CN103629877A

CN103629877A - Refrigerator

Info

Publication number: CN103629877A
Application number: CN201310333298.3A
Authority: CN
Inventors: 河井良二; 大平昭义; 冈留慎一郎; 小池畅志郎; 岩渕真也; 中村浩和
Original assignee: Hitachi Appliances Inc
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2012-08-23
Filing date: 2013-08-02
Publication date: 2014-03-12
Anticipated expiration: 2033-08-02
Also published as: JP2014040966A; CN103629877B; KR20140026243A; KR101445203B1; JP5909426B2

Abstract

The invention provides a refrigerator comprising a storage chamber, a cooler, an axial flow fan used for sending out the cold air after the heat exchange with the cooler, an air supply path used for leading the cold air into the storage chamber, and a return path used for returning the cold air to the cooler. At least one of the air supply path and the return path is provided with branches and the air path resistance of the branches is controlled by an air path resistance control unit. The storage chamber is composed of a first independent cooling area cooled by the cold air of one of the branches, a second independent cooling area cooled by the cold air of another one of the branches, and a common cooling area cooled by the cold air of all the branches. The refrigerator can be running in a plurality of air supply modes, wherein any one or the multiple combination of the first independent cooling area, the second independent cooling area and the common independent cooling area can be cooled. In anyone of the plurality of air supply modes, the axial flow fan is controlled in such a manner that the minimum point of an air volume-static pressure characteristic curve is dependent on the operating point of the small air volume.

Description

Refrigerator

Technical field

The present invention relates to refrigerator.

Background technology

As the background technology of the art, there are TOHKEMY 2012-26677 communique (patent documentation 1) and Japanese kokai publication hei 10-54642 communique (patent documentation 2).

In patent documentation 1, disclose and a kind ofly at refrigerating chamber, there is inboard and blow out two airduct air doors that wind path, ceiling blow side out wind path and switch wind path, thereby blow out the blow side detected temperatures of ceiling side temperature sensor of wind path of the inboard temperature sensor of wind path and ceiling based on inboard, controlled the deep freezer (patent documentation 1, Fig. 6 etc.) of the air conditioning quantity in two airduct air doors control refrigerating chambers.

In addition, in patent documentation 2, disclose a kind ofly at each local set temperature detecting unit, at switching air door and the airduct of each region division transporting cold wind, based on detected temperature, whether controlled the deep freezer (patent documentation 2, Fig. 1 etc.) of transporting cold wind.

Prior art document

Patent documentation

Patent documentation 1: TOHKEMY 2012-26677 communique

Patent documentation 2: Japanese kokai publication hei 10-54642 communique

Summary of the invention

Yet the refrigerator (deep freezer) that patent documentation 1 and patent documentation 2 are recorded, does not all take into full account the structure of wind path, has the not high enough situation of cooling effectiveness.

The present invention is in view of above-mentioned problem, and its object is, in switching, for the wind path of single storeroom, carries out in cooling refrigerator, obtains high cooling effectiveness.

For example, in order to solve above-mentioned problem, the formation that adopts claims to record.The method that the application comprises the above-mentioned problem of a plurality of solutions, be for example, possesses storeroom, cooler, to carry out the axial flow fan that the cold air after heat exchange is sent with described cooler, the cold air of being sent by this axial flow fan is guided to the air-supply path of described storeroom, the cold air that makes to deliver to described storeroom returns to the return path of described cooler, the at least one party of described air supply path warp and described return path there is path branches that cold air passes through individual path, the wind path resistance control module that possesses the wind path resistance of controlling this individual path, described storeroom has the 1st cooling independent cooled region of cold air that is passed a path in described individual path, be passed the 2nd cooling independent cooled region of cold air in another path in described individual path, be passed the cooling common cooled region of cold air in all paths of described individual path, have described the 1st independent cooled region, cooling a plurality of air supply patterns are carried out in any of described the 2nd independent cooled region and described common cooled region or a plurality of combinations, under arbitrary pattern in the plurality of air supply pattern, described axial flow fan is all controlled by the mode of the operating point of little air quantity side to become than the characteristic minimal point of air volume-static pressure.

According to the present invention, in switching, be directed to the wind path of single storeroom and carry out in cooling refrigerator, obtain high cooling effectiveness.

Accompanying drawing explanation

Fig. 1 is that the master of the refrigerator of the 1st embodiment of the present invention looks outside drawing.

Fig. 2 means the longitudinal section of the structure in the case of refrigerator of the 1st embodiment of the present invention.

Fig. 3 means the front view of structure of refrigerating chamber of the refrigerator of the 1st embodiment of the present invention.

Fig. 4 means the schematic diagram in circulating cold air path of the refrigerator of the 1st embodiment of the present invention.

Fig. 5 means the figure of pressure fan in the case of refrigerator of the 1st embodiment of the present invention.

Fig. 6 means the figure of refrigerating chamber air door of the refrigerator of the 1st embodiment of the present invention.

Fig. 7 means the figure of vacuum heat insulating material of the refrigerator of the 1st embodiment of the present invention.

Fig. 8 means the figure of installment state of vacuum heat insulating material of the refrigerator of the 1st embodiment of the present invention.

Fig. 9 means the figure of combination of air door open and-shut mode of the refrigerator of the 1st embodiment of the present invention.

Figure 10 is the characteristic of pressure fan and the key diagram of operating point of the refrigerator of the 1st embodiment of the present invention.

Figure 11 is the key diagram that blows out the flow direction of pressure fan of the refrigerator of the 1st embodiment of the present invention.

Figure 12 means the flow chart of control of the refrigerator of the 1st embodiment of the present invention.

Figure 13 means the figure of air measuring method of the refrigerator of embodiments of the present invention.

Figure 14 means the longitudinal section of the structure in the case of refrigerator of the 2nd embodiment of the present invention.

Figure 15 means the front view of structure of refrigerating chamber of the refrigerator of the 2nd embodiment of the present invention.

Figure 16 means the schematic diagram in circulating cold air path of the refrigerator of the 2nd embodiment of the present invention.

Figure 17 means the longitudinal section of the structure in the case of refrigerator of the 3rd embodiment of the present invention.

Figure 18 means the front view of structure of refrigerating chamber of the refrigerator of the 3rd embodiment of the present invention.

Figure 19 means the schematic diagram in circulating cold air path of the refrigerator of the 3rd embodiment of the present invention.

Figure 20 means the figure of combination of air door open and-shut mode of the refrigerator of the 3rd embodiment of the present invention.

In figure: 1-refrigerating chamber main body, 2-refrigerating chamber, 2c-region (the 2nd independent cooled region), 2d-region (the 1st independent cooled region), 2e-region (common cooled region), 3-deepfreeze chamber, 7-refrigerating chamber, 9-evaporimeter receiving room, 11-refrigerating chamber ajutage (air-supply path), 11a-refrigerating chamber the 1st ajutage (individual path), 11b-refrigerating chamber the 2nd ajutage (individual path), 15-refrigerating chamber recurrent canal (return path), 21-evaporimeter (cooler), pressure fan (axial flow fan) in 22-case, 24-refrigerating chamber air door (wind path resistance control module), 24a-refrigerating chamber the 1st air door, 24b-refrigerating chamber the 2nd air door, 31-refrigerating chamber blow-off outlet, 35-refrigerating chamber return port, 41a-refrigerating chamber the 1st temperature sensor (temperature detecting unit), 41b-refrigerating chamber the 2nd temperature sensor (temperature detecting unit), 42-deepfreeze room temperature sensor (temperature detecting unit), 46-shelf, 47-door pocket, 49-control substrate, 50-body of thermal insulating box, the adiabatic partition wall (separating part) of 51-upside, the adiabatic partition wall (separating part) of 52-downside, 55-ice making water tank, 60-vacuum heat insulating material.

The specific embodiment

Embodiment 1

With reference to Fig. 1～Figure 12, the 1st embodiment of refrigerator of the present invention is described.

Fig. 1 is that the master of the refrigerator of present embodiment looks outside drawing.Fig. 2 means the longitudinal section of the structure in the case of refrigerator of present embodiment.Fig. 3 means the front view of structure of refrigerating chamber of the refrigerator of present embodiment.Fig. 4 means the schematic diagram of wind path structure of the refrigerator of present embodiment.Fig. 5 means the figure of pressure fan in the case of refrigerator of present embodiment.Fig. 6 means the figure of refrigerating chamber air door of the refrigerator of present embodiment.

As shown in Figure 1, the refrigerator main body 1 of present embodiment possesses refrigerating chamber 2, ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6 and vegetable compartment 8 from top to bottom.And ice-making compartment 4 and epimere refrigerating chamber 5 left and right between refrigerating chamber 2 and hypomere refrigerating chamber 6 is set up in parallel.Refrigerating chamber 2 and vegetable compartment 8 are the storeroom of the refrigerated storage temperature section of for example 5 ℃ of left and right.And ice-making compartment 4, epimere refrigerating chamber 5 and hypomere refrigerating chamber 6 are for example-18 ℃ of storerooms to the cryogenic temperature section of-20 ℃ of left and right (following, ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6 are generically and collectively referred to as to refrigerating chamber 7).

Refrigerating chamber 2 forwardly side possesses clamshell type refrigerating-chamber door 2a, the 2b that left and right is cut apart.Ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6, vegetable compartment 8 possess respectively ice-making compartment door 4a, epimere refrigerating chamber door 5a, hypomere refrigerating chamber door 6a, the vegetable compartment door 8a of drawer type.

As shown in Figure 2, be adiabatic casing 50 and separate outside the case of the refrigerator of present embodiment and in case, this body of thermal insulating box 50 is formed by filling with foam insulation materials (polyurathamc) between outer container 1a and interior case 1b.And, the refrigerator of present embodiment be provided with overleaf vacuum heat insulating material 60(for the installment state of vacuum heat insulating material 60 by aftermentioned).

Storeroom inner side at refrigerating-

chamber door

2a, 2b possesses a plurality of pocket 47a～47c.And, in refrigerating chamber 2, possess a plurality of shelf 46a～46f(shelf 46a～46f with reference to Fig. 3).

And ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6 and vegetable compartment 8 possess and are arranged on door 4a, the 5a in the place ahead of each storeroom, accommodating

container

4b, 5b, 6b, the 8b that 6a, 8a move at fore-and-aft direction integratedly.

Door

4a, 5a, 6a, 8a pull out accommodating

container

4b, 5b, 6b, 8b by side in front of not shown handle portion being moved to hand respectively.

The refrigerator of present embodiment as shown in Figure 2, refrigerating chamber 2 and, epimere refrigerating chamber 5 and ice-making compartment 4(are with reference to Fig. 1) by the adiabatic partition wall 51 be adiabatic property of upside separate, hypomere refrigerating chamber 6 and vegetable compartment 8 by downside thermal insulation partition wall 52 being adiabatic property separate.In addition, between shelf 46f and the adiabatic partition wall 51 of upside, as an example, possesses deepfreeze (chilled) chamber 3 that remains-1～1 ℃ of left and right.Therefore,, in the refrigerator of present embodiment, in the storage area of the top of the adiabatic partition wall 51 of upside, the region except remaining the deepfreeze chamber 3 of low temperature becomes the storeroom of refrigerated storage temperature section.In addition, also deepfreeze chamber 3 can be suppressed to the decompression storeroom of Food Oxidation as keeping decompression state.

The refrigerator of present embodiment as shown in Figure 2, possesses evaporimeter receiving room 9 at the back of refrigerating chamber 7, evaporimeter receiving room 9 interior as cooling unit possess evaporimeter 21(as an example for fin tube heat exchanger).And, above evaporimeter 21, as blowing unit, possess pressure fan 22 in case.

As shown in Figure 5, pressure fan 22 is axial flow fans (propeller type fan) of the external diameter that drives by the motor (not shown) in central motor incorporating section 92 blade 91 that is 110mm in the case of the refrigerator of present embodiment.In addition, motor incorporating section 92 links by support 93 and housing 94.And, blow out area (π * [0.5 * blade external diameter] ²) as an example, be 9503.3mm ².

And, as shown in Figure 2, below evaporimeter receiving room 9, possess Defrost heater 56.Be formed at evaporimeter 21 with and the wall of the evaporimeter receiving room 9 of periphery on frost by the defrosting running that 56 energisings are carried out to Defrost heater, melt.Frost melts and the defrost water that produces flow into after the aqueduct 57 of the bottom that is arranged at evaporimeter receiving room 9, arrives the evaporating pan 59 that is disposed at Machine Room 10 via drainpipe 58.Defrost water in evaporating pan 59 is evaporated by being provided in compressor 23 in Machine Room 10 and the heating of condenser (not shown).

The refrigerator of present embodiment by with refrigerant pipe successively by the compressor 23 being provided in Machine Room 10, condenser (being for example fin tube heat exchanger), with between outer container 1a and interior case 1b and the radiating tube (not shown) that sets of the mode contacting with outer container 1a face, be provided in body of thermal insulating box 10 upper thermal barrier partition wall 51 above or the dewfall killer tube (not shown) above etc. of lower thermal barrier partition wall 52, for the drier (not shown) that the moisture drying of cold-producing medium is absorbed, capillary (not shown), and evaporimeter 21 connects, and formation freeze cycle.Wherein, cold-producing medium is iso-butane.

As shown in Figure 3, the substantial middle at the back side of refrigerating chamber 2 possess from below towards above refrigerating chamber the 1st ajutage 11a, refrigerating chamber the 2nd ajutage 11b that extend.Refrigerating chamber the 1st ajutage 11a in refrigerating chamber 2 back sides left sides possess cold air is blown to than shelf 46a, the 46b of epimere on the lower and than the top side's of shelf 46f of hypomere region 2d(with reference to Fig. 2 and Fig. 3) refrigerating chamber blow-off outlet 31a～31c.Wherein, the aperture area of refrigerating chamber blow-off outlet 31a is 1000mm ², refrigerating chamber blow-off outlet 31b aperture area be 500mm ², refrigerating chamber blow-off outlet 31c aperture area be 200mm ².And the region 2c(that refrigerating chamber the 2nd ajutage 11b in refrigerating chamber 2 back sides left sides possesses the top that blows to

shelf

46a, 46b is with reference to Fig. 2 and Fig. 3) refrigerating chamber blow-off outlet 31d, 31e.Wherein, the aperture area of refrigerating chamber blow-off outlet 31d is 500mm ², refrigerating chamber blow-off outlet 31e aperture area be 500mm ².And the minimum flow path cross sectional area of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b is respectively 1640mm ²and 1110mm ².

By the way, shelf 46a～46e is configured to and in prescribed limit, can changes height and position (wherein, shelf 46f fixes).Therefore, the size variation of 2cJi region, region 2d, however each distance (height H 1 shown in Fig. 3 and height H 2) that the variable range of shelf 46a and shelf 46b is set to from shelf 46a and shelf 46b to upper wall is less than the depth size separately of shelf 46a and shelf 46b.And making the volume arranging highly as the region 2c under minimum state of

shelf

46a, 46b is 50L, the volume of region 2d is 140L, and the volume that the region 2e of

pocket

47b, 47c and ice making water tank 55 is set is 40L.

As shown in Figure 3, control to the refrigerating chamber air door 24(wind path resistance control module of the air-supply of refrigerating chamber 2) be arranged in the back projection region of the adiabatic partition wall 51 of upside.Thus, can suppress food storing space minimizing air door is installed.

And as shown in Figure 6, refrigerating chamber air door 24 possesses opening 82a, 82b in 81 left and right, motor incorporating section.Opening 82a and opening 82b are opened and are closed by opening-closing plate 83a, 83b.Particularly, by being arranged on the stepper motor (not shown) in motor incorporating section 81, opening-

closing plate

83a, 83b can control at the full closing state of angle of release degree 0 degree respectively in the scope of the full open mode of angle of release degree 90 degree.Below, the function of the function of the open and-shut mode of the control opening 82a in the function of refrigerating chamber air door 24 is made as to refrigerating chamber the 1st air door 24a, controlling the open and-shut mode of opening 82b is made as refrigerating chamber the 2nd air door 24b.

As shown in Figure 3, refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b are separately positioned on the entrance of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b, control the air-supply to refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b.

As shown in FIG. 2 and 3, the back in the shelf 46f by hypomere and the region divided from the shelf 46d of lower several the 2nd section, possesses refrigerating chamber the 1st temperature sensor 41a(temperature detecting unit of the load of main surveyed area 2d).And, at the upper wall of refrigerating chamber 2, possess refrigerating chamber the 2nd temperature sensor 41b(temperature detecting unit of the load of main surveyed area 2c).And the back (back of deepfreeze chamber 3) in the region of being divided by shelf 46f and the adiabatic partition wall 51 of upside, possesses deepfreeze room temperature sensor 42(temperature detecting unit).Wherein, refrigerating chamber the 1st temperature sensor 41a, refrigerating chamber the 2nd temperature sensor 41b, deepfreeze room temperature sensor 42 are arranged on and do not contact velocity ratio and improved accuracy of detection compared with the place of high cold air.

And, at the back of refrigerating chamber 7 and the back of vegetable compartment 8, possess respectively freezer temperature sensor 43 and vegetable compartment temperature sensor 44(with reference to Fig. 2).

In addition, the left end in the region of being divided by the adiabatic partition wall 51 of shelf 46f and upside possesses the ice making water tank 55 of the water that storage ice making uses.Water in ice making water tank 55 passes through driving pump (not shown), and via pipe arrangement (not shown), is supplied to the ice-making disc (not shown) being arranged in ice-making compartment 4.

Fig. 7 means the figure of the vacuum heat insulating material of the refrigerator that is installed on present embodiment.Fig. 8 means the figure (near the enlarged drawing region A of Fig. 2) of the installment state of vacuum heat insulating material.

As shown in Figure 7, vacuum heat insulating material 60 is by be for example mineral wool by core 61() be for example synthetic zeolite with adsorbent 62() together with compression seal, be inserted into the laminated film that outer packaging material 64(comprises aluminium-vapour deposition rete) in, after vacuum filtration, thermally welded manufacture is carried out in end and form.Therefore, in the end of vacuum heat insulating material, there is the thermally welded 60a of portion shown in Fig. 7, but in the refrigerator of present embodiment, as shown in Figure 8, by the thermally welded 60a of portion go back to case inner side (foaming heat insulating material side) and fixing after, foaming heat insulating material is fills up between interior case 1b and outer container 1a, forms body of thermal insulating box 50.Therefore, vacuum heat insulating material 60 has the reflex part 60b that the thermally welded 60a of portion is turned back and formed in periphery.In addition, in the present embodiment, vacuum heat insulating material 60 is sticked on to outer container 1a inner face by stickers such as PURs, but be not limited to this.For example, can be the structure that sticks on interior case 1b inner face, can be also via support unit, to be configured in the structure of interior case 1b and outer container 1a, no matter which kind of structure, all by the thermally welded 60a of portion, to case inner side, (foaming heat insulating material side) turned back and configured.

In addition, if adopt, at inner bag 63(, be for example polyethylene) in take in core 61 as after temporarily compressive state is received in outer packaging material 64, again to internal bag 63 and outer packaging material 64 in carry out the structure of compression seal, improved the operability of core 61, can make manufacturing process's efficient activity.

As shown in the dotted line of Fig. 3, vacuum heat insulating material 60 is installed in the back side adiabatic wall of refrigerator, but has above-mentioned reflex part 60b(by the region of the dotted line in the dotted line of inner side and outside in periphery).In the refrigerator of present embodiment, as shown in Figure 3, when refrigerating chamber the 1st ajutage 11a is projected to the vacuum heat insulating material 60 at rear, from the beeline L of refrigerating chamber the 1st ajutage 11a end to the end of vacuum heat insulating material 60, be 100mm.And refrigerating chamber the 1st ajutage 11a is accommodated in than the reflex part 60b of vacuum heat insulating material 60 and compares regional center in the inner part.Thus, can suppress the metal level of the outer packaging material 64 by vacuum heat insulating material 60 and impact that the so-called heat bridge phenomenon of heat conduction brings does not relate to refrigerating chamber the 1st ajutage 11a.Detailed content aftermentioned.

Next, with reference to Fig. 4, suitably with reference to Fig. 2 and Fig. 3, the circulating cold air path of the refrigerator of present embodiment is described.

As shown in Figure 4, having carried out pressure fan 22 in the Quilt with air conditioning case of heat exchange with evaporimeter 21 boosts, under the state of opening at refrigerating chamber the 1st air door 24a, refrigerating chamber the 1st ajutage 11a flow and region 2d(in from from refrigerating chamber blow-off outlet 31a～31c to refrigerating chamber with reference to Fig. 2 and Fig. 3) blow out.The region 2e(of the cold airflow that blows to region 2d through being provided with pocket 47b, a 47c, ice making water tank 55 is with reference to Fig. 2 and Fig. 3), deepfreeze chamber 3, arrive refrigerating chamber return port 35.On the other hand, under the state of opening at refrigerating chamber the 2nd air door 24b, in refrigerating chamber the 2nd ajutage 11b, flow and region 2c(in from refrigerating chamber blow-off outlet 31d, from 31e to refrigerating chamber with reference to Fig. 2 and Fig. 3) blow out.The region 2e(of the cold airflow that blows to region 2c through being provided with pocket 47b, a 47c, ice making water tank 55 is with reference to Fig. 2 and Fig. 3), deepfreeze chamber 3, and arrive refrigerating chamber return port 35.

Cooling cold air has been carried out in

region

2c, 2d, 2e and deepfreeze chamber 3, from refrigerating chamber return port 35 enter refrigerating chamber recurrent canal 15(for example minimum flow path cross sectional area be 1700mm ²), arrive evaporimeter receiving room 9, again carry out heat exchange with evaporimeter 21.

Next, under the state of opening at refrigerating chamber air door 26, the cold air after being boosted by pressure fan in case 22 flows refrigerating chamber ajutage 13 is interior, and from refrigerating chamber blow-off outlet 33a～33c(with reference to Fig. 2) blow out to refrigerating chamber 7.Refrigerating chamber has been carried out to cooling cold air and from refrigerating chamber return port 36, be back to evaporimeter receiving room 9, again carried out heat exchange with evaporimeter 21.

Under the state of opening at vegetable compartment air door, the cold air after being boosted by pressure fan in case 22 blows out to vegetable compartment 8 from vegetable compartment blow-off outlet 34 interior the flowing of vegetable compartment ajutage 14.Vegetable compartment 8 has been carried out to cooling cold air and from vegetable compartment return port 37, entered vegetable compartment recurrent canal 17, arrived evaporimeter receiving room 9, again carried out heat exchange with evaporimeter 21.

Next, with reference to Fig. 9～Figure 11, the wind path resistance of each wind path in the characteristic of pressure fan in the case of the refrigerator of present embodiment and case is described.

Fig. 9 means the figure of combination of the open and-shut mode of air door, and Figure 10 means the figure of the air volume-static pressure characteristic of pressure fan 22 and the relation of operating point in case.And Figure 11 means the schematic diagram that blows out the flow direction of the air blowing out from pressure fan 22 in case.

The wind path resistance in circulating cold air path changes according to the open and-shut mode of air door.The refrigerator of present embodiment possesses refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b, refrigerating chamber air door 26, vegetable compartment air door 27, has respectively the two states of open mode and closed condition, thus the open and-shut mode of air door be combined as 16 kinds.Fig. 9 represents that refrigerating chamber the 1st air door 24a wherein or at least one in refrigerating chamber the 2nd air door 24b are open mode, carries out to the combination of the state of the air-supply of refrigerating chamber 2.

As shown in Figure 9, carrying out to the state of the air-supply of refrigerating chamber 2 is 12 kinds of state 1～state 12, and the wind path resistance in the circulating cold air path of each state is R1～R12.Wherein, in " size of wind path resistance " hurdle, about the magnitude relationship of R1～R12, according to wind path resistance order note from small to large, gone up 1～12 numbering.That is, the magnitude relationship of R1～R12 is " R6<R12<R4<R10LEss T.LTssT.LTR5<R11<R3LEssT.LTssT .LTR9<R1<R7<R2LEs sT.LTssT.LTR8 ".

The figure of operating point when Figure 10 means the air volume-static pressure characteristic of pressure fan 22 in case and the state 1～state 6 shown in Fig. 9.

As shown in Figure 10, the air volume-static pressure characteristic of the interior pressure fan 22 of case has slope in Wind Volume side and from rising, transfers the maximal point of decline to, has slope from declining, transfer the minimal point of rising in little air quantity side.This is the characteristic that can see in general axial flow fan, if the starting point that is 0 from static pressure starts to make air quantity to reduce, in the moment that arrives regulation air quantity, produces the stall that air-flow is peeled off from blade.The point that produces stall is called to stall point, and in general, the maximal point of air volume-static pressure characteristic is regarded as stall point.If start to reduce air quantity from stall point, there is the region (right rising characteristic territory) that static pressure reduces, due to centrifugal action, static pressure rises again after reaching minimal point, reaches air quantity and be 0 cut off.And, the Wind Volume side from starting point to maximal point, as shown in the arrow in Figure 11 (a), the air of producing by boasting from pressure fan 22 in case flows vertically, little air quantity side from minimal point to cut off, as shown in the arrow in Figure 11 (b), the air of producing by boasting from pressure fan 22 in case is (centrifugal direction) diverging flow radially.Therefore, below, be called " axial flow territory " till will be from starting point to maximal point, be called " right rising characteristic territory " till will be from maximal point to minimal point, be called " centrifugal basin " till will be from minimal point to cut off.

In the resistance curve of the resistance R1～R6 of the state 1～state 6 shown in Figure 10 and case, the characteristic intersection point of air volume-static pressure of pressure fan 22 becomes the operating point of each state.Therefore, the air quantity in the situation that making each air door become state 1～state 6 is the Q1～Q6 shown in Figure 10, and any one operating point all becomes centrifugal basin.And the magnitude relationship of air quantity is " Q6>Q4>Q5>Q3Gre atT.GreaT.GTQ1>Q2 ".By the way, though omit in Figure 10, but the air quantity of resistance R7～R12 is Q7～Q12, if represent the magnitude relationship of air quantity, be " Q6>Q12>Q4>Q10G reatT.GreaT.GTQ5>Q11>Q3Great T.GreaT.GTQ9>Q1>Q7GreatT.Gre aT.GTQ2>Q8 ".That is, exist the size of wind path resistance of each state less, the trend that air quantity is larger.

The refrigerator of present embodiment possesses (not shown) such as temperature setting devices of the Temperature Setting that carries out refrigerating chamber 2, deepfreeze chamber 3, refrigerating chamber 7, vegetable compartment 8, and the control substrate 49(that disposes the memory, interface circuit etc. that have carried CPU, ROM, RAM etc. at the top rear side of the upper wall of refrigerator main body 1 is with reference to Fig. 2).Control substrate 49 and above-mentioned refrigerating chamber the 1st temperature sensor 41a, refrigerating chamber the 2nd temperature sensor 41b, deepfreeze room temperature sensor 42, freezer temperature sensor 43, vegetable compartment temperature sensor 44 and be arranged at temperature setting device in refrigerating-chamber door 2a, case etc. and be connected.

By carrying in advance the program of ROM, undertaken compressor 23 ON/OFF, start refrigerating chamber air door 24, refrigerating chamber air door 26 and vegetable compartment air door 27 the control of each driver (not shown), in case, the ON/OFF of pressure fan 22 controls, rotating speed is controlled, the alarm bell ON/OFF control of notice door open mode, by these, form control device.

Next, with reference to Figure 12, the control of the refrigerator of present embodiment is described.

Figure 12 means the control flow chart of the control in the cooling running of refrigerator of present embodiment.The refrigerator of present embodiment is by the connection of power supply, and compressor 23 drives and begins to cool down running (beginning).At this, omit the state of a control before fully cooling off in case, from sufficiently cooled in case, the state of compressor 23 in stopping to the moment that meets the condition that compressor 23 drives, start to describe.Meet in the situation of drive condition of compressor 23 (about the drive condition aftermentioned of compressor 23), in compressor 23 and case, pressure fan 22 drives (step S101), judges whether the condition of opening of refrigerating chamber the 1st air door 24a sets up (step S102).In the refrigerator of present embodiment, the condition of opening of refrigerating chamber the 1st air door 24a is " compressor 23 is halted state, the detected temperatures of refrigerating chamber the 1st temperature sensor 41a is Tr1_a above (Tr1_a=3 ℃ in the refrigerator of present embodiment) " or, " compressor 23 is driving condition, refrigerating chamber air door 26 is closed condition, the detected temperatures of refrigerating chamber the 1st temperature sensor 41a is more than Tr1_a " or, " compressor 23 is driving condition, refrigerating chamber air door 26 is open mode, the detected temperatures of refrigerating chamber the 1st temperature sensor 41a is Tr1_b above (Tr1_b=7 ℃ in the refrigerator of present embodiment) " situation under set up.In the situation that step S102 sets up ("Yes"), refrigerating chamber the 1st air door 24a is opened (step S103), to the region 2d(in refrigerating chamber 2 with reference to Fig. 2 or Fig. 3) send cold air.

Whether the condition of opening of next, judging refrigerating chamber the 2nd air door 24b sets up (step S104).In the refrigerator of present embodiment, the condition of opening of refrigerating chamber the 2nd air door 24b is " compressor 23 is halted state, the detected temperatures of refrigerating chamber the 2nd temperature sensor 41b is Tr2_a above (Tr2_a=4 ℃ in the refrigerator of present embodiment) " or, " compressor 23 is driving condition, refrigerating chamber air door 26 is closed condition, the detected temperatures of refrigerating chamber the 2nd temperature sensor 41b is more than Tr2_a " or, " compressor 23 is driving condition, refrigerating chamber air door 26 is open mode, the detected temperatures of refrigerating chamber the 2nd temperature sensor 41b is Tr2_b above (Tr2_b=8 ℃ in the refrigerator of present embodiment) " situation under set up.In the situation that step S104 sets up ("Yes"), refrigerating chamber the 2nd air door 24b is opened (step S105), to the region 2c(in refrigerating chamber 2 with reference to Fig. 2 or Fig. 3) send cold air.

Whether the condition of closing of next, judging refrigerating chamber the 1st air door 24a sets up (step S106).In the refrigerator of present embodiment, the condition of closing of refrigerating chamber the 1st air door 24a " detected temperatures of refrigerating chamber the 1st temperature sensor 41a is (Tr1_c=2 ℃ in the refrigerator of present embodiment) below Tr1_c " or, in the situation of " detected temperatures of deepfreeze room temperature sensor 42 is Tc_a following (in the refrigerator of present embodiment, Tc_a=﹣ is 1 ℃) ", set up.In the situation that step S106 sets up ("Yes"), refrigerating chamber the 1st air door 24a is closed (step S107).

Whether the condition of closing of then, judging refrigerating chamber the 2nd air door 24b sets up (step S108).In the refrigerator of present embodiment, the condition of closing of refrigerating chamber the 2nd air door 24a " detected temperatures of refrigerating chamber the 2nd temperature sensor 41b is (Tr2_c=3 ℃ in the refrigerator of present embodiment) below Tr2_c " or, in the situation of " detected temperatures of deepfreeze room temperature sensor 42 is that Tc_a is following ", set up.In the situation that step S108 sets up ("Yes"), refrigerating chamber the 2nd air door 24b is closed (step S109).

Whether the condition of opening of next, judging refrigerating chamber air door 26 sets up (step S110).In the refrigerator of present embodiment, the condition of opening of refrigerating chamber air door 26 at " compressor 23 be that closed condition, refrigerating chamber the 2nd air door 24b are closed condition for driving condition, refrigerating chamber the 1st air door 24a " or, in the situation of " compressor is that the detected temperatures of driving condition, freezer temperature sensor 43 is Tf_a above (in the refrigerator of present embodiment, Tf_a=﹣ is 14 ℃) ", set up.In the situation that step S110 sets up ("Yes"), refrigerating chamber air door 26 is opened, and in refrigerating chamber 7, send cold air (step S111).

Whether the stop condition of then, judging pressure fan 22 in case sets up (step S112).In the refrigerator of present embodiment, in case, the stop condition of pressure fan 22 was set up in " compressor 23 is that halted state, refrigerating chamber the 1st air door 24a are that closed condition, refrigerating chamber the 2nd air door 24b are closed condition " in the situation that.In the situation that step S112 sets up ("Yes"), stop pressure fan 22 in case.

Whether the stop condition of next, judging compressor 23 sets up (step S114).In the refrigerator of present embodiment, the stop condition of compressor 23 in the situation that " detected temperatures of freezer temperature sensor 43 is (in the refrigerator of present embodiment, Tf_b=﹣ is 20 ℃) below Tf_b " set up.In the invalid situation of step S114 ("No"), again return to the judgement of step S102.

In the situation that step S114 sets up ("Yes"), compressor 23 stops, and refrigerating chamber air door 26 is closed (step S115).Whether the drive condition of next, judging compressor 23 sets up (step S116).In the refrigerator of present embodiment, the drive condition of compressor 23 in the situation that " detected temperatures of freezer temperature sensor 43 is more than Tf_c (in the refrigerator of present embodiment, Tf_c=﹣ is 16 ℃) " set up.In the invalid situation of step S116 ("No"), again return to the judgement of step S102.And in the situation that step S116 sets up ("Yes"), by step S101, pressure fan 22 in drive compression machine 23, case, moves on to the judgement of step S102.

In addition, in above control flow, omitted the explanation of the action of vegetable compartment air door 26, in the refrigerator of present embodiment, vegetable compartment air door 26 is opened with refrigerating chamber the 1st air door 24a or refrigerating chamber the 2nd opening in linkage of air door 24b, in the situation that the detected temperatures of vegetable compartment temperature sensor 44 is lower than Tv=3 ℃ in the refrigerator of lower limit temperature Tv(present embodiment) be closed.

Above, the structure of the refrigerator of present embodiment has been described, below, the effect that the refrigerator of present embodiment is played describes.

The refrigerator of present embodiment during in open mode, compares more by little air quantity side (centrifugal basin) (with reference to Figure 10) minimal point of operating point air volume-static pressure characteristic of pressure fan 22 in than case at least one party of refrigerating chamber the 1st air door 24a or refrigerating chamber the 2nd air door 24b.Thus, can provide the refrigerator that cooling effectiveness is high.Below give reasons.

The refrigerator of present embodiment possesses refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b as the air-supply path to refrigerating chamber 2, mainly by the cooling region 2d of refrigerating chamber the 1st ajutage 11a, be provided with refrigerating chamber the 1st temperature sensor 41a of detected temperatures, mainly by the cooling region 2c of refrigerating chamber the 2nd ajutage 11b, be provided with refrigerating chamber the 2nd temperature sensor 42b of detected temperatures.Detected temperatures based on refrigerating chamber the 1st temperature sensor 41a and refrigerating chamber the 2nd temperature sensor 42b is controlled the open and-shut mode (with reference to Figure 12) of refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b.Thus, if air output is excessive, 2cHe region, the region 2d(in refrigerating chamber 2 is with reference to Fig. 2 or Fig. 3) with the short time, complete cooling, if air output is little, although cool time elongated, can be cooled to reliably setting.That is, about 2c, region, region 2d, no matter air output how, does not have cooling mistake and deficiency, so can access the high efficiency state of cooling.On the other hand, no matter make which in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b become open mode, the region 2e that cold air passes through jointly so long as any one party in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b in open mode, just be cooled, so can not suppress cooling mistake and deficiency by switching ventilation state.For example, if excessive to the air output of region 2e, region 2c or the sufficiently cooled moment of region 2d, region 2e becomes too cooling state, if air output is too small, at region 2c or the abundant cooling moment of region 2d, the state of region 2e in cooling deficiency.Particularly, as the refrigerator of present embodiment, in the situation that the region 2e that cold air passes through jointly arranges ice making water tank 55, if region 2e, by too cooling, has the situation of the water freezing in ice making water tank 55.Therefore,, in order to prevent that icing in ice making water tank 55 from needing the heating of heater etc., so correspondingly increased thermic load, cooling effectiveness reduces.

Therefore, require to adjust the wind path resistance in the circulating cold air path under the state of opening refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b, the rotating speed of pressure fan 22 in case, to become, make the region 2e that cold air passes through jointly can be by suitable cooling air output.

In general, if stable according to the operating point of the air volume-static pressure characteristic of pressure fan in case and wind path resistance (resistance curve of Figure 10) decision, in air output and case, the rotating speed of pressure fan is proportional, so by changing rotating speed, can easily adjust air output.

On the other hand, in the situation that operating point changes significantly, the rotating speed of pressure fan and the relationship change of air output in case, so be difficult to obtain the air output of regulation.For example, in refrigerator in the past (, the refrigerator described in patent documentation 1 or patent documentation 2), due to the reason of the following stated, and the operating point in circulating cold air path changes significantly sometimes, follows this to occur the problem of the reduction of cooling effectiveness.

In general, axial flow fan is the pressure fan using by the axial flow territory (with reference to Figure 10) of Wind Volume side comparing with stall point.Therefore, for relatively, first illustrate and make the wind path resistance in circulating cold air path suppress littlely, the mode with operating point in axial flow territory forms the situation of wind path.

In refrigerator, in cooling running, at evaporimeter, produce frost, so can not avoid wind path resistance gradually to increase along with white generation.Now, if make operating point in axial flow territory, wind path resistance be suppressed littlely, the increase degree of the white wind path resistance that produces at evaporimeter of resulting from becomes large, along with white generation, operating point is changed to little air quantity side significantly.Therefore,, no matter make which in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b in open mode, the air output of the region 2e jointly passing through towards cold air changes significantly, causes the reduction of cooling effectiveness.

Therefore,, as the refrigerator of present embodiment, make wind path comparison of resistance large, mode with operating point in centrifugal basin forms in the situation of wind path, even if produce frost, the wind path comparison of resistance on basis is large, so result from the increase degree of wind path resistance of white generation, relatively diminishes.Therefore, the minimizing degree of air quantity diminishes, so no matter make which in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b in open mode, can both suppress the reduction of the cooling effectiveness of the region 2e that cold air passes through jointly.

And the right rising characteristic territory between axial flow territory and centrifugal basin is moved unstable sometimes.Therefore, in general, in order to obtain stable air output, hope is avoided, but the mode with operating point in axial flow territory forms in the situation of wind path, sometimes the wind path resistance increment along with white generation, operating point enters right rising characteristic territory and faces the state that cannot obtain towards the stable air output of region 2e.

Therefore, refrigerator as present embodiment, if make operating point in centrifugal basin, even the wind path resistance increment along with white generation, the minimizing degree of air quantity is also suppressed must be less, and, also can avoid entering and sometimes move unsettled right rising characteristic territory, so no matter make which in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b in open mode, all become and make the suitably cooling high refrigerator of cooling effectiveness of region 2e that cold air passes through jointly.

Wherein, for example can distinguish that operating point is in centrifugal basin by following mode.

First, based on JISB8330:2000, measure the air volume-static pressure characteristic of pressure fan monomer in case.Next, measure the air quantity of refrigerator.Figure 13 means the schematic diagram of the state that the mobile air quantity of the refrigerating chamber return port 35 of the refrigerator in present embodiment is measured.

As shown in figure 13, be arranged to open refrigerating-chamber door 2a, 2b, airduct 100 covers refrigerating chamber return port 35, utilizes the 2nd difference gauge 104 of differential pressure in downstream of upstream side that can calculate the throttling arrangement 102 of air quantity by measuring the pressure of inside of airduct 100 and the 1st difference gauge 103 of the differential pressure of outside pressure (atmospheric pressure), differential pressure based on upstream side and downstream, measure throttling arrangement 102, the apparatus for measuring air quantity that the pressure fan of the upstream side of throttling arrangement 101 forms is measured air quantity.Particularly, it is zero that adjustment pressure fan 101 makes the differential pressure of the 1st difference gauge 103, and the 2nd difference gauge 104 based on now can be measured at the mobile air quantity of refrigerating chamber return port 35.Wherein, refrigerating-chamber door 2a, 2b are open mode, and the differential pressure of still adjusting the 1st difference gauge is zero, so can be considered as the state almost identical with the state of closing cold room door 2a, 2b.By the way, also can make the state that arranges reversion that throttling arrangement 102 and pressure fan 101 record from Figure 13 and air in sucking-off airduct 100, thereby measure the air quantity blowing out from blow-off outlet.For example, if airduct 100 is set with guiding from the mode of the air-supply of blow-off outlet 31a～31c of refrigerating chamber the 1st ajutage 11a, differential pressure with the 1st difference gauge 103 becomes zero mode to adjust pressure fan 101, and the differential pressure based on the 2nd difference gauge 104 can be measured the air quantity that blows out from refrigerating chamber the 1st ajutage 11a.In addition, at this, example of the air measuring method of utilizing throttle mechanism has been described, but such as also utilizing other the mechanism such as thermal flowmeter to measure air quantity.

By above method, the air volume-static pressure characteristic of pressure fan monomer and the action air quantity of refrigerator become clearly, so according to both, can distinguish that whether operating point is in centrifugal basin with precision enough in practicality.

In addition, in the monomer performance of axial flow fan, in the situation that maximal point and minimal point do not manifest clearly, can confirm centrifugal basin by following method.

In general, in axial flow fan, in axial flow territory, flow vertically, (with reference to Figure 11) radially flows in centrifugal basin.Therefore,, in the situation that there is the pressure fan of the air volume-static pressure characteristic that maximal point and minimal point manifest ambiguously, according to blowing out the variation of stream, can distinguish axial flow territory and centrifugal basin.Particularly, as shown in Figure 11, prefer virtual (circular cone table tops) of 45 degree that tilt from the place ahead of the leading edge 91a of the blade periphery of axial flow fan 22, the inner side of face (the place ahead) is made as to front region, the outside of face is made as to radial zone, judge that when air-flow blows to front region, operating point is in axial flow territory, when air-flow blows to radial zone, operating point is in centrifugal basin.Therefore, for example, when carrying out the measurement of air volume-static pressure characteristic of pressure fan monomer, wind speed on the meridian plane of the leading edge 91a certain distance of measuring distance blade periphery, when the peaked point that represents wind speed enters front region, be judged to be axial flow territory, when entering radial zone, be judged to be centrifugal basin.By the way, the wind speed blowing out from pressure fan has axial composition, radially (centrifugal direction) composition and circumferential composition.Therefore, if for example measure with non-direction airspeedometer, what measure is the wind speed of these compositions after synthetic, but relatively diminishes towards axial air-flow, can pick out in forming the centrifugal basin towards air-flow radially.

The refrigerator of present embodiment possesses vacuum heat insulating material 60 in adiabatic wall overleaf, when by rearward vacuum heat insulating material 60 projection of refrigerating chamber the 1st ajutage 11a, the beeline L from refrigerating chamber the 1st ajutage 11a end to the end of vacuum heat insulating material 60 be divided into 50mm mutually more than (the refrigerator L=100mm of present embodiment).Under this state, implementing to make refrigerating chamber the 1st air door 24a to refrigerating chamber the 1st ajutage 11a air-supply is open mode, the operation mode (with reference to Fig. 3 and Figure 12) that to make to refrigerating chamber the 2nd air door 24b of refrigerating chamber the 2nd ajutage 12a air-supply be closed condition.Thus, can provide the refrigerator that cooling effectiveness is high.Below give reasons.

As the vacuum heat insulating material 60(of the refrigerator of present embodiment with reference to Fig. 7), the vacuum heat insulating material that the outer packaging material of the metal level that involved thermal conductivity is high (being the laminated film that comprises aluminium-vapour deposition rete in the refrigerator of present embodiment) covers, move owing to producing more heat via outer packaging material in region apart from the not enough 50mm of periphery, so become the so-called heat bridge region that heat-insulating property reduces.Therefore,, if set airduct in the place ahead in heat bridge region, thermal losses becomes greatly and cooling effectiveness reduction.Therefore, wish in the place ahead in heat bridge region, not set airduct.Yet, in order to carry out well cooling in refrigerating chamber, need to cold air be guided to assigned position with airduct.Particularly, for cold air being delivered to reliably to the region (the region 2c of the refrigerator of present embodiment) because of the top of the difficult refrigerating chamber arriving of free convection cold air, airduct need to be configured to the top of refrigerating chamber.Follow this, in the place ahead in heat bridge region, set airduct.

Therefore, in the refrigerator of present embodiment, when by rearward vacuum heat insulating material 60 projection of refrigerating chamber the 1st ajutage 11a, more than beeline L from refrigerating chamber the 1st ajutage 11a end to the end of vacuum heat insulating material 60 is divided into 50mm mutually, make refrigerating chamber the 1st ajutage 11a become the adiabatic wind path of the little height of thermal losses, carry out under the cooling state of region 2c there is no need, it is open mode that enforcement makes to refrigerating chamber the 1st air door 24a of refrigerating chamber the 1st ajutage 11a air-supply, the operation mode that to make to refrigerating chamber the 2nd air door 24b of refrigerating chamber the 2nd ajutage 12a air-supply be closed condition, thereby become the cooling effectiveness high refrigerator that has suppressed the thermal losses that heat bridge causes.

And, in adiabatic wall, possesses overleaf vacuum heat insulating material 60, be configured to when by rearward vacuum heat insulating material 60 projection of refrigerating chamber the 1st ajutage 11a, refrigerating chamber the 1st ajutage 11a is accommodated in the region of the reflex part 60b inner side of vacuum heat insulating material 60, it is open mode that enforcement makes to refrigerating chamber the 1st air door 24a of refrigerating chamber the 1st ajutage 11a air-supply, the operation mode (with reference to Fig. 2, Fig. 3, Fig. 8 and Figure 12) that to make to refrigerating chamber the 2nd air door 24b of refrigerating chamber the 2nd ajutage 12a air-supply be closed condition.The reflex part of vacuum heat insulating material has outer packaging material due to overlapping, so the impact of heat bridge becomes greatly.Therefore, in the refrigerator of present embodiment, adopt above-mentioned formation, implement to have suppressed to result from the cooling running of the caused thermal losses of heat bridge of reflex part 60b, thereby make refrigerating chamber the 1st ajutage 11a become the adiabatic wind path of the little height of thermal losses, improved cooling effectiveness.

And, possess to than the shelf 46a of epimere, refrigerating chamber the 2nd ajutage 11b of the top side's of 46b region 2c air-supply and to than refrigerating chamber the 1st ajutage 11a of shelf 46a, the 46b of epimere region 2d air-supply on the lower, it is open mode that enforcement makes to refrigerating chamber the 1st air door 24a of refrigerating chamber the 1st ajutage 11a air-supply, the operation mode (with reference to Fig. 2, Fig. 3 and Figure 12) that to make to refrigerating chamber the 2nd air door 24b of refrigerating chamber the 2nd ajutage 12a air-supply be closed condition.Thus, carry out under the cooling state of region 2c there is no need, than the shelf 46a of epimere, the air layer of the top side's of 46b region 2c as the heat insulation layer that suppresses heat affecting from refrigerating chamber 2 upper walls and involve region 2d, play a role, so can carry out high cooling of efficiency.

And, less than the depth size separately of shelf 46a and shelf 46b to each distance (H1 shown in Fig. 3 and H2) of upper wall from shelf 46a and shelf 46b.Thus, it is open mode that enforcement makes to refrigerating chamber the 1st air door 24a of refrigerating chamber the 1st ajutage 11a air-supply, the operation mode that to make to refrigerating chamber the 2nd air door 24b of refrigerating chamber the 2nd ajutage 12a air-supply be closed condition, when the air layer of region 2c is played a role as heat insulation layer, be difficult for producing the convection current in the 2c of region, so improve the insulation effect of region 2c, can implementation efficiency better cooling.

And, though make refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which in open mode, the volume in the region that cold air all passes through jointly (volume of region 2e) is set littlely than the volume (2cHe region, region 2d volume altogether) of controlling independently the region of air-supply by the open and-shut mode of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b.Thus, even operating point changes to little air quantity side a little owing to producing frost, the impact that also can suppress cooling effect reduction manifests significantly.

And, make the minimum flow path cross sectional area of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b set than pressure fan in case 22 to blow out area little.Thus, suppress airduct possessive volume, and the circulating cold air of increase refrigerating chamber 2 is the wind path resistance in path.Therefore, become the refrigerator that cooling effectiveness and space efficiency are high.

And, make pressure fan 22 in the minimum stream sectional area ratio case of refrigerating chamber recurrent canal 15 to blow out area little.Thus, suppress airduct possessive volume, the circulating cold air that increases refrigerating chamber 2 is the wind path resistance in path.Therefore, become the refrigerator that cooling effectiveness and space efficiency are high.

And, make the minimum flow path cross sectional area of minimum stream sectional area ratio refrigerating chamber the 2nd ajutage 11b of refrigerating chamber the 1st ajutage 11a large.Thus, in the situation that the both sides of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b become open mode, by the refrigerating chamber as high adiabatic wind path, the 1st ajutage 11a flows out more cold air, so can implement to have suppressed the high cooling running of cooling effectiveness of thermal losses.

And, at the cold air of sending from refrigerating chamber the 1st ajutage 11a and common mobile path (the region 2e of the cold air sent from refrigerating chamber the 2nd ajutage 11b, deepfreeze chamber 3, refrigerating chamber return port 35, refrigerating chamber recurrent canal 15) on, possesses temperature sensor (deepfreeze room temperature sensor 42), in sensor detected temperatures lower than set point of temperature (lower than Tc_a) in the situation that, make to refrigerating chamber the 1st air door 24a of refrigerating chamber the 1st ajutage 11a air-supply, refrigerating chamber the 2nd air door 24b blowing to refrigerating chamber the 2nd ajutage 12a is for becoming closed condition (with reference to Fig. 2, Fig. 3, Fig. 4 and Figure 12).Thus, can prevent that the region (the region 2e in the refrigerating chamber of the refrigerator of present embodiment, deepfreeze chamber 3) that is jointly cooled by the air-supply from refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b is by exceedingly cooling and icing undesirable condition.

In addition, in the refrigerator of present embodiment, because not possessing cold air blow-off outlet, deepfreeze chamber 3 can not be cooled to set point of temperature yet, so the blow-off outlet blowing out to deepfreeze chamber 3 is not set, yet can deepfreeze chamber blow-off outlet be set at refrigerating chamber the 1st ajutage 11a or refrigerating chamber the 2nd ajutage 11b yet.And, also can be provided for controlling the deepfreeze chamber air door from the air-supply of deepfreeze chamber blow-off outlet, form the structure that easily maintains set point of temperature.

Embodiment 2

With reference to Figure 14～Figure 16, the 2nd embodiment of refrigerator of the present invention is described.Figure 14 means the longitudinal section of structure of refrigerating chamber of the refrigerator of the 2nd embodiment.Figure 15 means the front view of structure of refrigerating chamber of the refrigerator of the 2nd embodiment.Figure 16 means the schematic diagram of wind path structure of the refrigerator of the 2nd embodiment.Wherein, except the structure shown in Figure 14～Figure 16, identical with the refrigerator of the 1st embodiment, so description thereof is omitted.And in Figure 14～Figure 16, also description thereof is omitted for the functional part mark same-sign identical with the refrigerator of the 1st embodiment.

The refrigerator of present embodiment the back side of refrigerating chamber 2 possess from below the minimum flow path cross sectional area 1700mm of refrigerating chamber ajutage 11(that extends upward ²) (with reference to Figure 14 and Figure 15).At refrigerating chamber ajutage 11, possesses refrigerating chamber blow-off outlet 31a～31c(with reference to Figure 14).Be equipped with adjacently the minimum flow path cross sectional area 1640mm of refrigerating chamber the 1st recurrent canal 15a(with the right side of refrigerating chamber ajutage 11 ²).Top at refrigerating chamber the 1st recurrent canal 15a possesses return port 35a, 35b.And, at the back side, deepfreeze chamber, possess the minimum flow path cross sectional area 1400mm of refrigerating chamber the 2nd recurrent canal 15b( ²), at refrigerating chamber, the 2nd recurrent canal 15b possesses return port 35c(with reference to Figure 15).The inflow of returning to cold air of returning to refrigerating chamber the 1st recurrent canal 15a and refrigerating chamber the 2nd recurrent canal 15b is by being provided in refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b(in the back projection region of the adiabatic partition wall 51 of upside with reference to Figure 15) open and-shut mode control.

Next, with reference to Figure 16, suitably with reference to Figure 14 and Figure 15, the circulating cold air path of the refrigerating chamber of the refrigerator of cooling present embodiment is described.

As shown in figure 16, boost with pressure fan 22 in Quilt with air conditioning case after evaporimeter 21 heat exchanges, under the state of opening at refrigerating chamber the 1st air door 24a, refrigerating chamber ajutage 11 flow and from refrigerating chamber blow-off outlet 31a～31c to refrigerating chamber internal ratio shelf 46a, the 46b of epimere on the lower and than the top side's of shelf 46f of hypomere region 2d(with reference to Figure 14 and Figure 15) blow out.The cold air that blows to region 2d at the region 2e(that is provided with a pocket 47b with reference to Figure 14) flow, via than shelf 46a, the top side's of 46b region 2c(with reference to Figure 14 and Figure 15), arrive refrigerating

chamber return port

35a, 35b(with reference to Figure 15).From refrigerating

chamber return port

35a, 35b(with reference to Figure 15) flow into refrigerating chamber the 1st recurrent canal 15a(with reference to Figure 15) and cold air turn back to evaporimeter receiving room 9 and again carry out heat exchange with evaporimeter 21.

And under the state of opening at refrigerating chamber the 2nd air door 24b, cold air flows at refrigerating chamber ajutage 11, from refrigerating chamber blow-off outlet, 31a～31c blows to region 2d.The cold air that blows to region 2d flows at region 2e, via the region 2f(that is provided with a pocket 47c, ice making water tank 55 with reference to Figure 14 and Figure 15), and cooling deepfreeze chamber 3 and arrive refrigerating chamber return port 35c(with reference to Figure 15).From refrigerating chamber return port 35c, flow into refrigerating chamber the 2nd recurrent canal 15b(with reference to Figure 15) cold air turn back to evaporimeter receiving room 9 and again carry out heat exchange with evaporimeter 21.

And in the refrigerator of present embodiment, as shown in figure 15, when by rearward vacuum heat insulating material 60 projection of refrigerating chamber ajutage 11, the beeline L from refrigerating chamber ajutage 11 ends to the end of vacuum heat insulating material 60 is 100mm.And refrigerating chamber ajutage 11 is accommodated in the inner side of the reflex part 60b of vacuum heat insulating material 60.

As above, the refrigerator of present embodiment possesses refrigerating chamber ajutage 11, refrigerating chamber the 1st recurrent canal 15a and refrigerating chamber the 2nd recurrent canal 15b, when by rearward vacuum heat insulating material 60 projection of refrigerating chamber ajutage 11, the beeline L from refrigerating chamber ajutage 11 ends to the end of vacuum heat insulating material 60 is more than 50mm.And when by rearward vacuum heat insulating material 60 projection of refrigerating chamber ajutage 11, refrigerating chamber ajutage is accommodated in the inner side of the reflex part 60b of vacuum heat insulating material 60.Thus, the refrigerating chamber ajutage 11 of the cold air of the low temperature that flows is provided in to the position that has suppressed the thermal losses that causes because of heat bridge, thereby becomes the refrigerator that cooling effectiveness is high.

And, in the refrigerator of present embodiment, can control to the air-supply of ice making water tank 55 setting unit peripheries (region 2f) by the open and-shut mode of refrigerating chamber the 2nd air door 24b.That is, not no matter the region (

region

2d, 2f) which of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b all passes through jointly in open mode cold air arranges ice making water tank 55.Thus, ice making water tank 55 peripheries are difficult to by exceedingly cooling, suppress to carry out in order to prevent the water freezing in ice making water tank 55 heating of heater etc., so become the refrigerator that cooling effectiveness is high.

Embodiment 3

With reference to Figure 17～Figure 20, the 3rd embodiment of refrigerator of the present invention is described.Figure 17 means the longitudinal section of the structure in the case of refrigerator of the 3rd embodiment, and Figure 18 means the front view of structure of refrigerating chamber of the refrigerator of the 3rd embodiment, and Figure 19 means the schematic diagram of wind path structure of the refrigerator of the 3rd embodiment.And Figure 20 means the figure of combination of air door open and-shut mode of the refrigerator of the 3rd embodiment.Wherein, in Figure 17～Figure 20, the identical functional part of the refrigerator with the 1st embodiment is marked to same-sign, and also description thereof is omitted.

As shown in figure 18, the refrigerator of present embodiment in the back side of refrigerating chamber 2 substantial middle, possess refrigerating chamber the 1st ajutage 11a from extending upward below refrigerating chamber 2, at the minimum flow path cross sectional area 1400mm of refrigerating chamber the 1st ajutage 11a( ²) top possess the minimum flow path cross sectional area 1400mm of refrigerating chamber the 2nd ajutage 11b( ²), at the inlet portion of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b, possess respectively refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b.In addition, as shown in Figure 17 and Figure 18, refrigerating chamber the 1st air door 24a is provided in the back projection region of the adiabatic partition wall 51 of upside, and refrigerating chamber the 2nd air door 24b is provided in the roughly back (height and position of shelf 46a is set to the situation of lower end) of shelf 46a.

Next, with reference to Figure 19, suitably with reference to Figure 17 and Figure 18, the circulating cold air path of the refrigerator of present embodiment is described.

As shown in figure 19, having carried out pressure fan 22 in the Quilt with air conditioning case of heat exchange with evaporimeter 21 boosts, at refrigerating chamber the 1st air door 24a, be that open mode, refrigerating chamber the 2nd air door 24b are in closed condition situation, refrigerating chamber the 1st ajutage 11a flow and from refrigerating chamber blow-off outlet 31a～31c(with reference to Figure 18) only to the region 2d(in refrigerating chamber with reference to Figure 17 and Figure 18) blow out.The cold air that blows to region 2d at the region 2e(that is provided with pocket 47b, a 47c with reference to Figure 17), flow through deepfreeze chamber 3, arrive refrigerating chamber return port 35.And, at refrigerating chamber the 1st air door 24a, be that open mode and refrigerating chamber the 2nd air door 24b are be open mode in the situation that, cold air region 2d mobile at refrigerating chamber the 1st ajutage 11a and in from refrigerating chamber blow-off outlet 31a～31c to refrigerating chamber blows out, and region 2c mobile at refrigerating chamber the 2nd ajutage 11b and in from refrigerating chamber blow-off outlet 31d, 31e to refrigerating chamber blows out (with reference to Figure 17 and Figure 18).The cold airflow that blows to region 2c is crossed region 2e, the deepfreeze chamber 3 that is provided with pocket 47b, a 47c, ice making water tank 55, arrives refrigerating chamber return port 35.

Cooling cold air has been carried out in

region

2c, 2d, 2e and deepfreeze chamber 3 and from refrigerating chamber return port 35, flowed into the minimum flow path cross sectional area 1700mm of refrigerating chamber recurrent canal 15( ²), arrive evaporimeter receiving room 9 and again carry out heat exchange with evaporimeter 21.

In addition, in the refrigerator of present embodiment, also possess refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b, refrigerating chamber air door 26, vegetable compartment air door 27, the two states respectively with open mode and closed condition, so the open and-shut mode of air door be combined as 16 kinds, but refrigerating chamber the 2nd air door 24b is positioned at the downstream of refrigerating chamber the 1st air door 24a, so only, when refrigerating chamber the 1st air door 24a is open mode, can opens refrigerating chamber the 2nd air door 24b and blow via refrigerating chamber the 2nd ajutage 11b.

Figure 20 represents under state that refrigerating chamber the 1st air door 24a opens, carries out to the combination of the state of the air-supply of refrigerating chamber 2.As shown in figure 20, carrying out to the state of the air-supply of refrigerating chamber 2 is 8 kinds of state 1～state 8, and the wind path resistance in the circulating cold air path of each state is made as to R1～R8.Wherein, in " size of wind path resistance " hurdle, about the magnitude relationship of R1～R8, according to wind path resistance order from big to small, be numbered with 1～8 numbering.That is, the magnitude relationship of R1～R8 is " R4<R8<R3<R7LEssT. LTssT.LTR2<R6<R1< R5 ".In the refrigerator of present embodiment, the operating point being determined by the characteristic intersection point of air volume-static pressure of pressure fan 22 in the resistance curve of the resistance R1～R8 of state 1～state 8 and case is all in centrifugal basin.

As above, in the refrigerator of present embodiment, refrigerating chamber the 2nd air door 24b is positioned at the downstream of refrigerating chamber the 1st air door 24a, so without being set up in parallel refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b.Therefore, can set compactly refrigerating chamber ajutage, become the refrigerator of the minimizing that has suppressed food storing space.

As above, various embodiments of the present invention play following effect.

, possesses storeroom (refrigerating chamber 2, deepfreeze chamber 3), cooler 21, the axial flow fan 22 that the cold air that has carried out heat exchange with cooler 21 is sent, the cold air of being sent by axial flow fan 22 is guided to the air-supply path 11 of storeroom, the cold air that makes to deliver to storeroom returns to the return path 15 of cooler 21, air supply path through 11 and at least one party of return path 15 there is individual path (refrigerating chamber the 1st ajutage 11a of the path branches that cold air passes through, refrigerating chamber the 2nd ajutage 11b), the wind path resistance control module 24 that possesses the wind path resistance of controlling individual path, storeroom has the 1st cooling independent cooled region 2d of cold air in the path (refrigerating chamber the 1st ajutage 11a) being passed in individual path, be passed the 2nd cooling independent cooled region 2c of cold air in another path (refrigerating chamber the 2nd ajutage 11b) in individual path, be passed the cooling common cooled region 2e of cold air in all paths of individual path, have the 1st independent cooled region 2d, any one of the 2nd independent cooled region 2c and common cooled region 2e or combine a plurality of and carry out cooling a plurality of air supply patterns, no matter in which kind of situation of the plurality of air supply pattern, axial flow fan 22 is controlled as becoming the operating point by little air quantity side than the characteristic minimal point of air volume-static pressure.

Thus, the minimizing degree of air quantity diminishes, so no matter in which kind of situation of a plurality of air supply patterns (no matter open refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which), can both suppress the reduction of the cooling effectiveness of the region 2e that cold air passes through jointly.

In addition, be not limited to refrigerating chamber 2, deepfreeze chamber 3, at other storeroom, also can be suitable for above-mentioned formation, so can similarly obtain high cooling effectiveness.

And, possesses storeroom (refrigerating chamber 2, deepfreeze chamber 3), cooler 21, the axial flow fan 22 that the cold air that has carried out heat exchange with cooler 21 is sent, the cold air of being sent by axial flow fan 22 is guided to the air-supply path 11 of storeroom, the cold air that makes to deliver to storeroom returns to the return path 15 of cooler 21, air supply path through 11 and at least one party of return path 15 there is individual path (refrigerating chamber the 1st ajutage 11a of the path branches that cold air passes through, refrigerating chamber the 2nd ajutage 11b), the wind path resistance control module 24 that possesses the wind path resistance of controlling individual path, storeroom has the 1st cooling independent cooled region 2d of cold air in the path (refrigerating chamber the 1st ajutage 11a) being passed in individual path, be passed the 2nd cooling independent cooled region 2c of cold air in another path (refrigerating chamber the 2nd ajutage 11b) in individual path, be passed the cooling common cooled region 2e of cold air in all paths of individual path, have the 1st independent cooled region 2d, any one of the 2nd independent cooled region 2c and common cooled region 2e or combine a plurality of and cooling a plurality of air supply patterns, no matter in which kind of situation of the plurality of air supply pattern, make to become the operating point flowing in centrifugal basin that blows out of axial flow fan 22.

Thus, if be configured to operating point in centrifugal basin, even the wind path resistance increment along with white generation, the minimizing degree of air quantity is also suppressed must be less, and, also can avoid entering and sometimes move unsettled right rising characteristic territory, so no matter in which kind of situation of a plurality of air supply patterns (no matter make refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which become open mode), also can become the region 2e suitably cold air being passed through jointly and carry out the refrigerator that cooling cooling effectiveness is high.

And the volume settings of common cooled region 2e is less than the volume of the 1st independent cooled region 2d and the 2nd independent cooled region 2c.Thus, even operating point changes to little air quantity side a little owing to producing frost, the impact that also can suppress the reduction of cooling effectiveness manifests significantly.

And, in arbitrary situation of common cooled region 2e or a plurality of air supply patterns cold air all jointly the region of mobile return path 15 possess temperature detecting unit 42, being become set point of temperature by the detected temperature of temperature detecting unit 42 following in the situation that, stop the air-supply to storeroom.Thus, can prevent that all jointly the region of mobile return path 15 is exceedingly cooling and icing by cold air in arbitrary situation of common cooled region 2e or a plurality of air supply patterns, can improve cooling effectiveness.

In addition, the invention is not restricted to each above-mentioned embodiment, comprise various variation.For example, the operating point being determined by the air volume-static pressure characteristic of axial flow fan and wind path resistance is in centrifugal basin, the air volume-static pressure characteristic of axial flow fan that can be based on using decides wind path structure, also can be after determining wind path structure, design or the axial flow fan of selection operating point in centrifugal basin.Or, in the situation that produce the not combination of the open and-shut mode of the air door in centrifugal basin of operating point, control as avoiding the use of its combination, or make air door in half-open position (for example, 45 ° of angle of release degree), adjust and make the operating point in axial flow territory or right rising characteristic territory in centrifugal basin.And, also can increase the Segmentation Number of ajutage or recurrent canal.And, as temperature detecting unit, can be suitable for the known temperature sensors such as thermistor (thermistor), thermocouple, semiconductor temperature sensor, digital temperature sensor, analog temperature sensor.And, also can adopt the unit of the detection reserve that possesses optical sensor, infrared ray sensor etc., the configuration of the reserve of combine detection and the detected temperatures of temperature detecting unit, thus based on this, control the switching of air door, the structure of air-supply.

That is, the above embodiments are at length illustrated in order easily the present invention to be described, but are not necessarily confined to possess the mechanism of illustrated whole structure.

Claims

1. a refrigerator, it is characterized in that, possess storeroom, cooler, will carry out axial flow fan that the cold air after heat exchange sends, the cold air of being sent by this axial flow fan is guided to the return path that described cooler is returned in the air-supply path of described storeroom, the cold air that makes to deliver to described storeroom with described cooler

At least one party of described air supply path warp and described return path there is path branches that cold air passes through individual path,

The wind path resistance control module that possesses the wind path resistance of controlling this individual path,

Described storeroom has the 2nd cooling independent cooled region of the cold air that is passed the 1st cooling independent cooled region of the cold air in a path in described individual path, is passed another path in described individual path, is passed the cooling common cooled region of cold air in all paths of described individual path

Have any or a plurality of combinations of described the 1st independent cooled region, described the 2nd independent cooled region and described common cooled region carried out to cooling a plurality of air supply patterns,

Under arbitrary pattern in the plurality of air supply pattern, described axial flow fan is all controlled by the mode of the operating point of little air quantity side to become than the characteristic minimal point of air volume-static pressure.

2. a refrigerator, it is characterized in that, possess storeroom, cooler, will carry out axial flow fan that the cold air after heat exchange sends, the cold air of being sent by this axial flow fan is guided to the return path that described cooler is returned in the air-supply path of described storeroom, the cold air that makes to deliver to described storeroom with described cooler

Have any one or a plurality of combinations of described the 1st independent cooled region, described the 2nd independent cooled region and described common cooled region carried out to cooling a plurality of air supply patterns,

Under arbitrary pattern in the plurality of air supply pattern, it is all the operating point flowing in centrifugal basin that blows out of described axial flow fan.

3. refrigerator according to claim 1 and 2, is characterized in that,

The volume settings of described common cooled region must be less than the volume of described the 1st independent cooled region and described the 2nd independent cooled region.

4. refrigerator according to claim 1 and 2, is characterized in that,

In the region of the described return path that cold air all flows jointly under arbitrary pattern of described common cooled region or described a plurality of air supply patterns, possess temperature detecting unit,

Being become set point of temperature by the detected temperature of described temperature detecting unit following in the situation that, stop the air-supply to described storeroom.