JPH07234058A - Ventilating passage arrangement structure for circulating cold air - Google Patents

Abstract

PURPOSE:To improve internal volume efficiency by a method wherein a volume, occupied by a ventilating passage and the like, is compacted to increase the internal volume of a refrigerating chamber, in a ventilating passage arrangement structure for circulating cold air. CONSTITUTION:In a refrigerator employing a radial centrifugal fan 8, cold air is sucked from the fore side of the fan and a ventilating passage, introducing the cold air, is connected to a trocoidal casing 9 above a cooler 6 while the ventilating passage is arranged at the side of the cooler 6 within the thickness of the cooler 6. According to this method, fore suction is adopted whereby a motor can be fitted directly into the back surface inner casing while the suction port is provided within the width same as the ventilating passage whereby a partitioning plate is lowered to the side of the cooling chamber, the internal volume of the refrigerating chamber is increased and an internal volume efficiency can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improving the internal volume efficiency by arranging a ventilation passage for cold air circulation on the side of a cooler to make the volume occupied by the ventilation passage compact and to expand the freezing chamber volume.
Further, the present invention relates to a structure suitable for low noise and low vibration in a refrigerator / refrigerator / cool air circulation fan.

[0002]

2. Description of the Related Art A conventional example will be described with reference to FIGS. 6 and 7. Reference numeral 15 denotes a rear vertical partition wall, which is a cooling chamber 7 and a freezing chamber 3.
And is configured to be positioned in front of the position of the cooler 6 except for the mounting portion 11 for fixing the fan motor 10. Reference numeral 9 denotes a spiral casing, which is formed by the ribs of the partition wall 15 and the partition plate 13 on the front side, and the gap in the circumferential direction of the centrifugal fan 8 is the largest on the blower outlet side, and along the circumference of the centrifugal fan 8. It has a scroll shape with a smaller gap as it goes down, and the air outlet side is
It has a scroll shape located below the central axis of rotation of the centrifugal fan 8. 14a and 14b are cold air ducts, which are formed by the ribs of the partition plates 15 and 13 like the spiral casing 9. A centrifugal fan 8 is housed in the space of the spiral casing 9.

Next, the operation will be described. The cool air sucked from the return duct 18 for the freezer compartment 3 and the return duct 19 for the refrigerating compartment 4 is cooled by the cooler 6, and the partition plate 15 is used.
The partition plate 1 passes through the fan 8 from the suction port 24 provided in the
5, the pressure is increased in the scroll-shaped spiral casing 9 formed by the ribs of the partition plate 13 and the blowing direction is determined, and the cool air ducts 14a and 14b are provided.
The cold air is blown out into the refrigerator.

Incidentally, Japanese Patent Laid-Open No. 4-9565 and the like are mentioned in the above embodiments.

Further, as a freezer-refrigerator cold air circulation fan, there is a fan using a centrifugal fan such as a sirocco fan as described in Japanese Patent Laid-Open No. 1-9565, but the description of the shape of the fan is insufficient.

[0006]

The structure of the ventilation passage for cold air circulation described in the prior art has the following problems.

1. As shown in FIG. 6, the cool air duct is formed on the side of the cooler through the front of the cooler, and the fan chamber partitioned by the spiral casing 9 to increase the wind pressure is formed like 14a and 14b. When the cold air duct is arranged in consideration of this, there is a problem that the cold air duct portion is exposed to the inside of the refrigerator, so that the volume of the freezing chamber is reduced and the internal volume efficiency is reduced.

2. Since the suction structure of the fan is the back suction (fan motor side), the fan motor shaft becomes long because a distance is provided between the motor unit and the suction port 24 shown in FIG. 1 in order to secure the amount of cool air to be sucked in. Eccentricity, surface wobbling, etc. will occur and fan characteristics will deteriorate, and the partition plate 1
Since the cool air ducts 14a and 14b formed by 5 and 13 are exposed to the inside of the refrigerator, there is a problem that the freezing chamber volume is reduced and the internal volume efficiency is reduced.

As described above, in the conventional structure for arranging the ventilation passage for cold air circulation, the internal volume efficiency is poor.

3. Centrifugal fans have various blade shapes, and the characteristics vary greatly, so this selection is an important issue. For example, in the sirocco fan (also referred to as a forward-blade fan or a multi-blade fan) described in the above-mentioned reference, the absolute flow velocity (dynamic pressure) of the discharge is large because the gap between the blades is narrowed on the fan outlet side, and the swirl The static pressure recovery effect in the casing is low, the wind pressure (total pressure) required for the fan is high, and the resistance in the duct part that winds and winds is increased, so the same air volume as the propeller fan that is generally used in the past is used. In order to obtain it, the noise is higher than that of a propeller fan, and if the fan is made large and the speed is reduced, a large output and torque are required for the fan motor, the motor becomes large, and the problem of the storage part
In addition to increasing vibration and input, it is difficult to design a low-speed, high-torque fan motor. Further, in order to increase the static pressure, there is a problem that the scroll size of the spiral casing becomes large and the storability is deteriorated.

When used without avoiding the problem of increasing the size, the air volume becomes insufficient, resulting in problems such as a reduction in refrigerating capacity and an increase in size of the compressor. Further, when the distribution duct is enlarged to reduce the ventilation resistance, there is a problem that the effective internal volume is directly reduced. On the other hand, in a centrifugal fan with backward blades with a swollen cross section in the direction of rotation,
There is a problem that the relative velocity between the blade and the flow becomes large and the noise becomes particularly large because the insufficient air volume must be obtained by increasing the rotation speed or the diameter of the impeller.

The increase in the size of the parts directly affects the reduction of the effective internal volume of the storage chamber, and the increase of the required pressure of the fan increases the fan noise and the pulsating vibration in the blower duct, which increases the refrigerator. As described above, since a large box having a large number of flat portions generates vibration noise with a slight vibration, it has been desired to provide a fan structure that solves these problems.

The present invention has been made to solve the above-mentioned problems of the prior art, and it is an object of the present invention to provide a fan for cold air circulation that can obtain low noise and low vibration together with a fan motor. Another object of the present invention is to provide a refrigerator-freezer which has excellent basic performance such as cooling power and power saving and has a large effective internal volume.

[0014]

According to the present invention, cool air is sucked in from the front of the fan, and a ventilation passage for guiding the cool air is connected from the spiral casing in the upper part of the refrigerator, and the ventilation passage is provided on the side of the cooler. Moreover, it is arranged within the thickness of the cooler,
Circulate the cool air from the ventilation passage to the cool air duct on the front of the cooler,
It is possible to provide a refrigerator having an improved internal volume efficiency by expanding the volume of the freezing chamber by adopting a structure for arranging a cooling air circulation passage for discharging cold air to the freezing chamber.

According to the present invention, by adopting the above-described structure for arranging the cooling air circulation ventilation passage, the spiral casing and the ventilation passage for guiding the cool air from the spiral casing are attached to the inner box surface in the inner part of the cooling chamber. And the suction of the fan is shared in the ventilation path of the partition plate with the freezer outlet and the rear partition plate with the spiral casing, the fan motor shaft becomes shorter, and fan characteristics such as eccentricity and runout Since the volume of the freezing chamber is not increased and an extra volume of the cold air duct is not taken, it is possible to expand the volume of the freezing chamber and provide a refrigerator with improved internal volume efficiency.

Further, the blade cross-sectional shape is dented in an arc shape on the side opposite to the rotating direction, the mounting angle of the blade is also inclined rearward on the side opposite to the rotating direction, and the blade outer peripheral end is a radial blade having a substantially radial direction. It is designed to obtain a high static pressure between the wings.

More specifically, the exit angle β at the outer peripheral edge of the blade
₂ is in the range of 70 ° to 105 °, and the flow width between blades is
The width is gradually made wider toward the outlet side b than the inlet side width a, and the inner peripheral end of the blade is positioned at least in the rotational direction rather than the radial direction, which is effectively performed.

Further, the inclination of the blade is gradually reduced from the inner peripheral side toward the outer peripheral side, and the center of gravity is moved inward.

Further, in addition to the above fan structure, the radial blade centrifugal fan and the spiral casing are placed side by side with the cooler within the depth dimension of the cooler, with the suction port facing forward on the back surface inside the box. It was made.

[0020]

As described above, according to the present invention, since the cool air is sucked in from the front of the fan, the spiral casing and the ventilation passage for guiding the cool air from the spiral casing are attached to the inner box surface or the like in the inner part of the cooling chamber, and Since the suction is shared in the ventilation passages of the partition plate having the freezing chamber discharge port and the rear partition plate having the spiral casing, the cooling chamber is lowered to the interior, increasing the internal volume and improving the internal volume efficiency. Further, since the above structure is adopted, the motor shaft is shortened, so that fan characteristics such as eccentricity and surface wobbling are improved, and vibration and noise are effectively reduced.

Explaining the fan itself, the indentation and the attachment of the blade toward the side opposite to the rotation direction of the cross section of the blade causes the inflow along the inclination of the inlet side of the blade and the discharge between the blades. The flow velocity is gradually reduced toward the side to increase the static pressure, and a flow along the rotational direction is created in the direction of the absolute velocity toward the discharge end of the blade. That is, not only after being discharged, but not only after the static pressure is increased between the blades, the pressure loss between the blades is reduced, and the pressure loss due to the spiral casing after the discharge is reduced. The velocity distribution of the discharge flow of
Therefore, it is easy to reduce the loss of the delivery duct and the blowing grill.

In addition, the multi-blade configuration allows the rotational primary frequency to move in a significantly higher direction, and the inclination of the blade cross section allows
The center of gravity can be moved inward, reducing resonance and resonance.

[0023]

1 is a refrigerator main body, 2 is a heat insulation layer, 3 is a freezer compartment, 4 is a refrigerating compartment, 5 is a refrigerating compartment 3 and a refrigerating compartment. A heat insulating wall that divides the chamber 4, 6 is a cooler arranged on the inner back surface, and 7 is a cooling chamber that houses the cooler 6. 15 is located at the rear and partitions the cooling chamber 7 and the freezing chamber 3, and a rib is provided at the front to partition the partition plate 1.
3 is a rear partition plate that forms the ventilation passages 14a, 14b and the like. The partition plate 13 is a freezer outlet 13a, 13b, 13c.
Is provided to partition the freezer compartment 2 and the ventilation paths 14a and 14b. The cool air circulation fan motor 10 is attached to the back inner box 25 with the back cover 9a and the motor support 11 via the anti-vibration rubber 12, and is housed in the motor housing case 2a. Reference numeral 8 is a radial centrifugal fan which is attached to a fan motor 10 for circulating cold air. Radial centrifugal fan 8
Is installed in the pressure chamber 16 formed by the spiral casing 9 integrated with the rear partition plate 15 and the rear cover 9a, and discharges the cool air toward the lower outlet 9c. The motor assembly described above is located above the cooler 6. As shown in FIG. 2, the accumulator 20 that prevents the reverse flow of the refrigerant is installed on the left side when viewed from the front, and the cooler indicator projection 21 is provided in the ventilation passage 17 that guides the cool air from the spiral casing 9 to install the cooler. did.

The spiral casing 9 and the ventilation passage 17 for guiding the cool air from the spiral casing 9 have a sealing structure in which, in the spiral casing 9, the rear cover 9a is provided at the fitting portion 23 to seal the ventilation passage 17 for guiding the cool air. In the above, the rear inner box 25 is provided at the fitting portion 22 and is sealed. More than,
It is a description of the configuration.

Next, the operation will be described. The cool air sucked from the return duct 18 for the freezer compartment 3 and the return duct 19 for the refrigerating compartment 4 is cooled by the cooler 6 and then from the suction port 24 provided in the spiral casing 9. After passing through the radial centrifugal fan 8, the pressure is increased by the spiral pressure chamber 16 described above and discharged to the side of the cooler (9c direction) and distributed to the ventilation passages 17 and the ventilation passages 14a and 14b, and the partition plate 13 The cold air is discharged from the cold air discharge ports 13b and 13c.

However, if the delivery duct, the grill, etc. are made compact in order to increase the amount of food to be stored, the ventilation resistance becomes large and a fan with a static pressure commensurate with the ventilation resistance is required. It is natural to upload. Here, the ventilation resistance is proportional to the square of the wind speed. If the cross section of the ventilation passage is reduced by 20% in area, the ventilation resistance will be 1.4 times and the noise will be proportional to the square of the pressure.
20 × log (1 + 0.4) = 2.9 (dB) will be high. The above-mentioned increase in noise can be said even when the absolute velocity of the discharge from the fan becomes large, or the wind velocity distribution is poor and the velocity is partially high.

[0027] However, in the present invention, recessed arcuate cross-sectional shape of the blade 8 _a in the opposite to the rotation direction N as shown in FIG. 3, is Ko傾across the side opposite to the rotation direction N, radially Since the blade outlet end 8 _aa of the blade is a radial blade centrifugal fan 8 having a substantially radial direction, the flow passage width between the blades is equal to the dimension a on the inlet side.
Since the dimension b of the outlet angle is larger than that, the flow between the blades becomes a decelerating flow, and the dynamic pressure is converted to static pressure by the time it exits from between the blades. And the dynamic pressure is increased). Therefore, static pressure recovery in the surrounding spiral casing 9 is not required so much, and the spiral casing 9 can be made small. Also, the flow velocity distribution delivered from the spiral casing 9, becomes satisfactory for the same reason, is static pressure perhaps in the pressure chamber 16, freezing chamber 3 from outlet 13 _b with less of ventilation resistance
To be easily blown into the refrigerating compartment 4 from the lower outlet 9 _c.
Accordingly, since the ventilation resistance is less well the pressure of the fan it may also lowered, as shown in FIG. 3, for a relative velocity W ₂ between the blade 8 _a and flows in the wing discharge end 8 _aa is small, not only the noise is reduced , The absolute velocity C ₂ along the rotational direction is gradually increased toward the blade discharge end 8 _aa , so that the collision with the spiral casing is reduced and the loss is reduced, while the radial blade inlet end 8 _{ab of the} blade 8 _a is reduced. In the above, since the rotation direction is continuously approached from the indented side along the direction of the relative inflow velocity W _1, the occurrence of turbulence at the time of inflow to the blade is low, and low noise is obtained. Since the static pressure is obtained by increasing the rotational speed to some extent, the required torque is small due to the high rotational speed in order to obtain the same output, and a normal small 2-pole induction motor can be used, resulting in a highly efficient speed point. Enabled and fun mode The input of the controller 10 can be lowered, and power saving and cooling capacity can be improved. Furthermore, since there is a large amount of static pressure between the blades, deceleration (expansion flow) in the spiral casing 9 and the pressure chambers 16 can be reduced, so that vortices are generated less and pulsating flow is also reduced. Resonance and resonance can be reduced. In addition, the inclination of the blade cross section becomes smaller as it goes outward in the radial direction, so that the center of gravity of the blade is in the center direction, the starting torque of the fan motor can be made small, and the vibration can be reduced. Further, since the number of blades is a multi-blade type, which is several times (5 to 10 times) larger than that of a conventional propeller fan, the rotation frequency of the blades can be increased several times, and the natural frequency of the refrigerator-freezer box (usually 100 to 100). 300Hz), the distance can be increased (150-200Hz for a 4-blade propeller fan, and the fan of the present invention has 20 or more blades, which is 5 times as high as 750Hz).
This means that even if vibration is applied via the fan motor 10 or air flow path is excited by a fluid, resonance or resonance is reduced.
Further, since the main frequency of noise is high due to the high rotation frequency of the blades, the sound insulation effect of the box body is large, but the radiated noise emitted to the outside is also low.

Next, advantages of the arrangement structure of the radial blade centrifugal fan 8 will be described. Radial blade centrifugal fan 8
And around the spiral casing 9, placed on the back of the box body section, the suction port 9 _b toward the front is opened, the pressure chamber 16
Is connected to the lateral side of the spiral casing 9, and the centrifugal casing 9 uses a centrifugal fan with radial blades. Therefore, static pressure progresses before the wind enters the spiral casing 9. Since it can be scrolled, the vertical dimension can be made small, so that it can be easily juxtaposed vertically within the thickness dimension of the front and rear of the cooler 6 arranged on the back surface inside the box body, and the effective internal volume that can store food is large. You are getting the effect. Experiments have confirmed that the size of the discharge port height (end _9e portion) can be reduced by 15 to 20% as compared with the case where a sirocco fan having the same diameter is used. Also,
With the above structure, the fan motor 10 can be housed on the side of the heat insulating layer 2 that is not related to the ventilation path, and the length of the shaft can be shortened, so that the amount of air can be increased and the vibration of the fan motor 10 can be reduced. , Spiral casing 9
For the fan motor 10 can be supported by the back plate 9 _a, without requiring a new part, moreover addition small axial support vibration is easily, the fan motor 1 by back plate 9 _a
0 is sealed in the dent 2 _a to prevent the occurrence of dew on the fan motor 10 and to radiate a part of the heat generated from the fan motor 10 from the rear to the outside of the box to improve the cooling capacity inside the box. The effect of improving is obtained. Next, in order to confirm that the radial blade centrifugal fan 8 is good, the actual measurement data will be described in detail with reference to FIG.

In the experiment, the outer diameter D ₂ was 80 mm and the inner diameter D ₁ was 68 m.
Using a fan of m, axial thickness 30 mm, and number of blades 30, under the same ventilation resistance load conditions as a refrigerator / refrigerator with an effective internal volume of 370 l, the air volume commensurate with the cooling capacity is 0.85 m ³ / min and the total pressure is constant (20 Pa). In order to obtain, the performance of the fan itself is measured by changing the blade cross-sectional shape variously, the noise level at the position 1 m in front of the spiral casing discharge port is SL, and the required rotation at that time is measured in relation to the outlet angle β ₂ of the blade. The numbers are arranged by N _f , required torque T, and total pressure efficiency η. In the figure, the alternate long and short dash line indicates the case of a so-called backward blade centrifugal fan in which the blade cross-sectional shape has a bulge with respect to the rotation direction and the whole is tilted backward in the opposite direction to the rotation direction. In the case of a so-called forward-blade centrifugal fan, which is dented with respect to the rotation direction and tilted forward in the rotation direction, the solid line indicates a radial that is dented with respect to the rotation direction in the present invention and tilts backward in the opposite direction to the rotation direction. It shows the case of a centrifugal fan.

As can be seen from the figure, the radial blade centrifugal fan has a noise S of 70 in the range of the outlet angle β ₂ of 70 ° to 105 °.
L is clearly lower than the forward-blade centrifugal fan. The reason for this is that, as described above, the relative velocity W ₂ of the flow with respect to the blades is the lowest, so there is little turbulence between the blades and at the blade outlet end 8 _aa , and the blade inlet end 8 _ab is along the inflow direction of the wind. This is because the static pressure recovery in the spiral casing is also performed gently. Therefore, the efficiency η of the fan is high, and the required number of revolutions N _f is 2000 revolutions per minute or more, so that a normal small-sized two-pole fan motor can be sufficiently operated.

Further, the noise is higher in the forward blade centrifugal fan in which the entire blade is inclined in the rotation direction than in the radial blade centrifugal fan. The reason for this is that the outlet side inter-blade air passage width dimension becomes small due to the inclination of the blades, and the relative speed W ₂ with the blades becomes large due to the increase in the absolute velocity C ₂ passing therethrough. This is because the turbulence increases and the absolute velocity of the dynamic pressure is large, so that the turbulence due to the enlarged passage of the spiral casing and the loss inside the casing due to the high speed portion increase. Further, because of this, the fan efficiency η is also reduced, and the required rotation speed N _f is also lower than 2000 rotations per minute, which is a point where the slip ratio is too large in a normal small 2-pole induction motor, that is, low rotation speed. It will be used in the area where the torque value decreases as the number increases,
There is a problem that the rotation speed fluctuates due to a slight fluctuation of the power supply voltage or a fluctuation of the fan load, and the two-pole induction motor cannot be practically used. Also, in order to perform the same work at low rotation speed, a low rotation speed and a large required torque are required, and the efficiency of the fan motor is reduced due to the large slip ratio of the rotation speed. There is a problem that the input also increases. On the other hand, it is possible to reduce the outer diameter of the fan in order to increase the rotation speed,
Since the air volume decreases in proportion to the cube of the outer diameter, there arises a problem of insufficient air volume.

On the other hand, the noise SL is high in the backward blade centrifugal fan. The reason for this is that the relative speed becomes large and the wind pressure becomes low because the rotational speed N _f is increased to cover the peripheral speed by increasing it. Therefore, the loss in the blade is large and the efficiency is reduced. In order to improve this, it becomes necessary to make it larger, and new problems arise such as storability, increase in material cost, and increase in vibration.

The data points with hunting in the figure are the actual air flow rate of 0.85 when only the built-in fan is operated in the refrigerator / freezer.
m ³ / min Set to the rotation speed that can be obtained (thus ignoring the fan unit test), β ₂ = 90 ° The radial blade centrifugal fan produces the same noise as the fan unit test (the front of the box. 35 m) with a microphone installed, and the noise was measured for a forward-blade centrifugal fan and a backward-blade centrifugal fan. %, The same air volume was obtained, and the noise increased by 3 dB. For this poor static pressure recovery, the outlet port 13 _b with a pressure chamber 16 and the grill portion of the high velocity flow, and such lower outlet 9 _c and the longitudinal duct 17, the ventilation resistance becomes larger It is due to. In the backward blade centrifugal fan, the noise increased by 1 dB. This was due to the high motor vibration due to the high rotation speed.

With the structure and operation described above, the rear suction is adopted as in the suction port 24 of the conventional example FIG. 1, but by adopting the front suction, the motor is directly fitted to the rear inner box 25, In addition, the suction port 24 through the ventilation paths 14a, 14
Since it is provided within the same width as b, the fan guard 13 is lowered toward the cooling chamber 7 to increase the internal volume of the freezing chamber 3 and improve the internal volume efficiency.
Also, by adopting front suction, the fan motor 10
Since the axis of is shortened, fan characteristics such as eccentricity and surface wobbling are improved, which is effective in reducing vibration and noise.

In the fan alone, the blade shape has a great influence on the performance, as described with reference to the measured performance based on the blade shape based on the data. Therefore, the radial blade centrifugal fan according to the present invention is used. As a result, low noise was obtained, and it was confirmed that the fan motor used in combination with this can also operate efficiently in combination with the small two-pole induction motor. It was also confirmed that when applied to a refrigerator / freezer that requires a delivery duct, a grill, etc., the effect is greater than the noise level difference between fans alone.

Next, the main specifications associated with the blade shape of the radial blade centrifugal fan of the present invention will be described. Inner diameter D
₁ 0.7D ₂ ~0.88D ₂ (the outer diameter and D _2), the wing number Z is 0.25D ₂ ~0.5D _2, the indentations curvature radius R of the blade 0.085D ₂ ~0.16D ₂ and the blade exit angle β ₂ is 7
It is preferable that the installation angle θ (inclination) of the entire blade is 0 ° to 105 °, and the blade is inclined rearward as opposed to the rotation direction.

[0037]

As described above, according to the present invention,
By adopting the front suction, the motor is directly fitted to the back inner box, and the suction port is provided in the same width as the ventilation passage, so the partition plate is lowered to the cooling chamber side and the freezing chamber volume is increased to improve the internal volume efficiency. I was able to do it. Also, by adopting front suction, the shaft of the fan motor becomes shorter, so eccentricity,
Fan characteristics such as surface runout are improved, and it is effective in reducing vibration and noise.

According to the present invention with respect to a single fan, according to the present invention, the shape of the blade is dented in an arc shape on the side opposite to the rotational direction, the mounting angle of the blade is inclined rearward opposite to the rotational direction, and the outer peripheral edge of the blade is directed substantially in the radial direction. A radial-blade centrifugal fan structure with the inner edge close to the rotation direction is used, and it is placed in a refrigerator / freezer that uses a distribution duct, a blow-out grill, etc., and is placed side by side with the cooler on the back of the inside within the depth dimension of the cooler. I used it, so
It is possible to provide a product with low noise and low vibration, and further, it is possible to provide a product having excellent cooling power, low power consumption, and large effective internal volume.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a structure for providing a ventilation passage for cold air circulation according to a conventional example of the present invention.

FIG. 2 is a front view of a cooling air circulation ventilation passage arrangement structure according to an embodiment of the present invention.

FIG. 3 is a cross-sectional view of a structure for providing ventilation passages for cold air circulation according to an embodiment of the present invention.

FIG. 4 is a diagram showing a partial enlargement and a structural specification of the radial centrifugal fan of FIG.

FIG. 5 is an explanatory diagram comparing the performance of the radial centrifugal fan of the present invention with other types of fans.

FIG. 6 is a vertical cross-sectional view of a ventilation passage arrangement structure for cold air circulation according to a conventional example of the present invention.

FIG. 7 is a perspective view of a main part of the same conventional example as in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Refrigerator main body, 2 ... Thermal insulation layer, 3 ... Freezing room, 4 ... Refrigerating room, 5 ... Thermal insulation wall, 6 ... Cooler, 7 ... Cooling room, 8 ... Radial centrifugal fan, 9 ... Swirl casing, 9a ... Rear surface Cover, 9b ... Mouth ring, 9c ... Downward outlet, 10 ... Cooling air circulation fan motor, 11 ... Motor support, 12 ... Anti-vibration rubber, 13 ... Partition plate, 13a, 13b, 13c ... Freezer outlet, 14a , 14b ... Ventilation passage (freezer compartment discharge), 15 ... Rear partition plate, 16 ... Pressure chamber, 17 ... Ventilation passage (9c), 18 ... Freezer compartment return duct, 19 ... Refrigerator compartment return duct, 20 ... Accumulator, 21 ... Cooling device support protrusions, 22 ... Fitting portion (rear inner box), 23 ... Fitting portion (rear cover), 24 ... Suction port (fan portion), 25 ... Rear inner box.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yutaka Shimoda 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Living Equipment Division, Hitachi, Ltd. Hitachi Ltd. Living Equipment Division (72) Inventor Takashi Tsuchiya 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Living Equipment Division, Hitachi Ltd.

Claims (2)

[Claims] 1. A cooler is provided below a suction side of a fan provided on the rear side of the inside of the refrigerator, a spiral casing is used around the fan, and a ventilation passage and a blowing grill are used on the discharge side to send cool air to a storage chamber. In a forced circulation type refrigerator / freezer, cold air is sucked in from the front of the fan, an air passage for guiding cold air is connected from the swirl casing at the top of the cooler, and the air passage is on the side of the cooler, and the thickness of the cooler. A ventilation passage arrangement structure for cold air circulation, which is arranged inside. 2. The ventilation passage arrangement structure for cold air circulation according to claim 1, wherein the ventilation passage is formed by a partition plate having a freezing chamber discharge port and a rear partition plate having a spiral casing.