JP4248491B2 - refrigerator - Google Patents

Description

  The present invention relates to a refrigerator.

  As a conventional technique for improving the performance in a state where the cooler is not frosted and maintaining the performance in a state where the chiller is frosted, there is a technique described in Patent Document 1, for example.

  The technology described in Patent Document 1 relates to the structure of a cooler. Regarding the fin arrangement of the cooler, the fin edge portion on the windward side is arranged so as not to overlap in the flow direction, and the fin is cut and raised. To improve heat transfer performance and improve heat exchange performance when there is no frost on the cooler. When frost is formed, heat is exchanged by concentrating frost on the cut and raised parts provided on the fins. Maintains performance.

JP 2002-277183 A

  When trying to improve the performance and downsizing of refrigerators for refrigerators, it is necessary to achieve both high performance without frost formation on the cooler and suppression of performance degradation when frost formation has occurred on the cooler. It becomes a problem.

  However, in the technique described in Patent Document 1, ventilation resistance is improved in a state where there is no frost formation, and the degree of frost formation expected in an ordinary refrigerator operating state is generated on the fin surface or the refrigerant pipe. When it occurs on the surface, it has become a practical problem that it is difficult to maintain its performance.

  The present invention has been made in view of the above problems, and in a state where there is no frost formation, the heat exchange performance is improved without improving the ventilation resistance, and even in a state where frost formation occurs, the actual use state is achieved. It aims at providing the refrigerator which can ensure the heat exchange performance in and the refrigerator which has the periphery structure.

In order to achieve the above object, the invention according to claim 1 of the present application is arranged in the refrigerator compartment of the refrigeration temperature zone and the freezer compartment of the refrigeration compartment disposed in the heat insulation box, and on the back side of the freezer compartment. A cooler for cooling the refrigerating chamber and the freezing chamber, a cooling chamber in which the cooler is accommodated, and a return from the freezing chamber to a front portion of the cooling chamber below the cooler. An opening through which cold air passes, a tub provided below the cooler, a drainage means for draining defrost water from the jar, a defrost heater disposed between the cooler and the jar, In the refrigerator, the depth of the cooler is set to be equal to or greater than the vertical dimension from the cooler lower surface to the ridge, and the vertical upper extension surface of the center line of the defrost heater intersects the cooler lower surface. To the front of the cooler is the lead of the center line of the defrost heater. A dimension larger than the dimension from the line where the upper extension surface intersects the lower surface of the cooler to the rear surface of the cooler, a gap is provided on the rear side of the cooler, and the height dimension of the gap is determined by the cooler. The gist is that the dimension is smaller than the depth dimension .

The invention according to claim 2 of the present application includes a refrigeration room having a refrigeration temperature zone and a freezing room having a refrigeration temperature zone disposed in a heat insulation box, and the refrigeration chamber and the freezer placed on the back side of the freezer compartment. A cooler for cooling the chamber, a cooling chamber in which the cooler is accommodated, an opening through which the return cold air from the freezer compartment passes through the front surface of the cooling chamber below the cooler, In the refrigerator comprising: a reed provided below the cooler; a drain hole for draining defrost water from the reed; and a defrost heater disposed between the cooler and the reed. The depth of the cooler is made larger than the vertical dimension from the lower surface of the cooler to the ridge, and the front surface of the cooler is separated from the line where the vertically upper extension surface of the center line of the defrost heater intersects the lower surface of the cooler. The vertical extension of the center line of the defrost heater and the cooling The dimension is larger than the dimension from the line where the lower surface intersects to the back of the cooler, a gap is provided on the back side of the cooler, and the height of the gap is smaller than the depth of the cooler. The summary is as follows.

The invention according to claim 3 of the present application is arranged in a refrigerating room having a refrigerating temperature zone disposed in a heat insulating box, a freezing room having a freezing temperature zone located below the refrigerating room, and a rear side of the freezing room. A cooler for cooling the refrigerating chamber and the freezing chamber, a cooling chamber in which the cooler is accommodated, and a return from the freezing chamber to a front portion of the cooling chamber below the cooler. An opening through which cool air passes, a ventilation path that is provided on the side of the cooling chamber and extends to a position below the cooler and through which return air from the refrigerating chamber passes, a trough that is provided below the cooler, and In a refrigerator comprising a drainage hole for draining defrost water from a reed and a defrost heater disposed between the cooler and the reed, the depth of the cooler is measured from the lower surface of the cooler to the reed with a vertical dimension or leading to, vertically upwardly extending centerline of the defrost heater The dimension from the line where the surface intersects the lower surface of the cooler to the front surface of the cooler reaches the rear surface of the cooler from the line where the vertically upper extension surface of the center line of the defrost heater intersects the lower surface of the cooler The gist is that the dimension is larger than the dimension, a gap is provided on the back side of the cooler, and the height dimension of the gap is smaller than the depth dimension of the cooler .

  Invention of Claim 4 of this application WHEREIN: In the refrigerator in any one of Claim 1 to 3, the said cooler depth dimension was made more than the vertical longest dimension from the said cooler lower surface to the said drain hole upper end. And

Invention of Claim 5 of this application WHEREIN: In the refrigerator of Claims 1 thru | or 4 , the said defrost heater was located back from the vertical longitudinal cross-section which passes the depth direction center of the said cooler. And

The invention according to claim 6 of the present application is the refrigerator according to claim 5 , wherein a dimension extending from a line intersecting a vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is The gist is that the size is larger than the opening width of the opening of the lower front portion of the cooling chamber.

The invention according to claim 7 of the present application is the refrigerator according to claim 5 or 6 , wherein the shortest dimension from the defrost heater to the thermoplastic peripheral structure through the space is the shortest from the defrost heater to the cooler. The gist is that the dimensions are larger than the dimensions.

The invention according to claim 8 of the present application is the above-described refrigerator, wherein a gap is provided on the front side of the cooler, and the height dimension of the gap is smaller than the depth dimension of the cooler. The summary is as follows.

The invention according to claim 9 of the present application is the refrigerator according to claim 8 , wherein the height dimension of the gap on the front side of the cooler is smaller than the height dimension of the gap on the back side of the cooler. The summary is as follows.

The invention according to claim 10 of the present application includes a refrigeration room having a refrigeration temperature zone disposed in a heat insulating box, a freezing room having a freezing temperature zone located below the refrigeration room, the refrigeration room, and the freezing room. A heat insulating partition that partitions the space between the refrigerator compartment, a cooler that is disposed on the back side of the freezer compartment and cools the refrigerator compartment and the freezer compartment, a cooling compartment that houses the cooler, and the freezer compartment A cool air return path which is a return path of cool air from the cooling chamber to the cooling chamber, a ridge provided below the cooler, and the cool air disposed above the cooler and cooled by the cooler. And in the refrigerator provided with the ventilation fan for sending to the freezer compartment, and the defrost heater arranged between the cooler and the basket ,
While making the said cooler depth dimension more than the vertical dimension from the said cooler lower surface to the said collar ,
The dimension extending from the line intersecting the vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is the vertical upper extension surface of the center line of the defrost heater and the lower surface of the cooler. The dimension is larger than the dimension from the intersecting line to the back of the cooler,
A gap is provided on the back side of the cooler, and the height dimension of the gap is smaller than the depth dimension of the cooler ,
The cold air return passage forms a boundary between the cold air return passage and the cooling chamber, and opens in a front side of the cooling chamber below the cooler, the cooling chamber side opening, the cold air return passage, and the freezer compartment A freezer compartment side opening that opens to the freezer compartment side, and the freezer compartment side opening is positioned lower than the cooling compartment side opening, and Communicated in a straight line or curved line,
By tilting the blower fan at an angle within the range of the tilt angle of the upper passage surface among the passage surfaces arranged vertically opposite to constitute the cold air return passage, the blower fan is The gist is that the effective storage volume in the warehouse is improved by being positioned below the projection surface of the heat insulating partition.

  According to the present invention as described above, heat exchange performance is improved without improving ventilation resistance in the absence of frost formation, and heat exchange performance in actual use is ensured even when frost formation occurs. It is possible to provide a refrigerator having such a cooler and a peripheral structure thereof.

  An embodiment of the present invention will be described with reference to FIGS. In the following description, the same functional parts are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 1 is a front view of the refrigerator of this embodiment. As shown in FIG. 1, the refrigerator 1 includes a refrigerator room 2, a vegetable room 3, an ice making room 4, an upper freezer room 5, and a lower freezer room 6 from above. In the present specification, the refrigerator compartment 2 and the vegetable compartment 3 are collectively referred to as a refrigerated temperature zone room group 12, the ice making room 4, the upper freezer compartment 5, and the lower freezer compartment 6 are collectively referred to as a frozen temperature zone compartment group 13. .

  FIG. 2 is a vertical cross-sectional view of the AA cross section shown in FIG. 1 as viewed from the direction of the arrow. As shown in FIG. 2, the outside of the refrigerator 1 and the inside of the refrigerator are separated by a heat insulating box 10. The inside of the refrigerator is kept at a temperature of about 5 ° C., a refrigerated room 2 kept at about 5 ° C., a vegetable room 3 kept at about 2-3 ° C., and below −18 ° C. by the partition wall 28 and the heat insulating partition wall 36. The upper freezer compartment 5 and the lower freezer compartment 6 are partitioned. Moreover, the lowest part of the refrigerator compartment 2 is equipped with the ice greenhouse 11 kept at about 0-1 degreeC.

  The refrigerator compartment 2 is opened and closed by a rotary door 2a, and the vegetable compartment 3, the upper freezer compartment 5, and the lower freezer compartment 6 are opened and closed by drawer type doors 3a, 5a and 6a provided in front of the respective compartments. The The drawer-type doors 3a, 5a, 6a are provided with storage containers 3b, 5b, 6b, respectively, and the storage containers 3b, 5b, 6b are pulled out as the drawer-type doors 3a, 5a, 6a are opened and closed. It is. These storage containers 3a can store, for example, vegetables, the storage container 5a, for example, ice cream, and the storage container 6a, for example, frozen food, according to their temperature zones. The ice making chamber 4 shown in FIG. 1 includes a drawer-type door (not shown) and a storage container (not shown), and ice is stored in the storage container of the ice making chamber 4.

  The cooler 7 is provided in a cooling chamber 8 provided at the back of the freezing temperature zone group 13, and air (in which heat is exchanged by the cooler 7 by an internal fan 9 provided above the cooler 7) Hereinafter, in this specification, the heat-exchanged low-temperature air may be referred to as cold air or cooling air). The air blowing to each chamber in the cabinet is controlled by opening / closing a damper 14 disposed in the cold air duct.

  When the damper 14 is in the open state, the cold air is distributed to the refrigeration temperature zone group 12 direction and the refrigeration temperature zone chamber group 13 direction to cool each chamber. Hereinafter, the operation mode when the damper 14 is in the open state is referred to as FR operation. During the FR operation, the cold air distributed to the refrigeration temperature zone group 12 direction is supplied to the refrigeration chamber discharge ports 24a, 24b, via the refrigeration chamber air duct 15 serving as a passage for the cold air sent to the refrigeration temperature zone chamber group 12. After flowing into the refrigerating chamber 2 from 24 c and cooling the refrigerating chamber 2, it flows into the vegetable chamber 3 through the vent hole 29 provided in the partition wall 28. The cold air that has finished cooling the vegetable compartment 3 returns to the cooling compartment 8 from an exhaust port (not shown) provided on the back of the vegetable compartment 3 via a refrigeration compartment return duct 37 provided on the side of the cooling compartment 8 ( FIG. 4). Next, the cold air distributed to the freezing temperature zone room group 13 direction passes through the freezer air blow duct 16 serving as a passage for the cold air sent to the freezing temperature zone room group 13, and the upper freezer discharge port 25 and the lower freezing air. From the chamber discharge port 26 and the ice making chamber discharge port (not shown), the air flows into the upper freezing chamber 5, the lower freezing chamber 6, and the ice making chamber 4, respectively. The cool air that has finished cooling the freezing temperature zone group 13 returns to the cooling chamber 8 via the freezer return duct 17.

  On the other hand, when the damper 14 is closed, the cold air is sent only to the freezing temperature zone group 13. Hereinafter, the operation mode when the damper 14 is in the open state is referred to as F operation.

  In addition, a machine room 19 is provided on the lower back side of the heat insulating box 10, and a compressor 20 and a radiator (not shown) are accommodated and ventilated by a fan outside the box (not shown). The compressor 20 and the cooler 7 constitute a refrigeration cycle, and are connected by a refrigerant pipe (not shown). The refrigerant evaporates in the cooler 7 to generate cool air and cool the interior. In the refrigerator of this embodiment, isobutane is used as a refrigerant.

  In this specification, W in FIG. 1 is called the width of the refrigerator 1, D in FIG. 2 is called the depth of the refrigerator 1, and H in FIG. 2 is called the height of the refrigerator 1. In addition, regarding the depth direction of the refrigerator 1, the side on which the doors 2a, 3a, 5a, 6a are provided is the front surface, and the side facing the front surface is the back surface. Therefore, the direction toward the front side of the refrigerator 1 may be referred to as the front, and the direction toward the back side of the refrigerator 1 may be referred to as the rear.

  FIG. 3 is a longitudinal sectional view showing the structure around the cooler 7 in FIG. As shown in FIG. 3, a defrost heater 22 is provided below the cooler 7. Further, a cover body 40 for protecting the defrost heater 22 from falling objects (frost, defrost water) is provided above the defrost heater 22, and defrost water is received below the defrost heater 22. A collar 23 is provided. The defrost water generated from the cooler 7 at the time of defrosting falls to the eaves 23 while avoiding dripping onto the main body portion of the defrost heater 22 by the cover body 40, and reaches the evaporating dish (not shown) through the drain hole 27. Evaporate. That is, the drain hole 27 communicates the inside of the cooling chamber 8 and the machine room 19, and the defrost water is guided to the evaporating dish in the machine room 19. Further, a gap 30 is provided between the cooler 7 and the heat insulating box 10 on the back side of the cooler 7, and a partition wall 31 that partitions the cooler 7 and the freezer compartment air duct 16 on the front side of the cooler 7. A gap 32 is provided between the two. The gaps 30 and 32 have structures 30a and 32a that reduce the gap stepwise or continuously on the cooler 7 side at predetermined positions.

  FIG. 4 is a cross-sectional view showing the structure around the cooler as seen from the front. As shown in FIG. 4, a refrigerating room return duct 37 is disposed on the side of the cooler 7. The refrigerator compartment return duct 37 communicates with an exhaust port (not shown) provided on the back of the vegetable compartment 3. Further, in order to prevent the air flowing into the cooling chamber from flowing into the bent portion 18a of the refrigerant pipe 18 on the side of the cooler 7 and reducing the amount of air flowing into the fin 21 installation area of the cooler 7. The air that has flowed into the cooling chamber is made difficult to flow into the refrigerant pipe bent portion 18a on the side of the cooler 7. Specifically, the partition between the refrigeration chamber return duct 37 and the cooling chamber 8 extends below the lowermost refrigerant pipe 1 of the cooler 7 and flows to a position above the refrigerant pipe bending portion 18a. A restricting member is arranged so that the return cold air is sent into the cooling chamber 8 as indicated by the arrow in the figure.

  FIG. 5 is a perspective view of a cooler mounted on the refrigerator of the present embodiment. As shown in FIG. 5, the cooler 7 mounted in the refrigerator of the present embodiment is a so-called fin tube type that includes an aluminum refrigerant pipe 18 and a plurality of aluminum fins 21. It is a heat exchanger (however, not all of the fins 21 are shown in FIG. 5). The width of the cooler 7 is defined as the maximum width direction dimension of the fin 21 installation area, the depth is the maximum depth direction dimension of the fin 21 installation area, and the height is the maximum height dimension of the fin 21 installation area. The lower surface of the cooler 7 is a horizontal plane that coincides with the lowermost end of the fin 21.

FIG. 6 is a diagram illustrating the positional relationship between the cooler 7 and the gaps 30 and 32 provided before and after the cooler 7 and the defrost heater 22 and the eaves 23 in FIG. In addition, in this specification, a defrost heater refers to the structure which has the heater wire which consists of metal resistors, and the glass tube which covers the circumference | surroundings. Symbol S1 in FIG. 6 is a reference plane representing the center of the cooler 7 in the depth direction. S2 is a reference surface formed by extending the center line of the defrosting heater 22 vertically upward. L1 is the shortest dimension from the defrost heater 22 to the thermoplastic peripheral structure (for example, resin inner box), L2 is the shortest dimension from the defrost heater 22 to the lower surface of the cooler 7, and L3 is The longest dimension from the front end of the lower surface of the cooler 7 to S2 , L4 is the longest dimension from the rear end of the lower surface of the cooler 7 to S2 , and L5 is continuous with the flange 23 or 23. The dimension from the upper end 23a on the front side of the member to the partition wall 17a that forms the freezer return duct 17 (that is, the opening dimension of the opening of the return duct 17), L6 is a clearance provided on the rear side of the cooler 7 30 is a height dimension from the lower surface of the cooler 7, L7 is a height dimension from the lower surface of the cooler 7 of the gap 32 provided on the front side of the cooler 7, L8 is a lower surface of the cooler 7, and the drain hole 27 This is the dimension that reaches the upper end and is the standard for the return cold air path. . In the case of having a wide portion around the upper end of the drainage hole 27 as in the present embodiment, the step position 27a in the figure is set as the reference position of the air passage. This situation will be described later. The drain hole 27 is arranged at a position substantially coincident with S1.

  In the refrigerator of the present embodiment, the defrost heater 22 is located on the back side from S1. Further, using the symbols shown in FIG. 6, the following relationships are satisfied: L1> L2, L3> L4, L3> L5, (L3 + L4)> L7, (L3 + L4)> L6, L7> L6, (L3 + L4) ≧ L8. Each configuration is arranged as described above.

  The technology for improving the performance and miniaturization of refrigerator coolers improves the heat exchange performance when frost formation is not occurring (hereinafter referred to as “no frost formation”), as well as the heat exchange performance during frost formation. It is realized by securing. In the following, the cooler mounted on the refrigerator of the present embodiment having the above-described configuration has high heat exchange performance during non-frosting, and can maintain heat exchange performance even during frost formation. This will be described with reference to FIGS.

  First, the heat exchange performance during non-frosting will be described.

  As shown in FIG. 3, the freezer return air flows from the lower front of the cooler 7 through the freezer return duct 17 into the cooler 8, and passes through the cooler 7 from the lower front to the rear upper side. Mainly flows towards. On the other hand, as shown in FIG. 4, the return air from the refrigerator compartment flows from the side below the cooler 7. The refrigeration chamber return air that has flowed into the cooling chamber flows in the vicinity of the area below the defrosting heater 22, and mainly flows toward the rear surface of the cooler 7 or toward the gap 30 on the rear surface side of the cooler. The refrigerating room return air passes through the vicinity of the back surface of the cooler 7 due to the freezer room return air having a momentum from the front side to the back side of the cooler 7.

  FIG. 7 is an explanatory diagram showing an outline of the flow field of FIG. In FIG. 7, a solid line arrow 33 indicates a flow mainly including freezer return air, a dotted line arrow 34 indicates a flow mainly including refrigerator compartment return air, and a broken arrow 35 indicates freezer return air and refrigerator compartment return air. The outlines of the flows in which are mixed are respectively shown. In order to enhance the heat exchange performance in the cooler 7 in consideration of such a flow field, it is effective to allow the arrows 33 to 35 to smoothly flow into the cooler 7.

  The main flow direction below the cooler 7 indicated by arrows 33 to 35, for example, the flow direction in the vicinity of S1 in FIG. Moreover, after flowing into the cooler, it mainly moves from below to above. Therefore, in order to smoothly turn the flow that flows in the lower part of the cooler 7 into the cooler 7, the representative height dimension L8 of the region where the flow is directed from the front to the rear under the cooler 7 (cooling). It is desirable to make the depth dimension of the inflow portion of the cooler 7 larger to reduce the flow and not increase the ventilation resistance.

  That is, it is effective to satisfy (L3 + L4) ≧ L8 using the symbols shown in FIG. In this way, by configuring the depth dimension (L3 + L4) of the cooler 7 to be equal to or larger than the passage width L8 below the cooler 7, the cool air flowing through the L8 dimension portion smoothly flows into the cooler 7. It is possible to keep the ventilation resistance low and increase the heat exchange efficiency in the cooler. Note that the ridge 23 and the drainage hole 27 are identified as a drainage hole in a region having a diameter of 20 mm or less and a ridge 23 and the drainage hole 27 as a ridge. However, when a recess appears clearly as shown in FIG. 6, the step position 27a or less of the recess is identified as a drain hole 27 and the recess or more is identified as a ridge. This is because if the diameter is 20 mm or less, the drain hole 27 has little influence on the return cold air from the freezer return duct 17 in the space below the cooler 7.

  In the present embodiment, the cool air flowing into the cooler 7 does not flow through the straight flow path, but flows from the front of the reference S with the front end of the cooler 7 as the reference S as shown in FIG. Since the cooling unit 7 is configured to pass upward, it is more effective to make the depth dimension (L3 + L4) of the cooling unit 7 larger than the passage width L8 below the cooling unit 7. That is, by setting (L3 + L4)> L8, a structure in which the cold air flowing through the L8 dimension portion smoothly flows into the cooler 7 can reduce the ventilation resistance and increase the heat exchange efficiency in the cooler. It becomes possible.

  In general, heat exchangers are known to have high heat exchange efficiency near the inflow portion. Regions a to c in FIG. 7 are regions where heat exchange efficiency is high particularly when freezer return air flows in, particularly heat exchange efficiency when refrigerator return air flowing into the gap 30 flows into the cooler. It represents a high region and a region where the heat exchange efficiency is high when a flow in which the freezer return air and the refrigerating chamber return air are mixed flows into the cooler. With S2 as a substantially boundary, on the back side from S2, the freezing chamber return air is mixed with the refrigeration chamber return air due to the agitating effect of the wake generated on the back side above the defrosting heater 22 and the cover body 40. It becomes.

  That is, the boundary between the region a and the region c can be set on the lower surface of the cooler by S2 which is the position of the defrost heater 22 serving as a resistance member for the cold air flow. Therefore, if the defrost heater 22a is positioned relatively forward with respect to the cooler 7, the area c is relatively increased with respect to the area a, and conversely, with respect to the cooler 7, the defrost heater 22 is increased. If is positioned relatively rearward, the area a is relatively increased with respect to the area c. Further, the position of the region b depends on the height of the gap 30. In order to improve the performance and size of the refrigerator cooler, it is effective to increase the size of the areas a to c.

  As described above, the operation mode of the refrigerator 1 includes the FR operation for cooling both the refrigeration temperature zone group 12 and the freezing temperature zone group 13 and the F operation for cooling only the freezing temperature zone group 13. Normally, during the FR operation, a large amount of cooling air is circulated in the direction of the freezing temperature zone group 13 where the temperature must be kept lower than that in the direction of the refrigeration temperature zone group 12 (the drying of the food). From the viewpoint of suppression, it is desirable that the air flow toward the refrigeration temperature zone group 12 direction is suppressed as compared with the refrigeration temperature zone group 13 direction). In the refrigerator 1 according to the present embodiment, the ratio of cold air distributed to the refrigerated temperature zone group 12 direction and cold air distributed to the refrigeration temperature zone group 13 direction is about 1: 4 during the FR operation. Therefore, during the FR operation, the freezing room return air has a larger amount of inflow into the cooling room 8 than the refrigerating room return air. Further, during the F operation, only the freezer return air flows into the cooling chamber 8.

  Therefore, in order to increase the efficiency of the cooler, it is effective to enlarge the region a into which the freezer return air flows, that is, L3> L4 in FIG.

  In order to reduce the ventilation resistance when the freezer return air flows into the region a, it is effective to satisfy L3> L5.

  Further, regarding the region b, although the heat exchange efficiency is high, the distance that passes through the cooler after flowing into the cooler 7 is shorter than the region a and the region c, so that the flow flowing into the region a and the region c The amount of heat exchange is smaller than that. Therefore, in order to perform the main heat exchange in the region a and the region c, the height L6 of the gap 30 is made smaller than the depth direction dimension L3 + L4 in which the inflow portions of the region a and the region c are combined. It is effective to satisfy (L3 + L4)> L6.

  With the above-described configuration, it is possible to improve the heat exchange performance of the cooler without improving the ventilation resistance when the frost is not formed.

  Below, it demonstrates that the refrigerator of a present Example has the cooler which can maintain heat exchange performance also at the time of frost formation, and its peripheral structure.

  FIGS. 8 to 10 are simplified diagrams showing the shape and positional relationship of the cooler 7, the gaps 30 and 32 provided before and after the cooler 7, and the frost formation.

  In general, in a refrigerator including the refrigeration temperature zone chamber group 12 and the refrigeration temperature zone chamber group 13, the return air (refrigeration chamber return air) from the refrigeration temperature zone chamber group 12 is highly humid. Therefore, the return air from the refrigerator compartment is the first factor of frost formation on the cooler.

  When the frost is not formed, the return air from the refrigerator compartment flows into the cooler 7 from the rear side as shown in FIG. Therefore, frosting starts from a region b where the refrigerating room return air flowing into the gap 30 flows into the cooler and a region c where the flow of mixing the freezer return air and the refrigerating chamber return air flows into the cooler.

  FIG. 8 shows a first stage state in which the main frost 39 is attached in the vicinity of the region b and the region c (a frosting state of about FIG. 8 is referred to as state A). In the state A, the flow mainly including the refrigerating room return air is represented by a dotted arrow 34A, and the flow in which the freezing room return air and the refrigerating room return air are mixed is represented mainly by a broken line arrow 35A. The refrigerating room return air 34A is pushed by the freezing room return air 35A and led to the rear part of the cooler 7 and reaches the gap 30 in the same manner as in the case of no frost formation. A passage passing between the frosts 39 and going upward of the cooler 7 is secured. However, when frosting further proceeds, the passage is covered with frost 39 by the flow represented by arrows 34A and 35A, as shown in FIG.

  The frost formation state shown in FIG. At the time of frosting in the state B or so, the amount of the refrigerating room return air passing through the gap 30 on the back side is remarkably reduced, and the flow mainly of the refrigerating room return air is indicated by a dotted arrow 34B. The flow in which the refrigeration room return air is mixed is mainly represented by a broken-line arrow 35B. Therefore, the state in which frosting has further advanced by the flow represented by the arrows 34B and 35B is as shown in FIG.

  The frosting state of FIG. In normal refrigerator operation, frost formation up to about state C is assumed.

  In the refrigerator of this embodiment, since (L3 + L4) ≧ L8 is satisfied as described above, the performance can be ensured even in the frosting state in this state C. L8 is a dimension from the defrost heater 22 to the ridge 23 that does not bury the defrost heater 22 even when the frost is dropped at the time of defrost, the height of the defrost heater, and the defrost. It is necessary to ensure the dimensions of the heater 22 and the lower surface of the cooler 7, and in particular, it is sufficient to ensure that the defrost heater 22 is not buried even if frost falls during defrosting. Designed as a large dimension. Therefore, if the depth dimension of the lower surface of the cooler 7 is sufficiently large, frost will reach the front side from the back side, and the flow path flowing into the cooler 7 will not easily be blocked. By making the depth dimension sufficiently large as (L3 + L4) ≧ L8, it is possible to maintain the heat exchange performance even during frost formation in the state C.

  In addition, since the gap 30 is provided on the back side of the cooler 7, the cooler return air is guided to the back side and sufficient frost formation is generated on the back side of the cooler 7. The growth of frost on the lower surface can be mitigated. Therefore, since the area | region with the high heat exchange efficiency of the lower surface of the cooler 7 which fully secured the dimension (L3 + L4) is hard to be obstruct | occluded, heat exchange performance can be maintained even at the time of frost formation.

  Further, since L3> L4, main frost formation is concentrated on the back side, and the front side is less likely to be blocked. Therefore, even when frost formation up to about state C occurs, the lower surface of the cooler 7 is unlikely to be blocked, so that the heat exchange performance during frost formation can be sufficiently maintained.

  In addition, even if frosting of about state C or more occurs, a gap 32 is provided on the front side of the cooler 7 in order to maintain the heat exchange performance in the cooler 7. The height L7 of the gap 32 is set to be equal to or higher than the height L6 of the gap provided on the back side so that a sufficient flow can flow even if frosting in the state C or higher occurs.

  Further, the height of the gap 32 is such that L7 is (L3 + L4)> L7, so that sufficient heat exchange can be performed for the flow that has passed through the gap 32.

  With the configuration described above, the heat exchange performance of the cooler can be maintained even during frost formation.

  Furthermore, since the defrost heater 22 is installed for the purpose of melting the frost generated in the cooler 7, it has the effect of improving the defrost efficiency by bringing the defrost heater 22 close to the frost spot of the cooler 7. However, it is not desirable to be in close proximity to surrounding structures, especially thermoplastic structures. Therefore, it is provided so as to satisfy L1> L2.

  As a result, the refrigerator has high reliability even during defrosting and suppresses the temperature rise in the refrigerator.

  Moreover, the heater 22 is installed behind S1. Thus, a portion where frost formation is likely to occur, that is, a portion where frost formation starts (illustrated in FIG. 8) can be efficiently heated, leading to a reduction in defrosting time and a configuration that contributes to power saving.

  Adopting the refrigerator cooler and its peripheral structure according to the present embodiment contributes to the improvement of the effective volume ratio in the refrigerator. The reason will be described below.

  As described above, L1 shown in FIG. 6 is usually secured to a predetermined dimension or more in order to prevent accidents such as product deformation. Further, L8 needs to have a predetermined height or more so that the defrost heater is not buried even if frost falls during defrosting. Therefore, when implementing the configuration of the refrigerator cooler and its peripheral structure of this embodiment, it is effective to increase the depth of the cooler. In the refrigerator of the present embodiment, the depth of the cooler, which was conventionally about 60 mm, is 77 mm. Thereby, in particular, since the area a shown in FIG. 7 is greatly increased, the height dimension of the cooler, which was conventionally about 210 mm, can be reduced to 149 mm. That is, since the region with high heat exchange efficiency is greatly expanded, the height of the cooler 7 can be kept small.

  This cooler (a cooler having a depth of 77 mm and a height of 149 mm) is employed, and as shown in FIG. 3, the front end portion of the cooler 7 is used as a reference S, and the refrigerator compartment air duct 15 to the refrigerator compartment zone 12 is used. Is positioned behind the reference S, sufficient performance can be ensured even as a cooler with a small height, and the internal blower fan 9 is tilted above the cooler 7 so that The blower fan 9 can be provided below the heat insulating partition wall 36 that partitions the refrigeration temperature zone chamber group 12 and the refrigeration temperature zone chamber group 13 and has not conventionally been a storage space in the warehouse (effective volume in the warehouse). The back area of the refrigerated temperature chamber group 12 can be used as a storage space.

  The effect by this structure is demonstrated using FIG. The cooling chamber 7 of the present embodiment is disposed on the back side of the freezing temperature chamber, and the freezer return to the freezing chamber serving as a return cold air passage is provided between the cooling chamber 8 in which the cooler 7 is housed and the freezing chamber. The duct 17 communicates. The freezer compartment return duct 17 has a cooling chamber side opening (L5 size portion) and a freezer compartment side opening, and the freezer compartment side opening is closer to the freezer compartment side opening. Is positioned low. With these configurations, the return cold air is sent from the freezing chamber to the cooling chamber 8 while rising. The cold air return duct 17 is connected between these openings in a straight line or a curved line. Therefore, the freezer return duct 17 extends from the lower front position of the refrigerator to the upper rear position from the upstream side to the downstream side of the return cold air.

  In the present embodiment, of the passage surfaces disposed vertically opposite to form the freezer return duct 17, an angle within the range of the inclination angle of the upper passage surface (partition wall 17a) (angle T2). ), The internal blower fan 9 is tilted by an angle T1, so that the internal blower fan 9 is positioned below the projection surface of the heat insulating partition wall 36 to improve the effective storage capacity in the store. By tilting the internal blower fan 9 by the angle T1, the cool air supplied from the freezer return duct 17 to the cooling chamber 8 is sent to the rear side of the cooler 7 as shown by the arrow in FIG. Therefore, the supply of cool air to each room by the inclined internal fan 9 becomes smooth. Therefore, ventilation resistance can be reduced.

  Further, the upper extension of the reference S and the bottom surface (the heat insulating partition wall 36) of the refrigerated temperature zone (vegetable room 3) located above the freezing temperature zone group 13 are configured to cross the front of the damper 14. The end portion is positioned rearward of the reference S, and the rear end portion of the damper 14 is positioned forward of the rear end portion of the cooler 7, so that the storage space area on the back side of the refrigeration temperature zone chamber group 12 can be reduced. It can be taken big. Further, a plurality of vacuum heat insulating materials 38 are disposed in the heat insulating box 10 separating the outside of the refrigerator from the inside of the refrigerator, and the vacuum insulating is provided in the heat insulating boxes 10 on both sides and the back of the freezing temperature zone chamber group 13. A material 38 is disposed, and a vacuum heat insulating material 38 is disposed in the pull-out doors 5a and 6a located in front of the upper freezing chamber 5 and the lower freezing chamber 6, and the vegetable room 3 and the freezing temperature zone group. By disposing the vacuum heat insulating material 38 in the heat insulating partition wall 36 that divides 13, the heat insulating portion can be reduced, and the effective volume in the warehouse can be increased.

  Further, as shown in FIG. 2, the reference S is positioned rearward from the front end of the machine room 19, and the ratio of the effective internal volumes of the refrigeration temperature zone chamber group 12 and the refrigeration temperature zone chamber group 13 is about 75:25. . As described above, in the refrigerator that performs cooling control by two operations of the F operation and the FR operation in consideration of the ratio of the amount of cold air circulation to each temperature zone group during the FR operation as described above, This is an internal volume ratio that greatly contributes to the improvement of the efficiency.

  With the above configuration, for example, a sufficient storage space can be secured even for a refrigerator having a normal height of 600 mm and a height H of 1798 mm, both of the approximate width W of the refrigerator and the approximate depth D. It is possible to make the effective volume inside the cabinet 385 liters or more.

  As described above, since the air volume of the return air in the refrigerator compartment is generally smaller than the air volume in the freezer room return air, even if the freezer return air flows from the front side below the cooling room. In this case, since the freezer return air has a strong influence, a flow field similar to the flow field shown in FIG. 7 is formed regardless of the inflow location (direction) of the refrigerating room return air. Therefore, using the symbols shown in FIG. 6, the following relationships are satisfied: L1> L2, L3> L4, L3> L5, (L3 + L4)> L7, (L3 + L4)> L6, L7> L6, (L3 + L4) ≧ L8. Arranging the components in this manner is effective regardless of the inflow location (direction) of the return air of the refrigerator compartment.

The front view of the refrigerator which concerns on the Example of this invention. The longitudinal cross-sectional view showing the AA cross section of FIG. The longitudinal cross-sectional view showing the cooler concerning the Example of this invention, and its surrounding structure. The cross section showing the cooler concerning the example of the present invention, and its peripheral structure. The perspective view of the cooler concerning the example of the present invention. The figure showing the cooler concerning the example of the present invention, and its peripheral structure. The figure showing the cooler concerning the example of the present invention, and its peripheral structure. The figure showing the cooler concerning the example of the present invention, and its peripheral structure. The figure showing the cooler concerning the example of the present invention, and its peripheral structure. The figure showing the cooler concerning the example of the present invention, and its peripheral structure.

Explanation of symbols

1: refrigerator, 2: refrigerator compartment, 2a: rotary door, 3: vegetable room, 4: ice making room, 5: upper freezer room, 6: lower freezer room, 3a, 5a, 6a: drawer door, 3b 5b, 6b: storage container, 7: cooler, 8: cooling chamber, 9: fan in the cabinet, 10: heat insulation box, 11: ice greenhouse, 12: refrigeration temperature zone group, 13: freezing temperature zone chamber Group: 14: damper, 15: refrigerator compartment air duct, 16: freezer compartment air duct, 17: freezer compartment return duct, 17a: partition wall forming the freezer compartment return duct, 18: refrigerant pipe, 19: machine room, 20 : Compressor, 21: fin, 22: defrost heater, 23: firewood, 23a: upper end of firewood front edge, 24a-24c: refrigerator compartment outlet, 25: upper freezer compartment outlet, 26: lower freezer compartment outlet 27: Drain hole, 28, 31 partition wall, 29: Vent, 30, 32: Clearance, 30a, 32a: Reduce the clearance Structure: 33: Flow mainly composed of freezer return air, 34: Flow mainly composed of refrigerator return air, 35: Flow mixed with refrigerator return air and freezer return air, 36: Thermal insulation partition wall, 37 : Refrigerating room return duct, 38: Vacuum heat insulating material, 39: Main frost, 40: Cover body, W: Width, D: Depth, H: Height, S, S1, S2: Reference line (reference surface), L1 -L8: Dimensions.

Claims (10)

A refrigerating room having a refrigeration temperature zone and a freezing room having a freezing temperature zone disposed in the heat insulation box;
A cooler disposed on the back side of the freezer compartment for cooling the refrigerator compartment and the freezer compartment;
A cooling chamber in which the cooler is housed;
An opening through which the return cold air from the freezer compartment passes through the front portion of the cooling chamber below the cooler;
A gutter provided below the cooler;
Drainage means for draining defrost water from the dredger,
A defrosting heater disposed between the cooler and the soot;
In the refrigerator with
The cooler depth dimension is equal to or greater than the vertical dimension from the cooler bottom surface to the flange ,
The dimension extending from the line intersecting the vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is the vertical upper extension surface of the center line of the defrost heater and the lower surface of the cooler. The dimension is larger than the dimension from the intersecting line to the back of the cooler,
The refrigerator which provided the clearance gap in the back side of the said cooler, and was made into the dimension whose height dimension of the said clearance gap is smaller than the depth dimension of the said cooler . A refrigerating room having a refrigeration temperature zone and a freezing room having a freezing temperature zone disposed in the heat insulation box;
A cooler disposed on the back side of the freezer compartment for cooling the refrigerator compartment and the freezer compartment;
A cooling chamber in which the cooler is housed;
An opening through which the return cold air from the freezer compartment passes through the front portion of the cooling chamber below the cooler;
A gutter provided below the cooler;
A drain hole for draining defrost water from the dredger,
A defrosting heater disposed between the cooler and the soot;
In the refrigerator with
While making the said cooler depth dimension larger than the vertical dimension from the said cooler lower surface to the said collar ,
The dimension extending from the line intersecting the vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is the vertical upper extension surface of the center line of the defrost heater and the lower surface of the cooler. The dimension is larger than the dimension from the intersecting line to the back of the cooler,
The refrigerator which provided the clearance gap in the back side of the said cooler, and was made into the dimension whose height dimension of the said clearance gap is smaller than the depth dimension of the said cooler . A refrigerating room of a refrigerating temperature zone disposed in the heat insulation box, and a freezing room of a refrigerating temperature zone located below the refrigerating room,
A cooler disposed on the back side of the freezer compartment for cooling the refrigerator compartment and the freezer compartment;
A cooling chamber in which the cooler is housed;
An opening through which the return cold air from the freezer compartment passes through the front portion of the cooling chamber below the cooler;
A ventilation path that is provided on a side of the cooling chamber and extends to a position below the cooler and through which return air from the refrigerating chamber passes;
A gutter provided below the cooler;
A drain hole for draining defrost water from the dredger ,
A defrosting heater disposed between the cooler and the soot;
In the refrigerator with
While making the said cooler depth dimension more than the vertical dimension from the said cooler lower surface to the said collar ,
The dimension extending from the line intersecting the vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is the vertical upper extension surface of the center line of the defrost heater and the lower surface of the cooler. The dimension is larger than the dimension from the intersecting line to the back of the cooler,
The refrigerator which provided the clearance gap in the back side of the said cooler, and was made into the dimension whose height dimension of the said clearance gap is smaller than the depth dimension of the said cooler .   The refrigerator according to any one of claims 1 to 3, wherein the cooler depth dimension is equal to or greater than a vertical longest dimension extending from the cooler lower surface to the drain hole upper end. The refrigerator according to any one of claims 1 to 4, wherein the defrosting heater is positioned rearward from a vertical longitudinal section passing through a center in the depth direction of the cooler. The dimension from the line where the upper vertical extension surface of the center line of the defrost heater intersects the lower surface of the cooler to the front surface of the cooler is larger than the opening width of the opening of the lower front surface portion of the cooling chamber. The refrigerator according to claim 5. The refrigerator according to claim 5 or 6, wherein the shortest dimension from the defrost heater through the space to the thermoplastic peripheral structure is larger than the shortest dimension from the defrost heater to the cooler. The refrigerator according to any one of claims 1 to 7, wherein a gap is provided on a front side of the cooler, and a height dimension of the gap is smaller than a depth dimension of the cooler. The refrigerator according to claim 8, wherein the height of the gap on the front side of the cooler is larger than the height of the gap on the back side of the cooler. A refrigerating room of a refrigerating temperature zone disposed in the heat insulating box and a freezing room of a refrigerating temperature zone located below the refrigerating room,
A heat insulating partition that partitions the refrigerator compartment and the freezer compartment;
A cooler that is disposed on the back side of the freezer compartment and cools the refrigerator compartment and the freezer compartment;
A cooling chamber in which the cooler is stored;
A cold air return passage which is a cold air return path from the freezer compartment to the cooling chamber;
A gutter provided below the cooler;
A blower fan for sending cold air disposed above the cooler and cooled by the cooler to the refrigerator compartment and the freezer compartment;
A defrosting heater disposed between the cooler and the soot;
In the refrigerator with
While making the said cooler depth dimension more than the vertical dimension from the said cooler lower surface to the said collar,
The dimension extending from the line intersecting the vertically upper extension surface of the center line of the defrost heater and the lower surface of the cooler to the front surface of the cooler is the vertical upper extension surface of the center line of the defrost heater and the lower surface of the cooler. The dimension is larger than the dimension from the intersecting line to the back of the cooler,
A gap is provided on the back side of the cooler, and the height dimension of the gap is smaller than the depth dimension of the cooler,
The cold air return passage forms a boundary between the cold air return passage and the cooling chamber, and opens in a front side of the cooling chamber below the cooler, the cooling chamber side opening, the cold air return passage, and the freezer compartment A freezer compartment side opening that opens to the freezer compartment side, and the freezer compartment side opening is positioned lower than the cooling compartment side opening, and Communicated in a straight line or curved line,
By tilting the blower fan at an angle within the range of the tilt angle of the upper passage surface among the passage surfaces arranged vertically opposite to constitute the cold air return passage, the blower fan is The refrigerator which located below the projection surface of the said heat insulation partition and improved the effective storage volume in a warehouse.

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