JP5315179B2 - refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerator improved in inner volume efficiency and energy-saving performance with respect to the refrigerator including a damper for controlling air distribution to food storage compartments. <P>SOLUTION: This refrigerator includes a freezing temperature-zone compartment and a refrigerating temperature-zone compartment sectioned and formed in a refrigerator body to store foods, a cooler in which cold air for cooling the freezing temperature-zone compartment and the refrigerating temperature-zone compartment exchanges heat, a cooler receiving compartment in which the cooler is disposed, an inside fan for distributing the cold air exchanging heat by the cooler to the freezing temperature-zone compartment and the refrigerating temperature-zone compartment, a fan cover disposed while covering the inside fan and having an opening communicated with the freezing temperature-zone compartment or the freezing temperature-zone compartment, and the damper disposed on the opening of the fan cover for controlling the air distribution, and the fan cover has an air trunk gradually enlarged from the upstream to the downstream in the rotating direction of the inside fan, and has the opening at the downstream of the air trunk. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a refrigerator.

  Patent Document 1 describes a configuration in which cold air heat-exchanged by a cooler is blown by a blower, and blown out from a blowout port provided in multiple stages on the back side of the freezer compartment to a freezer compartment via a freezer compartment duct. ing.

JP 2009-14320 A

  However, in the refrigerator described in Patent Document 1, sufficient consideration is not given to the cold air flow formed by the blower. Therefore, there has been a problem that the loss of the flow is large, and the power of the internal fan for obtaining the necessary air volume becomes large.

  This invention is made | formed in view of the above problems, and it aims at obtaining the refrigerator which suppressed the loss of cold air flow and improved energy saving property.

In order to solve the above-described problems, the present invention provides a freezing temperature zone and a refrigeration temperature zone that are partitioned in the refrigerator main body to store foods, and cool air that cools the freezing temperature zone and the refrigeration temperature zone, respectively. A cooler in which heat is exchanged, a cooler storage chamber at the back of the freezing temperature zone chamber in which the cooler is provided, and cold air heat-exchanged by the cooler in the freezing temperature zone chamber and the refrigeration temperature zone chamber An internal fan that is disposed above the cooler that is inclined to the back side from the vertical surface, and an opening that is provided so as to cover the front of the internal fan and communicates with the upper portion of the freezing temperature zone chamber. A fan cover having a fan control unit that is provided above the internal fan and that is provided in the opening of the fan cover and controls air flow, and a duct between the cooler storage chamber and the freezing temperature zone chamber. And the fan cover is in the cabinet. Has the air passage gradually expanding from the upstream to the downstream in the rotational direction of the § down, the opening is provided to be inclined in the in-compartment fan side downstream of 該風Ro, said to be located ahead of the in-compartment fan An air outlet for blowing cold air into the freezing temperature zone is provided above the opening .

  In addition, the air passage has an expansion angle for enlarging the air passage in a range of 5 degrees to 20 degrees.

  The air passage has an angle greater than 180 degrees or greater than 180 degrees from upstream to downstream.

  Further, the fan cover has a recess at a position facing the internal fan.

  The opening is horizontally long, and the longitudinal direction of the opening is located downstream of the air passage and above the internal fan.

  ADVANTAGE OF THE INVENTION According to this invention, the loss of cold air flow can be suppressed and the refrigerator which improved energy saving property can be obtained.

The front external view of the refrigerator which concerns on embodiment of this invention. XX sectional drawing of FIG. 1 showing the structure in the refrigerator compartment which concerns on embodiment of this invention. The front view showing the structure in the refrigerator compartment which concerns on embodiment of this invention. The principal part expansion explanatory drawing of FIG. The principal part expansion explanatory drawing of FIG. The flowchart showing control of the refrigerator which concerns on embodiment of this invention. The time chart showing control of the refrigerator which concerns on embodiment of this invention. The front view showing the fan peripheral structure of the refrigerator which concerns on embodiment of this invention. The longitudinal cross-sectional view showing the fan peripheral structure of the refrigerator which concerns on embodiment of this invention. The perspective view showing the freezer compartment damper of the refrigerator which concerns on embodiment of this invention. The figure showing the flow volume-static pressure characteristic of an air blower. The figure showing the inlet speed and outlet speed of a fan in case air path resistance is small. The figure showing the inlet speed and outlet speed of an air blower in case air path resistance is large. The disassembled perspective view which looked at the air blower periphery structure from the back side.

  An embodiment of a refrigerator according to the present invention will be described with reference to FIGS. 1 to 13.

  FIG. 1 is a front external view of a refrigerator 1 according to the present embodiment, FIG. 2 is a vertical sectional view taken along line XX in FIG. 1 showing a configuration inside the refrigerator 1, and FIG. FIG. 4 is a front view showing the internal configuration, showing the arrangement of the cold air duct and the outlet, and FIG. 4 is an enlarged explanatory view of the main part of FIG. FIG. 5 is an enlarged explanatory view of the main part of FIG.

  As shown in FIG. 1, the refrigerator 1 of this embodiment is equipped with the refrigerator compartment 2, the ice-making room 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 from upper direction as a food storage room. In the following description, the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are collectively referred to as a freezing temperature zone 60, and the refrigerating chamber 2 and vegetable room 6 are collectively referred to as a refrigerating temperature zone 61. is there.

  The refrigerating room 2 includes front and rear refrigerating room doors 2a and 2b which are divided into left and right sides. The ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 are each a drawer-type ice making room door. 3a, an upper freezer compartment door 4a, a lower freezer compartment door 5a, and a vegetable compartment door 6a. Hereinafter, the refrigerator compartment doors 2a and 2b, the ice making compartment door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are simply referred to as doors 2a, 2b, 3a, 4a, 5a, and 6a.

  The refrigerator 1 includes a door sensor (not shown) that detects the open / closed state of each door of the doors 2a, 2b, 3a, 4a, 5a, and 6a, and a state determined to be the door open state for a predetermined time, for example, 1 minute. When the operation is continued, an alarm (not shown) for notifying the user, a temperature setting device (not shown) for setting the temperature of the refrigerator compartment 2 and the vegetable compartment 6 and the temperature setting of the freezing temperature zone 60 are provided.

  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 formed by filling a foam heat insulating material (foamed polyurethane). The heat insulating box 10 of the refrigerator 1 is mounted with a vacuum heat insulating material 25.

  The inside of the refrigerator is separated from the refrigerator compartment 2 by the heat insulating partition wall 28, the upper freezing chamber 4 and the ice making chamber 3 (see FIG. 1, the ice making chamber 3 is not shown in FIG. 2). The lower freezer compartment 5 and the vegetable compartment 6 are separated.

  A plurality of door pockets 32 are provided on the inner side of the doors 2a and 2b (see FIG. 1). The refrigerator compartment 2 is partitioned into a plurality of storage spaces in the vertical direction by a plurality of shelves 36.

  As shown in FIG. 2, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are withdrawn integrally with doors 4a, 5a, 6a provided in front of the respective compartments, and storage containers 4b, 5b, 6b. Are respectively provided, and the storage containers 4b, 5b, 6b can be pulled out by putting a hand on a handle portion (not shown) of the doors 4a, 5a, 6a and pulling it out to the front side. Similarly, the ice making chamber 3 shown in FIG. 1 is provided with an unillustrated storage container (indicated by (3b) in FIG. 2) integrally with the door 3a. The container 3b can be pulled out by pulling it out. The upper freezer compartment 4 can be used as a quick freezer compartment. In order to improve the quick freezing performance, the storage container 4b of the upper freezer compartment 4 is provided with an aluminum tray (not shown) so that the freezing speed is improved.

  As shown in FIG. 2 (refer to FIGS. 3 to 5 as appropriate), the cooler 7 is provided in a cooler storage chamber 8 provided substantially at the back of the lower freezing chamber 5 and provided above the cooler 7. The air that has been cooled by exchanging heat with the cooler 7 by the blower 9 (cold air; hereinafter, low-temperature air that has been cooled by the cooler 7 is referred to as cold air) passes through the refrigerator compartment duct 11 and the freezer compartment duct 12. Then, it is sent to the refrigerator compartment 2, the upper freezer compartment 4, the lower freezer compartment 5, and the ice making room 3. Air blowing to each room is controlled by opening and closing the refrigerator compartment damper 20 and the freezer compartment damper 50.

  Incidentally, the refrigerator compartment duct 11 and the freezer compartment duct 12 are provided on the back side of each room of the refrigerator 1 as indicated by broken lines in FIG.

Specifically, when the refrigerator compartment damper 20 is in the open state and the freezer compartment damper 50 is in the closed state, the cold air is sent to the refrigerator compartment 2 from the outlets 2 c provided in multiple stages via the refrigerator compartment duct 11.
After the cooling of the refrigerating room 2 is finished, the cold air flows in from the refrigerating room return port 2d provided at the lower right side of the back side of the refrigerating room 2 and the back of the vegetable room 6 through the refrigerating room-vegetable room communication duct 16. The vegetable compartment 6 is cooled by flowing into the vegetable compartment 6 from the vegetable compartment outlet 6c provided on the upper right side. The cold air that has cooled the vegetable compartment 6 is returned from the vegetable compartment return port 6d provided in front of the lower part of the heat insulating partition wall 29 through the vegetable compartment return duct 18, and returned to the vegetable compartment having a width substantially equal to the width of the cooler 7. It flows in from the outlet 18a (see FIG. 3 or FIG. 5).

  Although the freezer damper 50 is omitted in FIG. 3, when the freezer damper 50 is in an open state, the cold air heat-exchanged by the cooler 7 is boosted by the blower 9, passes through the freezer duct 12, The air is blown from 4c and 5c to the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5, respectively. In addition, as shown in FIG. 3, in the refrigerator 1 of this embodiment, a total of seven outlets 3c to 5c of the freezing temperature zone 60 are provided, and the total circumference of the outlets 3c to 5c is 1200 mm. is there.

  As shown in FIG. 4, in the refrigerator 1 of the present embodiment, a blower 9 is provided above the cooler 7, and a freezer compartment damper 50 is provided above the blower 9. Further, an upper freezer compartment outlet 4c and an ice making room outlet 3c (see FIG. 3) for sending cold air to the upper freezer compartment 4 located above the freezer temperature zone 60 are provided above the freezer damper 50. The upper freezer compartment outlet 4c has the largest opening area among the outlets of the freezer compartment.

  As shown in FIG. 5, the cold air that has cooled the refrigerator compartment 2 flows into the vegetable compartment 6 through the refrigerator compartment-vegetable compartment communication duct 16 provided on the side of the cooler storage compartment 8. The return cold air from the vegetable compartment 6 flows in from the vegetable compartment return port 6d (see FIG. 2), and cools through the vegetable compartment return duct 18 provided in the heat insulating partition wall 29 as shown in FIG. It flows into the cooler storage chamber 8 from the vegetable room return outlet 18a (see FIG. 5) provided in front of the lower portion of the cooler storage chamber 8 and having a width approximately equal to the width of the cooler 7. On the other hand, as shown in FIG. 4, the cold air that has cooled the refrigeration temperature zone chamber 60 is approximately equal to the width of the cooler 7 provided at the lower part of the partition plate 54 that partitions the cooler storage chamber 8 and the refrigeration temperature zone chamber 60. It flows into the cooler storage chamber 8 through the freezer return port 17 having the same width. A defrost heater 22 is provided below the cooler storage chamber 8. The defrost heater 22 is a glass tube heater, and an aluminum radiating fin 22a is provided on the outer periphery of the glass tube.

  An upper cover 53 is provided above the defrost heater 22 in order to prevent defrost water from dripping onto the defrost heater 22. In addition, as shown in FIG. 5, a warm air storage space 26 is provided in front of the lower portion of the cooler storage chamber 8. The warm air storage space 26 is a space into which the ascending air current during the defrosting of the cooler 7 flows. The warm air storage space 26 can suppress warm air (updraft) generated during the defrosting operation performed by energizing the defrost heater 22 from flowing into the refrigeration temperature zone chamber 60.

  The frost adhering to the wall of the cooler 7 and the surrounding cooler storage chamber 8 is dissolved at the time of the defrosting operation, and the defrost water generated at that time is stored in the bowl 23 provided at the lower part of the cooler storage chamber 8. After flowing in, it reaches an evaporating dish 21 disposed in a machine room 19 to be described later via a drain pipe 27, and generates heat by the compressor 24 and a condenser (not shown) disposed in the machine room 19 and the compressor 24. Evaporate.

  A cooler temperature sensor 35 attached to the cooler 7 is located at the upper left as viewed from the front of the cooler 7. The temperature of the cooler 7 (hereinafter referred to as “cooler temperature”), the temperature of the refrigerator compartment 2 (hereinafter referred to as “refrigerator compartment temperature”), and the temperature of the lower freezer compartment 5 (hereinafter referred to as “freezer compartment temperature”). Can be detected). Furthermore, the refrigerator 1 includes an outside temperature sensor (not shown) that detects the temperature outside the refrigerator. The vegetable compartment 6 is also provided with a vegetable compartment temperature sensor 33a.

  Incidentally, in this embodiment, isobutane is used as a refrigerant, and the amount of refrigerant enclosed is as small as about 80 g.

  A control board 31 on which a CPU, a memory such as a ROM and a RAM, an interface circuit, and the like are mounted is arranged on the upper surface of the ceiling wall of the refrigerator 1 (see FIG. 2). Temperature sensor 35, refrigerator temperature sensor 33, vegetable room temperature sensor 33a, freezer temperature sensor 34, door sensor for detecting the open / closed state of each door of doors 2a, 2b, 3a, 4a, 5a, 6a, Connected to a temperature setter (not shown) provided on the inner wall of the refrigerator compartment 2, and controls the ON / OFF of the compressor 24, the refrigerator compartment damper 20 and the freezer compartment damper 50 individually by a program preinstalled in the ROM. ON / OFF control of each actuator (not shown) that is driven to ON, ON / OFF control and rotation speed control of the blower, and ON / O of an alarm that informs the door open state described above It performs the control of F, and the like.

  Next, the detailed structure around the blower 9 and the freezer compartment damper 50 of the refrigerator 1 of the present embodiment will be described with reference to FIGS. 8 to 10 and FIG. 13.

  FIG. 8 is a front view of the structure around the blower 9 and the freezer damper 50 of the refrigerator 1 according to the present embodiment. FIG. 9 shows the structure around the blower 9 and the freezer damper 50 of the refrigerator 1 according to the present embodiment. It is the longitudinal cross-sectional view seen from the side. FIG. 10 is a perspective view of the freezer damper 50 of the refrigerator 1 of the present embodiment, and FIG. 13 is an exploded perspective view of the peripheral structure of the blower 9 as seen from the back side.

As shown in FIG. 10, a freezer damper 50 used in the refrigerator 1 according to the present embodiment includes a horizontally elongated frame 103 made of, for example, resin, having an opening 102 on one side, and one end (rectangular shape) of the frame 103. The driving means 100 includes a driving system such as a motor and a reduction gear. One surface of the opening / closing plate 104 includes a buffer member 104a formed of a flexible material such as urethane foam or polyethylene foam. The freezer compartment damper 50 is closed when the buffer member 104a is pressed against the inner surface (the surface facing the opening / closing plate) 103a in the vicinity of the opening 102 of the frame 103. Therefore, the sealing performance depends on the peripheral length 102 a of the opening 102. Here, the opening 102 is provided with a connecting portion 103b where the upper side and the lower side of the frame 103 are connected, but this is provided for suppressing deformation and does not directly contribute to the sealing performance. Therefore, when considering the sealing performance of the freezer damper 50, the peripheral length 102a of the opening 102 does not include the length of the connecting portion 103b that does not directly contribute to the sealing performance. In addition, the magnitude | size of the opening 102 of the freezer damper 50 used with the refrigerator 1 of this embodiment is 180 mm x 35 mm, and the perimeter 102a which contributes to sealing performance is 430 mm. Further, a rib 103c is provided on the outer periphery of the opening 102. The rib 103c serves as both a positioning when the freezer compartment damper 50 is attached and a reinforcement of the opening 102.

  As shown in FIG. 8, the blower of the refrigerator 1 of the present embodiment is a motor-integrated type propeller fan in which the shape of the casing 9 a is substantially square and the boss portion includes a motor. A fan cover 70 is provided on the discharge side of the blower 9 so as to form a cold air collecting duct 13 for collecting cold air. The fan cover 70 is provided so as to cover the front of the blower 9. The outer peripheral portion 13a of the cold air collecting duct 13 is from upstream to downstream in the direction of rotation of the internal fan from the position where the distance from the rotation center of the blower 9 to the outer peripheral portion 13a is minimum (minimum dimension position shown in FIG. 8). It becomes the expansion wind path 13b so that it may expand gradually toward.

Note that the outer peripheral portion 13a of the cold air collecting duct 13 expands at the expansion angle γ ₁ from the minimum dimension position shown in FIG. 8 based on the formula (1).

Here, R _min is the minimum dimension of the distance from the rotation center of the blower 9 to the outer peripheral portion 13a, γ ₁ is the flow path enlargement angle, and γ ₂ is the minimum dimension position shown in FIG. Angle. Specifically, in the refrigerator of this embodiment, R _min = 140 mm, γ ₁ = 10 degrees, and γ ₂ = 200 degrees.

  Further, in the refrigerator 1 of the present embodiment, the enlarged air passage 13b of the cold air collecting duct 13 is 180 degrees in the direction of rotation of the internal fan from the position where the distance from the internal fan rotation center to the air passage outer peripheral wall is minimized. Have more.

  That is, the enlarged air passage 13b has an angle larger than 180 degrees or 180 degrees from the start end (upstream) to the end end (downstream). The outlet opening 13c is horizontally long, and the longitudinal direction of the outlet opening 13c is located at the end (downstream) of the enlarged air passage 13b. The fan cover 70 has a recess 70 a at a position facing the blower 9, and an enlarged air passage 13 b is provided around the recess. That is, the cold air flows through the enlarged air passage 13b and is rectified, so that it smoothly passes through the outlet opening 13b and flows into the upper freezer compartment 4. Thereby, the cooling efficiency of the upper freezer compartment 4 can be improved.

  Moreover, as shown in FIG. 4, the freezer compartment duct 12 is provided so that the front of the fan cover 70 may be covered. That is, the cool air collecting duct 13 and the freezer compartment duct 12 are disposed between the cooler storage chamber 8 and the upper freezer compartment 4 and the lower freezer compartment 5. As a result, an air insulation layer is formed behind the storage space, so that the upper freezing chamber 4 and the lower freezing chamber 5 are affected by heat from the cooler storage chamber 8 (for example, the temperature rise during the defrosting operation of the cooler 7). Etc.) is suppressed, and the temperature change of the storage space can be suppressed.

  Further, as shown in FIG. 8, the blower 9 is disposed to be inclined from the horizontal plane by an angle β1 (β1 is 10 degrees in the refrigerator 1 of the present embodiment).

  As shown in FIG. 9, the freezer compartment damper 50 is arranged so that the opening 102 faces substantially forward, but the arrangement position is such that the rib 103 c of the freezer compartment damper 50 is connected to the cold air collecting duct shown in FIG. 8. It is easily determined by matching with the 13 outlet openings 13c (the outlet opening 13c is larger than the opening 102 of the freezer damper 50). Moreover, as shown in FIG. 9, the freezer damper 50 is arrange | positioned so that the rotating shaft 101 may become an upper side. Furthermore, the open / close plate 104 of the freezer damper 50 opens to the back side, and the opening angle θ varies depending on the operating state, and is used in a state of 0 degrees (fully closed), 60 degrees, and 90 degrees (fully opened) ( Details of the relationship between the operating state and the opening angle will be described later).

  As shown in FIG. 8, the freezer damper 50 is installed to be inclined from the horizontal plane by an angle β2 (β2 is 6 degrees in the refrigerator 1 of the present embodiment). 9, the blower 9 is inclined backward by an angle α1 (α1 is 13 degrees in the refrigerator 1 of the present embodiment), and the freezer damper 50 is angled α2 (α2 is 6 in the refrigerator 1 of the present embodiment). It is designed to be tilted backward by a degree.

The size of the outlet opening 13c of the cold air collecting duct 13 is 188.5 mm × 43 mm, and its peripheral length 13d is 463 mm.

  The fan hold 71 is provided with a communication hole 75 through which the cold air collecting duct 13 and the cooler storage chamber 8 communicate. The communication hole 75 is provided at the lower end in the cold air collecting duct 13.

  In addition, a fan cover heater 76 is disposed in a region below the blower 9 in the cold air collecting duct 13 (fan cover inner surface 70a). As shown in FIG. 9, the fan cover heater 76 has a portion 76 a that extends from the inside of the cool air collecting duct 13 through the communication hole 75 into the cooler chamber 8.

  As shown in FIG. 13, the fan cover 70 is an integrally molded product with the partition plate 54. Further, the member (fan hold 71) for holding the blower 9 is separate from the fan cover 70, and is assembled to the back side of the fan cover as shown in FIG.

Next, control of the cooling operation of the refrigerator 1 of the present embodiment will be described with reference to FIG.
FIG. 6 is a control flowchart showing basic control of the refrigerator 1 of the present embodiment. The control is performed by the CPU of the control board 31 (see FIG. 2) executing a program stored in the ROM.

  The cooling operation of the refrigerator 1 of the present embodiment includes a freezer operation, a refrigerating room operation, a refrigerating operation, a frost cooling operation, and OFF. The freezer operation is the state of “fan in the refrigerator ON, refrigerator colder damper closed, freezer damper open (open angle θ = 90 degrees (see FIG. 9 for definition of open angle)), compressor ON (high rotation)” The operation of cooling the refrigeration temperature zone 60 is as follows. The operation of the refrigeration chamber includes “an internal fan ON, a refrigeration chamber damper open, a freezer compartment damper closed (open angle θ = 0 °), and a compressor ON (low rotation). The operation for cooling the refrigeration temperature zone 61 in the state of “)” and the refrigeration / freezing operation are “internal fan ON, refrigeration chamber damper open, freezer compartment damper open (open angle θ = 60 degrees), compressor” This is an operation for cooling both the refrigeration temperature zone chamber 61 and the freezing temperature zone chamber 60 in the “ON (high rotation)” state. The frost cooling operation is an operation for cooling the refrigeration temperature zone chamber 61 in the state of “internal fan ON, refrigeration chamber damper open, freezer compartment damper close, compressor OFF”. And the compressor are stopped and cooling is not performed.

As shown in FIG. 6, when the refrigerator 1 is started to operate when the power is turned on (start), each chamber in the refrigerator 1 is cooled, and the basic heat load is only the heat intrusion from the outside. From then on, if the user opens and closes the door and the heat load increases, or the outside temperature and humidity environment changes and the amount of heat penetration does not change, a certain operation pattern is repeated (stable Cooling operation). In FIG. 6, the control process up to this stable cooling operation state is omitted.
In addition, at the time of the stable cooling operation of the refrigerator 1 of this embodiment, since control based on the temperature of the vegetable compartment 6 is not performed, description regarding the vegetable compartment 6 is abbreviate | omitted (in the description of the following control, vegetables are contained in the refrigerator compartment 2). Including chamber 6).

  During the stable cooling operation, a constant operation pattern (operation cycle) is repeated. Here, the operation will be described from the state in which the freezer operation is performed (step S101). The freezer operation is an operation in which the freezing temperature zone 60 is cooled in the state of “internal fan ON, refrigerator colder damper closed, freezer damper open, compressor ON (high rotation)”.

  When opening / closing of the refrigerating room door 2a or 2b is detected by the refrigerating room door sensor that detects opening / closing of the refrigerating room door 2a or 2b in the state where the freezer operation is being performed (step S102), step The process proceeds to S201 (step S201 will be described later). If the refrigerator compartment door 2a or 2b is not opened and closed, the refrigerator compartment upper limit temperature TR_2 in which the refrigerator compartment temperature detected by the refrigerator compartment temperature sensor 33 is preset (TR_2 = in the refrigerator 1 of the present embodiment) is set. It is determined whether the temperature is higher than 6 ° C. (step S103).

  When the temperature of the refrigerating room is not higher than the refrigerating room temperature TR_2 (No) (the control when the refrigerating room temperature is higher than the refrigerating room upper temperature TR_2 (Yes) will be described later), the temperature is detected by the freezing room temperature sensor 34. It is determined whether or not the freezer compartment temperature is lower than a preset freezer compartment lower limit temperature TF_1 (TF_1 = −21 ° C. in the refrigerator 1 of the present embodiment) (step S104). In addition, when it is not freezer compartment temperature <freezer compartment lower limit temperature TF_1 (No), it returns to step S101 again.

In step S104, if the freezer compartment temperature is smaller than the freezer compartment lower limit temperature TF_1 (Yes), then the refrigerator compartment temperature and the preset reference temperature TR_a (TR_a = 5 in the refrigerator 1 of the present embodiment) are set. C) and TR_b (TR_b = 4 ° C. in the refrigerator 1 of the present embodiment), and the value of the reference temperature Tevp related to the detected temperature of the cooler temperature sensor 35 is selected based on the comparison result. Specifically, if the refrigerating room temperature> TR_a, Tevp = Tevp_1 (Tevp_1 = 3 ° C. in the refrigerator 1 of the present embodiment), and if TR_a ≧ refrigerating room temperature> TR_b, Tevp = Tevp_2 (the present embodiment In refrigerator 1, Tevp_2
= −10 ° C.) and TR_b ≧ refrigeration room temperature, Tevp = Tevp_3 (Tevp_2 = −18 ° C. in the refrigerator 1 of the present embodiment) (step S105).

  Therefore, Tevp_1 is selected when the outside air temperature is high and the refrigerator temperature is likely to rise, and Tevp_3 is selected when the outside temperature is low and the refrigerator temperature is difficult to rise. If the outside air temperature is about, Tevp_2 is selected. In addition, for example, a food gap may be sandwiched between the refrigerator compartment door 2a or 2b, and a slight gap is generated, which steadily increases the heat load. However, the refrigerator compartment sensor has a small gap so that the door is closed. It may be in a state where an alarm that recognizes the state and notifies the door open state does not sound. In this case, even if the outside air temperature is relatively low, the temperature of the refrigerator compartment may easily rise, and Tevp_2 or Tevp_1 may be selected as the value of Tevp.

Subsequently, a frost cooling operation is performed (step S106). The frost cooling operation is an operation in which the refrigerating temperature zone chamber 61 is cooled in a state of “internal fan ON, refrigerating chamber damper open, freezer compartment damper closed, compressor OFF”. In the state in which the frost cooling operation is performed, whether or not the refrigerator compartment temperature is lower than a preset refrigerator compartment lower limit temperature TR_1 (TR_1 = 1.5 ° C. in the refrigerator 1 of the present embodiment) (step S107). It is determined whether or not the cooler temperature is higher than the reference temperature Tevp set in step S105 (step S108), the refrigerator temperature does not satisfy the refrigerator compartment temperature <refrigerator compartment lower limit temperature TR_1 (No), and the refrigerator temperature> reference. When the temperature Tevp is not satisfied (No), it is determined whether or not the freezer temperature is higher than the preset compressor ON temperature TF_2 (TF_2 = −19 ° C. in the refrigerator 1 of the present embodiment) ( In step S109), when the freezer temperature> compressor ON temperature TF_2 is not satisfied (No), the process returns to step S107 again.

In step S109, when it is determined that the freezer temperature> compressor ON temperature TF_2 (Yes), the compressor is subsequently turned on and the low rotation (in the refrigerator 1 of the present embodiment, the compression at this time). The refrigerator is operated at a machine speed of 1200 min ⁻¹ ) (step S110). That is, the refrigerating room operation is an operation for cooling the refrigerating temperature zone chamber 61 in the state of “internal fan ON, refrigerating room damper open, freezer compartment damper closed, compressor ON (low rotation)”.

  In the state in which the refrigerator compartment operation is carried out, it is determined whether or not the freezer compartment temperature is higher than the preset freezer compartment upper limit temperature TF_3 (TF_3 = −16 ° C. in the refrigerator 1 of the present embodiment) (step). S111), when it is determined that the temperature of the freezer compartment> the freezer compartment upper limit temperature TF_3 is not satisfied (No) (if the freezer compartment temperature> the freezer compartment upper limit temperature TF_3 is satisfied (Yes), the control will be described later). The process proceeds to determination of room temperature <refrigeration room lower limit temperature TR_1 (step S112). When the refrigerator compartment temperature <the refrigerator compartment lower limit temperature TR_1 is not satisfied (No), the process returns to step S111 again.

In step S112, when the refrigerator compartment temperature <the refrigerator compartment lower limit temperature TR_1 is satisfied (Yes), “freezer compartment damper open, refrigerator compartment damper closed” is set (step S113). In the refrigerator 1 of the embodiment, the compressor rotation speed at this time is 1900 min ⁻¹ ) and the blower 9 is stopped (step S114). After a predetermined time (30 seconds in the refrigerator 1 of the present embodiment) has elapsed (step S115), the blower 9 is operated and the freezer operation is started (step S116). Since the freezer compartment operation in step S116 is the state of the freezer compartment operation described in step S101, the above is the operation cycle during the stable cooling operation of the refrigerator 1 of the present embodiment.

  In general, in a refrigerator, when a door is opened or closed or food having a relatively high temperature is stored, the heat load temporarily increases. Below, control when the heat load of the refrigerator 1 of this embodiment increases temporarily is demonstrated.

  In the refrigerator 1 of the present embodiment, whether or not the refrigerator compartment door 2a or 2b is opened or closed is determined in step S102, and if the refrigerator compartment door 2a or 2b is opened or closed, the process proceeds to step S201. It is like that. In step S201, the refrigerator compartment upper limit temperature TR_2 is replaced with TR_2 '(TR_2 = 6 ° C. becomes TR_2 ′ = 8 ° C. in the refrigerator 1 of the present embodiment). When the refrigerating room upper limit temperature TR_2 is overwritten with TR_2 ', the process returns to step S101. Returning to step S101, if the door has already been closed (if step S102 is determined to be No), then in step S103, the determination of refrigeration room temperature> refrigeration room upper limit temperature TR_2 is performed. Here, in step S201, since the refrigerator compartment upper limit temperature TR_2 is overwritten with TR_2 ', the refrigerator compartment upper limit temperature is high. Therefore, it is difficult to satisfy the refrigerator temperature> the refrigerator temperature upper limit temperature TR_2 in step S103 as compared with the case where the refrigerator compartment 2 is not opened and closed. When the temperature of the refrigerating room> the refrigerating room upper limit temperature TR_2 in Step S103 is satisfied (Yes), it is considered that the refrigerating room 2 is in an indispensable state, the refrigerating room damper 20 is opened, and the refrigerating operation, that is, “ As the operation of the internal fan ON, refrigerator compartment damper open, freezer compartment damper open, compressor ON (high rotation), both the refrigerator temperature zone chamber 61 and the refrigerator temperature zone chamber 60 are cooled (step S301). After the refrigeration operation is started in step S301, the process proceeds to step S112. Note that the refrigerator compartment upper limit temperature TR_2 returns from TR_2 '(= 8 ° C.) to the original value TR_2 (= 6 ° C.) again after a predetermined time (30 minutes in the refrigerator 1 of the present embodiment). .

  Further, in step S112, the determination of the freezer temperature> the freezer upper limit temperature TF_3 is performed during the refrigerator operation. When the freezer temperature> freezer upper limit temperature TF_3 is satisfied (Yes), it is considered that cooling of the freezing temperature zone 60 is indispensable, the compressor 24 is set to a high rotation speed, the freezer compartment damper 50 is opened, and refrigeration is performed. In the refrigeration operation, that is, the operation of “internal fan ON, refrigerator compartment damper open, freezer compartment damper open, compressor ON (high rotation)”, both the refrigerator temperature zone chamber 61 and the refrigerator temperature zone chamber 60 are cooled. (Step S301). After the refrigeration operation is started in step S501, the process proceeds to step S112.

  Further, if either step S107 (refrigeration room temperature <refrigeration room lower limit temperature TR_1) or step S108 (cooler temperature> Tevp (reference temperature set in step S105)) is satisfied (Yes), frost The internal fan is stopped during the cooling operation (step S401), and the process proceeds to step S109.

  FIG. 7 shows the temperature change in the refrigerator when the refrigerator 1 of the present embodiment is installed in an environment where the outside air temperature is 30 ° C. and the relative humidity is 70%, and the stable cooling operation is performed, the blower 9 and the refrigerator compartment. 3 is a time chart showing control states of a damper 20, a freezer damper 50, and a compressor 24. The detailed measurement conditions are in accordance with JIS C9801: 2006.

  As shown in FIG. 7, the freezer operation performed in the state of “internal fan ON, refrigerator colder damper closed, freezer damper open, compressor ON (high rotation)” is performed at the freezer temperature at the elapsed time ta. Has reached the freezer compartment lower limit temperature TF_1 (step S104 in FIG. 6), and subsequently, a frost cooling operation performed in the state of “internal fan ON, refrigerator compartment damper closed, freezer compartment damper open, compressor OFF” (Step S106 in FIG. 6). In step S105 in FIG. 6, the temperature in the refrigerator compartment is greater than TR_a (TR_a = 5 ° C.), so Tevp is Tevp = Tevp_1 (Tevp_1 = 3 ° C.). During the frost cooling operation, since the freezing temperature zone 60 is not cooled, the freezing chamber temperature rises and reaches the compressor ON temperature TF_2 at the elapsed time tb (step S109 in FIG. 6). Subsequently, the compressor 24 is operated at a low rotation speed, and the operation of the refrigerator compartment of “internal fan ON, refrigerator compartment damper open, freezer compartment damper closed, compressor ON (low revolution)” is performed (step S110 in FIG. 6). ). Until the elapsed time tb, the frost cooling was performed while the compressor 24 was not operated. From the elapsed time tb, the refrigeration temperature zone chamber 61 was cooled due to the operation of the refrigerating room where the compressor 24 was operated. It is accelerated and reaches the refrigerator compartment lower limit temperature TR_1 at the elapsed time tc (step S112 in FIG. 6). Therefore, the operation proceeds to the freezer operation (“internal fan ON, refrigerating chamber damper closed, freezer damper open, compressor ON (high rotation)”), but at the start of the freezer operation, a predetermined time Δt (Δt = For 30 seconds, the blower 9 is stopped (steps S113 to S115 in FIG. 6), and after the predetermined time Δt has elapsed, the blower 9 is operated and cooling is started (step S116 in FIG. 6).

  The structure and basic control method of the refrigerator 1 according to the present embodiment have been described above, but the effects exerted by the refrigerator 1 according to the present embodiment will be described below.

  The refrigerator 1 of the present embodiment includes a cold air collecting duct 13 to collect cold air toward the food storage room (the freezing temperature zone chamber 60) located in front of the blower 9, and the cold air collecting duct 13 is disposed in front of the blower 9. A cold air collecting duct outlet opening 13c communicating with the refrigeration temperature zone chamber 60 located is provided, and a fan cover outlet opening 70a is provided with a damper (freezer compartment damper 50) for controlling air flow to the refrigeration temperature zone chamber 60. The air blowing to the belt chamber 60 is performed only through the opening of the freezer compartment damper 50. Further, the cold air collecting duct 13 includes an enlarged air passage 13b that sequentially expands in the direction of rotation of the internal fan from a position where the cross section of the cold air collecting duct flow path is the minimum (position of the minimum dimension shown in FIG. 8).

  Thereby, energy saving property improves. The reason will be described below with reference to FIGS. 11, 12A and 12B.

  The refrigerator of the present embodiment flows between the blower 9 and a chamber (freezer compartment 60) provided with a plurality of outlets provided in front of the blower 9 toward a chamber provided in front of the blower 9. The cold air collecting duct 13 is sequentially expanded from the position where the cross section of the cold air collecting duct flow path is minimum (minimum dimension position shown in FIG. 8) in the fan rotation direction. An enlarged air passage 13b is provided.

  Thereby, energy saving property improves. The reason will be described below with reference to FIGS.

  Since the refrigerator cooler generally has a negative temperature, frost formation occurs. And when frost grows in a cooler, wind path resistance increases. In addition, since the refrigerator is intended to store food, it is desirable to make the food storage space as large as possible. That is, it is desirable to make the cold air duct, which is a space where food cannot be stored, as compact as possible.

  Here, in a refrigerator, a propeller fan which is an axial fan is generally used as a blower. FIG. 11 is a general air volume-static pressure characteristic diagram of the propeller fan when the rotation speed is constant. As shown in FIG. 11, when the rotational speed is constant, the air volume Q1 is obtained when the air path resistance is small, and the air volume Q2 is obtained when the air path resistance is small. Here, the relationship is Q1> Q2.

Next, FIG. 12A and FIG. 12B are diagrams showing a speed change (speed triangle) between the inlet and the outlet of the blade 90 of the propeller fan. FIG. 12A is a case where the air path resistance is small, and FIG. The case where is large. In FIG. 12A, c ₁ is the inlet absolute speed, u ₁ is the inlet peripheral speed (rotational speed), w ₁ is the inlet relative speed (relative speed to the blade), c ₂ is the outlet absolute speed, and _{cm 2} is the axis of the outlet absolute speed. direction component, c _.theta.2 is circumferential component of the outlet absolute velocity, u ₂ is the outlet peripheral velocity, w ₂ represents the outlet relative velocity. When the air volume in the air volume-static pressure characteristic of FIG. 11 is large (for example, in the state of the air volume Q1 of FIG. 11), that is, in FIG. 12A, the axial direction of the inlet peripheral speed u ₁ (or the outlet peripheral speed u ₂ ) The velocity component (c ₁ (= c _m2 )) becomes relatively large. Moreover, as shown in FIG. 11, when there is much air volume, a static pressure becomes low. This means that the deceleration between the blade inlet relative velocity w ₁ and the outlet relative velocity w ₂ is small. Therefore, when the air volume is large, a speed triangle as shown in FIG. 12A is obtained. On the other hand, when the air volume is small (for example, the state of the air volume Q2 in FIG. 11), a speed triangle as shown in FIG. 12B is obtained.

In the case of a constant rotational speed, the peripheral speeds are the same in FIGS. 12A and 12B, and u ₁ = u ₁ ′ (u ₂ = u ₂ ′). From this, it can be seen that when the rotational speed is constant, the circumferential component of the outlet absolute speed is large when the wind path resistance is large (FIG. 13) compared to when the wind path resistance is small (FIG. 12) (c _θ2 < _Cθ2 ′).

As described above, when the wind path resistance is large, a strong swirl flow caused by the circumferential component _cθ2 is formed in the blowing area of the propeller fan. The energy of this swirl flow is lost without being used effectively for cooling. Therefore, when the wind path resistance increases due to frost formation, the energy saving performance can be improved by effectively using the strong swirl flow which is a loss.

  The refrigerator of the present embodiment includes a cold air collecting duct 13, and the cold air collecting duct 13 includes an enlarged air passage 13 b that sequentially expands in the rotation direction of the blower 9 from a position where the cross section of the cold air collecting duct flow path is minimized. ing. As a result, the swirling flow flows into the enlarged air passage 13b, and the swirling flow can be pressure-recovered by sequentially expanding the cross-section of the flow path. That is, since the swirl flow that has been conventionally lost can be effectively used as the pressure, the fan power for obtaining the necessary air volume can be suppressed, and the energy saving performance is improved.

  Further, the distance between the outer peripheral surface 13a of the cold air collecting duct 13 and the rotation center of the blower 9 is formed so as to sequentially increase in the rotation direction of the blower 9 from the position where the cross section of the cold air collecting duct flow path is minimized. The flow blown out from the blower 9 is blown out mainly in the circumferential direction of the blower 9. Thereby, since the pressure of the swirling flow blown out in the circumferential direction can be smoothly recovered, the energy saving property is improved.

  Further, the air passage expansion angle of the expansion air passage 13b of the cold air collecting duct 13 is 10 degrees, and is an expansion angle of 5 degrees or more and 20 degrees or less that is effective for pressure recovery and can be installed in a space-saving manner. Thereby, energy saving property is high and the expansion wind path 13b can be made compact.

  Further, the enlarged air passage 13b of the cold air collecting duct 13 is provided with 180 degrees or more (200 degrees) in the fan rotation direction. In order to recover the pressure of the swirling flow, it is advantageous that the distance is long. However, this makes the expanded air passage 13b a sufficient distance, and the swirling flow can be pressure-recovered effectively, so that energy saving is improved.

  The cold air collecting duct 13 is opened upward so as to direct the flow flowing out through the enlarged air passage 13b upward. As a result, the chamber (freezer chamber 60) in front of the internal fan can be cooled well, and the energy saving performance is also improved. The reason will be described below.

  Generally, cold air having a low temperature relative to the ambient temperature forms a downward flow from the upper side to the lower side. Therefore, the storage chamber can be favorably cooled by supplying more cold air to the upper side of the storage chamber. In conventional refrigerators, the opening area of the lower freezer compartment outlet is reduced, the amount of air blown from the lower freezer compartment outlet is relatively lowered, and the amount of air blown from the upper freezer compartment outlet is relatively I was trying to raise it. That is, a swirling flow is blown out below the internal fan, and a flow toward the lower side of the internal fan is generated. For this reason, if the opening area of the lower freezer compartment outlet is large, a large amount of air is blown out from the lower freezer compartment outlet. And the balance of the blowing amount with the freezer compartment outlet on the upper stage side is relatively lost. Therefore, the amount of air blown from the lower freezer compartment outlet is adjusted by reducing the opening area of the lower freezer compartment outlet and adding resistance.

  However, with this configuration, the air path resistance increases as a result, and it is necessary to increase the internal fan rotation speed to obtain the necessary air volume. That is, it has become a factor that deteriorates energy saving.

  Therefore, in the refrigerator of the present embodiment, the cold air collecting duct 13 is opened upward so that the flow flowing out through the enlarged air passage 13b is directed upward, so that the blower 9 as seen in the conventional refrigerator is used. The swirling flow going downward is recovered by pressure by the enlarged air passage 13b and is turned upward. Thereby, while being able to cool well the chamber (refrigeration temperature zone room 60) ahead of an internal fan, energy-saving property can be improved.

  In addition, the inner surface of the fan cover 70 that forms the cold air collecting duct 13 is provided with a recess 70 a formed with a smooth curved surface in the vicinity of the intersection with the line extending the rotation axis of the blower 9. As described above, the blowout flow of the blower 9 is strong in the circumferential direction, but the axial component remains. Since the recess 70a can smoothly direct the axial component in the circumferential direction, loss during turning is reduced. Therefore, energy saving property becomes high.

  In addition, a damper (freezer compartment damper 50) that controls opening and closing of air blown to a chamber (freezing temperature zone chamber 60) provided in front of the blower 9 is provided with an enlarged air passage 13 b of the cold air collecting duct 13. At the exit. In this way, the air flow can be efficiently collected by providing the enlarged air passage 13b. Thereby, the ventilation control means (freezer compartment damper 50) to the room provided with the several blower outlet provided in front of the air blower 9 can be reduced in size, and space saving can be achieved.

  In addition, although the refrigerator of this embodiment uses the propeller fan as the air blower 9, even when it is a case where the shape of a wing | blade is a centrifugal wing | blade (when a centrifugal fan is employ | adopted), a fan blowing flow is used. Since a flow (swirl flow) directed in the circumferential direction occurs, the same effect can be obtained.

  Moreover, in the refrigerator 1 of this embodiment, in the air path from the air blower 9 to the food storage room (freezing temperature zone room 60) provided with the several blower outlet provided in front of the air blower 9, the cold air | gas concentration duct 13 is provided. The cold air collecting duct 13 includes a cold air collecting duct outlet opening 13c communicating with the refrigeration temperature zone chamber 60 located in front of the blower 9, and the cold air collecting duct outlet opening 13c sends air to the refrigeration temperature zone chamber 60. In order to control, a damper (freezer compartment damper 50) is provided, and air is sent to the freezing temperature zone chamber 60 only through the opening of the freezer compartment damper 50. By forming the cold air collecting duct 13 in this way, it is possible to reliably guide the air blown to the room having a plurality of outlets provided in front of the blower 9 to the cold air collecting duct outlet opening 13c. A damper that is large enough to be installed in the outlet opening 13c can control the total amount of cold air that flows toward the freezing temperature zone chamber 60. Therefore, since it is not necessary to install a large damper 90 that closes the entire fan discharge space in the cabinet, the refrigerator is efficient in space and suppresses an increase in cost.

  In the refrigerator 1 of the present embodiment, the number of the outlet openings 13 a of the cold air collecting duct 13 is set to be smaller than the plurality of outlets 3 c to 5 c of the refrigeration temperature zone chamber 60 positioned in front of the blower 9 in order to provide the freezer damper 50. Yes. Thereby, space efficiency is good and it becomes a low-cost refrigerator.

  In the refrigerator 1 of the present embodiment, the peripheral length 13d of the outlet opening 13c of the cold air collecting duct 13 is provided to the freezing room damper 50 so as to be provided with the freezing room dampers 50 of the plurality of outlets 3c to 5c of the freezing temperature zone 60 positioned in front of the blower 9. It is shorter than the total circumference. Further, the peripheral length 102 a of the opening 102 of the freezer compartment damper 50 is made shorter than the total peripheral length of the plurality of outlets 3 c to 5 c of the freezing temperature zone chamber 60 located in front of the blower 9. These make the refrigerator highly reliable. The reason will be explained below.

  In general, the purpose of installing a damper is to shut off cold air when closed. Therefore, even if it is an air path provided with a damper, unless cool air is reliably interrupted | blocked, it will happen that desired performance will not come out, and reliability falls. On the other hand, since a minute gap is generally generated at the contact portion between the structure and the structure, for example, the open / close plate 104 (more precisely, the open / close plate 104 is provided even when the freezer damper 50 is closed). A small amount of cold air leaks from a minute gap formed between the buffer member 104 a) and the frame 103. Further, as shown in FIG. 9, the freezer compartment damper 50 is installed at the outlet opening 13c portion of the cold air collecting duct 13. However, a minute gap is generated between the outlet opening 13c and the freezer compartment damper 50, and a small amount of Cold air leaks out. In order to reduce the problem of cold air leakage and to make a highly reliable refrigerator, it is effective to shorten the length of the seal portion from which cold air leaks. For example, when it is considered that a damper is installed at each of the outlets 3c to 5c, at first glance, it seems that the air flow to the freezing temperature zone 60 can be surely blocked, but the seal part of the damper itself, And the lengths of the sealing portions between the blowout ports 3c to 5c forming members (each approximately equal to the circumferential length of the blowout port) become long, and the cold air easily leaks out. On the other hand, in the refrigerator 1 of the present embodiment, the circumferential length 13d of the outlet opening 13c of the cold air collecting duct 13 is set to 463 mm, and the total circumference of the plurality of outlets 3c to 5c of the refrigeration temperature zone chamber 60 located in front of the blower 9 is used. The length is sufficiently shorter than 1200 mm. Further, the peripheral length 102a of the opening 102 of the freezer compartment damper 50 is set to 430 mm, which is sufficiently shorter than the total peripheral length 1200 mm of the plurality of outlets 3c to 5c of the freezing temperature zone chamber 60. Thereby, since the influence of the cold air leak at the time of making the freezer compartment damper 50 into a closed state can be reduced, it becomes a highly reliable refrigerator.

In the refrigerator 1 of this embodiment, the area of the outlet opening 13c of the cold air collecting duct 13 is made larger than the opening area of the freezer damper so as to include the freezer damper 50. When the opening area of the freezer damper 50 and the area of the outlet opening 13c of the cold air collecting duct 13 coincide with each other, the mounting position of the freezer damper 50 may slightly shift due to the influence of the skill of the assembly operator. In this case, the cross section of the air path through which the cold air passing through the freezer compartment damper 50 is reduced may cause a problem that the ventilation resistance is increased. In the refrigerator 1 of the present embodiment, than the opening area 6300Mm ² of the freezing chamber damper is the area of the outlet opening 13c of the cool air aggregate duct 13 to prepare for the freezer compartment damper 50 to increase the 8105.5mm ^2. Therefore, it becomes a highly reliable refrigerator that is unlikely to have a problem that the ventilation resistance changes due to the influence of the skill of the assembly operator.

  In the refrigerator 1 of this embodiment, a single damper (freezer compartment damper 50) is disposed in the outlet opening 13 c of the cold air collecting duct 13. In general, in a refrigerator such as this embodiment, damper opening / closing control is performed by a preinstalled program, but the program is accompanied by bugs (it is extremely difficult to create a program without bugs). In consideration of this, when a plurality of freezer compartment dampers 50 are provided to control the blowing of air to the freezing temperature zone chamber 60, the control program becomes more complicated, and the probability of an unintended operation due to a bug increases. Therefore, in the refrigerator 1 of the present embodiment, the single freezer damper 50 is not only space efficient and low cost, but also a highly reliable refrigerator that is unlikely to malfunction due to bugs. Yes.

  The refrigerator 1 of the present embodiment includes a blower 9 above the cooler 7, and includes an outlet opening 13 c of the cold air collecting duct 13 above the blower 9. Thereby, it becomes a refrigerator excellent in energy saving. The reason will be explained below.

  In general, when the flow flowing in the flow path is turned, the ventilation resistance increases, and the degree of the resistance increases as the flow rate increases. The refrigerator 1 of the present embodiment performs the freezer operation. During the operation of the freezer, all the cold air that has been pressurized by the blower 9 after passing through the cooler 7 is opened at the outlet of the cold air aggregation duct 13 by the cold air aggregation duct 13. It flows without diverting toward 13c (toward freezer damper 50). Accordingly, since a large amount of flow goes to the freezer compartment damper 50, the airflow resistance increases when the cool air that has passed through the cooler 7 and is turned to be directed to the freezer compartment damper 50 is turned. As described above, the refrigerator 1 of the present embodiment includes the blower 9 above the cooler 7 and the outlet opening 13c of the cold air collecting duct 13 in which the freezer compartment damper 50 is installed above the blower 9. The airflow resistance is not increased by suppressing the turning of the cold air, which has been pressurized by the blower 9 after passing through the cooler 7, toward the freezer compartment damper 50. Thereby, since the fan power for obtaining the predetermined air volume can be suppressed, the refrigerator has high energy saving performance.

  In the refrigerator 1 of the present embodiment, as shown in FIG. 9, the blower 9 is disposed so as to be inclined toward the cooler storage chamber 8 (back side) by an angle α1 from the vertical plane. As a result, since the flow through the cooler 7 can be smoothly directed to the outlet opening 13c (freezer compartment damper 50) of the cold air collecting duct 13, the fan power when sending the necessary air volume can be suppressed, and the energy saving performance is improved. improves.

  The refrigerator 1 of this embodiment is located in front of the air blower 9 above the cooler 7, the outlet opening 13 c of the cold air collecting duct 13 above the air blower 9, and above the cold air collecting duct outlet opening 13 c. An air outlet (upper freezer compartment outlet 4c) is provided to blow out the main cooling air in the food storage room (freezing temperature zone 60). Thereby, it is a refrigerator with high energy-saving property. The reason will be explained below.

  In general, the cold air that has been heat-exchanged by the cooler 7 and has a low temperature relative to the ambient temperature forms a downward flow from the upper side to the lower side after being blown into the food storage chamber, so that more cold air is supplied to the upper side of the chamber. By doing so, the room can be cooled well. Therefore, the upper stage freezer compartment outlet 4c requires a large amount of discharged air. Therefore, in the refrigerator 1 of the present embodiment, the upper stage freezer compartment outlet 4c is the largest among the outlets of the freezing temperature zone chamber 60. Although the opening area is used, in order to obtain a large amount of discharge air, not only the size of the opening area but also the ventilation resistance in the route to the outlet is a problem. In the refrigerator 1 of the present embodiment, as described above, the blower 9 is above the cooler 7, the outlet opening 13 c (the freezer damper 50) of the cold air collecting duct 13 is above the fan 9, and the outlet opening of the cold air collecting duct 13. Since the upper freezer compartment outlet 4c is provided above 13c (freezer compartment damper 50), the cool air smoothly flows toward the upper freezer compartment outlet 4c that requires a large amount of discharge airflow. Thereby, since the fan power at the time of sending required air volume can be suppressed, energy-saving property improves.

  As shown in FIG. 9, the refrigerator 1 of the present embodiment is configured such that the opening 102 of the freezer damper 50 is inclined from the vertical plane toward the internal fan side by an angle α2. As a result, the cool air smoothly flows toward the upper freezer compartment outlet 4c that requires a large amount of discharged air, and the fan power when sending the required amount of air can be suppressed, thus improving energy saving.

  The refrigerator 1 of this embodiment is provided with another food storage room (refrigeration room 2) above the food storage room (freezing temperature zone room 60) located in front of the blower 9. The refrigerator 1 of the present embodiment has a structure including a blower 9 above the cooler 7 and an outlet opening 13c of the cool air collecting duct 13 above the blower 9, and the cool air flows smoothly upward. . Therefore, if another food storage room is provided further upward, cold air can be fed smoothly, so the fan power when sending the necessary air volume to another food storage room (refrigeration room 2) can be suppressed, thus saving energy. Improves.

  In the refrigerator 1 of the present embodiment, the food storage chamber located in front of the internal fan is a freezing temperature zone 60 that is maintained in the freezing temperature zone. Thereby, it becomes a refrigerator with high energy-saving property. The reason will be explained below.

  In general, in a refrigerator that cools the inside of a refrigerator by boosting the cold air cooled by the cooler with an internal fan and circulating it in the internal compartment, the cold air cooled by the cooler is near the internal fan discharge area. Since the temperature has not risen, the temperature tends to be the lowest. Therefore, if the food storage room located in front of the blower 9 is, for example, a refrigeration room or vegetable room maintained in a refrigeration temperature zone, the food is frozen to a temperature (minus temperature) below the refrigeration temperature zone. Such a problem may occur. In order to avoid such a situation, it must be heated by a heater and maintained in a refrigerated temperature zone. Therefore, since the electric power for performing heater heating is newly required for temperature compensation, while cooling the inside of a store | warehouse | chamber, energy-saving property is low. On the other hand, as a refrigerator 1 of the present embodiment, when the food storage room located in front of the blower 9 is a room maintained in the freezing temperature zone (the freezing temperature zone room 60), it tends to be low in temperature. Since it can be used effectively, energy saving is high.

  In addition, when the food storage chamber located in front of the blower 9 is the freezing temperature zone chamber 60, even if the freezing chamber damper 50 is in a closed state, a minute amount generated between the open / close plate 104 of the freezing chamber damper 50 and the frame 103 is generated. Cold air leaks from a small gap or a minute gap formed between the outlet opening 13c of the cold air collecting duct 13 where the freezer damper 50 is installed and the freezer damper 50. When the food storage chamber located in front of the blower 9 is the refrigeration temperature zone chamber 60, this cold air leakage may cause a significant decrease in reliability and energy saving. The reason will be explained below.

  As described above, the refrigerator of the present embodiment performs the refrigerator compartment operation and the frost cooling operation with the freezer damper 50 closed. In this operation mode, since only the refrigerated temperature zone 61 is blown, cold air having a relatively high temperature circulates. Therefore, in these operation modes, if cool air having a relatively high temperature leaks into the freezing temperature zone chamber 60, the freezing temperature zone chamber 60 will be warmed, and the problem that the frozen food can be dissolved may occur. . Moreover, warming the freezing temperature zone chamber 60 increases the thermal load when cooling the freezing temperature zone chamber 60. In order to cool the freezing temperature zone chamber 60, it is necessary to set a cooler temperature as low as, for example, −25 ° C., which is lower than the freezing temperature zone temperature. Low (low coefficient of performance). Therefore, if cold air leaks and the freezing temperature zone chamber 60 is heated, the load during the freezing chamber operation is increased and energy saving performance is reduced. As described above, when there is a cold air leak to the freezing temperature zone chamber 60 in the cold room operation or the frost cooling operation performed in the closed state of the freezer damper 50, the problem of reliability that the frozen food can be dissolved, Problems such as reduced energy savings occur. Therefore, when the food storage chamber located in front of the blower 9 is the refrigeration temperature zone chamber 60, the structure for reducing the cold air leakage described above is particularly effective.

  The refrigerator 1 of the present embodiment includes a refrigerator compartment 2 that is maintained in a refrigeration temperature zone above a food storage chamber (a freezing temperature zone chamber 60) located in front of the blower 9. As described above, it is advantageous to provide another food storage chamber further upward in order to efficiently cool by using the upward flow. However, since the distance from the blower 9 is long (the wind path is long), and the low-temperature cold air may have a large density and a downward force may be applied, the air volume is the food storage chamber located in front of the blower 9. Compared to (refrigeration temperature zone chamber 60). Therefore, a room maintained in a freezing temperature zone that requires a lot of cold air (air volume) to maintain a low temperature is disposed above the food storage room (freezing temperature zone room 60) located in front of the blower 9. It is not desirable to do so. That is, it is desirable to dispose a room maintained in the refrigerated temperature zone above the food storage chamber (freezing temperature zone chamber 60) located in front of the blower 9.

  The refrigerator 1 of the present embodiment includes a refrigerator compartment 2 above a food storage room (freezing temperature zone room 60) located in front of the blower 9, and a vegetable compartment 6 below. This makes it easier to keep the refrigeration room and vegetable room at the proper temperature. The reason will be explained below.

  In general, the refrigerated room and the vegetable room are both kept in the refrigerated temperature range, but the vegetable room may contain foods that are sensitive to low temperatures (foods that cause low temperature damage). On the other hand, it is desirable to keep the temperature slightly higher (for example, 3 ° C. in the refrigerator compartment, 5 ° C. in the vegetable compartment, etc.). Therefore, when the vegetable room is a refrigerator that is too cold, it is necessary to provide a heater in the vegetable room and maintain it at a predetermined temperature by heating the heater. In the case of such a refrigerator, the energy saving performance is deteriorated by the heater power. In order to avoid such a situation, it is necessary to cool the vegetable room with a cooling capacity lower than that of the refrigerator room. That is, it is effective to send cold air having a higher temperature than the cold air sent to the refrigerator compartment 2 to the vegetable compartment 6, or to send a small amount of cold air than the refrigerator compartment 2 at the same temperature. In the refrigerator 1 of this embodiment, the refrigerator compartment 2 is provided above the freezing temperature zone chamber 60, and the vegetable compartment 6 is provided below the freezing temperature zone chamber 60. Thus, as in the refrigerator 1 of this embodiment. In the case where the refrigerator compartment 2 and the vegetable compartment 6 are arranged in series, cold air whose temperature has been increased by cooling the refrigerator compartment 2 can be sent to the vegetable compartment 6, so that even if the air volume is the same, it is sent to the refrigerator compartment 2 Cold air having a temperature higher than that of the cold air can be sent to the vegetable compartment 6, and the refrigerator compartment 2 and the vegetable compartment 6 can be easily maintained at an appropriate temperature.

Moreover, as another embodiment, the case where the refrigerator compartment 2 and the vegetable compartment 6 are arranged in parallel is also considered.
In this case, as described above, the cold air from the blower 9 that is easily directed to the upper refrigerating chamber 2 is forced to be turned downward to be directed to the vegetable compartment 6, so no particular consideration is given. In both cases, the draft resistance of the air passage toward the vegetable compartment 6 increases. Therefore, in this case, the cold air having the same temperature reaches the refrigerator compartment 2 and the vegetable compartment 6, but the air volume to the vegetable compartment 6 can be easily kept low, and the refrigerator compartment 2 and the vegetable compartment 6 are kept at an appropriate temperature. It becomes easy.

  For the above reasons, it is easy to keep the refrigerator compartment 2 and the vegetable compartment 6 at an appropriate temperature by arranging the refrigerator compartment 2 above the freezing temperature compartment 60 and the vegetable compartment 6 below the freezing compartment 60.

  In the refrigerator 1 of the present embodiment, the main surface forming the freezer damper 50 (the surface forming the frame 103) is disposed so as to be inclined by β2 from the horizontal plane. Even when water is dripped into the freezer compartment damper 50 during the defrosting operation or the like, this causes water to flow down from the freezer compartment damper 50, so that the water stays in the freezer compartment damper 50 and then freezes. Such a faulty accident can be prevented and the refrigerator becomes highly reliable. In addition, β2 is set to 6 degrees, but if β2 is set to 6 degrees or more, water can easily flow down, and the probability of a defective accident caused by freezing of accumulated water can be sufficiently lowered, and reliability is improved. It becomes a high refrigerator.

  In the refrigerator 1 of the present embodiment, the freezer damper 50 includes an opening 102, a rotating shaft 101 near one side of the opening 102, and an opening / closing plate 104 that is linked to the rotating operation of the rotating shaft 101. The opening / closing control of the opening 102 is performed by the angular position of the opening / closing plate 104 around the rotation shaft 101. By utilizing the rotational movement of the opening / closing plate 104, the opening / closing plate 104 can be pressed against the surface 102 a of the opening 102 facing the opening / closing plate 104 by a simple mechanism, and the closed state of the opening 102 can be reliably formed. Thereby, it becomes a low-cost and highly reliable damper.

  In the refrigerator 1 of this embodiment, the freezer compartment damper 50 is arrange | positioned so that the rotating shaft 101 of the freezer compartment damper 50 may become an upper side. As a result, a highly reliable refrigerator in which a malfunction such as the freezer compartment damper 50 becoming unrotatable due to water remaining in the vicinity of the rotating shaft 101 and freezing is unlikely to occur.

  In the refrigerator 1 of the present embodiment, the open / close plate 104 of the freezer damper 50 is disposed so as to open to the cold air collecting duct 13 side. When the closed state of the freezer damper 50 is considered, for example, when it is arranged to open to the freezing temperature zone 60 side, the cold air collecting duct 13 side, i.e., the discharge region side of the blower 9 is pressurized. Since the pressure is low on the freezing temperature zone chamber 60 side, a force is applied in the direction in which the opening / closing plate 104 opens. On the other hand, if the opening / closing plate 104 is opened to the cold air collecting duct 13 side, a force is applied in the direction of increasing the sealing degree. Therefore, in the refrigerator 1 of the present embodiment, the open / close plate 104 of the freezer compartment damper 50 is disposed so as to open to the cold air collecting duct 13 side, so that leakage from the seal portion 102a of the freezer compartment damper 50 is less likely to occur. It has become a highly reliable refrigerator.

  In the refrigerator 1 of the present embodiment, the open angle θ of the freezer damper 50 is set to 60 degrees during the refrigeration operation. This is because, as shown in FIG. 9, the degree of blockage of the inflow portion of the refrigerator compartment duct 11 is controlled by the opening angle of the freezer damper 50 so that the amount of cool air blown into the refrigerator compartment 61 is made appropriate. is there. For example, if the opening angle θ of the freezer damper 50 is increased (for example, 90 degrees) during the refrigerating operation, the degree of blockage of the inflow portion of the refrigerating room duct 11 increases, so that the ventilation resistance of the refrigerating room duct 11 increases. The air volume to the refrigerated temperature zone 61 is reduced. Therefore, cooling of the refrigeration temperature zone 61 is suppressed. On the other hand, if the open angle θ of the freezer damper 50 is made smaller (for example, 45 degrees), the ventilation resistance of the refrigerator compartment duct 11 becomes smaller, and the refrigerator compartment 61 is further cooled. In addition, when the opening angle of the freezer compartment damper 50 is made smaller than 60 degrees, the ventilation resistance of the flow toward the refrigeration temperature zone chamber 61 is decreased and the ventilation resistance of the flow toward the freezer temperature zone chamber 60 is increased. Therefore, it is possible to perform cooling with emphasis on the refrigeration temperature zone chamber 61 while cooling the freezing temperature zone chamber 60. That is, in the refrigerator 1 of the present embodiment, the air volume of the freezing temperature zone chamber 60 and the refrigeration temperature zone chamber 61 can be adjusted by the open angle θ of the freezing chamber damper 50, and each chamber is easily set to an appropriate temperature.

The refrigerator 1 of this embodiment is provided with a heater that is in thermal contact with the freezer damper 50.
Thereby, even if the freezer compartment damper 50 freezes and cannot be rotated, it can be melted by the heater, so that the refrigerator is highly reliable.

DESCRIPTION OF SYMBOLS 1 Refrigerator 2 Refrigeration room 3 Ice making room 4 Upper freezing room 5 Lower freezing room 6 Vegetable room 7 Cooler 8 Cooler storage room 9 Blower 10 Insulation box 11 Refrigeration room duct 12 Freezing room duct 13 Cold air collecting duct 16 Refrigeration room-Vegetable Room communication duct 17 Freezer compartment return port 18 Vegetable room return duct 18a Vegetable room return outlet 19 Machine room 20 Refrigeration room damper 21 Evaporation dish 22 Defrost heater 23 樋 24 Compressor 26 Warm air storage space 31 Control board 33 Refrigeration room temperature sensor 33a Vegetable room temperature sensor 34 Freezer room temperature sensor 35 Cooler temperature sensor 50 Freezer room damper 53 Upper cover 54 Partition plate 60 Freezing temperature zone room 61 Refrigeration temperature zone room 70 Fan cover 71 Fan hold 75 Communication hole 100 Driving means 101 Rotating shaft 102 Opening 103 Frame 104 Opening and closing plate

Claims (5)

A freezing temperature zone and a refrigeration temperature zone chamber that are compartmentally formed in the refrigerator main body and each store food,
A cooler in which cold air that cools the freezing temperature zone chamber and the refrigeration temperature zone chamber is heat-exchanged;
A cooler storage chamber at the back of the freezing temperature zone in which the cooler is provided;
An in-compartment fan arranged to be inclined from the vertical surface to the back side above the cooler for blowing cold air heat-exchanged by the cooler to the freezing temperature zone chamber and the refrigeration temperature zone chamber;
A fan cover provided to cover the front of the internal fan and having an opening communicating with the upper part of the freezing temperature zone chamber ;
Blower control means for controlling the ventilation provided above the internal fan and at the opening of the fan cover;
A duct between the cooler storage chamber and the refrigeration temperature zone chamber ,
The fan cover has an air passage that gradually expands from upstream to downstream in the direction of rotation of the internal fan, and the opening is provided on the downstream side of the air passage so as to incline toward the internal fan .
A refrigerator characterized in that an air outlet for blowing cold air to the freezing temperature zone located in front of the internal fan is provided above the opening .   2. The refrigerator according to claim 1, wherein the air passage has an expansion angle for enlarging the air passage in a range of 5 degrees to 20 degrees.   2. The refrigerator according to claim 1, wherein the air passage has an angle greater than 180 degrees or greater than 180 degrees from upstream to downstream.   2. The refrigerator according to claim 1, wherein the fan cover has a recess at a position facing the internal fan.   The refrigerator according to any one of claims 1 to 3, wherein the opening is horizontally long, and a longitudinal direction of the opening is located downstream of the air passage and above the internal fan.

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