WO2005124249A1 - Cooling device - Google Patents

Abstract

The inside of a box body (1, 5) is partitioned into two rooms by a partition plate (7). An object to be cooled is received in a storage room (10) of the front face side, and a cooler (8) and a fan (11) are received in a cooler room (9) on the rear face side. An opening (14) for connecting the cooler room (9) and the storage room (10) is formed in the partition plate (7). The opening (14) is greater than the diameter of the fan (11) and positioned, when seen in the direction of the rotation axis of the fan (11), so as to surround the outer periphery of the fan (11) with a gap maintained. The area (S) of the opening (14) is defined to be 1.8 x π(R/2)2 ≤ S ≤ 2.5 x π(R/2)2 with R being the diameter of the fan (11). The distance between a border surface on the storage room side of the opening (14) and the foremost portion of the fan (11) is not less than 0 and not more than 0.2R.

Description

 Specification

Cooling system

Technical field

 The present invention relates to a cooling device, particularly to a cooling device suitable for freezing and refrigeration of foodstuffs.

Background art

 For cooling devices such as freezers and refrigerators, a method is used in which the air is cooled by cooling and forcedly circulated in the refrigerator. According to such a forced air circulation system, since the cool air is forcibly circulated in the refrigerator using a fan, the temperature fluctuation force S in the refrigerator is small, and the cooling time is shortened. There are advantages. However, in the cold air forced circulation system, when heat is exchanged in the cooler, the problem is that moisture contained in the air solidifies and adheres to the cooler.

 For example, in the refrigerator described in Japanese Patent Application Laid-Open No. 62-169988, a cooler and a fan are arranged behind the freezer. The circulating air from the refrigerator compartment and the freezer compartment is sucked in from a suction port provided in the lower portion of the freezer compartment, cooled through a cooler, and then blown out to the freezer compartment again by a fan. In a freezer-refrigerator, the reflux air from the refrigerator compartment and the reflux air from the freezer compartment are combined before reaching the cooler, so that the amount of frost to the cooler is reduced.

However, in this freezer-refrigerator, when the flowing air from inside the refrigerator passes through the cooler and is guided to the fan, the air flows in a one-way direction. It is necessary to provide a road. As a result, the number of parts is large and the fortification is complicated. The configuration uses low-temperature circulating air from the refrigeration system to reduce frost formation on the cooler due to the circulating air from the refrigeration system.Cooling by the circulating air from the freezer compartment It is not possible to reduce the frost on the vessel.

 Further, Japanese Patent Application Laid-Open No. 6-273030 or Patent No. 33

In the freezer described in 6 6 9 7 7 JP is disposed cooler behindゝfreezing chamber, is output-blown cold vis ^s from fan provided on the front surface of the cooler, the refrigerator is cooled . In such a device, since a fan is arranged on one side of the cooler, a part of the reflux air is introduced from the freezer to the rear of the fan, and passes through the cooler. It is possible to make the fluid flow without flowing, and it is possible to reduce the amount of phase formation to the cooler.

を減少 させる こ と はでき るが、 冷却器室と 冷凍室の境界が明 確でな く 、 それぞれの室の熱交換効率も フ ァ ンか ら の距離が 離れる ほ ど悪く なる。 特に、 冷却器室側では 、 冷却器の背面 がほぼ塞がれているため、 冷却器の熱交換効率も悪いもので めつ 7こ 0 However, in such a freezer, frost is formed on the cooler.

However, the boundary between the cooler room and the freezer room is not clear, and the heat exchange efficiency of each room becomes worse as the distance from the fan increases. In particular, since the back of the cooler is almost completely closed on the cooler room side, the heat exchange efficiency of the cooler is poor, so the

Disclosure of the invention

 The present invention has been made in view of the above-described problems of the conventional cooling device. The purpose of the present invention is to provide a simple structure, suitable for miniaturization, and a cooling coil. Frost amount is P

 O To provide a cooling device that is difficult to dry

 The cooling device of the present invention

A box composed of heat insulating members, A cooler for cooling the air by heat exchange, a box inside, a cooler for accommodating the cooler, and a storage room for accommodating the object to be cooled, and A partition plate formed with an opening P connecting these two chambers,

 A fan that is disposed in the cooler and feeds the air cooled by the cooler into the storage through the opening;

 In a cooling device equipped with

 The opening P is formed such that, when viewed from the direction of the rotation axis of the fan, the opening m surrounds the outer periphery of the fan with a gap.

 ,

 The area S of the opening P is defined as follows:

1.8 π (R / 2) 2 ≤ S <2.5 X π (R, / 2) 2,

 The distance between the boundary surface on the storage side of the msc mouth and the top of the fan is not less than 0 and not more than 0.2 R.

 According to the cooling device of the present invention, by the rotation of the fan, the discharge flow is blown out from the cooler through the m opening to the HIJ shell and chamber.

Accordingly, a suction flow is generated from the storage power U through the opening and sucked into the cooling device. The discharge flow and the suction flow collide with each other, and the flow speed with respect to the momentum of the cold air is suppressed.o As a result, the frost formation on the IU cooler is suppressed, and at the same time, the drying of the food is performed. Can be prevented.

 ■■ 、 ■ / ■■

Furthermore, by making the area S of the opening P to satisfy the above equation, the area S of the opening P can be reduced by the action of both the outflow and inflow of air through the opening. Each room has a good balance. It is possible to reduce the average flow velocity while increasing the heat exchange efficiency. Preferably, such an arrangement is adopted that the U gci fan is arranged above the cooler ij The size of the cooling device can be reduced because the depth dimension cannot be increased.

 Preferably, a slit is formed in the partition plate at a position facing the cooler or at a position below the iu cooler. In this way, the slit is formed at the J'J opening. In addition, it is possible to finely adjust the flow of air within the cooling margin by providing a storage roll and a reflux roll path to the cooler room and adjusting the layout.

 It should be noted that a plurality of combinations of the U fan and the opening may be provided. With this configuration, the cooling performance can be improved.

 According to the cooling device of the present invention, the same cooling performance can be exerted from the force S whose structure is simpler than that of the conventional cold air forced circulation system, and the amount of frost on the cooler is also reduced. be able to

Brief Description of Drawings

 FIG. 1 is a vertical sectional view showing one example of the cooling device of the present invention. FIG. 2 is a front view of a main body of the cooling device shown in FIG. 1. FIG. 3 is a horizontal sectional view of the cooling device shown in FIG.

 FIG. 4 is a front view of an opening portion of the cooling device shown in FIG. 1. FIG. 5 is a diagram for explaining the flow near the fan in the cooling device of the present invention.

 FIG. 6 is a diagram for explaining the flow near the fan in the cooling device of Comparative Example 1.

Figure 7 shows the flow near the fan in the cooling device of Comparative Example 2. FIG.

 FIG. 8 is a vertical sectional view without the cooling device of Comparative Example 3.

 FIG. 9 is a front view of the main body of the cooling device shown in FIG. 8. o FIG. 10 is a vertical sectional view showing another example of the cooling device of the present invention. BEST MODE FOR CARRYING OUT THE INVENTION

 Figure:! 4 to 4 show examples of the cooling device based on the present invention (Example 1). In the figure, 9 is a cooler room, 10 is a storage room, 7 is a partition plate

8 indicates a cooler, 11 indicates a fan, and 14 indicates an opening.

 FIG. 1 is a longitudinal sectional view of the cooling device. The body is the body

It is composed of 1 and door 5. The main body 1 is formed by filling a heat insulating material 4 between the outer box and the inner box. Similarly, the door 5 is formed by filling the door panel with the heat insulating material 4.

 The inside of the box is partitioned by a partition plate 7 into a storage room 10 on the front side and a cooler room 9 on the back side. The cooler 8 is accommodated in the cooler room 9. Cooling 8, 1 Z8 of the thickness of the cooler 8 due to the wall force behind it: A gap of about 1 Z4 is provided. In this example, the cooler 8 is a cooling tube of a Fin Tube type. Air exchanged in the cooler 8 is accumulated in the cooler room 9. Fans 11 are arranged in front of the cooler 8 and run. The fan 11 is mounted on a rotating shaft of a driving motor and is laid. The motor can, for example, be mounted on the partition plate 7 via a bracket (not shown) ο

Note that a compressor, a heat exchanger, a condenser, etc. (not shown) are connected to the cooler 8 via piping, and the refrigerant supplied from the condenser is Evaporates in cooler 8 and returns to the compressor. The compressor is housed in, for example, a machine room (not shown) provided with a BX at a lower portion on the rear side of the main body 1. The condenser is for example embedded in the insulation 4 of the body 1.

 FIG. 2 is a front view of the cooling device shown in FIG. 1, viewed from the front side (from the direction of arrow A in FIG. 1) with the door 5 removed. The partition plate 7 is provided with a circular opening 14. The diameter of opening 14 (dimension B) is larger than the diameter of the fan.

\ BX 5+ has been.

 FIG. 3 is a cross-sectional view of the cooling device shown in FIG. 1 in the horizontal direction. In the fan 11, a part of the blade thickness (dimension D) overlaps with the thickness (dimension E) of the partition plate 7. In such a position, the blade is disposed at a position where the frontmost portion of the blade faces the extended surface on the rear surface of the partition plate 7 with a slight gap (dimension C). Here, the upper limit of the dimension C is about 0.2 R, where R is the diameter of the fan 11.

 FIG. 4 shows a partially enlarged view (front view) of the opening 14. In this example, opening 14 contains a human body or P to fan 11

 Grating 17 is installed to prevent contact of eclipse PP ο

 FIG. 5 shows the state of air flow around fan 11 in the cooling device according to the present invention. For comparison, FIGS. 6 and 7 show the flow of air around the fan 11 when the arrangement of the partition plate 7 or the fan 11 is changed. Here, in FIG. 6 (Comparative Example 1), the partition plate (7 in FIG. 1)

(8, Fig. 1) only, and close to fan 11 In FIG. 7 (Comparative Example 2), fan 11 is open.

It is arranged so as to protrude from P 14 toward fu (that is, toward the storage room 10 side).

 In the case shown in FIG. 5, a narrow flow path through which the air flows is formed between the outer periphery of the fan 11 and the opening 14. Also, in the case shown in FIG. On the other hand, a space formed between the rear wall and the partition plate 7 is formed around the fan 11, whereas in the case shown in FIG. 6, the flow around the fan 11 is There is nothing to block

 In the case shown in FIG. 5, near the inner periphery of the opening 14, the air in the storage room 10 is sucked by the suction force of the fan 11, and Because of this, the flow blown from the cooler room 9 to the storage room 10 and the storage room 1

Due to the one-way sky flow with the flow sucked into the cooler room 9 from the 0 force, a one-way flow occurs at a limited opening 14. Then, as shown by the broken line in Fig. 5, the storage chamber

When the discharge flow blown out at 10 and the suction flow sucked into the cooler room 9 collide with each other, a phenomenon occurs where the discharge flow and the suction flow collide with each other. A flow state is formed, and the flow velocity of the discharge flow of the storage chamber 10 is weakened. That is, in the case shown in FIG.

Due to the action of both the outflow and inflow of air via 4, the flow velocity of the discharge flow to the storage chamber 10 is weakened compared to the cold momentum.

In the case shown in FIG. 6 (Comparative Example 1), the air flow is in a state where the discharge flow and the suction flow are clearly separated. In the case (Comparative Example 2), fan 11 was rotated forward.

 ,

In addition to the rear of fan 11, the air in the IU storage room 10 of fan 11 is also sucked in by the rotation of fan 11, and blows forward of fan 11. What is to be served

 Next, the results of a performance confirmation test of a cooling device manufactured based on the present invention will be described with reference to FIG.

 In the first embodiment, the internal volume of the storage 10 is set to 405 L (900 mm in width, 750 mm in height, 600 mm in depth), and the fan 1

1 has a diameter of 250 mm, the open P 14 has a diameter of 350 mm, and the partition plate 7

 The distance (dimension C in Fig. 3) from the extended surface of the surface to the m-th part of the blade of fan 11 was set to 0 mm. Also, the input power

An AC 220 V, 60 Hz, a 150 W output compressor was used, and a DC 220 V, 40 W fan motor was used. The refrigerant was R 2 2 0

 In the experiment, this cooling device was used to control the air flow by the smoke movement and small pieces attached to the grid 17 (Figure 4) in front of the fan 11. Observed ο Also, for comparison, the fan

The same observations were made for the mouth (comparative example 1, equivalent to FIG. 6) with the partition plate removed around 11.

In Example 1, not only the discharge flow but also the suction flow was observed in the rotation region 30 (FIG. 4) of the fan 11 o The outer circumference of the fan 11 and the open P 14 Even in the area 31 between the circumference and 周, the suction flow and the discharge flow are mixed. When observing the strip-shaped small pieces attached to the grid 17 in this area, it was clear that there were many points where the tips of the small pieces moved back and forth, and whether it was a suction flow or a discharge flow. In confirmation There were many parts that didn't work.

 On the other hand, in the mouth of Comparative Example 1, a discharge flow was observed in the rotation area of fan 11 (the area corresponding to rotation area 30 in FIG. 4), and the discharge flow was observed outside fan 11. Suction flows were observed and these could be clearly distinguished

 In Example 1, the flow of air blown from fan 11 to the left was observed, but compared to the configuration of Comparative Example 1, the blowout intensity was significantly reduced. For example, In Comparative Example 1, the fan

It was observed that the air was blown out from 11 with a strong force, and that the air was flowing to the front (door part) of the storage room 10. On the other hand, in Example 1, it was observed that air was blown up to almost the center in the depth direction of the storage room, but at the front of the storage room 10, air was blown out in the blow-out direction. The flow could not be clearly confirmed.

 From these experimental results, in Example 1, it was found that there was a flow of both outflow and inflow of air through the opening 14 and that the storage room

It can be seen that the flow velocity of the discharge flow into 10 is relatively low. The air flow near the fan 11 is such that the turbulent state occupies a large proportion in Example 1 while the discharge flow and the suction flow can be clearly distinguished in Comparative Example 1. Understand

According to the configuration of the first embodiment, the air in the storage room 10 and the air accumulated in the cooler room 9 can be exchanged via the opening 14, and thus the air in the cooler 8 can be exchanged. The heated air can flow into the storage room 10, and the air whose temperature has risen in the storage room 10 can be returned to the cooler 8. For this reason, even in a configuration in which a dedicated suction port is not provided separately from the opening 14, heat exchange by the cooler 8 can be performed. Is possible o

The area of the opening P 1 4 are too large Hazuki close to the case of FIG. 6, lost effect force ^s weakening the flow velocity of the discharge flowゝother hand, if too small, condenser chamber which is through the opening P 1 4 The suction flow to 9 is reduced. Therefore, it is appropriate that the area s of the open P14 is 1.8 times or more and 25 times or less the area of the fan-shaped mussels (the area of the circular region where the fan 11 rotates) o That is. The area S of the opening P 14 is defined as the range defined by the following equation, where R is the diameter of the fan 11.

1 8 X pit (R 2) 2 ≤ S ≤ 2.5 X π (R / 2) 2 In Example 1, the diameter of fan 11 is 250 mm and the area of fan is 49 1 0 0 0 mm, the diameter of the apertures 1 4 3 o 0 mm, since the surface禾貝S of apertures 1 4 is a ^{9 6 2 0 0 0 mm 2} , the open mouth, the area of the fan It will be 1.96 times higher. In the first embodiment, the distance (D dimension in FIG. 3) from the back of the partition plate 7 to the frontmost portion of the fan 11 was set to 0 mm. Depending on the size (diameter and thickness), it may be about 0 to 50 mm inward of the cooler room 8, o

 Next, the results of comparison with the conventional cold forced circulation freezer will be described.

 Fig. 8 shows a vertical cross-sectional view of the device used for comparison (Comparative Example 3). O Fig. 9 shows a partially enlarged view of the opening of the device of Fig. 8. In the configuration, the interior of the freezer is separated north by a divider.

The cooler room 43 is divided into a cooler room 43 on the front side and a storage room 46 on the front side, and a cooler 40 is housed in the cooler room 43. Ο The fan 42 is arranged on the cooler 40 side, and the periphery of the fan 42 is surrounded by a duct h44. Suction port 41 is provided on the back side of refrigerator 40

The air in 46 is sucked in from suction P 41, sucked and drawn into duct 44 by fan 42, and discharged from discharge P 45 o The diameter of fan 11 Is 250 mm Duct 44 has an inner diameter of 27

O m m.吴 The storage volume of Ml Example 1 (Figure 1 Figure 5) and Comparative Example 3 are the same because the equipment main body is the same. The parts other than the shape of the partition plate and the arrangement in the cooler are common, and the parts related to the cooling system such as the cooler, the fan, and the fan motor compressor are also common.ο

 The experiment conditions were as follows: ambient iJin. Degree 20 C relative humidity 60 storage tank Internal load: water volume: 100 000 g (200 000 g X 5 stages) Water temperature 1

6 C.

Example 1, Neite the case of Rere deviation of Comparative Example 3 also, about 1 0 0 minutes to about - and a 2 0 ° reaches a stable state of C o ^v this ~, Example

1. The cooling performance of Comparative Example 3 was confirmed to be almost the same as that of RJ.

6 g in Comparative Example 3 was 9 7 4 2 g

Here, although the configuration of the flow path is different between Example 1 and Comparative Example 3, both of them differ in terms of circulating air to the cooler and discharging the cooler of the cooler to the storage. O In the first embodiment, although the turbulence state in which the speed of the air flow is low occurs, the air in the cooler room and the storage room Transported to the cooler room where the stored treasure air flows Heat exchange is performed in the heat exchanger, and the cooling capacity is exhibited. In the experiment described above, the difference between the temperature at the inlet and the outlet of the cooler (the temperature near the pipe) was about 10 ° C at the time of temperature decrease, and was about 4 at stable time. C, and sufficient heat exchange was performed.

 On the other hand, with regard to frost formation on the cooler, in Comparative Example 3, frost formation was found on the entire cooler, whereas in Example 1, a small amount of frost formation was found on the back side of the fan. I just stopped. In Comparative Example 3, the air whose temperature rose in the storage room 46 reaches the cooler 40 via the suction port 41 0 and the flow velocity in the storage room 46 is lower than that of the first embodiment. The residence time in the storage room 46 is also shorter than that in the first embodiment, and therefore, the air flow in the comparative example 3 is such that the moisture-containing air in the storage room 46 is very fast. At the same time, the frost on the cooler 40 tends to increase because it is continuously transported to the cooler 40 at the speed o

 On the other hand, in Example 1, the flow of air was slower overall than in Comparative Example 3, and the residence time in the storage room 10 was longer than that of Comparative Example 3. Since the air discharged from the opening 14 is sucked into the same opening P 14, the air flows into the storage room 10, and the discharge flow and the suction flow collide and merge. The ratio is also high. For this reason, while the water-containing sky is steadily staying in the storage room 10, this effect (D also causes the water to solidify in the storage room 10 o The reason why the amount of frost in Example 1 is small is that this is the case.

8 tends to reduce frost formation. It also helps to prevent the drying of ingredients o In the first embodiment, a slot having a slot shape penetrating the partition plate 7 is provided at a portion corresponding to the upper and lower portions of the cooling plate 8 of the partition plate 7. Experiments were also conducted on the formation of air, but the basic flow of air at the opening 14 was not particularly changed.

 This can be considered as follows. In the first embodiment, as described above, the flow of air at the opening 14 is not one-way, and there are both inflow and outflow of air. The average wind speed of the air discharge to 0 was slower than that of the configuration of Comparative Example 3. This is the same in the cooler room 9, and in the part where the cooling 8 is arranged, the air flow is not one-way, and the average wind speed of the flow is also gentle. For this reason, the partition plate

Even if a V-cut is formed in the part opposite to the cooler 8 or in the upper and lower two parts of the cooler 8 among 17, the air suddenly flows from the storage room 10 to the cooler room 9. Therefore, it is considered that the air flowing at the opening 14 does not undergo any special change.

It's in the presence or absence of the scan Li Tsu Bok, the put that empty basic flowing operation to open Ρ 1 4, there is no change in Te is Rere toゝcooling performance, was seen some of the changes in force ^s. For this reason, the cooling performance can be adjusted according to the presence or absence of the slit and the size of the slit, and the degree of freedom in design can be increased.

 FIG. 10 shows another example of the cooling device of the present invention.

In this example, a cooler 8 is accommodated in a lower portion of the cooling chamber 9, and a fan 11 is arranged above the cooler 8. This is a fan If the pin 11 is arranged, the depth dimension does not need to be particularly large, which is advantageous for miniaturization. Furthermore, a dedicated duct that constitutes a flow path for air to flow between the cooler 8 and the fan 11, and an air duct that guides air from the fan 11 to an outlet < The part roll does not require a BX, so the structure can be simplified and the number of parts PP can be reduced.

 According to the cooling device of the present invention, the same cooling performance can be exerted from the force S whose structure is simpler than that of the ordinary cold air forced circulation system. In addition, the amount of frost on the cooler is small, and it is possible to prevent the food from drying. The cooling device of the present invention can be applied to various uses such as a refrigerator, a freezer, a freezing device, a cooling device for a vending machine, an insulated car, a freezer car, regardless of whether it is for business use or for home use. Since the cooling device of the present invention is advantageous for miniaturization, it is particularly suitable for home refrigerators and refrigerators.

 The cooling device of the present invention can be variously modified in addition to the above examples. For example, in the examples shown in FIGS. 1 and 10, the inside of the storage room 10 is one room,

The interior of 0 can be further divided into a plurality of sections, and rooms with different i-degree conditions, such as a freezing room and a refrigerator room, can be provided. If a dedicated fan and opening are provided corresponding to each of the five ports and each room, it becomes easy to control the temperature of each room independently.o In the above example, The cooler is placed on the back of the box, but it may be placed on the side, or on the back and side.o In the above example, the shape of the opening 14 is circular. However, if the diameter of the opening 14 is larger than the diameter of the fan 11, other shapes are acceptable. It can be a quadrangle, another polygon, or a shape similar to these,

Claims

1. A box composed of a disconnecting member,  A cooler that cools the air by heat exchange,  The inside of the box was divided into two chambers, a cooler room in which the cooler was stored and a storage room in which the object to be cooled was stored, and an opening was formed to connect these two chambers. It is located in the partition plate and the cooler room, and opens the air cooled by the cooler ^ A fan that feeds into the storage room through the mouth,  In the cooling device provided with  The opening P is larger than the diameter of the fan, and when viewed from the direction of the rotation of the rotating fan of the fan, the opening P is equal to the outer periphery of the fij fan. Are arranged so that there is a gap  The area S of the open P is given by the diameter of the fan 1.8 X π (R / 2) 2 ≤ S ≤ 2.5 X π (R, / 2) 2  A cooling device, wherein the distance between the boundary surface on the storage side of the opening P and the m 刖 portion of the marking fan is 0 or more and 0.2 R or less.  2-The cooling device according to claim 1, wherein the fan is disposed above the cooler and is arranged.  3. On the partition plate, make sure that a slit is formed at a position just below the gri cooler, or at a position below the chill cooler. Ffs cooling device according to claim 2 □  4. The cooling device irf o according to O5 Menaga 1 wherein a plurality of combinations of the fan and the BU opening are provided.