JP2011058684A - Damper device and refrigerator equipped with the damper device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a refrigerator with high energy-saving performance, carrying out reliable temperature control by securely closing the opening of an electric damper. <P>SOLUTION: The refrigerator comprises a freezing-temperature zone chamber provided for a refrigerator body, a cooler chamber provided behind the freezing-temperature zone chamber and installed with a cooler, a blower for blowing cold air from the cooler chamber to the freezing-temperature zone chamber, a partition plate which partitions between the cooler chamber and the freezing-temperature zone chamber and has an outlet port for blowing the cold air blown by the blower to the freezing-temperature zone chamber, and a freezing chamber damper controlling an air supply amount to the freezing-temperature zone chamber. The freezing chamber damper comprises a frame having an opening which communicates the cooler chamber with the outlet port, an opening/closing body opening/closing the opening, and a driving means for driving the opening/closing body. An area of the opening of the freezing chamber damper is larger than an area of the outlet port. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a damper device and a refrigerator including the damper device.

  In the cold air forced circulation type refrigerator that cools the refrigerator compartment and the freezer compartment with a common cooler, the temperature of the refrigerator compartment is controlled to about 3 to 5 [° C.], and the temperature of the freezer compartment is controlled to about −18 [° C.], respectively. The band is different. Therefore, when distributing cold air from the cooling chamber to the refrigerator compartment and the freezer compartment via the cold air duct, it is necessary to switch the cold air flow rate.

  As a conventional technique related to an electric damper, which is a means for switching a cold air flow rate, techniques of Patent Document 1 and Patent Document 2 are known.

  Patent Document 1 includes a cold room damper provided in a cold room cooling duct and a freezer damper provided in the freezer cooling duct, and only the cold room damper is opened to cool only the cold room. The structure to be described is described.

  Patent Document 2 has a configuration in which air paths for supplying cold air from the cooling chamber to the freezing room and the refrigerating room are provided in parallel, a damper is provided inside the air path from the cooling room to the freezing room, and the air flow is controlled to an appropriate level. Are listed.

JP 2005-180719 A JP 2002-31466 A

  In the configurations described in Patent Document 1 and Patent Document 2, the cooling efficiency is improved and the energy is saved by cooling only the refrigerator room on the high temperature side separately from the freezer room on the low temperature side.

  Here, the damper device is provided in the cold air duct. From this, in order to reduce the blowing resistance, it is conceivable to enlarge the opening area when the damper device is opened. In particular, in recent refrigerators, an increase in the internal volume is required, and it is desirable that the volume in the storage space is not reduced while the opening area is enlarged.

  On the other hand, when the volume occupied by the cold air duct is reduced, the air blowing resistance of the cold air is increased. Then, the power consumption of the blower (blower fan) for blowing the necessary cool air increases, and there is a risk that the energy saving performance is lowered.

  Therefore, in order to improve the energy saving performance without reducing the volume in the storage space, a configuration in which the cold air duct is flattened to reduce the dimension in the depth direction of the refrigerator is preferable. As a shape of the damper device for that purpose, it is desirable to use a horizontally long and narrow rectangular shape with a small depth dimension and a wide width.

  As an example, when the refrigerator compartment damper is closed and the freezer compartment damper is opened, if there is a gap in the refrigerator compartment damper, cold air flows into the refrigerator compartment from the gap. Then, originally, cold air for cooling only the freezer compartment is required, but an additional amount of cooling heat for the cold air leaking into the refrigerator compartment is required. Therefore, from the viewpoint of energy saving, it is desirable to increase the sealing degree when closing the electric damper.

  That is, it is desirable to improve the hermeticity when closed while increasing the opening area of the damper device. However, when the opening area of the damper device is increased, each component is increased in size, so that there is a problem that the rigidity of the component is reduced and elastic deformation is easily caused, and a gap is easily generated at the time of closing so that it is difficult to seal.

  Patent Document 1 and Patent Document 2 do not describe the magnitude relationship between the opening area of the freezer damper and the air outlet to the freezer. Moreover, it does not describe about the closing property of the baffle which is an opening / closing body and the appropriate aspect ratio of the baffle shape. In other words, there is no mention of a desirable magnitude relationship between the opening of the baffle and the blowout nozzle or fan size of the freezer, or the appropriate ratio of the vertical and horizontal dimensions of the baffle.

  Accordingly, in view of the above-described problems of the prior art, an object of the present invention is to obtain a damper device that can perform highly reliable temperature control by reliably closing an opening of an electric damper. Moreover, it aims at obtaining the refrigerator with high energy saving performance by performing reliable temperature control by closing the opening of an electric damper reliably.

  In order to achieve the above object, a refrigerator according to the present invention includes a refrigeration temperature zone chamber provided in a refrigerator body, a cooler chamber provided behind the refrigeration temperature zone chamber and provided with a cooler, and the cooler. A blower that blows cool air from a room to the freezing temperature zone chamber, a partition plate that partitions the cooler chamber and the freezing temperature zone chamber, and has a blowout port that blows off the cold air blown by the blower to the freezing temperature zone chamber; A refrigerator including a freezer damper that controls the amount of air blown to the freezing temperature zone chamber, wherein the freezer damper includes a frame having an opening communicating the cooler chamber and the outlet, and the opening And an opening / closing body that opens and closes the opening / closing body, and a drive unit that drives the opening / closing body, wherein the area of the opening of the freezer compartment damper is larger than the area of the outlet.

  Further, a plurality of the outlets are provided, and the area of the opening of the freezer compartment damper is larger than the total area of the plurality of outlets.

  Further, the opening of the freezer damper is rectangular and has an aspect ratio of 4 to 11.

The area of the opening is 6000 to 6500 mm ² .

Further, the damper device of the present invention is a damper device comprising a frame having a rectangular opening, an opening / closing body for opening / closing the opening, and a driving means for driving the opening / closing body, wherein the aspect ratio of the opening is 4 to 11 and the area of the opening is 6000 to 6500 mm ² .

  ADVANTAGE OF THE INVENTION According to this invention, the damper apparatus which can perform reliable temperature control can be obtained by closing the opening of an electric damper reliably. Moreover, the refrigerator with high energy saving performance can be obtained by performing reliable temperature control by closing the opening of the electric damper with certainty.

It is a front external view of the refrigerator which concerns on embodiment of this invention. It is XX sectional drawing of FIG. 1 showing the structure in the store | warehouse | chamber of a refrigerator. It is a front view showing the structure in the store | warehouse | chamber of a refrigerator. FIG. 3 is an enlarged explanatory view of a main part of FIG. 2. FIG. 3 is an enlarged explanatory view of a main part of FIG. 2. It is an expansion perspective view which shows F range in FIG. FIG. 7 is a perspective view taken along the line E-E in FIG. 6. It is a perspective view which shows the whole structure of a damper. It is a perspective view which shows the whole structure of a damper. It is YY sectional drawing of FIG. 8 which shows the structure of a damper. It is the schematic which looked at the drive means of the damper in the arrow Z direction of FIG. It is the schematic which looked at the drive means of the damper in the arrow Z direction of FIG. It is the schematic which looked at the drive means of the damper in the arrow Z direction of FIG. It is the schematic which looked at the drive means of the damper in the arrow Z direction of FIG. It is a schematic perspective view explaining the state where the uniform press-contact force was added to the circumference | surroundings of the opening / closing body. It is a graph which shows the relationship between the short side ratio of an opening-closing body, and a moment ratio.

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

  FIG. 1 is a front outline view of the refrigerator of the present embodiment. FIG. 2 is an XX longitudinal cross-sectional view in FIG. 1 illustrating a configuration inside the refrigerator. FIG. 3 is a front view illustrating a configuration inside the refrigerator, and is a diagram illustrating the arrangement of the cold air duct and the outlet. 4 and 5 are enlarged views for explaining the main part of FIG.

  As shown in FIG. 1, the refrigerator 1 of this embodiment is comprised from the upper part from the refrigerator compartment 2, the ice-making room 3, the upper stage freezer room 4, the lower stage freezer room 5, and the vegetable compartment 6. FIG.

  The refrigerating room 2 is provided with front-opening refrigerating room doors 2a and 2b divided into left and right, and 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.

  In the refrigerator 1, the door sensor (not shown) that detects the open / closed state of the doors 2a, 2b, 3a, 4a, 5a, and 6a and the state determined as the door open state are continued for a predetermined time, for example, 1 minute or more. In this case, an alarm (not shown) for notifying the user, a temperature setting unit (not shown) for setting the temperature of the refrigerator compartment 2 and the temperature of the upper freezer compartment 4 and the lower freezer compartment 5 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 has a plurality of vacuum heat insulating materials 25 mounted thereon.

  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 integrated with doors 4a, 5a, 6a provided in front of the respective chambers, and storage containers 4b, 5b, 6b are respectively provided. Is provided. The storage containers 4b, 5b, and 6b can be pulled out by placing a hand on a handle portion (not shown) of the doors 4a, 5a, and 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.

  As shown in FIG. 2 (refer to FIGS. 3 to 7 as appropriate), the cooler 7 is provided in a cooler storage chamber 8 provided substantially at the back of the lower freezing chamber 5. An internal fan 9 (blower) is provided above the cooler 7. The air cooled by the heat exchange with the cooler 7 (hereinafter, the low-temperature air cooled by the cooler 7 is referred to as “cold air”) is supplied by the internal fan 9 to the refrigerator compartment air duct 11 and the vegetable compartment air duct 14. , Upper freezer compartment air duct 12, cold air duct 13 which is a lower freezer compartment air duct, and ice making room air duct (not shown), refrigerator room 2, vegetable room 6, upper freezer room 4, lower freezer room 5, ice making room 3 Sent to each room. Air blowing to each room is controlled by opening and closing the refrigerator compartment cooling damper 20 and the freezer compartment cooling damper 50.

  Incidentally, the air ducts to the refrigerator compartment 2, the ice making room 3, the upper freezer room 4, the lower freezer room 5, and the vegetable room 6 are provided on the back side of each room of the refrigerator 1 as indicated by broken lines in FIG. Yes. Specifically, when the refrigerator compartment cooling damper 20 is in the open state and the freezer compartment cooling damper 50 is in the closed state, the cold air is sent to the refrigerator compartment 2 from the outlets 2c provided in multiple stages through the refrigerator compartment air duct 11. It passes through the vegetable room air duct 14 branched from the refrigerator compartment air duct 11, and is sent to the vegetable room 6 from the blower outlet 6c.

  Note that the cold air that has cooled the refrigerator compartment 2 is, for example, in the lower right portion as viewed from the front of the cooler storage chamber 8 through the refrigerator outlet return duct 16 from the return port 2d provided on the lower surface of the refrigerator compartment 2. Return. As another configuration, the air is sent from the return port 2d through the vegetable room air duct 14 to the vegetable room 6 from the blowout port 6c, and then returns from the return port 6d to the cooler storage chamber 8.

  In FIG. 3, when the freezer cooling damper 50 is in the open state, the cold air heat-exchanged by the cooler 7 is blown out by the internal fan 9 through the ice making fan blow duct and the upper freezer blower duct 12 (not shown). , 4c are sent to the ice making chamber 3 and the upper freezing chamber 4, respectively, and are sent from the outlet 5c to the lower freezing chamber 5 through the cold air duct 13. Also from this point, the freezer compartment cooling damper 50 is attached above a blower cover 56 part described later, and facilitates air blowing to the ice making chamber 3.

  In addition, the cold air that has cooled the upper freezing chamber 4, the lower freezing chamber 5, and the ice making chamber 3 returns to the cooler storage chamber 8 through the freezing chamber return port 17 provided below the rear portion of the lower freezing chamber 5.

  FIG. 4 shows a state where both the freezer cooling damper 50 and the refrigerating room cooling damper 20 are opened, and FIG. 5 shows a state where the freezing room cooling damper 50 is closed and only the refrigerating room cooling damper 20 is opened. 6 is a perspective view showing a configuration from the freezer return port 17 to the refrigerator compartment duct 15, and FIG. 7 is a cross-sectional perspective view in the EE direction in FIG.

  4 to 7, the partition plate 54 forms the outlets 3c, 4c, and 5c. This partition 54 partitions the freezer compartment 4, the lower freezer compartment 5, and the cooler storage compartment 8.

  Reference numeral 55 denotes a fan motor fixing portion to which the internal fan 9 is attached. The fan motor fixing part 55 partitions the cooler storage chamber 8 and the partition plate 54. The internal fan 9 is attached to the fan motor fixing portion 55.

  A blower cover 56 covers the front surface of the internal fan 9. A cool air duct 13 is formed between the blower cover 56 and the partition plate 54. In addition, a blowout port 56 a of the freezer compartment cooling damper 50 is formed in the upper part of the blower cover 56.

  The blower cover 56 includes a rectifying unit 56b that rectifies turbulent flow caused by the cool air blown from the blower 9 covering the front surface and prevents noise and the like from being generated.

  The blower cover 56 forms an upper freezer compartment air duct 12 and a cold air duct 13 so as to guide the cold air blown from the internal fan 9 to the air outlets 3c, 4c, 5c and the like between the blower cover 56 and the partition plate 54. ing.

  Further, the blower cover 56 also plays a role of blowing the cool air blown out by the internal blower 9 to the refrigerator compartment cooling damper 20 side.

  That is, the cold air that does not enter the freezer compartment cooling damper 50 provided in the blower cover 56 part goes to the refrigerator compartment cooling damper 20 side via the refrigerator compartment duct 15 as shown in FIG.

  Then, as shown in FIG. 4, when sending cold air to both the freezing temperature zone chamber including the ice making chamber 3 and the refrigeration temperature zone chamber including the vegetable chamber 6, a large amount of cold air is sent to the freezing chamber cooling damper 50 side. A small amount of cool air is sent to the refrigerator compartment duct 15 side.

  The refrigerating room cooling damper 20 is attached to the rear part of the refrigerating room 2 as shown in FIGS. Further, as shown in FIG. 3, the cold room cooling damper 20 is disposed so as to be inclined with respect to the horizontal when viewed from the front, and a driving means 60 such as a motor is provided at a higher position.

  Next, a defrost heater 22 is installed below the cooler 7. An upper cover 53 is provided above the defrost heater 22 in order to prevent defrost water from dripping onto the defrost heater 22.

  When the frost adhering to the cooler 7 and the wall of the cooler storage chamber 8 in the vicinity thereof is melted by defrosting, the defrost water flows into the eaves 23 provided at the lower portion of the cooler storage chamber 8. After that, it reaches the evaporating dish 21 disposed in the machine room 19 through the drain pipe 27 and is evaporated by the heat of the condenser described later.

  In addition, a cooler temperature sensor 35 attached to the cooler is located in the upper right portion when viewed from the front of the cooler 7, a refrigerator temperature sensor 33 is provided in the refrigerator compartment 2, and a freezer compartment temperature sensor 34 is provided in the lower freezer compartment 5. Is provided. The temperature of the cooler 7 (hereinafter referred to as the cooler temperature), the temperature of the refrigerator compartment 2 (hereinafter referred to as the refrigerator compartment temperature), and the temperature of the lower freezer compartment 5 (hereinafter referred to as the freezer compartment temperature) are detected. It can be done.

  Furthermore, the refrigerator 1 includes an outside air temperature sensor and an outside air humidity sensor (not shown) that detect a temperature and humidity environment (outside air temperature, outside air humidity) outside the refrigerator. Note that the vegetable room temperature sensor 33a may also be arranged in the vegetable room 6.

  A machine room 19 is provided on the lower back side of the heat insulating box 10. The machine room 19 contains a compressor 24 and a condenser (not shown). Is removed. 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 disposed on the top surface side of the refrigerator 1. The control board 31 opens and closes the doors of the outside temperature sensor, the outside humidity sensor, the cooler temperature sensor 35, the refrigerator temperature sensor 33, the freezer temperature sensor 34, and the doors 2a, 2b, 3a, 4a, 5a, and 6a. It is connected to a door sensor for detecting the state, a temperature setter (not shown) provided on the inner wall of the refrigerator compartment 2, a temperature setter (not shown) provided on the inner wall of the lower freezer compartment 5, and the like. And by control of ON / OFF of the compressor 24 by the program previously mounted in the ROM, control of respective driving motors to be described later for individually driving the cold room cooling damper 20 and the freezing room cooling damper 50, the interior Control such as ON / OFF control and rotation speed control of the blower 9, ON / OFF control and rotation speed control of the outside fan, and control of ON / OFF of an alarm for notifying the door open state described above are performed.

  Next, the refrigerator compartment cooling damper 20 is closed and the freezer compartment cooling damper 50 is opened, and only the freezing temperature zone (ice-making compartment 3, upper freezer compartment 4 and lower freezer compartment 5) is cooled. In the state, the air in the direction of arrow 80 toward the refrigerator compartment 2 shown by the broken line in FIG. 4 does not flow. That is, all of the cool air blown from the internal fan 9 is sent to the ice making room, the upper freezer room 4 and the lower freezer room 5 through the freezer cooling damper 50.

  The cold air blown to the ice making chamber 3 through the ice making chamber blow duct and the cold air blown to the upper freezer compartment 4 through the upper freezer blower duct 12 (see FIG. 2) descends to the lower freezer compartment 5 and then falls to the lower stage. Along with the cold air blown into the freezer compartment 5 through the cold air duct 13 (see FIG. 2), the flow of the freezer return air indicated by an arrow C in FIG. That is, it flows into the cooler storage chamber 8 from the lower front of the cooler storage chamber 8 through the freezer return port 17 disposed in the lower part of the back wall of the lower freezing chamber 5, and a large number of fins are formed in the cooler piping 7a. Heat exchange is performed with the cooler 7 that is installed.

  In addition, the width dimension of the freezer compartment return port 17 is a width substantially equal to the width dimension of the cooler 7.

  Next, when both the refrigerating room cooling damper 20 and the freezing room cooling damper 50 are in the open state, the air in the direction of the arrow 80 toward the refrigerating room 2 indicated by a broken line in FIG. 4 also flows. Then, a part of the cool air blown from the internal blower 9 is blown through the refrigerator compartment cooling damper 20 to the refrigerator compartment 2 (refrigeration temperature zone compartment), and the other is passed through the freezer compartment cooling damper 50 to the ice making compartment 3. , Are sent to the upper freezer compartment 4 and the lower freezer compartment 5 (freezing temperature zone). Here, when the freezer compartment cooling damper 50 is opened, an end of an opening / closing body 64 described later provided in the freezer compartment cooling damper 50 is disposed with an appropriate gap so as not to completely block the refrigerator compartment duct 15. ing.

  On the other hand, as shown in FIG. 5, when the refrigerator compartment cooling damper 20 is in the open state and the refrigerator compartment cooling damper 50 is in the closed state, only the refrigerator temperature zone (refrigerator compartment 2 and vegetable compartment 6) is being cooled. Then, the return cold air from the refrigerating room 2 is transferred to the side of the cooler storage room 8 via the vegetable room air duct 14 or the refrigerating room return duct 16 like the refrigerating room return air indicated by the arrow D in FIG. It flows into the cooler storage chamber 8 from the lower part and exchanges heat with the cooler 7.

  As shown in FIG. 4, the cold air that has cooled the vegetable compartment 6 flows into the lower portion of the cooler storage chamber 8 through the vegetable compartment return port 6 d (see FIG. 4). Less than the amount of air circulating and the amount of air circulating through the refrigerator compartment 2.

  As described above, the cooling air in the refrigerator 1 is switched by opening and closing the refrigerator compartment cooling damper 20 and the freezer compartment cooling damper 50 as appropriate.

  Next, an example of the configuration and operation of the electric damper will be described using the freezer compartment cooling damper 50 as an example with reference to FIGS. 8 to 14.

  8 and 9 are perspective views showing an example of the configuration of the freezer compartment cooling damper 50. FIG. 9 is a view seen from the direction of arrow S in FIG. 8, and FIG. 10 is a cross-sectional view in the YY direction in FIG.

  The freezer compartment cooling damper 50 includes an opening 62 on one surface, and includes, for example, a resin frame 63 and a driving means 60 having a built-in driving system such as a motor and a reduction gear at one end of the frame 63. Is output.

  The opening / closing body 64 includes a resin plate-like opening / closing plate 64a and a sealing member 64b provided on one surface of the opening / closing plate 64a. The sealing member 64 b is formed of a flexible material such as foamed urethane or foamed polyethylene, and is provided to face the opening 62 having a width W and a height h provided in the frame 63.

  One end of the opening / closing body 64 is pivotally supported by the drive shaft 61, and the other end is rotatably provided around a support shaft 65 provided on the frame 63. The opening / closing body 64 can swing around a rotation shaft connecting the drive shaft 61 and the support shaft 65, and the rotation shaft is parallel to one side in the longitudinal direction of the opening / closing body 64 and in the vicinity of the one side. Is arranged. A reinforcing column 62 a for suppressing deformation of the opening 62 is provided at a substantially central portion in the longitudinal direction of the opening 62 of the frame 63.

  8 to 10 show a state in which the opening / closing body 64 is closed. In the closed position, the opening / closing body 64 seals the opening 62 by contacting a flexible sealing member 64 b with a contact portion 66 provided along the inner periphery of the opening 62 provided in the frame 63. When the motor is rotated, the opening / closing body 64 is rotated by about 90 ° in the direction of the arrow through the drive shaft 61, so that the opening / closing body is in the open position indicated by 64 '. The opening / closing body 64 rotates between the open position and the closed position, so that cool air can pass through the opening 62 in the open position, and the cool air flow is blocked and closed in the closed position. .

  Next, an example of the configuration and operation of the driving unit 60 will be described with reference to FIGS. 11 to 14 are schematic views of the driving means 60 as viewed in the direction of arrow Z in FIG. The driving means 60 has a motor 70, and an output shaft 71 of the motor 70 is provided with a pinion gear 72, which rotates with the driving of the motor 70 and outputs torque. The idler gear 73 is a reduction gear that is rotatably supported around an idler fulcrum 74.

  The outer periphery of the idler gear 73 has a gear 73a that meshes with the pinion gear 72, and transmits torque while decelerating the torque from the pinion gear 72. A partial gear 73 b is provided on a part of the idler gear 73. The partial gear 73b is provided only in a range in which, for example, the idler gear 73 rotates 90 °. A cylindrical portion 73c having a cylindrical shape is provided at a portion of the partial gear 73b other than the gear shape. The gear 73 a and the partial gear 73 b are provided at positions shifted from each other with respect to the height direction of the idler gear 73.

  The output gear 75 is pivotally supported around the drive shaft 61 and is fitted to the opening / closing body 64. The opening / closing body 64 and the output gear 75 are connected and rotate as a unit. A partial gear 75 b is provided at a part of the output gear 75. The partial gear 75 b meshes with a partial gear 73 b provided at a part of the idler gear 73 and rotates by 90 ° in conjunction with the idler gear 73. To do.

  On both sides of the partial gear 75b of the output gear 75, an arc-shaped first stopper 75c and a second stopper 75d are provided. The first stopper 75c and the second stopper 75d are in a positional relationship in which the opening / closing body 64 is fitted to the cylindrical portion 73c of the idler gear 73 at the open position and the closed position, respectively. The opening / closing body 64 connected to the output gear 75 is rotated by rotating the output gear 75 by approximately 90 °, which is a range where the partial gear 75b is engaged.

  Next, the operation of the driving unit 60 will be described.

  FIG. 11 shows the drive unit 60 in a state similar to that shown in FIGS. A cylindrical portion 73c provided on the idler gear 73 is fitted with the second stopper 75d of the output gear 75, and holds the opening / closing body 64 in a closed state.

  12 shows a state in which the motor 70 is driven from the state of FIG. 11 and the pinion gear 72, the idler gear 73, and the output gear 75 are rotated in the directions of the arrows, respectively. The partial gear 75b and the idler gear 73 that are part of the output gear 75 are shown. Is engaged with a partial gear 73b provided at a part of the gear. The second stopper 75 d of the output gear 75 is positioned away from the cylindrical portion 73 c of the idler gear 73.

  FIG. 13 shows a position rotated further in the direction of the arrow as compared with FIG. FIG. 14 shows a state in which the meshing between the partial gear 75 b that is a part of the output gear 75 and the partial gear 73 b that is provided in a part of the idler gear 73 is completed after being rotated approximately 90 °. In this state, the first stopper 75c of the output gear 75 is in a position where it is engaged with the cylindrical portion 73c of the idler gear 73, and holds the opening / closing body 64 in an open state. When the opening / closing body 64 is closed again, the state shown in FIG. 11 is reached from the state shown in FIG. 14 via the states shown in FIGS.

  By operating as described above, the damper 50 opens and closes the opening / closing body 64.

  Here, in order to preserve the frozen food stored in the frozen temperature zone chamber for a long period of time, it is desirable to reduce the temperature unevenness inside the frozen temperature zone chamber and cool it as uniformly as possible. That is, as described with reference to FIG. 2 or FIG. 4 and the like, the outlets 3c, 4c, and 5c for blowing cool air into the refrigeration temperature zone chamber are on the back side of the refrigeration temperature zone chamber. For this reason, the temperature tends to rise in the refrigeration temperature zone until the cool air is blown to the near side. This tendency becomes more prominent as the flow rate of cold air is smaller and the flow rate is slower. Therefore, in order to reduce the temperature unevenness in the freezing temperature zone, it is effective to blow a predetermined amount or more of cool air from the outlets 3c, 4c, 5c into the freezing temperature zone and increase the flow rate of the cold air.

  In order to increase the flow rate and increase the flow velocity, it is effective to increase the size of the internal fan 9, but this is not desirable from the viewpoint of energy saving. Moreover, since there is a problem such as an increase in noise, it is desirable not to increase the size of the internal fan 9 but to reduce the loss by reducing the blowing resistance and increase the flow rate of the cold air.

  Next, a configuration for reducing the blowing resistance will be described with reference to FIGS.

  The cool air discharged with the pressure increased by the internal blower 9 flows along the blower cover 56 as indicated by an arrow 57 in FIG. The cold air after passing through the opening of the freezer compartment cooling damper 50 is discharged from the outlets 3c, 4c, 5c via the arrows 58a to 58b.

  Here, the cool air discharged from the internal blower 9 is rectified by the rectifying unit 56b, and most of the air flows as indicated by an arrow 57a. This is because the rectifying unit 56b forms an air passage that gradually spreads from upstream to downstream. However, some of the cold air diffuses as indicated by arrows 57. Therefore, the width dimension W of the freezer cooling damper 50 is made larger than the diameter D of the internal fan 9. Thereby, cold air can be smoothly introduced into the freezer compartment cooling damper 50, which is preferable.

  The pressure of the cold air once increased by the internal blower 9 gradually decreases on the downstream side due to the resistance in the air flow path of the cold air, and finally the outlets 3c, 4c, whose area is reduced to increase the flow velocity, 5c is discharged into the freezing temperature zone.

  Here, if there is a local minimum portion in the cool air blowing path from the internal blower 9 to the outlets 3c, 4c, 5c, the flow velocity is locally increased in that portion to form an orifice. Therefore, a pressure difference is generated between the upstream side and the downstream side, and the pressure on the downstream side, that is, the blowing nozzle side is reduced. Then, since the flow velocity and flow rate of the cold air at the blowout nozzle with a reduced area are reduced, temperature unevenness is likely to occur.

  That is, in order to reduce the ventilation resistance of the cold air from the internal blower 9 to the blowout ports 3c, 4c, 5c, it is preferable that there is no portion where the area is minimized in the blower path. That is, the opening area of the freezer compartment cooling damper 50 provided in the cold air duct between the internal blower 9 and the outlets 3c, 4c, 5c is larger than the area of the outlets 3c, 4c, 5c. Is preferred.

  Here, the area of the outlet is determined by the flow rate and flow rate of the cold air. Hereinafter, those appropriate values are calculated.

  First, the amount of heat leakage that leaks from the freezer to the outside is estimated. The dimensions of the refrigerator 1 having an internal capacity of 600 L are approximately a width of 750 [mm], a depth of 700 [mm], and a height of 1800 [mm]. The height occupied by the freezer compartment is approximately 700 [ mm].

When calculating the surface area of a freezer room as a cube having a vertical and horizontal height of 700 × 750 × 700 [mm], the upper and lower surfaces are in contact with the refrigerator room or vegetable room,
0.7 [m] × 0.75 [m] × 2 = 1.05 [m ² ] (1)
It becomes.

The surfaces in contact with the outside air at room temperature are four surfaces other than the upper and lower surfaces, and the surface area is
0.7 [m] × 0.7 [m] × 2 + 0.7 [m] × 0.75 [m] × 2 = 2.03 [m ² ] (2)
It becomes.

Here, when estimating the heat leakage amount Q leaking to the outside air from the freezing chamber, on the assumption that observed heat leakage from the surface in contact with ambient air for the sake of simplicity, an area 2 [m ^2], the outside air from the refrigeration compartment of the wall If the heat transfer rate K = 0.35 [W / (m ² · K)], the internal temperature is −18 [° C.], and the outside air temperature is +30 [° C.], the amount of heat leakage Q is surface area × heat transfer rate X Expressed by temperature difference,
Q = 2 [m ² ] × 0.35 [W / (m ² · K)] × 48 [K] = 33.6 [W] (3)
It becomes.

  Next, the required cold air flow is estimated.

  The cold air cooled by the cooler 7 is blown into the freezing temperature zone chamber to take heat away from the stored food and the like, and after a part of the heat leaks from the surface of the refrigerator 1 to the outside of the freezing temperature zone chamber and the temperature rises. Return to the cooler 7 from the freezer return port 17.

Here, the flow rate of cold air is V [m ³ ], the temperature rise of cold air is Δt [° C.], the specific heat of air is Cp [kJ / (kg · K)], and the density of air is ρ [kg / m ³ ]. Then, the amount of heat Q [kJ / min] taken from the cold air is
Q = V × Δt × Cp × ρ (4)
It is represented by To obtain the flow rate V from the required amount of heat Q,
V = Q / (Δt × Cp × ρ) (5)
It becomes.

Here, as shown in Equation (3), if the amount of heat leakage is 33.6 [W], and the amount of heat necessary for lowering the temperature of food is 33.6 [W], which is equivalent to heat leakage, The amount of heat required is
Q = 67.2 [W] = 4.03 [kJ / min]
It is.

Here, if the cold air flows into the freezing temperature zone at −20 ° C. and returns to the cooler at −15 [° C.], the temperature rise of the cold air Δt = 5 [° C.] and the specific heat Cp = 1.01 [kJ] / (Kg · K)], air density ρ = 1.4 [kg / m ³ ])
V = 4.03 / (5 × 1.01 × 1.4) = 0.57 [m ³ / min] (6)
Therefore, the flow rate of the cold air needs to be about 0.6 [m ³ / min].

In order to prevent temperature unevenness in the freezer compartment, the flow rate of the cold air discharged from the blowing nozzle is required to be about 2 [m / s]. Here, if the flow rate of cold air is approximately 0.6 [m ³ ] per minute and the flow rate is approximately 2 [m / s] as estimated by the equation (6), the area S of the discharge port is approximately ,
S = 0.6 / (2 × 60) = 0.005 [m ² ] = 5000 [mm ² ] (7)
It becomes. The area of the opening 62 of the freezer compartment cooling damper 50 is conveniently larger than this. For example, if it is about 20% to 30% larger, it is preferably 6000 to 6500 [mm ² ].

  Next, the shape of the opening 62 of the freezer compartment cooling damper 50 will be described. As described above, the width W of the opening 62 is preferably larger than the diameter D of the fan. However, when the width W is enlarged while keeping the area of the opening 62 constant, the height dimension h is reduced to form an elongated shape with a large aspect ratio.

  The opening / closing body 64 that performs the opening / closing operation is slightly larger than the opening 62 and is configured to close the opening 62. The aspect ratio is substantially the same as the aspect ratio of the opening 62.

  The opening / closing body 64 is plate-shaped, and the range of the aspect ratio appropriate for improving the sealing performance will be described with reference to FIG.

  FIG. 15 shows a state in which the opening / closing body 64 rotates in the direction of the arrow 59 around the rotation shaft composed of the drive shaft 61 and the support shaft 65 so that the sealing member 64b is uniformly in contact with the contact portion 66 (not shown). Show. In this state, a distributed load p [N / mm] is generated as a uniform pressing force over the entire circumference of the contact surface. In FIG. 15, the distributed load p is schematically indicated by an arrow. r1 is the distance from the drive shaft 61 to the farthest side 68a of the contact portion 66, and r2 is the distance from the drive shaft 61 to the nearest side 68b of the contact portion 66.

Here, when the distribution load p is simplified as a concentrated load P applied to the center of each side for calculation, and P1 [N] and P2 [N] are respectively set on the long side and the short side,
P1 = p × W (8)
P2 = p × h (9)
It becomes.

here,
h = r1-r2 (10)
The moment around the drive shaft 61 that occurs on the long side is
(1) In the side 68a farthest from the drive shaft 61, M1 = P1 × r1 = p × W × r1 (11)
(2) In the side 68b closest to the drive shaft 61, M2 = P1 × r2 = p × W × r2 (12)
(3) For the side 68c, M3 = P2 × (h / 2 + r2) = p × h × (h / 2 + r2) (13)
It is.

Therefore, the moment M generated around the drive shaft 61 is the sum of them, and there are two sides,
M = M1 + M2 + 2 × M3 (14)
= P * W * r1 + p * W * r2 + 2 * p * h * (h / 2 + r2)
= P × {W × (r1 + r2) + h × (h + 2 × r2)}
= P × {W × (h + 2 × r2) + h × (h + 2 × r2)}
= P × (W + h) × (h + 2 × r2) (15)
It becomes.

  The meaning of the equation (15) is to calculate the driving torque M required when the uniform distributed load p is applied to the entire circumference. Here, as the calculated driving torque M is smaller, the same distributed load p is obtained with a smaller torque. Therefore, it is shown that the smaller the M is, the more the pressure of contact with the opening 62 of the sealing member 64b is maximized.

That is, assuming that the distributed load p is unit load 1 and the non-dimensional moment ratio is M ′,
M ′ = (W + h) × (h + 2 × r2) (16)
It becomes.

  Therefore, the relationship between the width W and the height h of the opening / closing body 64 that minimizes the right side of Expression (16) is the most desirable shape.

Here, as described above, when the area of the opening 62 is 6400 [mm ² ] and the opening 62 is a square, both the width W and the height h are 80 [mm].

On the other hand, when the opening 62 has an elongated rectangular shape, the width W is enlarged and the height h is reduced, and the area is 6400 [mm ² ]. Therefore, as an example, W = 160 [mm], h = 40 [ mm].

  Here, the dimension of the h dimension which is the short side of the opening 62 and the length W of one side in the case of a square W = 80 [mm] is made dimensionless as the short side ratio C. In the case of a square, h = 80 [mm] and C = 1. In the case of a rectangle of W = 160 [mm] and h = 40 [mm], C = 0.5. That is, the smaller the short side ratio C is, the longer the shape is.

  FIG. 16 shows the relationship between the short side ratio and the moment ratio. In FIG. 16, when r2 = 6 [mm] as an example of a size that can be realized in mounting, the moment ratio M is in a range where C≈0.2 to 1.0, that is, in a range of h = 15 to 80 [mm]. The result of calculating 'by the equation (16) is shown.

  As shown in FIG. 16, the moment ratio M ′ has a minimum value at C = 0.4. This is about 70% compared to the case of C = 1 square, and it can be seen that the preferred range of the short side ratio C is about 0.3 to 0.5. That is, a preferable range of width W × height h is 267 [mm] × 24 [mm] to 160 [mm] × 40 [mm]. The optimum value is 183 [mm] × 35 [mm].

  When the short side ratio C is expressed as an aspect ratio that is a ratio of the long side W to the short side h, the short side ratio C is 11.125 when the short side ratio is 0.3, and 4 when the short side ratio is 0.5. That is, when expressed in terms of aspect ratio, the range of 4 to 11 is suitable, and the optimum value is 5.23.

  As described above, it is desirable to make the fan diameter D smaller than the width W of the damper opening 62 obtained here in order to reduce the air blowing resistance. Therefore, the fan diameter D is not more than φ150 [mm]. It is desirable to do.

  Next, the arrangement of the freezer compartment cooling damper 50 will be described. As shown in FIGS. 3 to 7, the freezer compartment cooling damper 50 is not arranged in parallel to the horizontal plane, but in FIG. Place it at an angle. Accordingly, moisture condensed on a part of the freezer cooling damper 50 can be drained along the slope, which is preferable because moisture does not stay inside the damper and freeze. Further, the driving means 60 provided at one end of the freezer compartment cooling damper 50 is disposed on the inclined high place side. Accordingly, the drainage does not enter the driving means 60, which is more preferable.

  As described above, in the present invention, the area of the opening 62 of the freezer compartment cooling damper 50 is larger than the area of the cold air outlet to the freezer compartment.

  Thereby, the pressure loss of a ventilation path can be reduced and the refrigerator with little ventilation resistance can be provided.

  Furthermore, the dimension of the opening 62 of the freezer cooling damper 50 is 0.3 to 0.5 in the short side ratio C in which the length of one side of the square having the same area and the length of the short side h are compared, and The range of 4 to 11 is expressed by the aspect ratio which is the ratio of the short sides.

  This is preferable because the contact pressure between the sealing member 64b and the contact portion 66 of the opening 62 is maximized, the sealing performance is improved, and the leakage of cold air can be prevented. That is, the width W × height h is preferably in the range of 267 [mm] × 24 [mm] to 160 [mm] × 40 [mm], and the optimum value is 183 [mm] × 35 [mm]. The size of the baffle which is 64 is also slightly larger than the opening 62, but is substantially the same size. Since the depth dimension of the opening / closing body 64 is 24 to 40 [mm], which is smaller than the width, it is convenient because the depth dimension of the cold air duct 13 can be reduced and the depth of the refrigerator 1 can be reduced.

  With the above configuration, it is possible to provide a refrigerator that has less ventilation resistance and improves airtightness, thereby reducing leakage of cold air and saving energy. Accordingly, it is possible to obtain a refrigerator capable of ensuring energy saving performance while maintaining the food storage temperature while maintaining the food in the refrigerator within a predetermined temperature range.

  As described above, the present invention reduces the pressure loss of the ventilation path and reduces the ventilation resistance by making the area of the opening of the freezer cooling damper larger than the area of the cold air outlet to the freezer. Can be provided.

  Furthermore, the dimension of the opening of the freezer cooling damper is 0.3 to 0.5 in the short side ratio C in which the length of one side of the square having the same area is compared with the length of the short side h, and the long side and the short side. By expressing the ratio in the range of 4 to 11, the contact pressure between the sealing member and the opening contact portion is maximized, improving the sealing property and preventing the leakage of cold air. Energy saving can be achieved.

1 Refrigerator 2 Refrigerated room (refrigerated temperature zone)
3 Ice making room (freezing temperature zone)
4 Upper freezer room (freezing temperature room)
5 Lower freezer compartment (freezing temperature zone)
6 Vegetable room (refrigerated temperature room)
7 Cooler 8 Cooler storage chamber 9 Blower (blower)
DESCRIPTION OF SYMBOLS 10 Heat insulation box 11 Refrigerating room ventilation duct 12 Upper stage freezing room ventilation duct 13 Cold air duct 15 Refrigerating room duct 16 Refrigerating room return duct 17 Freezing room return port 19 Machine room 20 Refrigerating room cooling damper 21 Evaporating dish 22 Defrosting heater 23 樋 24 Compressor 31 Control board 33 Refrigerating room temperature sensor 33a Vegetable room temperature sensor 34 Freezer room temperature sensor 35 Cooler temperature sensor 50 Freezer room cooling damper 53 Upper cover 54 Partition plate 55 Fan motor fixing part 56 Blower cover 56a Air outlet 56b Rectification part 60 driving means 61 driving shaft 62 opening 62a support 63 frame 64 opening / closing body 64a opening / closing plate 64b sealing member 65 support shaft 66 contact portion 67 pressure contact force 70 motor 71 output shaft 72 pinion gear 73 idler gear 74 idler fulcrum 75 output gear

Claims (5)

A freezing temperature zone provided in the refrigerator body,
A cooler chamber provided behind the freezing temperature zone chamber and provided with a cooler;
A blower for blowing cool air from the cooler room to the freezing temperature zone;
A partition plate that partitions the cooler chamber and the refrigeration temperature zone chamber and has a blowout port that blows out the cold air blown by the blower to the refrigeration temperature zone chamber;
In a refrigerator including a freezer damper that controls the amount of air blown to the freezing temperature zone chamber,
The freezer damper is
A frame having an opening communicating the cooler chamber and the outlet;
An opening and closing body for opening and closing the opening;
Driving means for driving the opening and closing body,
The refrigerator characterized in that the area of the opening of the freezer damper is larger than the area of the outlet.   The refrigerator according to claim 1, wherein a plurality of the outlets are provided, and an area of the opening of the freezer damper is larger than a total area of the plurality of outlets.   The refrigerator according to claim 1, wherein the opening of the freezer damper is rectangular and has an aspect ratio of 4 to 11. The refrigerator according to claim 1, wherein an area of the opening is 6000 to 6500 mm ² . A frame having a rectangular opening;
An opening and closing body for opening and closing the opening;
In a damper device comprising a driving means for driving the opening and closing body,
The damper device according to claim ¹ , wherein an aspect ratio of the opening is 4 to 11, and an area of the opening is 6000 to 6500 mm ² .

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