CN103629877B

CN103629877B - Refrigerator

Info

Publication number: CN103629877B
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 Air Conditioning Systems Co Ltd
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2012-08-23
Filing date: 2013-08-02
Publication date: 2015-11-04
Anticipated expiration: 2033-08-02
Also published as: JP5909426B2; KR20140026243A; CN103629877A; JP2014040966A; KR101445203B1

Abstract

Refrigerator of the present invention possesses storeroom, cooler, by with cooler heat exchange after the axial flow fan sent of cold air, the cold air sent is guided to the air-supply path of storeroom, cold air is made to return the return path of cooler, the at least one party of air-supply path and return path has individual path, possesses the wind path resistance control unit of the wind path resistance controlling individual path, storeroom has the 1st independent cooled region of the cold air cooling in the path be branched in path, be branched the 2nd independent cooled region of the cold air cooling in another path in path, be branched the common cooled region of the cold air cooling in all paths in path, have the 1st independent cooled region, the multiple air supply patterns cooled are carried out in any one or multiple combinations of the 2nd independent cooled region and common cooled region, under arbitrary pattern in the plurality of air supply pattern, axial flow fan all controls than the mode of the characteristic minimal point of air volume-static pressure by the operating point of little air quantity side to become.

Description

Refrigerator

Technical field

The present invention relates to refrigerator.

Background technology

As the background technology of the art, there are Japanese Unexamined Patent Publication 2012-26677 publication (patent document 1) and Japanese Unexamined Patent Publication 10-54642 publication (patent document 2).

In patent document 1, disclose a kind of two airduct air doors at refrigerating chamber with inboard blowout wind path, ceiling side blowout wind path and switching wind path, the detected temperatures based on the inboard temperature sensor of inboard blowout wind path and the ceiling side temperature sensor of ceiling side blowout wind path controls two airduct air door thus controls the deep freezer (patent document 1, Fig. 6 etc.) of the air conditioning quantity in refrigerating chamber.

In addition, in patent document 2, disclose a kind of at each local set temperature detecting unit, opening and closing air door and the airduct of transporting cold wind is set in each region, control the deep freezer (patent document 2, Fig. 1 etc.) of whether transporting cold wind based on the temperature detected.

Prior art document

Patent document

Patent document 1: Japanese Unexamined Patent Publication 2012-26677 publication

Patent document 2: Japanese Unexamined Patent Publication 10-54642 publication

Summary of the invention

But patent document 1 and the refrigerator described in patent document 2 (deep freezer), all do not take into full account the structure of wind path, have the situation that cooling effectiveness is not high enough.

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

In order to solve above-mentioned problem, such as, adopt the formation described in claims.The application comprises the method for the above-mentioned problem of multiple solution, be such as, possesses storeroom, cooler, by the axial flow fan that the cold air after carrying out heat exchange with described cooler is sent, the cold air sent by this axial flow fan is guided to the air-supply path of described storeroom, the cold air delivering to described storeroom is made to return the return path of described cooler, the at least one party of described air-supply path and described return path has the individual path of the path branches that cold air passes through, possesses the wind path resistance control unit of the wind path resistance controlling this individual path, described storeroom has the 1st independent cooled region cooled by the cold air by the path of in described individual path, by the 2nd independent cooled region of the cold air cooling by another path in described individual path, by the common cooled region of the cold air in all paths by described individual path cooling, have described 1st independent cooled region, the multiple air supply patterns cooled are carried out in any one or multiple combinations of described 2nd independent cooled region and described common cooled region, under arbitrary pattern in the plurality of air supply pattern, described axial flow fan all controls than the mode of the characteristic minimal point of air volume-static pressure by the operating point of little air quantity side to become.

According to the present invention, be directed to the wind path of single storeroom in switching and carry out in the refrigerator cooled, obtaining 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 is the longitudinal section of the structure in the case of the refrigerator representing the 1st embodiment of the present invention.

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

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

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

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

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

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

Fig. 9 is the figure of the combination of the air door open and-shut mode of the refrigerator representing 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 the blowout of the pressure fan of the refrigerator of the 1st embodiment of the present invention flows to.

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

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

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

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

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

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

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

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

Figure 20 is the figure of the combination of the air door open and-shut mode of the refrigerator representing 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 room, 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 unit), 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) in 51-upside, the adiabatic partition wall (separating part) in 52-downside, 55-ice making water tank, 60-vacuum heat insulating material.

Detailed description of the invention

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 is the longitudinal section of the structure in the case of the refrigerator representing present embodiment.Fig. 3 is the front view of the structure of the refrigerating chamber of the refrigerator representing present embodiment.Fig. 4 is the schematic diagram of the wind path structure of the refrigerator representing present embodiment.Fig. 5 be the refrigerator representing present embodiment case in the figure of pressure fan.Fig. 6 is the figure of the refrigerating chamber air door of the refrigerator representing 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 such as about 5 DEG C.And ice-making compartment 4, epimere refrigerating chamber 5 and hypomere refrigerating chamber 6 is the storeroom (following, ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6 are generically and collectively referred to as refrigerating chamber 7) of the cryogenic temperature section of such as-18 DEG C to about-20 DEG C.

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

As shown in Figure 2, be adiabatic casing 50 outside the case of the refrigerator of present embodiment and in case and separate, 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 is provided with vacuum heat insulating material 60 (for the installment state of vacuum heat insulating material 60 by aftermentioned) overleaf.

Multiple pocket 47a ~ 47c are possessed inside the storeroom of refrigerating-chamber door 2a, 2b.And, in refrigerating chamber 2, possess multiple shelf 46a ~ 46f (shelf 46a ~ 46f is with reference to Fig. 3).

And ice-making compartment 4, epimere refrigerating chamber 5, hypomere refrigerating chamber 6 and vegetable compartment 8 possess with door 4a, 5a, 6a, the 8a in the front being arranged on each storeroom integratedly at accommodating container 4b, 5b, 6b, 8b of fore-and-aft direction movement.Door 4a, 5a, 6a, 8a pull out accommodating container 4b, 5b, 6b, 8b respectively by moving not shown handle portion to front side with hand.

The refrigerator of present embodiment as shown in Figure 2, refrigerating chamber 2 is separated to insulated property by the adiabatic partition wall 51 in upside with, epimere refrigerating chamber 5 and ice-making compartment 4 (with reference to Fig. 1), and hypomere refrigerating chamber 6 and vegetable compartment 8 are separated to insulated property by the adiabatic partition wall 52 in downside.In addition, between the adiabatic partition wall 51 of shelf 46f and upside, deepfreeze (chilled) room 3 remaining about-1 ~ 1 DEG C is possessed as an example.Therefore, in the refrigerator of present embodiment, in the storage area of the top of the adiabatic partition wall 51 in upside, the region except the deepfreeze room 3 remaining low temperature becomes the storeroom of refrigerated storage temperature section.In addition, also deepfreeze room 3 can be suppressed 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, in evaporimeter receiving room 9, possess evaporimeter 21 (be fin tube heat exchanger as an example) as cooling unit.And, above evaporimeter 21, possess pressure fan 22 in case as blowing unit.

As shown in Figure 5, the axial flow fan (propeller type fan) of pressure fan 22 to be the external diameters driven by the motor (not shown) in the motor incorporating section 92 of central authorities the be blade 91 of 110mm in the case of the refrigerator of present embodiment.In addition, motor incorporating section 92 is linked by support 93 and housing 94.And, blowout area (π × [0.5 × outer blade diameter] ²) be 9503.3mm as an example ².

And, as shown in Figure 2, possess Defrost heater 56 in the below of evaporimeter receiving room 9.The defrosting that the frost be formed on the wall of the evaporimeter receiving room 9 of evaporimeter 21 and its periphery passes through to be energized to Defrost heater 56 and carries out operates and melts.After the defrost water that frost melts and produces flow into the aqueduct 57 of the bottom being arranged at evaporimeter receiving room 9, arrive the evaporating pan 59 being configured at Machine Room 10 via drainpipe 58.Defrost water in evaporating pan 59 is by being disposed in the heating of compressor 23 in Machine Room 10 and condenser (not shown) and being evaporated.

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

As shown in Figure 3, refrigerating chamber the 1st ajutage 11a, refrigerating chamber the 2nd ajutage 11b that extend upward is from below possessed in the substantial middle at the back side of refrigerating chamber 2.Refrigerating chamber the 1st ajutage 11a on the left of refrigerating chamber 2 back side possesses the refrigerating chamber blow-off outlet 31a ~ 31c of shelf 46a, 46b shelf 46f region 2d by the top (with reference to Fig. 2 and Fig. 3) on the lower and than lowermost blown to by cold air than uppermost.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 refrigerating chamber the 2nd ajutage 11b on the left of refrigerating chamber 2 back side possesses refrigerating chamber blow-off outlet 31d, 31e of the region 2c (with reference to Fig. 2 and Fig. 3) of the top blowing to shelf 46a, 46b.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 change height and position (wherein, shelf 46f is fixing) in prescribed limit.Therefore, the size variation of region 2c and region 2d, but 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 respective depth size of shelf 46a and shelf 46b.And making the rational height of shelf 46a, 46b be the volume of region 2c under minimum state is 50L, and the volume of region 2d is 140L, and the volume arranging the region 2e of pocket 47b, 47c and ice making water tank 55 is 40L.

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

And as shown in Figure 6, refrigerating chamber air door 24 possesses opening 82a, 82b in motor incorporating section about 81.Opening 82a and opening 82b is undertaken opening closedown by opening-closing plate 83a, 83b.Specifically, by being arranged on the stepper motor (not shown) in motor incorporating section 81, opening-closing plate 83a, 83b can control respectively in the scope of the full closing state of angle of release degree 0 degree to the full open mode of angle of release degree 90 degree.Below, the function of the open and-shut mode of the control opening 82a in the function of refrigerating chamber air door 24 is set to refrigerating chamber the 1st air door 24a, the function of open and-shut mode that controls opening 82b is set to 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 is separately positioned on the entrance of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b, controls the air-supply to refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b.

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

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

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

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

As shown in Figure 7, vacuum heat insulating material 60 passes through core 61 (being such as mineral wool) compression seal together with adsorbent 62 (being such as synthetic zeolite), be inserted in outer packaging material 64 (comprising the laminated film of aluminium-vapour deposition rete), after vacuum filtration, thermally welded manufacture is carried out to end and forms.Therefore, the thermally welded portion 60a shown in Fig. 7 is there is in the end of vacuum heat insulating material, but in the refrigerator of present embodiment, as shown in Figure 8, thermally welded portion 60a to be gone back to inside case (foamed heat insulation material side) and fixing after, foamed heat insulation 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 turned back by thermally welded portion 60a in periphery.In addition, in the present embodiment, vacuum heat insulating material 60 is pasted onto outer container 1a inner face by stickers such as PURs, but is not limited thereto.Such as, can be the structure being pasted onto interior case 1b inner face, also can be the structure being configured in interior case 1b and outer container 1a via support unit, and regardless of which kind of structure, all by thermally welded portion 60a, inside case, (foamed heat insulation material side) is turned back and configure.

In addition, after in inner bag 63 (being such as polyethylene), storage core 61 is received in outer packaging material 64 as temporary transient compressive state, again to internal bag 63 and outer packaging material 64 in carry out the structure of compression seal, then improve the operability of core 61, manufacturing process's efficient activity can be made.

As is shown in phantom in fig. 3, vacuum heat insulating material 60 is installed in the back side adiabatic wall of refrigerator, but has above-mentioned reflex part 60b (region by 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, be 100mm from the beeline L of refrigerating chamber the 1st ajutage 11a end to the end of vacuum heat insulating material 60.And refrigerating chamber the 1st ajutage 11a is accommodated in and compares regional center in the inner part than the reflex part 60b of vacuum heat insulating material 60.Thereby, it is possible to suppress the impact that the so-called heat bridge phenomenon of heat conduction brings by the metal level of outer packaging material 64 of vacuum heat insulating material 60 not relate to refrigerating chamber the 1st ajutage 11a.Detailed content is 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, in the Quilt with air conditioning case having carried out heat exchange with evaporimeter 21, pressure fan 22 is boosted, under the state that refrigerating chamber the 1st air door 24a opens, flow at refrigerating chamber the 1st ajutage 11a and blow out to the region 2d (with reference to Fig. 2 and Fig. 3) in refrigerating chamber from refrigerating chamber blow-off outlet 31a ~ 31c.The cold airflow blowing to region 2d, through being provided with pocket 47b, a 47c, the region 2e (with reference to Fig. 2 and Fig. 3) of ice making water tank 55, deepfreeze room 3, arrives refrigerating chamber return port 35.On the other hand, under the state that refrigerating chamber the 2nd air door 24b opens, flow in refrigerating chamber the 2nd ajutage 11b and blow out to the region 2c (with reference to Fig. 2 and Fig. 3) in refrigerating chamber from refrigerating chamber blow-off outlet 31d, 31e.Blow to the cold airflow of region 2c through being provided with pocket 47b, a 47c, the region 2e (with reference to Fig. 2 and Fig. 3) of ice making water tank 55, deepfreeze room 3, and arrive refrigerating chamber return port 35.

To the cold air that region 2c, 2d, 2e and deepfreeze room 3 cool, (such as minimum flow path cross sectional area is 1700mm to enter refrigerating chamber recurrent canal 15 from refrigerating chamber return port 35 ²), arrive evaporimeter receiving room 9, again carry out heat exchange with evaporimeter 21.

Next, under the state that refrigerating chamber air door 26 is opened, the cold air after being boosted by pressure fan in case 22 flows in refrigerating chamber ajutage 13, and from refrigerating chamber blow-off outlet 33a ~ 33c (with reference to Fig. 2) blowout to refrigerating chamber 7.From refrigerating chamber return port 36, evaporimeter receiving room 9 is back to the cold air that refrigerating chamber cools, again carries out heat exchange with evaporimeter 21.

Under the state that vegetable compartment air door is opened, the cold air after being boosted by pressure fan in case 22 flows and blows out to vegetable compartment 8 from vegetable compartment blow-off outlet 34 in vegetable compartment ajutage 14.From vegetable compartment return port 37, vegetable compartment recurrent canal 17 is entered to the cold air that vegetable compartment 8 cools, arrives evaporimeter receiving room 9, again carry 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 is the figure of the combination of the open and-shut mode representing air door, Figure 10 is the figure representing the air volume-static pressure characteristic of pressure fan 22 in case and the relation of operating point.And Figure 11 is the schematic diagram representing that the blowout of the air that pressure fan 22 blows out in case flows to.

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 the two states of open mode and closed condition respectively, thus the open and-shut mode of air door be combined as 16 kinds.Fig. 9 represent in refrigerating chamber the 1st air door 24a wherein or refrigerating chamber the 2nd air door 24b at least one be open mode, carry out the combination of the state of the air-supply to refrigerating chamber 2.

As shown in Figure 9, carrying out is 12 kinds of state 1 ~ state 12 to the state of the air-supply of refrigerating chamber 2, 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, go up the numbering of 1 ~ 12 according to wind path resistance order note from small to large.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 is air volume-static pressure characteristic and the state 1 ~ state 6 shown in Fig. 9 representing pressure fan 22 in case.

As shown in Figure 10, in case, the air volume-static pressure characteristic of pressure fan 22 has slope from the maximal point transferring decline to that rises in Wind Volume side, has slope from the minimal point transferring rising to that declines in little air quantity side.This is the characteristic can seen in general axial flow fan, if make air quantity reduce from the starting point that static pressure is 0, then, when arriving regulation air quantity, produces the stall that air-flow is peeled off from blade.The point producing stall is called stall point, and in general, the maximal point of air volume-static pressure characteristic is regarded as stall point.If reduce air quantity from stall point, then occur the region (right rising characteristic territory) that static pressure reduces, after reaching minimal point, due to centrifugal action, static pressure rises again, reaches the cut off that air quantity is 0.And, in the Wind Volume side from starting point to maximal point, as shown in the arrow in Figure 11 (a), the air that pressure fan 22 is produced by boasting 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 that pressure fan 22 is produced by boasting in case is (centrifugal direction) diverging flow radially.Therefore, following, will from starting point to maximal point till be called in " axial flow territory ", will from maximal point to minimal point till be called in " right rising characteristic territory ", will from minimal point to cut off till be called in " centrifugal basin ".

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 when 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 Fig. 10, but the air quantity of resistance R7 ~ R12 is Q7 ~ Q12, if represent the magnitude relationship of air quantity, be then " Q6>Q12>Q4>Q10G reatT.GreaT.GTQ5>Q11>Q3Great T.GreaT.GTQ9>Q1>Q7GreatT.Gre aT.GTQ2>Q8 ".That is, the size that there is the wind path resistance of each state is less, the trend that air quantity is larger.

The refrigerator of present embodiment possesses the temperature setting device etc. (not shown) of temperature setting carrying out refrigerating chamber 2, deepfreeze room 3, refrigerating chamber 7, vegetable compartment 8, is configured with the control substrate 49 (with reference to Fig. 2) of the memory, interface circuit etc. that have carried CPU, ROM, RAM etc. in the upper back side of the upper wall of refrigerator main body 1.Control substrate 49 to be connected with 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 the temperature setting device etc. be arranged in refrigerating-chamber door 2a, case.

The ON/OFF control, the rotating speed that carry out pressure fan 22 in the ON/OFF of compressor 23, the control starting each driver (not shown) of refrigerating chamber air door 24, refrigerating chamber air door 26 and vegetable compartment air door 27, case by carrying the program of ROM in advance control, notify the alarm bell ON/OFF control of door open mode, form control device by these.

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

Figure 12 is the control flow chart of the control in the cooling running of the refrigerator representing present embodiment.The refrigerator of present embodiment is by the connection of power supply, and compressor 23 carries out driving and beginning to cool down running (beginning).At this, omit in case the state of a control before fully cooling off, be described to the moment meeting the condition that compressor 23 drives from sufficiently cooled in case, that compressor 23 is in stopping state.When meeting the drive condition of compressor 23 (drive condition about compressor 23 is aftermentioned), in compressor 23 and case, pressure fan 22 carries out driving (step S101), judges whether the condition of opening of refrigerating chamber the 1st air door 24a is set 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 more than Tr1_a (in the refrigerator of present embodiment Tr1_a=3 DEG C) " 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 more than Tr1_b (in the refrigerator of present embodiment Tr1_b=7 DEG C) " when sets up.When step S102 sets up ("Yes"), refrigerating chamber the 1st air door 24a is opened (step S103), send cold air to the region 2d (with reference to Fig. 2 or Fig. 3) in refrigerating chamber 2.

Next, judge whether the condition of opening of refrigerating chamber the 2nd air door 24b is set 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 more than Tr2_a (in the refrigerator of present embodiment Tr2_a=4 DEG C) " 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 more than Tr2_b (in the refrigerator of present embodiment Tr2_b=8 DEG C) " when sets up.When step S104 sets up ("Yes"), refrigerating chamber the 2nd air door 24b is opened (step S105), send cold air to the region 2c (with reference to Fig. 2 or Fig. 3) in refrigerating chamber 2.

Next, judge whether the closedown condition of refrigerating chamber the 1st air door 24a is set up (step S106).In the refrigerator of present embodiment, the closedown condition of refrigerating chamber the 1st air door 24a " detected temperatures of refrigerating chamber the 1st temperature sensor 41a is below Tr1_c (in the refrigerator of present embodiment Tr1_c=2 DEG C) " or, " detected temperatures of deepfreeze room temperature sensor 42 is below Tc_a (in the refrigerator of present embodiment Tc_a=﹣ 1 DEG C) " when, sets up.When step S106 sets up ("Yes"), refrigerating chamber the 1st air door 24a is closed (step S107).

Then, judge whether the closedown condition of refrigerating chamber the 2nd air door 24b is set up (step S108).In the refrigerator of present embodiment, the closedown condition of refrigerating chamber the 2nd air door 24a " detected temperatures of refrigerating chamber the 2nd temperature sensor 41b is below Tr2_c (in the refrigerator of present embodiment Tr2_c=3 DEG C) " or, " detected temperatures of deepfreeze room temperature sensor 42 is below Tc_a " when, sets up.When step S108 sets up ("Yes"), refrigerating chamber the 2nd air door 24b is closed (step S109).

Next, judge whether the condition of opening of refrigerating chamber air door 26 is set up (step S110).In the refrigerator of present embodiment, the condition of opening of refrigerating chamber air door 26 " compressor 23 is driving condition, refrigerating chamber the 1st air door 24a is closed condition, refrigerating chamber the 2nd air door 24b be closed condition " or, " compressor be driving condition, the detected temperatures of freezer temperature sensor 43 be more than Tf_a (in the refrigerator of present embodiment Tf_a=﹣ 14 DEG C) " when, sets up.When step S110 sets up ("Yes"), refrigerating chamber air door 26 is opened, and send cold air (step S111) in refrigerating chamber 7.

Then, judge whether the stop condition of pressure fan 22 in case is set 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 halted state, refrigerating chamber the 1st air door 24a is closed condition, refrigerating chamber the 2nd air door 24b be closed condition ".When step S112 sets up ("Yes"), stop pressure fan 22 in case.

Next, judge whether the stop condition of compressor 23 is set up (step S114).In the refrigerator of present embodiment, the stop condition of compressor 23 was set up in " detected temperatures of freezer temperature sensor 43 is below Tf_b (in the refrigerator of present embodiment Tf_b=﹣ 20 DEG C) ".In the invalid situation of step S114 ("No"), again return the judgement of step S102.

When step S114 sets up ("Yes"), compressor 23 stops, and refrigerating chamber air door 26 is closed (step S115).Next, judge whether the drive condition of compressor 23 is set up (step S116).In the refrigerator of present embodiment, the drive condition of compressor 23 was set up in " detected temperatures of freezer temperature sensor 43 is more than Tf_c (in the refrigerator of present embodiment Tf_c=﹣ 16 DEG C) ".In the invalid situation of step S116 ("No"), again return the judgement of step S102.And, when step S116 sets up ("Yes"), driven pressure fan 22 in compressor 23, case by step S101, move on to the judgement of step S102.

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

Above, describe the structure of the refrigerator of present embodiment, below, the effect that the refrigerator of present embodiment plays is described.

The refrigerator of present embodiment, when at least one party of refrigerating chamber the 1st air door 24a or refrigerating chamber the 2nd air door 24b is in open mode, makes operating point compare more by little air quantity side (centrifugal basin) (with reference to Figure 10) at the minimal point of the air volume-static pressure characteristic than pressure fan in case 22.Thereby, it is possible to the refrigerator providing cooling effectiveness 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, be provided with refrigerating chamber the 1st temperature sensor 41a of detected temperatures at the region 2d cooled mainly through refrigerating chamber the 1st ajutage 11a, be provided with refrigerating chamber the 2nd temperature sensor 42b of detected temperatures at the region 2c cooled mainly through refrigerating chamber the 2nd ajutage 11b.Detected temperatures based on refrigerating chamber the 1st temperature sensor 41a and refrigerating chamber the 2nd temperature sensor 42b controls 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, then the region 2c in refrigerating chamber 2 and region 2d (with reference to Fig. 2 or Fig. 3) completes cooling with the short time, if air output is little, although then cool time elongated, reliably can be cooled to setting.That is, about region 2c, region 2d, no matter air output how, not have mistake and the deficiency of cooling, so can obtain the high efficiency state of cooling.On the other hand, no matter make in refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which become open mode, as long as any one party in region 2e refrigerating chamber the 1st air door 24a that cold air passes through jointly and refrigerating chamber the 2nd air door 24b is in open mode, just cooled, so do not suppress mistake and the deficiency of cooling by switching ventilation state.Such as, if excessive to the air output of region 2e, then the moment that region 2c or region 2d is sufficiently cooled, region 2e becomes the state too cooled, if air output is too small, then when region 2c or region 2d fully cools, region 2e is in the not enough state of cooling.Particularly, as the refrigerator of present embodiment, when the region 2e that cold air passes through jointly arranges ice making water tank 55, if region 2e is too cooled, then there is the situation of the water freezing in ice making water tank 55.Therefore, in order to prevent the icing heating needing heater etc. in ice making water tank 55, so correspondingly increase thermic load, cooling effectiveness reduces.

Therefore, require to adjust the rotating speed of pressure fan 22 in the wind path resistance in circulating cold air path under the state opening refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b, case, so as to become cold air is passed through jointly region 2e by the air output suitably cooled.

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

On the other hand, when operating point changes significantly, the rotating speed of pressure fan and the relationship change of air output in case, so be difficult to the air output obtaining specifying.In refrigerator (such as, patent document 1 or the refrigerator described in patent document 2) in the past, due to the reason of the following stated, and the operating point in circulating cold air path changes significantly sometimes, occurs the problem of the reduction of cooling effectiveness with this.

In general, axial flow fan is the pressure fan used in the axial flow territory (with reference to Figure 10) by Wind Volume side compared with stall point.Therefore, in order to compare, first illustrate and make the wind path resistance in circulating cold air path suppress less, the mode being in axial flow territory with operating point is formed the situation of wind path.

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

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

And the right rising characteristic territory action sometimes between axial flow territory and centrifugal basin is unstable.Therefore, in general, in order to obtain stable air output, wish to avoid, but when being formed wind path in the mode that operating point is in axial flow territory, sometimes along with the generation of frost, wind path resistance increases, and operating point enters right rising characteristic territory and faces the state that cannot obtain towards the stable air output of region 2e.

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

Wherein, such as distinguish that operating point is in centrifugal basin by following mode.

First, the air volume-static pressure characteristic of pressure fan monomer in case is measured based on JISB8330:2000.Next, the air quantity of refrigerator is measured.Figure 13 is the schematic diagram representing the state that the air quantity flowed to 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, utilize by the 1st difference gauge 103 of the differential pressure of the pressure of the inside measuring airduct 100 and outside pressure (atmospheric pressure), based on upstream side and downstream differential pressure and the throttling arrangement 102 of air quantity can be calculated, the 2nd difference gauge 104 of differential pressure measuring the downstream of the upstream side of throttling arrangement 102, apparatus for measuring air quantity that the pressure fan 101 of the upstream side of throttling arrangement is formed measure air quantity.Specifically, adjustment pressure fan 101 makes the differential pressure of the 1st difference gauge 103 be zero, can measure the air quantity flowed at refrigerating chamber return port 35 based on the 2nd difference gauge 104 now.Wherein, refrigerating-chamber door 2a, 2b are open mode, but the differential pressure of adjustment 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 throttling arrangement 102 and pressure fan 101 from the state that the arranges reversion described in Figure 13 the air in sucking-off airduct 100, thus measure the air quantity from blow-off outlet blowout.Such as, if arrange airduct 100 to guide the mode from the air-supply of the blow-off outlet 31a ~ 31c of refrigerating chamber the 1st ajutage 11a, become the mode of zero to adjust pressure fan 101 with the differential pressure of the 1st difference gauge 103, then can measure the blowout air quantity from refrigerating chamber the 1st ajutage 11a based on the differential pressure of the 2nd difference gauge 104.In addition, herein illustrating an example of the air measuring method utilizing throttle mechanism, but other the mechanism such as thermal flowmeter such as also can be utilized 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 clear and definite, so according to both, can distinguish whether operating point is in centrifugal basin with precision enough in practicality.

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

In general, in axial flow fan, flow vertically in axial flow territory, radially flow in centrifugal basin (with reference to Figure 11).Therefore, when having the pressure fan of the air volume-static pressure characteristic that maximal point and minimal point manifest ambiguously, axial flow territory and centrifugal basin can be distinguished according to the change of blowout stream.Specifically, as shown in Figure 11, prefer virtual (circular cone table top) of the front inclination 45 degree of the leading edge 91a of the blade periphery from axial flow fan 22, the inner side (front) in face is set to front region, the outside in face is set to radial zone, when judging that air-flow blows to front region, operating point is in axial flow territory, and when air-flow blows to radial zone, operating point is in centrifugal basin.Therefore, such as, while 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, being judged to be axial flow territory when the point of the maximum representing wind speed enters front region, being judged to be centrifugal basin when entering radial zone.By the way, from the wind speed of pressure fan blowout, there is axial composition, radial direction (centrifugal direction) composition and circumferential composition.Therefore, if such as measure with non-direction airspeedometer, then what measure is wind speed after the synthesis of these compositions, but relatively to diminish towards the air-flow of axis, can pick out the centrifugal basin being in and being formed towards the air-flow of radial direction.

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

As the vacuum heat insulating material 60 (with reference to Fig. 7) of the refrigerator of present embodiment, the vacuum heat insulating material that the outer packaging material (being the laminated film comprising aluminium-vapour deposition rete in the refrigerator of present embodiment) of the metal level that involved thermal conductivity is high covers, move owing to producing more heat via outer packaging material apart from periphery less than the region of 50mm, so become the so-called heat bridge region of heat-insulating property reduction.Therefore, if arrange airduct in the front in heat bridge region, then thermal losses becomes large and cooling effectiveness reduction.Therefore, it is desirable to not arrange airduct in the front in heat bridge region.But, in order to carry out the cooling in refrigerating chamber well, need, with airduct, cold air is guided to assigned position.Particularly, in order to cold air reliably being delivered to the region (the region 2c of the refrigerator of present embodiment) of the top of the refrigerating chamber that cold air not easily arrives because of free convection, top airduct being configured to refrigerating chamber is needed.With this, arrange airduct in the front in heat bridge region.

Therefore, in the refrigerator of present embodiment, when the rearward vacuum heat insulating material 60 of refrigerating chamber the 1st ajutage 11a is projected, more than 50mm is divided into from refrigerating chamber the 1st ajutage 11a end to the beeline L phase of the end of vacuum heat insulating material 60, refrigerating chamber the 1st ajutage 11a is made to become the adiabatic wind path of the little height of thermal losses, under the state that there is no need the cooling carrying out region 2c, implement to make refrigerating chamber the 1st air door 24a blown to refrigerating chamber the 1st ajutage 11a be open mode, refrigerating chamber the 2nd air door 24b blown to refrigerating chamber the 2nd ajutage 12a is made to be the operation mode of closed condition, thus the refrigerator that the cooling effectiveness becoming the thermal losses that inhibit heat bridge to cause is high.

And, vacuum heat insulating material 60 is possessed overleaf in adiabatic wall, be configured to when the rearward vacuum heat insulating material 60 of refrigerating chamber the 1st ajutage 11a is projected, refrigerating chamber the 1st ajutage 11a is accommodated in the region inside the reflex part 60b of vacuum heat insulating material 60, implement to make refrigerating chamber the 1st air door 24a blown to refrigerating chamber the 1st ajutage 11a be open mode, make refrigerating chamber the 2nd air door 24b blown to refrigerating chamber the 2nd ajutage 12a be the operation mode (with reference to Fig. 2, Fig. 3, Fig. 8 and Figure 12) of closed condition.The reflex part of vacuum heat insulating material is outer packaging material because overlap has, so the impact of heat bridge becomes large.Therefore, adopt above-mentioned formation in the refrigerator of present embodiment, implement to inhibit and result from the cooling running of the thermal losses caused by heat bridge of reflex part 60b, thus make refrigerating chamber the 1st ajutage 11a become the adiabatic wind path of the little height of thermal losses, improve cooling effectiveness.

And, refrigerating chamber the 1st ajutage 11a possessing refrigerating chamber the 2nd ajutage 11b that blows to the region 2c by the top of shelf 46a, the 46b than uppermost and blow to the region 2d on the lower of shelf 46a, the 46b than uppermost, implement to make refrigerating chamber the 1st air door 24a blown to refrigerating chamber the 1st ajutage 11a be open mode, make refrigerating chamber the 2nd air door 24b blown to refrigerating chamber the 2nd ajutage 12a be the operation mode (with reference to Fig. 2, Fig. 3 and Figure 12) of closed condition.Thus, under the state that there is no need the cooling carrying out region 2c, play a role, so the high cooling of efficiency can be carried out as suppressing the heat insulation layer involving region 2d from the heat affecting of refrigerating chamber 2 upper wall than the air layer of shelf 46a, 46b region 2c by the top of uppermost.

And each distance (H1 and H2 shown in Fig. 3) from shelf 46a and shelf 46b to upper wall is less than the respective depth size of shelf 46a and shelf 46b.Thus, implement to make refrigerating chamber the 1st air door 24a blown to refrigerating chamber the 1st ajutage 11a be open mode, refrigerating chamber the 2nd air door 24b blown to refrigerating chamber the 2nd ajutage 12a is made to be the operation mode of closed condition, when the air layer of region 2c is played a role as heat insulation layer, not easily produce the convection current in the 2c of region, so improve the insulation effect of region 2c, can better cool by implementation efficiency.

And, though make refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which be in open mode, the volume (volume of region 2e) in the region that cold air passes through all jointly sets less than the volume (region 2c and region 2d volume altogether) being controlled the region of blowing by the open and-shut mode of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b independently.Thus, even if operating point changes to little air quantity side a little owing to producing frost, the impact that also cooling effect can be suppressed to reduce 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 less than the blowout area of pressure fan in case 22.Thus, suppress airduct possessive volume, and increase the wind path resistance in the circulating cold air system path of refrigerating chamber 2.Therefore, cooling effectiveness and the high refrigerator of space efficiency is become.

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

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, when the both sides of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b become open mode, more cold air is flowed out, so the cooling running that inhibit the cooling effectiveness of thermal losses high can be implemented by refrigerating chamber the 1st ajutage 11a as the adiabatic wind path of height.

And, at the cold air sent from refrigerating chamber the 1st ajutage 11a and path (the region 2e jointly flowed from the cold air that refrigerating chamber the 2nd ajutage 11b sends, deepfreeze room 3, refrigerating chamber return port 35, refrigerating chamber recurrent canal 15) on possess temperature sensor (deepfreeze room temperature sensor 42), when sensor detected temperatures is lower than set point of temperature (lower than Tc_a), make refrigerating chamber the 1st air door 24a blown to refrigerating chamber the 1st ajutage 11a, refrigerating chamber the 2nd air door 24b blown to refrigerating chamber the 2nd ajutage 12a becomes closed condition (with reference to Fig. 2, Fig. 3, Fig. 4 and Figure 12).Thereby, it is possible to the undesirable condition preventing the region (the region 2e refrigerating chamber of the refrigerator of present embodiment in, deepfreeze room 3) jointly cooled by the air-supply from refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b to be excessively cooled and freeze.

In addition, in the refrigerator of present embodiment, also set point of temperature can be cooled to because deepfreeze room 3 does not possess cold air blow-off outlet, so the blow-off outlet blown out to deepfreeze room 3 is not set, but also can arrange deepfreeze room blow-off outlet at refrigerating chamber the 1st ajutage 11a or refrigerating chamber the 2nd ajutage 11b.And, the deepfreeze room air door for controlling the air-supply from deepfreeze room blow-off outlet also can be set, form the structure easily maintaining 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 is the longitudinal section of the structure of the refrigerating chamber of the refrigerator representing the 2nd embodiment.Figure 15 is the front view of the structure of the refrigerating chamber of the refrigerator representing the 2nd embodiment.Figure 16 is the schematic diagram of the wind path structure of the refrigerator representing the 2nd embodiment.Wherein, except the structure shown in Figure 14 ~ Figure 16, identical with the refrigerator of the 1st embodiment, so omit the description.And in Figure 14 ~ Figure 16, the functional part identical with the refrigerator of the 1st embodiment marks same-sign and omits the description.

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

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 the Quilt with air conditioning case after evaporimeter 21 heat exchange, under the state that refrigerating chamber the 1st air door 24a opens, to flow and from refrigerating chamber blow-off outlet 31a ~ 31c to shelf 46a, 46b of refrigerating chamber internal ratio uppermost on the lower and than shelf 46f region 2d by the top (with reference to Figure 14 and Figure 15) blowout of lowermost at refrigerating chamber ajutage 11.The cold air blowing to region 2d is being provided with region 2e (with reference to Figure 14) flowing of a pocket 47b, via than shelf 46a, 46b region 2c by the top (with reference to Figure 14 and Figure 15), arrive refrigerating chamber return port 35a, 35b (with reference to Figure 15).The cold air flowing into refrigerating chamber the 1st recurrent canal 15a (with reference to Figure 15) from refrigerating chamber return port 35a, 35b (with reference to Figure 15) turns back to evaporimeter receiving room 9 and again carries out heat exchange with evaporimeter 21.

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

And, in the refrigerator of present embodiment, as shown in figure 15, when rearward for refrigerating chamber ajutage 11 vacuum heat insulating material 60 is projected, from refrigerating chamber ajutage 11 end to the beeline L of the end of vacuum heat insulating material 60 be 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 rearward for refrigerating chamber ajutage 11 vacuum heat insulating material 60 is projected, from refrigerating chamber ajutage 11 end to the beeline L of the end of vacuum heat insulating material 60 be more than 50mm.And when being projected by rearward for refrigerating chamber ajutage 11 vacuum heat insulating material 60, 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 cold air of flowing low temperature is disposed in the position that inhibit the thermal losses caused because of heat bridge, thus becomes the high refrigerator of cooling effectiveness.

And, in the refrigerator of present embodiment, the air-supply that can control to ice making water tank 55 setting unit periphery (region 2f) by the open and-shut mode of refrigerating chamber the 2nd air door 24b.That is, no matter, which of refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b is not in the region (region 2d, 2f) that open mode cold air passes through all jointly and arranges ice making water tank 55.Thus, ice making water tank 55 periphery is difficult to be excessively cooled, and suppresses the heating in order to prevent the water freezing in ice making water tank 55 from carrying out heater etc., so become the high refrigerator of cooling effectiveness.

Embodiment 3

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

As shown in figure 18, present embodiment refrigerator the back side substantial middle of refrigerating chamber 2 possess extend upward from the below of refrigerating chamber 2 refrigerating chamber the 1st ajutage 11a, at refrigerating chamber the 1st ajutage 11a (minimum flow path cross sectional area 1400mm ²) top possess refrigerating chamber the 2nd ajutage 11b (minimum flow path cross sectional area 1400mm ²), possess refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b respectively at the inlet portion of refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b.In addition, as shown in Figure 17 and Figure 18, refrigerating chamber the 1st air door 24a is disposed in the back projection region of the adiabatic partition wall 51 in upside, and refrigerating chamber the 2nd air door 24b is disposed in the roughly back (height and position of shelf 46a being 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, in the Quilt with air conditioning case having carried out heat exchange with evaporimeter 21, pressure fan 22 is boosted, be open mode at refrigerating chamber the 1st air door 24a, under refrigerating chamber the 2nd air door 24b is closed condition situation, flow and from refrigerating chamber blow-off outlet 31a ~ 31c (with reference to Figure 18) only to region 2d (with reference to Figure 17 and Figure 18) blowout in refrigerating chamber at refrigerating chamber the 1st ajutage 11a.The cold air blowing to region 2d, being provided with the region 2e of pocket 47b, 47c (with reference to Figure 17), flowing through deepfreeze room 3, arrives refrigerating chamber return port 35.And, when refrigerating chamber the 1st air door 24a is open mode and refrigerating chamber the 2nd air door 24b is open mode, cold air flows at refrigerating chamber the 1st ajutage 11a and blows out from refrigerating chamber blow-off outlet 31a ~ 31c to the region 2d in refrigerating chamber, and flows at refrigerating chamber the 2nd ajutage 11b and blow out (with reference to Figure 17 and Figure 18) from refrigerating chamber blow-off outlet 31d, 31e to the region 2c in refrigerating chamber.The cold air blowing to region 2c flows through and is provided with pocket 47b, a 47c, the region 2e of ice making water tank 55, deepfreeze room 3, arrives refrigerating chamber return port 35.

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

In addition, in the refrigerator of present embodiment, also refrigerating chamber the 1st air door 24a, refrigerating chamber the 2nd air door 24b, refrigerating chamber air door 26, vegetable compartment air door 27 is possessed, there is the two states of open mode and closed condition respectively, 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, refrigerating chamber the 2nd air door 24b can be opened and blows via refrigerating chamber the 2nd ajutage 11b.

Figure 20 carries out the combination of the state of the air-supply to refrigerating chamber 2 under representing the state that refrigerating chamber the 1st air door 24a opens.As shown in figure 20, carrying out is 8 kinds of state 1 ~ state 8 to the state of the air-supply of refrigerating chamber 2, and the wind path resistance in the circulating cold air path of each state is set to R1 ~ R8.Wherein, in " size of wind path resistance " hurdle, about the magnitude relationship of R1 ~ R8, the numbering of 1 ~ 8 has been numbered with according to wind path resistance order from big to small.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 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 the need to being set up in parallel refrigerating chamber the 1st ajutage 11a and refrigerating chamber the 2nd ajutage 11b.Therefore, it is possible to arrange refrigerating chamber ajutage compactly, become the refrigerator of the minimizing that inhibit food storing space.

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

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

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

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

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

Thus, if be configured to operating point to be in centrifugal basin, even if wind path resistance increases along with the generation of frost, the minimizing degree of air quantity is also suppressed must be less, and, the right rising characteristic territory of action instability when also can avoid being with, so no matter in which kind of situation of multiple air supply pattern (no matter make refrigerating chamber the 1st air door 24a and refrigerating chamber the 2nd air door 24b which become open mode), the refrigerator that cooling effectiveness that the region 2e that suitably jointly passes through cold air cools is high also can be become.

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 if operating point changes to little air quantity side a little owing to producing frost, the impact of the reduction of cooling effectiveness also can be suppressed to manifest significantly.

And, in arbitrary situation of common cooled region 2e or multiple air supply pattern, the region of the return path 15 that cold air all jointly flows possesses temperature detecting unit 42, when the temperature detected by temperature detecting unit 42 becomes below set point of temperature, stop the air-supply to storeroom.Thereby, it is possible under preventing the arbitrary situation by common cooled region 2e or multiple air supply pattern the return path 15 that cold air all jointly flows region transitions cool and freeze, can cooling effectiveness be improved.

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

That is, the above embodiments are illustrated in detail in order to easily the present invention is described, but are not necessarily confined to the mechanism possessing illustrated whole structure.

Claims

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

At least one party of described air-supply path and described return path has the individual path of the path branches that cold air passes through,

Possess the wind path resistance control unit of the wind path resistance controlling this individual path,

Described storeroom have the 1st independent cooled region cooled by the cold air by the path of in described individual path, the 2nd independent cooled region cooled by the cold air by another path in described individual path, by the common cooled region of the cold air in all paths by described individual path cooling

There are the multiple air supply patterns cooled any one or multiple combinations of described 1st independent cooled region, described 2nd independent cooled region and described common cooled region,

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

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

Under arbitrary pattern in the plurality of air supply pattern, the blowout stream of described axial flow fan is all in centrifugal basin.

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 1st independent cooled region and described 2nd independent cooled region.

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

Under arbitrary pattern of described common cooled region or described multiple air supply pattern the described return path that cold air flows all jointly region in, possess temperature detecting unit,

When the temperature detected by described temperature detecting unit becomes below set point of temperature, stop the air-supply to described storeroom.