat exchanger 1, particularly a large amount of frostings on the edge 3d of the plate wing 3 of the periphery of refrigerant pipe 2 and air-flow contact.Meanwhile, leading portion one side from air-flow X is stopped up between adjacent plate wing 3, and the ventilation between the adjacent plate wing 3 of the back segment of flowing through is controlled gradually.

But, in present embodiment 1, in plate wing 3, form through hole 3c with refrigerant pipe 2 a distance side farthest, therefore, utilize the heat-blocking action of this through hole 3c, the heat exchange of the part 3f far away apart from refrigerant pipe 2 in the plate wing 3 is few, is difficult to frosting.

So near the edge 3d frosting refrigerant pipe 2, refrigerant pipe 2 under the situation that wind path between the plate wing 3 takes place to stop up, is compared with through hole 3c and to be positioned at more that the part 3f of distant positions also can become bypass because of frosting degree is few.So just can guarantee the ventilation of the plate wing 3 of a certain amount of back segment of flowing through, the performance degradation when suppressing frosting.Not only can continue to utilize heat exchange action like this, and can improve the frosting resistance performance, reduce the defrosting number of times.

Particularly through hole 3c is positioned at staggered up and down position along airflow direction, and above-mentioned bypass is formed uniformly up and down heat exchanger 1, therefore, can suppress the too early defrosting running that causes because of frosting is uneven.

In addition,, so just can obtain high initial stage refrigeration performance if dwindle size as the width 3g of the through hole 3c of hot conduction orientation, on the other hand, the decline of frosting resistance performance.On the contrary, if increase the width dimensions of through hole 3c, so, the initial stage refrigeration performance is low, on the other hand, can obtain good frosting resistance performance.Equally, in through hole 3c, the length 3h by changing through hole 3c or apart from the distance of the configuration through hole 3c of refrigerant pipe 2, the so also characteristic that can obtain to be similar to.

Therefore, by regulating, set size (width 3g or length 3h) and the position of through hole 3c, the state of formed bypass in the time of so just controlling frosting.Thus, according to the design of above-mentioned through hole 3c, can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

In addition, continuing frosting, for example utilize (not shown) such as Defrost heater to melt under the situation of frost from lower heating refrigerant pipe 2, the plate wing 3 of heat exchanger 1, also the defrosting of various piece is carried out in the convection effects of cold-producing mediums such as the heat conduction by this heating generation, thermal siphon effect and the convection current of heated air-flow etc.

In addition, because along with away from Defrost heater, the heat liter of heat exchanger, promptly thermal capacity increases, and the latent heat of frost increases and the defrosting initial stage does not almost have convection current, and therefore, the defrosting effect that thermosyphon action takes place is big.

The edge 3d of frosting utilizes the thermal siphon effect of the heated cold-producing medium of the refrigerant pipe 2 that is heated by Defrost heater, its inside of flowing through, and conducts heat to the edge of plate wing 3 3d from refrigerant pipe 2, defrosts.At this moment, therefore through hole 3c control, not only can improve the heat effect of refrigerant pipe 2 peripheries, and can shorten defrosting time to the heat conduction of the distance end farthest of plate wing 3.

That is, heat exchanger of the present invention is the heat exchanger of fin tube type fully independently, and it comprises a plurality of be arranged in parallel and air communication is crossed therebetween rectangular slab wing, slightly connected this plate wing and the fluid refrigerant pipe in internal flow with meeting at right angles.In heat exchanger of the present invention, refrigerant pipe is the clathrate setting with respect to air-flow, and the plate wing with respect to refrigerant pipe by row separately.And also setting is used for interdicting from the heat conducting through hole of refrigerant pipe to ora terminalis on the part of this plate wing.

According to this structure, be clathrate and dispose refrigerant pipe, make the air-flow of the heat exchanger of flowing through become disorderly, the boundary layer leading edge effect according to its turbulence effects and plate wing can improve heat exchange performance.In addition, by setting be used for interdicting to have and refrigerant pipe to the heat conducting through hole of the ora terminalis of the airflow direction almost parallel relation of plate wing, thereby suppress through hole to the frosting between the plate wing end.Like this, even, near under the state that stops up, also can between plate wing end, ventilate between the plate wing at through hole in the frosting of refrigerant pipe periphery.Not only can carry out like this with airflow direction on the heat exchange of back segment plate wing, continue to utilize heat exchange action, and the frequency of the running that can suppress to defrost.

According to the direction of through hole along air current flow, the mode that is positioned at upper end one side and lower end one side alternately disposes the plate wing.

According to this structure, bypass balancedly forms respectively in the top and bottom of heat exchanger, not only can improve the frosting resistance performance like this, and can prolong continuous cooling duration of runs.

As mentioned above, the heat exchanger of the fully independently fin tube type in the present embodiment 1 not only can be realized high-performance, and can defrost effectively.

(embodiment 2)

Fig. 5 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 2.Fig. 6 is the profile along the 6A-6A line of Fig. 5 of the heat exchanger in this embodiment 2.Fig. 7 is the enlarged drawing that constitutes the plate wing of the heat exchanger in this embodiment 2.Fig. 8 is the profile along the 8A-8A line of Fig. 7 that constitutes the plate wing of the heat exchanger in this embodiment 2.

In Fig. 5 to Fig. 8, fully independently fin tube type heat exchanger 1 is by being that the refrigerant pipe 12 made of raw material and a plurality of plate wings 13 of adopting identical materials to make constitute with the high aluminium of pyroconductivity, copper

Plate wing 13 forms identical shape and identical size, and along the airflow direction separate configuration shown in the arrow X.On this plate wing 13, be provided with: the hole 13a (Fig. 7) that refrigerant pipe 12 connects wherein; The fin cannula portion 13b (Fig. 8) that around the 13a of this hole, gives prominence to towards direction of principal axis; And be the circular-arc through hole 13c at center with hole 13a.

The hole 13a of through hole 13c is set at the position of the summary of plate wing 13 near the below as shown in Figure 7, and forms in the distance side farthest with refrigerant pipe 12.Through hole 13c is used for stopping the heat conduction from refrigerant pipe 12, and it also can be slot-shaped or blind shaped.In addition, through hole 13c is not limited to circular-arc, also can be along the linearity that extends with the slightly parallel direction of airflow direction.

Plate wing 13 roughly form waveform (below be called " waveform ") with the slightly rectangular edge 13d of airflow direction.

Because this waveform is to be that a plurality of round 13e at center is the shape of keynote with hole 13a, therefore, with the line L that intersects that slightly meets at right angles of the air-flow shown in the arrow X be standard shaft, on the airflow direction apart from a1, a2 formation arc track, form different shapes simultaneously.Therefore, on edge 13d, has nearest protuberance ora terminalis 13f, range line L the recess ora terminalis 13g farthest of range line L alternately apart from a2 apart from a1.In addition, the profile of center zero to the edge 13d of each hole 13a is the size of fixing apart from r (except the part that each circle 13e intersects).

The separate configuration of plate wing 13 on airflow direction makes plate wing 13 counter-rotating alternately up and down as shown in Figure 6, and the recess ora terminalis of the edge 13d of adjacent plate wing 13 is mutually opposed with the protuberance ora terminalis 13f of edge 13d across the distance of regulation.

Like this, the configuration relation of the refrigerant pipe 12 on the airflow direction is continuous and nonoverlapping cancellate configurations on airflow direction, and through hole 13c also is configured in along the staggered up and down position of airflow direction.According to the mutually arranged opposite of raised part ora terminalis 13f with recess ora terminalis 13g, dwindled the size of the plate wing 13 on the airflow direction, realized the miniaturization of heat exchanger 11.

Adopt the assembling of the heat exchanger 11 of above-mentioned structure to assemble, therefore, omit its explanation according to well-known processing step.

Below, the heat exchanger 11 of the above-mentioned structure situation as cooler is described.

At first, according to cooling operation, air-flow flows along the direction shown in the arrow X, contacts with plate wing 13 and begins heat exchange.At this moment, the edge 13d of plate wing 13 forms protuberance ora terminalis 13f and the continuous waveform shape of recess ora terminalis 13g alternating expression, therefore, is that the plate wing of straight line is compared with the edge in past, adopts the contact site of this shape and air-flow many, and contact area is big.Like this, boundary layer leading edge effect increases, and heat exchange action obtains promoting, can increase refrigerating capacity.

In addition, shown in arrow Y, the refrigerant pipe 12 that the air-flow that runs into refrigerant pipe 12 is had a circular cross section separately, therefore, in sealing region alpha as the refrigerant pipe rear portion formation air-flow of the opposing face that contact with air-flow of refrigerant pipe 12.

But in present embodiment 2, because refrigerant pipe 12 is the clathrate configuration in the face of air-flow, this separated air-flow runs into the refrigerant pipe 12 of leeward, therefore, can carry out more effective heat exchange.

Below, if continue cooling operation, so, will frosting on whole heat exchanger 11, particularly in the fin end of the plate wing 13 of the periphery of refrigerant pipe 12 and air-flow contact, i.e. a large amount of frostings on the edge of waveform shape 13d.Meanwhile, because of the frosting between adjacent plate wing 3 of one side of the leading portion from air-flow X is stopped up, be controlled gradually to the ventilation of back segment.

But, in present embodiment 2, in plate wing 13, form through hole 13c with refrigerant pipe 2 a distance side farthest, therefore, utilize the heat-blocking action of this through hole 13c, the heat exchange of the part 13h far away apart from refrigerant pipe 12 in the plate wing 13 is few, is difficult to frosting.

So near the edge 13d frosting of the waveform shape refrigerant pipe 12, refrigerant pipe 12 under the situation that wind path between the adjacent plate wing 13 takes place to stop up, also can guarantee to flow to the ventilation of the plate wing 13 of back segment.Its reason is, compares with through hole 13c to be positioned at more that the part of distant positions becomes bypass less because of frosting degree.So just can guarantee to flow to the ventilation of the plate wing 13 of back segment.

Performance degradation in the time of not only can suppressing frosting like this, and can continue to utilize heat exchange action, improve the frosting resistance performance, reduce the defrosting number of times.

Particularly through hole 13c is positioned at staggered up and down position along airflow direction, and above-mentioned bypass is formed uniformly up and down heat exchanger 11, therefore, can suppress the too early defrosting running that causes because of frosting is uneven.

In addition, if dwindle the size of the width 13j of through hole 13c, so just can obtain high initial stage refrigeration performance, on the other hand, the frosting resistance performance descends.On the contrary, if increase the size of the width 13j of through hole 13c, so, the initial stage refrigeration performance is low, on the other hand, can obtain good frosting resistance performance.

Equally, in through hole 13c, by change length 13k or with the distance of refrigerant pipe 12, the so also characteristic that can obtain to be similar to.

Therefore, by regulating and set size and the position of through hole 13c, the state of formed bypass in the time of so just controlling frosting.Thus, can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

In addition, continuing frosting, for example utilize (not shown) such as Defrost heater to melt under the situation of frost, the defrosting that also heat that produces by this heating is conducted, various piece is carried out in the convection current of thermal siphon effect such as the convection effects of cold-producing medium and heated air-flow etc. from lower heating refrigerant pipe 12, the plate wing 13 of heat exchanger 1.

In addition, because along with away from Defrost heater, the heat liter of heat exchanger, promptly thermal capacity increases, and the latent heat of frost increases and the defrosting initial stage does not almost have convection current, and therefore, the defrosting effect of thermal siphon effect performance is big.

The edge 13d of the waveform shape of frosting utilizes the thermal siphon effect of the heated cold-producing medium of the refrigerant pipe 12 that is heated by Defrost heater, its inside of flowing through, and conducts heat to the edge of the waveform shape of plate wing 13 13d from refrigerant pipe 12.At this moment, in present embodiment 2, the refrigerant pipe 12 in the plate wing 13 is the same substantially apart from r to edge 13d's, therefore, can heat the edge 13d of waveform shape unanimous on the wholely.So just the defrosting of edge 13d can be carried out unanimous on the wholely, thereby it is uneven to suppress defrosting.And, because through hole 13c suppresses the heat conduction to the end of plate wing 13, therefore, can improve the heat effect of refrigerant pipe 12 peripheries, and can shorten the required defrosting time of effective defrosting effect.

In addition, unanimous on the whole to reduce on the uneven this point of defrosting in the distance that makes itself and refrigerant pipe 12, the waveform shape of the edge 13d of plate wing 13 preferably is the shape of keynote with the circle.But, consider the easy degree of the molded work of fin stamped metal and the intensity of plate wing 13 etc., the waveform shape of edge 13d also can be the straight line waveform that triangle or polygonal form.

That is, heat exchanger of the present invention is the heat exchanger of fin tube type fully independently, and it comprises a plurality of be arranged in parallel and air communication is crossed therebetween plate wing, connected this plate wing and the fluid refrigerant pipe in internal flow.In heat exchanger of the present invention, the refrigerant pipe relative wind is the clathrate setting, and the relative refrigerant pipe of plate wing by row separately.And the line that the fin ora terminalis of the plate wing that intersects with air-flow of heat exchanger of the present invention forms to intersect with air-flow is a standard shaft, and with the different waveform shape of the distance of standard shaft.

According to this structure, because of the complications configuration of refrigerant pipe, make the air-flow of the heat exchanger of flowing through become disorderly, form the roughly boundary layer leading edge effect of the plate wing of waveform shape according to its turbulence effects and ora terminalis, can improve heat exchange performance.

In addition, the fixed distance of the ora terminalis of refrigerant pipe and plate wing.According to this structure, not only can be much the samely to the heat and the heat of its inner cold-producing medium of flowing through of the periphery conduction refrigerant pipe of plate wing, and can suppress heat conducting inequality.Like this, at this heat exchanger during as the defrost operation of cooler, can be much the samely to the periphery of plate wing conduct the heat of heated refrigerant pipe and this refrigerant pipe of flowing through in the heat of thermal siphon effect of cold-producing medium.Not only can defrost effectively like this, and can shorten defrosting time.

In addition, dispose a plurality of plate wings, and dispose to opposed mode according to the protuberance ora terminalis of the formation waveform shape of the back segment plate wing of the recess ora terminalis of the formation waveform shape of plate wing and plate wing along the direction of air current flow.

According to this structure, not only can guarantee the proportional spacing of the plate wing on the direction of air current flow, and can dwindle heat exchanger.

In addition, on the part of plate wing, also be provided with and be used for stopping from the heat conducting through hole of refrigerant pipe to the ora terminalis parallel with the direction of air current flow.

According to this structure, through hole is the heat conduction of baffle board wing partly, postpones the frosting time, forms bypass simultaneously under the state of heat exchanger frosting, can carry out heat exchange by this bypass.So just can improve the frosting resistance performance, reduce the defrosting number of times.Therefore, can reduce the power consumption of the equipment that has carried this heat exchanger.

According to the direction of aforementioned through hole along air current flow, the mode that is positioned at upper end one side and lower end one side alternately disposes the plate wing.

According to this structure, bypass balancedly forms to prevent frosting in the upper end of heat exchanger one side and lower end one side, therefore, not only can improve the frosting resistance performance, and can prolong the continuous cooling duration of runs of heat exchanger.

As mentioned above, the heat exchanger of the fully independently fin tube type in the present embodiment 2 not only can be realized high-performance, and can defrost effectively.

(embodiment 3)

Fig. 9 is the schematic diagram of the structure of the article stowage arrangement in the expression embodiments of the present invention 3.Structure when herein, the heat exchanger 11 that embodiment 2 is described is as the evaporimeter of cooler.

As shown in Figure 9, stowage arrangement main body 21 has front openings and centered on by heat-barrier material in inside the first storeroom 22a and the second storeroom 22b, have first 23a and second 23b of opening and closing with the first storeroom 22a and the second storeroom 22b corresponding opening 23c, 23d in front, they have thermal insulation.In addition, the first storeroom 22a and the second storeroom 22b are communicated with by service channel 24a, 24b.

Be provided with in the inside of stowage arrangement main body 21 by pipe arrangement with compressor 25, condenser 26, decompressor 27, link the freeze cycle that forms ring-types as the heat exchanger 11 of evaporimeter, heat exchanger 11 for example is configured among the first storeroom 22a.In addition, in the first storeroom 22a, shown in arrow 9A, be provided with the air blast 28 that the cold air that is cooled is circulated energetically in heat exchanger 11 in the first storeroom 22a.The second storeroom 22b utilizes the circulation by the part cold air shown in the arrow 9B of the first storeroom 22a of service channel 24a, 24b inflow to be cooled.

Therefore, stowage arrangement main body 21 is as illustrated in the embodiment 2, even adopt a kind of heat exchanger 11 frostings, also some is difficult to the structure of frosting.Therefore, even 21 frostings of stowage arrangement main body also suppress to enter immediately the defrosting running, the cooling operation that the number of times that defrosts is few can carry out effective cooling operation.Therefore, can obtain to suppress the article stowage arrangement of power consumption.

That is, article stowage arrangement of the present invention comprises: the article storeroom that is formed by insulated space; Compressor, condenser, decompressor and evaporimeter are linked the freeze cycle that forms ring-type by pipe arrangement; The cooling flow of evaporimeter is sent into air blast in the article storeroom.The evaporimeter of article stowage arrangement of the present invention is above-mentioned heat exchanger.

According to this structure, can reduce the defrosting number of times, thereby obtain stable heat exchange action, and can carry out effective cooling operation.Therefore, can obtain to suppress the article stowage arrangement of power consumption.

In present embodiment 3, the heat exchanger that adopts embodiment 2 structure as evaporimeter is illustrated, still, adopt the structure of the heat exchanger of embodiment 1, also can obtain same action effect.

(embodiment 4)

Figure 10 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 4.Figure 11 is the profile along the 11A-11A line of Figure 10 of the heat exchanger in this embodiment 4.Figure 12 is the enlarged drawing that constitutes the plate wing of the heat exchanger in this embodiment 4.Figure 13 is the profile along the 13A-13A line of Figure 12 that constitutes the plate wing of the heat exchanger in this embodiment 4.

In Figure 10 to Figure 13, fully independently fin tube type heat exchanger 101 is by being that the refrigerant pipe 102 made of raw material and a plurality of plate wings 103 of adopting identical materials to make constitute with the high aluminium of pyroconductivity, copper.

Plate wing 103 forms identical shape and identical size, and along the airflow direction separate configuration shown in the arrow X.On this plate wing 103, be provided with: the hole 103a that refrigerant pipe 102 connects wherein; The fin cannula portion 103b (with reference to Figure 13) that around the 103a of this hole, gives prominence to towards direction of principal axis; With hole 103a is the circular-arc through hole 103c at center; And circumferential rib 103h.This circumferential rib 103h processes by metal pattern, forms around the annular of the breakthrough part of refrigerant pipe 102.In other words, circumferential rib 103h is positioned at the periphery of hole 103a, and is outstanding towards the direction identical with fin cannula portion 103b.

The hole 103a of through hole 103c as shown in figure 12, be set at the position of the summary of plate wing 103 near the below, form in the distance side farthest with refrigerant pipe 102, be used for interdicting the heat conduction from refrigerant pipe 102, it also can be slot-shaped or blind shaped.

In addition, plate wing 103 roughly forms waveform with the slightly rectangular edge 103d of airflow direction.

Because this waveform is to be that a plurality of round 103e at center is the shape of keynote with hole 103a, therefore, with the line L that intersects that slightly meets at right angles of the air-flow shown in the arrow X be standard shaft, on the airflow direction apart from a1, a2 formation arc track, form different shapes simultaneously.Therefore, alternating expression has nearest protuberance ora terminalis 103f, the range line L recess ora terminalis 103g apart from a2 farthest apart from a1 of range line L on edge 103d.In addition, the profile of center zero to the edge 103d of each hole 103a is the size of fixing apart from r (except the part that each circle 103e intersects).

For the separate configuration of plate wing 103 on airflow direction, make plate wing 103 counter-rotating alternately up and down, the mode that the recess ora terminalis of the edge 103d in the adjacent plate wing 103 docks with protuberance ora terminalis 103f among the edge 103d across the distance of regulation disposes.

Like this, the configuration relation of the refrigerant pipe 102 on the airflow direction is continuous and nonoverlapping cancellate configurations on airflow direction, and through hole 103c also is configured in along the staggered up and down position of airflow direction.According to the mutually arranged opposite of raised part ora terminalis 103f with recess ora terminalis 103g, dwindled the size of the plate wing 103 on the airflow direction, realize the miniaturization of heat exchanger 101.

Adopt the assembling of the heat exchanger 101 of above-mentioned structure to assemble, therefore, omit its explanation according to well-known processing step.

Below, the heat exchanger 101 of the above-mentioned structure situation as cooler is described.

At first, according to cooling operation, air-flow flows along the direction shown in the arrow X, contacts with plate wing 103 and begins heat exchange.At this moment, the edge 103d of plate wing 103 forms protuberance ora terminalis 103f and the continuous waveform shape of recess ora terminalis 103g alternating expression, therefore, is that the plate wing of straight line is compared with the edge in past, and the contact site of this shape and air-flow is many, and contact area is big.Like this, boundary layer leading edge effect increases, and heat exchange action obtains promoting, can increase refrigerating capacity.

In addition, shown in the arrow Y among Figure 11, the refrigerant pipe 102 that the air-flow that runs into refrigerant pipe 102 is had a circular cross section separately, it is disorderly that air-flow becomes.By interflow once more behind the refrigerant pipe 102, therefore, in sealing region alpha as the refrigerant pipe rear portion formation air-flow of the opposing face that contact with air-flow of refrigerant pipe 102.

By near the refrigerant pipe 102 and the air-flow of plate wing 103 near surfaces shown in the dotted arrow Z among Figure 11, with the outstanding circumferential rib 103h collision that forms, form turbulent flow on the surface of plate wing 103, return the sealing region alpha at refrigerant pipe 102 rear portions then.Therefore, because of 102 pairs of air-flows of refrigerant pipe separately and the turbulent flow of circumferential rib 103h, a large amount of air-flows can return the sealing region alpha.Like this and the heat exchange of refrigerant pipe 102 obtain promoting, can increase refrigerating capacity.

Herein, circumferential rib 103h is preferably formed as around the continuous shape of refrigerant pipe 102, but, if consider the factors such as ponding in circumferential rib 103h when control defrosts, also can adopt and form separately shape of discharging the space or the roughly semicircular shape that partly centers on refrigerant pipe 102 in position.

If consider the flow direction of wind, so, circumferential rib 103h is the toroidal of curve preferably, still, according to the situations such as easy degree of making the fin metal pattern, also can be the polygonal that straight line links to each other.

If it is more than needed that the area of plate wing 103 has, so,, the diameter difference also can be set and form concentrically ringed a plurality of circumferential rib 103h in order to promote turbulence effects.

In present embodiment 4, refrigerant pipe 102 is the clathrate configuration towards air-flow, and therefore, this separated air-flow runs into the refrigerant pipe 102 of leeward, forms the sealing region alpha equally, therefore, can carry out more effective heat exchange.

Then, if proceed cooling operation, so, and will frosting on whole heat exchanger 101, particularly in the fin end of the plate wing 103 of the periphery of refrigerant pipe 102 and air-flow contact, i.e. a large amount of frostings on the edge of waveform shape 103d.

But, in present embodiment 4, in plate wing 103, form through hole 103c apart from refrigerant pipe 102 side farthest.Therefore, utilize the heat-blocking action of this through hole 103c, the heat exchange of the part far away apart from refrigerant pipe 102 in the plate wing 103 is few, is difficult to frosting.

So near the edge 103d frosting of the waveform shape refrigerant pipe 102, refrigerant pipe 102 under the situation that wind path between the plate wing 103 takes place to stop up, is compared with through hole 103c and to be positioned at more that the part of distant positions also becomes bypass less because of frosting degree.Like this, in heat exchanger 101, the performance degradation in the time of not only can suppressing frosting, and can improve the frosting resistance performance, reduce the defrosting number of times.

Particularly through hole 103c is positioned at staggered up and down position along airflow direction, and above-mentioned bypass balancedly forms at the upper-lower position of heat exchanger 101, therefore, can suppress because of the uneven running that defrosts prematurely that causes of frosting.

In addition, as illustrated in the enforcement mode 2, if dwindle the width dimensions of through hole 103c, so just can obtain high initial stage refrigeration performance, on the other hand, the frosting resistance performance descends.On the contrary, if increase the width dimensions of through hole 103c, so, the initial stage refrigeration performance is low, on the other hand, can obtain good frosting resistance performance.

Equally, in through hole 103c, the length by changing circular arc or with the distance of refrigerant pipe 102, the so also characteristic that can obtain to be similar to.

Therefore, by regulating, set size and the position of through hole 103c, the state of formed bypass in the time of so just controlling frosting.Thus, not only can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

In addition, continuing frosting, for example utilize (not shown) heating and cooling agent pipe 102, plate wing 103 such as Defrost heater to melt under the situation of frost, the defrosting that also heat that produces by this heating is conducted, various piece is carried out in the convection current of thermal siphon effect such as the convection effects of cold-producing medium and heated air-flow etc.

In addition, because along with away from Defrost heater, the heat liter of heat exchanger, promptly thermal capacity increases, and the latent heat of frost increases and the defrosting initial stage does not almost have convection current, and therefore, the defrosting effect of thermal siphon effect performance is big.

The edge 103d of the waveform shape of frosting utilizes the thermal siphon effect of the heated cold-producing medium of the refrigerant pipe 102 that is heated by Defrost heater, its inside of flowing through, and conducts heat to the edge of the waveform shape of plate wing 103 103d from refrigerant pipe 102.At this moment, in present embodiment 4, the refrigerant pipe 102 in the plate wing 103 is the same substantially apart from r to edge 103d's, therefore, can heat the edge 103d of waveform shape unanimous on the wholely.So just the defrosting of edge 103d can be carried out unanimous on the wholely, thereby it is uneven to suppress defrosting.Therefore, not only can defrost effectively, and can shorten defrosting time.

In addition, make with the distance of refrigerant pipe 102 unanimous on the wholely to reduce on the uneven this point of defrosting, the waveform shape of the edge 103d of plate wing 103 preferably is the shape of keynote with the circle.But according to the easy degree of the molded work of fin stamped metal and the intensity of plate wing 103 etc., it also can be the straight line waveform that triangle or polygonal form.

Heat exchanger of the present invention is the heat exchanger of fin tube type fully independently, and it comprises a plurality of be arranged in parallel and air communication is crossed therebetween plate wing, connected this plate wing and the fluid refrigerant pipe in internal flow.In heat exchanger of the present invention, refrigerant pipe is the clathrate setting with respect to air-flow, and the plate wing with respect to refrigerant pipe by row separately also is provided with around the circular circumferential rib of the breakthrough part of refrigerant pipe on the plate wing.The line that the fin ora terminalis of the plate wing that intersects with air-flow of heat exchanger of the present invention forms to intersect with air-flow is a standard shaft, and with standard shaft apart from different waveform shape.

According to this structure, because of the configuration of the clathrate of refrigerant pipe and form circumferential rib, make the air-flow of the heat exchanger of flowing through become disorderly, roughly form the boundary layer leading edge effect of the plate wing of waveform shape according to its turbulence effects and ora terminalis, can improve heat exchange performance.

In addition, the fixed distance at the edge of refrigerant pipe and plate wing.According to this structure, not only can conduct the heat of refrigerant pipe, the heat of its inner cold-producing medium of flowing through to the periphery of plate wing much the samely, and can suppress heat conducting inequality.Therefore, when the defrost operation of this heat exchanger when the cooler, can be much the samely to the periphery of plate wing conduct the heat of heated refrigerant pipe and this refrigerant pipe of flowing through in the heat of thermal siphon effect of cold-producing medium.Not only can defrost effectively like this, and can shorten defrosting time.

In addition, dispose a plurality of plate wings along the direction of air current flow, the opposed mode of protuberance ora terminalis that forms the formation waveform shape of plate wing and back segment plate wing according to the recess ora terminalis of the formation waveform shape of plate wing disposes.

According to this structure, not only can guarantee the proportional spacing of the plate wing on the direction of air current flow, and can dwindle heat exchanger.

In addition, on the part of plate wing, also be provided with and be used for interdicting from the heat conducting through hole of refrigerant pipe to ora terminalis.

According to this structure, through hole is the heat conduction of baffle board wing partly, can form bypass under the state of heat exchanger frosting simultaneously.So just can improve the frosting resistance performance, reduce the defrosting number of times.Therefore, can reduce the power consumption of the equipment that has carried this heat exchanger.

According to the direction of through hole along air current flow, the mode that is positioned at upper end one side and lower end one side alternately disposes the plate wing.

According to this structure, bypass balancedly forms in the top and bottom of heat exchanger, not only can improve the frosting resistance performance like this, and can prolong continuous cooling duration of runs.

As mentioned above, the heat exchanger of the fully independently fin tube type in the present embodiment 4 not only can be realized high-performance, and can defrost effectively.

(embodiment 5)

Figure 14 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 5.Figure 15 is the profile along the 15A-15A line of Figure 14 of the heat exchanger in this embodiment 5.Figure 16 is the enlarged drawing that constitutes the plate wing of the heat exchanger in this embodiment 5.Figure 17 is the profile along the 17A-17A line of Figure 16 that constitutes the plate wing of the heat exchanger in this embodiment 5.Figure 18 is the profile along the 18A-18A line of Figure 16 that constitutes the plate wing of the heat exchanger in this embodiment 5.

In Figure 14 to Figure 18, fully independently fin tube type heat exchanger 201 is by being that the refrigerant pipe 202 made of raw material and a plurality of plate wings 203 of adopting identical materials to make constitute with the high aluminium of pyroconductivity, copper.

Plate wing 203 forms identical shape and identical size, and along the airflow direction separate configuration shown in the arrow X.On this plate wing 203, be provided with: the hole 203a that refrigerant pipe 202 connects wherein; The fin cannula portion 203b (with reference to Figure 17) that around the 203a of this hole, gives prominence to towards direction of principal axis; And be the circular-arc through hole 203c at center with hole 203a.

The hole 203a of through hole 203c as shown in figure 16, be set at the position of the summary of plate wing 203, form, be used for stopping heat conduction from refrigerant pipe 202 in a distance side farthest with refrigerant pipe 202 near the below, therefore, also can be slot-shaped or blind shaped.

Plate wing 203 form the roughly shape of waveform with the slightly rectangular edge 203d of airflow direction.

Because this waveform is to be the shape of a plurality of round 203e at center as keynote with hole 203a, therefore, with the line L that intersects that slightly meets at right angles of the air-flow shown in the arrow X be standard shaft, the track apart from a1, a2 formation circular arc of airflow direction forms different shapes simultaneously.Therefore, alternating expression has nearest protuberance ora terminalis 203f, the range line L recess ora terminalis 203g apart from a2 farthest apart from a1 of range line L on edge 203d.In addition, the profile of center zero to the edge 203d of each hole 203a is the size of fixing apart from r (except the part that each circle 203e intersects).

For the separate configuration along airflow direction of plate wing 203, make plate wing 203 counter-rotating alternately up and down, the recess ora terminalis of the edge 203d of adjacent plate wing 203 is across the distance of regulation and the protuberance ora terminalis 203f configuration opposed to each other mutually of edge 203d.

Like this, the configuration relation of the refrigerant pipe 202 on the airflow direction is continuous and nonoverlapping cancellate configurations on airflow direction, and through hole 203c also is configured in along the staggered up and down position of airflow direction.According to disposing opposed to each other mutually of raised part ora terminalis 203f and recess ora terminalis 203g, dwindled the size of the plate wing 203 on the airflow direction, realize the miniaturization of heat exchanger 201.

In addition, the periphery of the breakthrough part of the refrigerant pipe 202 in plate wing 203 is provided with a plurality of incision rising portions 203h that center on refrigerant pipe 202 across the interval of regulation.This cuts rising portions 203h along airflow direction, forms on the direction that direction that upper reaches one side enlarges and a dirty side are dwindled respectively, and towards the direction of passing through of air-flow, intersects with predetermined angular and this air-flow.

Like this, the effect that particularly is positioned at the incision rising portions 203h of a dirty side is, assembles cooled dose of pipe 202 air-flows that separate, and makes it return sealing region alpha as the formed air-flow of a dirty side at refrigerant pipe 202 rear portions.

The shape of cutting rising portions 203h preferably according to along airflow direction from front and back and the mode that clips refrigerant pipe 202 up and down dispose so that the air-flow approximate equality return the rear portion of refrigerant pipe 202.But, fast at the flow velocity of air-flow, under the situations such as air drag increase, only also can adopt in front and back or the arrangement of a side up and down (a perhaps side of a front side, a rear side, a upside, a downside).If it is more than needed that the area of plate wing 203 has, so just can dispose multiple row and cut rising portions 203h.

Adopt the heat exchanger 201 of above-mentioned structure to assemble, therefore, omit its explanation according to well-known process sequence.

Below, the heat exchanger 201 of the above-mentioned structure situation as cooler is described.

At first, according to cooling operation, air-flow flows along the direction shown in the arrow X, contacts with plate wing 203 and begins heat exchange.At this moment, the edge 203d of plate wing 203 forms protuberance ora terminalis 203f and the continuous waveform shape of recess ora terminalis 203g alternating expression, therefore, with the edge in past be the plate wing of straight line compare and the contact site of air-flow many, contact area is big.Like this, the boundary layer leading edge effect of heat exchanger 201 increases, and heat exchange action obtains promoting, can increase refrigerating capacity.

In addition, shown in the arrow Y of Figure 15, the refrigerant pipe 202 that the air-flow that runs into refrigerant pipe 202 is had a circular cross section separately, it is disorderly that air-flow becomes.By converging once more behind the refrigerant pipe 202, therefore, in the sealing region alpha that forms air-flow as the refrigerant pipe rear portion of the opposing face that contacts with air-flow of refrigerant pipe 202.

The air-flow of the near surface by near the of refrigerant pipe 202 and plate wing 203 is shown in the dotted arrow Z among Figure 15, with after the outstanding incision rising portions 203h collision that forms in the surface of plate wing 203, become turbulent flow, return the sealing region alpha at refrigerant pipe 202 rear portions then.Therefore, because of 202 pairs of air-flows of refrigerant pipe separately and cut the turbulent flow that rising portions 203h is produced, a large amount of air-flows can return the sealing region alpha.Like this and the heat exchange of refrigerant pipe 202 obtain promoting, and can increase refrigerating capacity.

In addition, in present embodiment 5, refrigerant pipe 202 is the clathrate configuration with respect to air-flow, and therefore, this separated air-flow runs into the refrigerant pipe 202 of leeward, forms the sealing region alpha equally, therefore, can carry out more effective heat exchange.

Then, if proceed cooling operation, so, and will frosting on whole heat exchanger 201, particularly in the fin end of the plate wing 203 of the periphery of refrigerant pipe 202 and air-flow contact, i.e. a large amount of frostings on the edge of waveform shape 203d.

But, in present embodiment 5, in plate wing 203, form through hole 203c apart from refrigerant pipe 202 side farthest, therefore, utilize the heat-blocking action of this through hole 203c, the heat exchange of the part far away apart from refrigerant pipe 202 in the plate wing 203 is few, is difficult to frosting.

So frosting near the edge 203d of the waveform shape refrigerant pipe 202, the refrigerant pipe 202 under the situation that the wind path between the adjacent plate wing 203 takes place to stop up, also can be guaranteed the ventilation to back segment plate wing 203.Compare with through hole 203c and to be positioned at more that the part of distant positions becomes bypass less because of frosting degree, the performance degradation in the time of not only can suppressing frosting like this, and can improve the frosting resistance performance, reduce the defrosting number of times.

Particularly through hole 203c is positioned at staggered up and down position along airflow direction, and above-mentioned bypass balancedly forms up and down heat exchanger 201, therefore, can suppress the too early defrosting running that causes because of frosting is uneven.

In addition, if dwindle the width dimensions of through hole 203c, so just can obtain high initial stage refrigeration performance, on the other hand, the frosting resistance performance descends.On the contrary, if increase the width dimensions of through hole 203c, so, the initial stage refrigeration performance is low, on the other hand, can obtain good frosting resistance performance.

Equally, in through hole 203c, the length by changing circular arc or with the distance of refrigerant pipe 202, the so also characteristic that can obtain to be similar to.

Therefore, by regulating, set size and the position of through hole 203c, the state of formed bypass in the time of so just controlling frosting.Thus, not only can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

In addition, continuing frosting, for example utilize (not shown) heating and cooling agent pipe 202, plate wing 203 such as Defrost heater to melt under the situation of frost, the defrosting that also heat that produces by this heating is conducted, various piece is carried out in the convection current of thermal siphon effect such as the convection effects of cold-producing medium and heated air-flow etc.

In addition, along with away from Defrost heater, the heat liter of heat exchanger, promptly thermal capacity is big, and the latent heat of frost increases and the defrosting initial stage does not almost have convection current, and therefore, the defrosting effect of thermal siphon effect performance is big.

The edge 203d of the waveform shape of frosting utilizes the thermal siphon effect of the heated cold-producing medium of the refrigerant pipe 202 that is heated by Defrost heater, its inside of flowing through, and conducts heat to the edge of the waveform shape of plate wing 203 203d from refrigerant pipe 202.At this moment, in present embodiment 5, the refrigerant pipe 202 in the plate wing 203 is the same substantially apart from r to edge 203d's, therefore, can heat the edge 203d of waveform shape unanimous on the wholely.Like this, by carrying out the defrosting of edge 203d unanimous on the wholely, thereby it is uneven to suppress defrosting.Therefore, not only can defrost effectively, and can shorten defrosting time.

In addition, make with the distance of refrigerant pipe 202 unanimous on the wholely to reduce on the uneven this point of defrosting, the waveform shape of the edge 203d of plate wing 203 preferably is the shape of keynote with the circle.But, consider the easy degree of fin diel making, the intensity of plate wing 203 etc., also can be the straight line waveform that triangle or polygonal form.

Heat exchanger of the present invention is the heat exchanger of fin tube type fully independently, and it comprises a plurality of be arranged in parallel and air communication is crossed therebetween plate wing, connected this plate wing and the fluid refrigerant pipe in internal flow.In heat exchanger of the present invention, refrigerant pipe is the clathrate setting with respect to air-flow, and the plate wing with respect to refrigerant pipe by row separately also is provided with a plurality of incision rising portions around refrigerant pipe at the breakthrough part periphery of the refrigerant pipe of plate wing.The line that the fin ora terminalis of the plate wing that intersects with air-flow of heat exchanger of the present invention forms to intersect with air-flow is a standard shaft, and with the different waveform shape of the distance of standard shaft.

According to this structure, because of the configuration of the clathrate of refrigerant pipe makes the air turbulence of the heat exchanger of flowing through, form the roughly boundary layer leading edge effect of the plate wing of waveform shape according to its turbulence effects and edge, can improve heat exchange performance.And, utilize a plurality of incision rising portions around refrigerant pipe, make near the air-flow of refrigerant pipe of flowing through return the sealing zone of the air-flow that forms at the refrigerant pipe rear portion, promote the heat exchange of refrigerant pipe and air-flow, thereby can increase the heat-exchange capacity of cooling.

In addition, passing through on the direction of air current flow, the mode of angular cross according to the rules forms the incision rising portions.

According to this structure, on one side can suppress to cut the gas-flow resistance that rising portions produces, make this air-flow return the sealing zone, and can suppress the increase of cutting the flowing resistance that rising portions causes because of forming.

In addition, the fixed distance at the edge of refrigerant pipe and plate wing.According to this structure, not only can be much the samely to the heat and the heat of its inner cold-producing medium of flowing through of the periphery conduction refrigerant pipe of plate wing, and can suppress heat conducting inequality.Like this, when the defrost operation of this heat exchanger when the cooler, can be much the samely to the periphery of plate wing conduct the heat of heated refrigerant pipe and this refrigerant pipe of flowing through in the heat of thermal siphon effect of cold-producing medium.Not only can defrost effectively like this, and can shorten defrosting time.

In addition, dispose a plurality of plate wings along the direction of air current flow, and according to the formation of this plate wing roughly the opposed mode of protuberance ora terminalis of the formation waveform shape of the back segment plate wing of the recess ora terminalis of waveform shape and plate wing dispose.

According to this structure, not only can guarantee the proportional spacing of the plate wing on the direction of air current flow, and can dwindle heat exchanger.

In addition, setting is used for blocking from the extrorse heat conducting through hole of refrigerant pipe on the part of plate wing.

According to this structure, through hole is the heat conduction of barrier plate wing partly, can form bypass under the frosting state of heat exchanger simultaneously.So just can improve the frosting resistance performance, reduce the defrosting number of times.Therefore, can reduce the power consumption of the equipment that has carried this heat exchanger.

According to the direction of aforementioned through hole along air current flow, the mode that is positioned at upper end one side and lower end one side alternately disposes the plate wing.

According to this structure, bypass balancedly forms in the upper end of heat exchanger one side and lower end one side, therefore, not only can improve the frosting resistance performance, and can prolong continuous cooling duration of runs.

As mentioned above, the heat exchanger of the fully independently fin tube type in the present embodiment 5 not only can be realized high-performance, and can defrost effectively.

(embodiment 6)

Figure 19 is the stereogram of the fully independently fin tube type heat exchanger in the embodiments of the present invention 6.Figure 20 is the profile along the 20A-20A line of Figure 19 of the heat exchanger in this embodiment 6.Figure 21 is the enlarged drawing that constitutes the plate wing of the heat exchanger in this embodiment 6.Figure 22 is the profile along the 22A-22A line of Figure 21 that constitutes the plate wing of the heat exchanger in this embodiment 6.Figure 23 is the profile along the 23A-23A line of Figure 21 that constitutes the plate wing of the heat exchanger in this embodiment 6.

In Figure 19 to Figure 23, fully independently fin tube type heat exchanger 301 is by being that the refrigerant pipe 302 made of raw material and a plurality of plate wings 303 of adopting identical materials to make constitute with the high aluminium of pyroconductivity, copper.

Plate wing 303 forms identical shape and identical size, and along the airflow direction open configuration shown in the arrow X.This plate wing 303 has with respect to the airflow direction shown in the arrow X, along the outstanding protuberance 303h of the direction that stops this air-flow X and opposite direction (in present embodiment 6, for example form 3), so just form the roughly section of waveform, promptly form the corrugation shape.

On plate wing 303, be provided with: the hole 303a that refrigerant pipe 302 connects wherein; The fin cannula portion 303b (with reference to Figure 22) that around the 303a of this hole, gives prominence to towards direction of principal axis; And be the circular-arc through hole 303c at center with hole 303a.

The hole 303a of through hole 303c as shown in figure 21, be set at the position of the summary of plate wing 303, form, be used for interdicting heat conduction from refrigerant pipe 302 in a distance side farthest with refrigerant pipe 302 near the below, therefore, it also can be slot-shaped or blind shaped.In addition, through hole 303c is not limited to circular-arc, also can be along the linearity that extends with the direction of airflow direction almost parallel.

If consider the factors such as ponding of the frost that control is melted, so, also can be provided as the planar portions of discharging the space in position, perhaps change the angle of bend that forms protuberance 303h.

In addition, on plate wing 303,, also can adopt the shape that planar portions is set around fin cannula portion 303b according to factors such as the making of fin die are easy.

The corrugation shape still, is considered the factors such as wind speed of air-flow X by being bent to form the shape of the roughly waveform with 3 protuberance 303h for three times, according to employed condition, and also can be crooked more than 4 times.

In addition, the height H of protuberance 303h is preferably considered to set after the factors such as draining of fin material, fin die, air-flow wind speed, fin surface again.

Therefore, the corrugation shape is suitably set the height H of number of bends and protuberance 303h according to purposes of heat exchanger 301 etc., so just can control heat exchange performance.Thus, not only can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

Plate wing 303 roughly form waveform with the slightly rectangular edge 303d of airflow direction.

Because this waveform mainly is to be that a plurality of round 303e at center is the shape of keynote with hole 303a, therefore, with the line L that intersects that roughly meets at right angles of the air-flow shown in the arrow X be standard shaft, on the airflow direction apart from a1, a2 formation circular arc, form different shapes simultaneously.Therefore, alternating expression has nearest protuberance ora terminalis 303f, the range line L recess ora terminalis 303g apart from a2 farthest apart from a1 of range line L on edge 303d.In addition, the center O of each hole 303a is the size of fixing to the profile of edge 303d apart from r (except the part that each circle 303e intersects).

Herein, the plate wing 303 of corrugation shape is pre-formed the above-mentioned waveform that is keynote with a plurality of round 303e.Then, the order as the processing of the bending machining of carrying out the corrugation shape and hole 303a, fin cannula portion 303b so just can reduce the distortion of hole 303a, fin cannula portion 303b, forms effectively.

Therefore, in Figure 21, for convenience of explanation, be round with each circle 303e of plate wing 303, through hole 303c is also according to the record of the circular arc of certain curvature.But the plate wing 303 that is processed to the corrugation shape sees it is oval from the front, and through hole 303c also is the different circular arc continuum of states of curvature.

The separate configuration of the airflow direction in the plate wing 303 as shown in figure 20, make plate wing 303 up and down alternately the counter-rotating, the recess ora terminalis 303g of the edge 303d in the adjacent plate wing 303 across the regulation distance according to edge 303d in the opposed mode of protuberance ora terminalis 303f dispose.

Like this, the configuration relation of the refrigerant pipe 302 in the airflow direction is continuous and nonoverlapping cancellate configurations on airflow direction, and through hole 303c also is configured in along the staggered up and down position of airflow direction.Because the size in the air-flow directions X has so just been dwindled in the opposed configuration of raised part ora terminalis 303f and recess ora terminalis 303g, realize the miniaturization of heat exchanger 301.

Adopt the assembling of the heat exchanger 301 of above-mentioned structure to assemble, therefore, omit its explanation according to well-known processing step.

Below, the heat exchanger 301 of the above-mentioned structure situation as cooler is described.

At first, according to cooling operation, air-flow flows along the direction shown in the arrow X, contacts with plate wing 303 and begins heat exchange.At this moment, the edge 303d of plate wing 303 forms protuberance ora terminalis 303f and the continuous waveform shape of recess ora terminalis 303g alternating expression, therefore, is that the plate wing of straight line is compared with the past edge, and the contact site of this shape and air-flow is many, and contact area is big.Like this, boundary layer leading edge effect increases, and heat exchange action obtains promoting, can increase refrigerating capacity.

In addition, shown in the arrow Y of Figure 20, the refrigerant pipe 302 that the air-flow that runs into refrigerant pipe 302 is had a circular cross section separately, it is disorderly that air-flow becomes.By converging once more behind the refrigerant pipe 302, therefore, in the sealing region alpha that forms air-flow as the refrigerant pipe rear portion of the opposing face that contacts with air-flow of refrigerant pipe 302.

The air-flow of the near surface by plate wing 303 is processed formed protuberance 303h because of the corrugation of plate wing 303 and is become turbulent flow shown in the dotted arrow Z among Figure 20, walks around the sealing region alpha at refrigerant pipe 302 rear portions then.Therefore, because of 302 pairs of air-flows of refrigerant pipe separately and the turbulent flow that produced of protuberance 303h, a large amount of air-flows can return the sealing region alpha.Like this and the heat exchange of refrigerant pipe 302 obtain promoting, and can increase refrigerating capacity.

Therefore the 303h that plate wing 303 has a plurality of protuberances that produce by formation corrugation shape, compares with the smooth plate wing in past, can improve fin strength.Therefore, in manufacturing process and freezing equipment packaging technology, can reduce because of the distortion of operation heat exchanger caused plate wing 303 etc.

Even reduce the thickness of slab of plate wing 303, can guarantee that also it has and the in the past smooth identical intensity of plate wing, therefore, can reduce the fee of material of heat exchanger, thereby can reduce manufacturing cost.

In present embodiment 6, refrigerant pipe 302 is the clathrate configuration with respect to air-flow, and therefore, this separated air-flow runs into the refrigerant pipe 302 of leeward, can promote heat exchange, therefore, can carry out more effective heat exchange.

Then, if proceed cooling operation, so, and will frosting on whole heat exchanger 301, particularly in the fin end of the plate wing 303 of the periphery of refrigerant pipe 302 and air-flow contact, i.e. a large amount of frostings on the edge of waveform shape 303d.

But, in present embodiment 6, in plate wing 303, form through hole 303c apart from refrigerant pipe 302 side farthest, therefore, utilize the heat-blocking action of this through hole 303c, the heat exchange from refrigerant pipe 302 part far away in the plate wing 303 is few, is difficult to frosting.

So even frosting near the edge 303d of the waveform shape refrigerant pipe 302, the refrigerant pipe 302, the wind path between the adjacent plate wing 303 stops up, and also can guarantee the ventilation to the plate wing 303 of back segment.Compare with through hole 303c be positioned at distant positions more part because frosting degree becomes bypass less, the degradation in the time of not only can suppressing frosting like this, and can improve the frosting resistance performance reduces the defrosting number of times.

Particularly through hole 303c is positioned at staggered up and down position on airflow direction, and above-mentioned bypass balancedly forms up and down heat exchanger 301, therefore, can suppress the too early defrosting running that causes because of the frosting inequality.

In addition, if dwindle the width dimensions of through hole 303c, so just can obtain high initial stage refrigeration performance, on the other hand, the frosting resistance performance descends.On the contrary, if increase the width dimensions of through hole 303c, so, the initial stage refrigeration performance is low, on the other hand, can obtain good frosting resistance performance.

Equally, in through hole 303c, change circular arc length or with the distance of refrigerant pipe 302, the so also characteristic that can obtain to be similar to.

Therefore, by regulating, set size and the position of through hole 303c, the state of formed bypass in the time of so just controlling frosting.Thus, not only can constitute the heat exchanger of the suitable equipment that carries, and can improve the running efficiency of freezing equipment, reduce power consumption.

In addition, continuing frosting, for example utilize (not shown) such as Defrost heater to melt under the situation of frost, the defrosting that also heat that produces by this heating is conducted, various piece is carried out in the convection current of thermal siphon effect such as the convection effects of cold-producing medium and heated air-flow etc. from lower heating refrigerant pipe 302, the plate wing 303 of heat exchanger 301.

In addition, along with away from Defrost heater, the heat liter of heat exchanger, promptly thermal capacity is big, and the latent heat of frost increases, the defrosting initial stage almost do not have convection current, and therefore, the defrosting effect of thermal siphon effect performance is big.

The edge 303d of the waveform shape of frosting conducts heat to the edge of the waveform shape of plate wing 303 303d from refrigerant pipe 302 according to the thermal siphon effect of the heated cold-producing medium of the refrigerant pipe 302 that is heated by Defrost heater and its inside of flowing through.At this moment, in present embodiment 6, the refrigerant pipe 302 in the plate wing 303 is the same substantially apart from r to edge 303d's, therefore, can heat the edge 303d of waveform shape unanimous on the wholely.Like this, by carrying out the defrosting among the edge 303d unanimous on the wholely, thereby it is uneven to suppress defrosting.Therefore, not only can defrost effectively, and can shorten defrosting time.

In addition, roughly one show and reduce on the uneven this point of defrosting making with the distance of refrigerant pipe 302, the waveform shape of the edge 303d of plate wing 303 is the shape of keynote with circle, ellipse preferably.But according to the easy degree of fin diel making, the intensity of plate wing 303 etc., it also can be the straight line waveform that triangle or polygonal form.

Heat exchanger of the present invention is the heat exchanger of fin tube type fully independently, and it comprises that a plurality of heat exchangers are arranged in parallel and air communication is crossed therebetween plate wing, connected this plate wing and the fluid refrigerant pipe in internal flow.In heat exchanger of the present invention, refrigerant pipe is the clathrate setting with respect to air-flow, and the plate wing separates by row with respect to refrigerant pipe, and the plate wing forms the corrugation shape.The line that the fin ora terminalis of the plate wing that intersects with air-flow of heat exchanger of the present invention forms to intersect with air-flow is a standard shaft, and with the different waveform shape of the distance of standard shaft.

According to this structure, because of the clathrate configuration of refrigerant pipe and the corrugation shape of plate wing, make the air-flow of the heat exchanger of flowing through become disorderly, form the roughly boundary layer leading edge effect of the plate wing of waveform shape, can improve heat exchange performance according to its turbulence effects with the edge.And, because the plate wing is the corrugation shape, therefore, compare with common smooth fin, can improve the intensity of fin.Not only can reduce the fin thickness of slab like this, and can also reduce cost.

The corrugation shape of plate wing can adopt the shape that has at the outstanding protuberance of the direction of blocking air-flow.

According to this structure, can bring into play the turbulence effects that the corrugation shape produces to greatest extent, improve the performance of heat exchanger.

In addition, the fixed distance at the edge of refrigerant pipe and plate wing.According to this structure, not only can be much the samely to the heat and the heat of its inner cold-producing medium of flowing through of the periphery conduction refrigerant pipe of plate wing, and can suppress heat conducting inequality.Like this, when the defrost operation of this heat exchanger when the cooler, can be much the samely to the periphery of plate wing conduct the heat of heated refrigerant pipe and this refrigerant pipe of flowing through in the heat of thermal siphon effect of cold-producing medium.Not only can defrost effectively like this, and can shorten defrosting time.

In addition, dispose a plurality of plate wings along the direction of air current flow, the recess ora terminalis of the formation waveform shape of plate wing is mutually opposed with the protuberance ora terminalis of the formation waveform shape of the back segment plate wing of this plate wing.

According to this structure, not only can guarantee the proportional spacing of the plate wing on the air current flow direction, and can dwindle heat exchanger.

In addition, the extrorse heat conducting through hole of blocking refrigerant pipe is set on the part of plate wing.

According to this structure, through hole is the heat conduction of baffle board wing partly, can form bypass under the frosting state of heat exchanger simultaneously.So just can improve the frosting resistance performance, reduce the defrosting number of times.Therefore, can reduce the power consumption of the equipment that has carried this heat exchanger.

Dispose the plate wing according to aforementioned through hole along the mode that the direction alternating expression of air current flow is positioned at upper end one side and lower end one side.

According to this structure, bypass is formed uniformly in the upper end of heat exchanger one side and lower end one side, not only can improve the frosting resistance performance like this, and can prolong continuous cooling duration of runs.

As mentioned above, the heat exchanger of the fully independently fin tube type in the present embodiment 6 not only can be realized high-performance, and can defrost effectively.

(embodiment 7)

Figure 24 is the schematic diagram of the structure of the article stowage arrangement in the expression embodiments of the present invention 7.Illustrate that the heat exchanger 301 that adopts embodiment 6 is used as the structure of evaporimeter (cooler) herein.

In Figure 24, stowage arrangement main body 321 has front openings and centered on by heat-barrier material in inside the first storeroom 322a and the second storeroom 322b, have first 323a and second 323b of opening and closing with the first storeroom 322a and the second storeroom 322b corresponding opening in front, they have thermal insulation.

In addition, the first storeroom 322a and the second storeroom 322b are communicated with by service channel 324a, 324b.

Be provided with in the inside of stowage arrangement main body 321 by pipe arrangement compressor 325, condenser 326, decompressor 327, heat exchanger (evaporimeter) 301 are connected to the freeze cycle of ring-type, heat exchanger 301 for example is configured among the first storeroom 322a.In addition, in the first storeroom 322a, be provided with, shown in arrow 24A, the air blast 328 that the cold air that is cooled in heat exchanger 301 is circulated in the first storeroom 322a energetically.The second storeroom 322b is according to the circulation of a part of cold air that passes through the first storeroom 322a that service channel 324a, 324b flow into shown in the arrow 24B and cooled.

Therefore, stowage arrangement main body 321 is as illustrated in the embodiment 6, even owing to adopt heat exchanger 301 frostings, also some is difficult to the structure of frosting, therefore, suppress to enter immediately the defrosting running, the cooling operation that the number of times that defrosts is few so just can carry out effective cooling operation.

In addition, in present embodiment 7, the structure that the heat exchanger that adopts embodiment 6 is used as evaporimeter is illustrated, and still, adopts the structure of the heat exchanger of embodiment 5, also can obtain same action effect.

In the case, the turbulent flow according to the incision rising portions that forms on the plate wing is produced can improve refrigeration performance, and can access the few cooling operation of defrosting number of times, therefore, can obtain the article stowage arrangement that power consumption is inhibited.

Equally, in present embodiment 7, adopt the heat exchanger of embodiment 4, also can obtain same action effect.

In the case, on the plate wing of heat exchanger, adopt the shape have around the circular circumferential rib of the breakthrough part of refrigerant pipe, the turbulent flow according to the complexity of air-flow can improve refrigeration performance.Like this, because the raising of refrigeration performance and the few cooling operation effect of defrosting number of times can obtain the article stowage arrangement that power consumption is inhibited.

Article stowage arrangement of the present invention comprises: the article storeroom that is formed by insulated space; Compressor, condenser, decompressor and evaporimeter are connected to the freeze cycle of ring-type by pipe arrangement; The cooling flow of evaporimeter is sent into air blast in the article storeroom.The evaporimeter of article stowage arrangement of the present invention is as heat exchanger.

According to this structure, not only can reduce the defrosting number of times, obtain stable heat exchange action, and can carry out effective cooling operation.Meanwhile, can obtain the article stowage arrangement that power consumption is inhibited.

As above-mentioned illustrated, the heat exchanger of fin tube type of the present invention can be realized the purpose of miniaturization and high performance, and can improve defrosting efficiency, realizes energy-conservation purpose, therefore, can be widely used in the refrigeration plants such as freezer, vending machine.

Claims (20)

1. heat exchanger, it is fin tube type heat exchanger fully independently, it is characterized in that:

Comprise: a plurality of be arranged in parallel and air communication is crossed therebetween rectangular slab wing; With connect described plate wing and fluid refrigerant pipe in internal flow,

Described refrigerant pipe is the clathrate configuration with respect to described air-flow,

Described plate wing separates by row with respect to described refrigerant pipe,

On the part of described plate wing, be provided with and be used for interdicting from the heat conducting through hole of described refrigerant pipe to the ora terminalis parallel with the flow direction of described air-flow.

2. heat exchanger, it is fin tube type heat exchanger fully independently, it is characterized in that,

Comprise: a plurality of be arranged in parallel and air communication is crossed therebetween rectangular slab wing; With connect described plate wing and fluid refrigerant pipe in internal flow,

Described refrigerant pipe is the clathrate configuration with respect to described air-flow,

Described plate wing separates by row with respect to described refrigerant pipe,

The shape of the ora terminalis of the described plate wing that intersects with described air-flow forms, with described air-flow meet at right angles the line that intersects be standard shaft and with the different waveform shape of the distance of described standard shaft.

3. heat exchanger as claimed in claim 2 is characterized in that, the fixed distance of the described ora terminalis of described refrigerant pipe and described plate wing.

4. as claim 2 or 3 described heat exchangers, it is characterized in that, flow direction along air-flow disposes a plurality of described plate wings, disposes according to the opposed mode of protuberance ora terminalis of the formation waveform shape of the back segment plate wing of the recess ora terminalis of the formation waveform shape of described plate wing and described plate wing.

5. heat exchanger as claimed in claim 2 is characterized in that, is provided with to be used for interdicting from the heat conducting through hole of described refrigerant pipe to the ora terminalis parallel with the flow direction of described air-flow on the part of described plate wing.

6. as claim 1 or 5 described heat exchangers, it is characterized in that, dispose described plate wing along the mode that the flow direction of described air-flow is positioned at upper end one side and lower end one side alternately according to described through hole.

7. heat exchanger as claimed in claim 2 is characterized in that, also is provided with around the circular circumferential rib of the breakthrough part of refrigerant pipe on described plate wing.

8. heat exchanger as claimed in claim 2 is characterized in that, at the breakthrough part periphery of the described refrigerant pipe of described plate wing a plurality of incision rising portions around described refrigerant pipe is set also.

9. heat exchanger as claimed in claim 8 is characterized in that, forms described incision rising portions according to the mode that direction intersects that flows through with angle and the described air-flow of regulation.

10. as claim 8 or 9 described heat exchangers, it is characterized in that the fixed distance of the described ora terminalis of described refrigerant pipe and described plate wing.

11. as claim 8 or the described heat exchanger of claim 9, it is characterized in that, flow direction along described air-flow disposes a plurality of described plate wings, disposes according to the opposed mode of protuberance ora terminalis of the formation waveform shape of the back segment plate wing of the recess ora terminalis of the formation waveform shape of described plate wing and described plate wing.

12., it is characterized in that setting is used for interdicting from the heat conducting through hole of described refrigerant pipe to the edge parallel with the flow direction of described air-flow on the part of described plate wing as claim 8 or 9 described heat exchangers.

13. heat exchanger as claimed in claim 12 is characterized in that, disposes described plate wing according to described through hole along the mode that the flow direction of described air-flow is positioned at upper end one side and lower end one side alternately.

14. heat exchanger as claimed in claim 2 is characterized in that, described plate wing forms the corrugation shape.

15. heat exchanger as claimed in claim 14 is characterized in that, described corrugation shape has the outstanding shape of direction towards the described air-flow of blocking.

16., it is characterized in that the fixed distance at the described edge of described refrigerant pipe and described plate wing as claim 14 or 15 described heat exchangers.

17. as claim 14 or 15 described heat exchangers, it is characterized in that, flow direction along described air-flow disposes a plurality of described plate wings, disposes according to the opposed mode of protuberance ora terminalis of the formation waveform shape of the back segment plate wing of the recess ora terminalis of the formation waveform shape of described plate wing and described plate wing.

18., it is characterized in that setting is used for interdicting from the heat conducting through hole of described refrigerant pipe to the edge parallel with the flow direction of described air-flow on the part of described plate wing as claim 14 or 15 described heat exchangers.

19. heat exchanger as claimed in claim 18 is characterized in that, disposes described plate wing according to described through hole along the mode that the flow direction of described air-flow is positioned at upper end one side and lower end one side alternately.

20. an article stowage arrangement is characterized in that:

Comprise: the article storeroom that forms by insulated space;

Compressor, condenser, decompressor and evaporimeter are connected to the freeze cycle of ring-type by pipe arrangement; And

The cooling flow of described evaporimeter is sent into air blast in the described article storeroom,

In this article stowage arrangement,

Described evaporimeter is any described heat exchanger in the claim 1 to 19.

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