JP2575519B2 - Combination refrigerator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial application field) The present invention relates to a combination refrigerator configured by combining a machine room unit and a heat insulation room unit.

(Related Art) In recent years, refrigerators have been increasing in capacity in refrigerators, so that external dimensions have been increased and weight has been significantly increased. For this reason, in the conventional structure in which the machine room in which the compressor and the like are arranged and the heat insulation room for storing food are integrally connected, various obstacles have occurred during transportation, loading into the house, etc. It is. In addition, along with the diversification of lifestyles, there has been a remarkable diversification of user needs for refrigerators, for example, a demand for a refrigerator having only a large freezer compartment or no need for a chilled compartment. Body refrigerators cannot meet a wide variety of needs.

Therefore, conventionally, for example, the machine room unit and the heat insulation room unit as shown in Japanese Utility Model Application Laid-Open No. 53-18675 are configured as independent separate units so that the user can combine them as necessary. The possibility of a combined refrigerator has been studied.

(Problems to be Solved by the Invention) However, in this type of configuration, a machine room unit is provided with a compressor room provided with a compressor and the like and a cooler room surrounded by heat insulating walls. It is necessary to provide a duct for supplying cold air and returning the cool air from the heat insulating room unit and a fan for blowing the cool air, so that there is a problem that the machine room unit tends to be large in size.

Therefore, an object of the present invention is to make the machine room unit as compact as possible while minimizing the overall size while configuring the machine room unit and the heat insulation room unit in a combined form, and various types of devices can be used as necessary. It is an object of the present invention to provide a combined refrigerator in which heat insulating units can be freely combined.

[Composition of the Invention] (Means for Solving the Problems) A combination refrigerator of the present invention comprises a machine room unit having a compressor room accommodating a compressor and a cooler room in which the periphery is insulated and houses a cooler; A heat-insulating chamber unit provided with a storage room for storage and configured as a separate unit independent of the machine room unit, and capable of functioning as a refrigerator by coupling the machine room unit and the heat-insulating chamber unit In, while placing the cooler horizontally in the cooler room of the machine room unit,
A cool air guide duct that guides cool air from the cooler room to the storage room of the heat insulation room unit and a return duct that returns the air of the storage room to the cooler room are provided along the wall of the machine room unit, inside the start end of the cool air guide duct. It is characterized in that a centrifugal fan for cooling air is arranged (the invention of claim 1).

In this case, a defrost heater for heating the cooler arranged in the cooler room may be provided, and the defrost heater may be arranged at least in the vicinity of the air inlet to the cooler room. Invention).

Also, at the bottom of the cooler room, a drainage channel is provided which is connected to a drainage hole for guiding defrost water generated in the cooler room to an evaporating dish provided in the compressor chamber, and the drainage channel and the drainage channel are so closed that the inside thereof is closed. It may be configured to house the porous water absorbing body (the invention of claim 3).

In addition, a porous water absorber is arranged between a plurality of radiating fins constituting a capacitor provided in the capacitor chamber, and the radiating fin is in contact with the porous water absorbing body and has a wind between the radiating fin and the porous water absorbing body. (A fourth aspect of the present invention).

Furthermore, on the front of the machine room unit, an intake grill that takes in outside air for cooling the compressor room and an exhaust grill that discharges hot air that cools the compressor room are provided. It is preferable to provide a wind guide plate for guiding the windshield (the invention of claim 5).

(Operation) According to the first aspect of the present invention, since the cooler is disposed horizontally in the cooler chamber, the vertical dimension can be reduced. Further, since the cool air guide duct and the return duct are provided along the wall surface of the machine room unit, and the centrifugal cold air blower fan is disposed inside the start end of the cool air guide duct, the lateral dimension is also reduced. be able to.

According to the second aspect of the present invention, frost formation in the cooler room can be effectively performed in accordance with the fact that it is likely to occur near the air inlet of the cooler room.

According to the invention of claim 3, the defrosted water is efficiently guided by the capillary phenomenon of the porous water absorbing body in the drainage channel, and during normal operation, the porous water absorbing body freezes and blocks the drain port. Therefore, it is possible to prevent high-temperature air in the compressor chamber from entering the cooler chamber.

According to the fourth aspect of the present invention, the heat generated in the condenser can be used for evaporating the defrosted water, and the air passage between the radiation fin and the porous water absorbing body can be secured by the spacer projection. Can be made more effective.

According to the invention of claim 5, since the hot air cooled in the compressor chamber by the wind guide plate is guided in a direction different from that of the intake grill, the short circuit phenomenon that the hot air is sucked into the compressor chamber again from the intake grill is minimized. Can be prevented.

Embodiment An embodiment of the present invention will be described below with reference to FIGS. 1 to 20.

<I> Basic Configuration In the present embodiment, one refrigerator is configured by vertically combining the machine room unit 1, the heat insulation room unit 2, and the bottom unit 3. The bottom unit 3 is arranged at the lowermost position, the machine room unit 1 is arranged at the uppermost position, and the heat insulation room unit 2 is arranged such that one or a plurality of heat insulating room units are stacked between them. As the adiabatic room unit 2, a freezing room unit 2a having a different internal maintenance temperature and volume,
There are types such as a refrigerator room unit 2b, a chilled room unit 2c, a vegetable room unit 2d, and an ice making room unit 2e. The width and depth of each unit are the same, so that when they are stacked, no step is formed on the appearance. Various insulation room units 2a to 2e are purchased by the user as needed,
They can be freely combined, and the combinations are exemplified as shown in FIGS. 4 (A) to 4 (C). The configuration for enabling such a free combination is as described below.

<II> Machine Room Unit 1 As shown in FIG.
A cooler room 5 and a compressor room 6 are formed by dividing the inside into right and left, and the cooler room 5 is surrounded by a heat insulating material 7 and is insulated from the surroundings.

(1) Cooler room 5 First, the configuration inside the cooler room 5 will be described. Cooler room 5
A heat insulating partition wall 8 is provided at the bottom of the cooling air passage 9, and a cold air passage 9 extending in the front and rear direction is formed at the bottom of the cooling air passage 9. A return duct 10 formed along the back wall 5 a of the cooler room 5 is formed at the rear of the cold air passage 9.
And a front portion of the cool air passage 9 communicates with a suction port 11 formed in the partition wall 8, so that the inside of the return duct 10 and the suction port 11, and furthermore, the inside of the cooler room 5 communicate with each other through the cool air passage 9. It has been done. The cooler 12 has a well-known structure including a refrigerant pipe and a large number of fins integrated with the refrigerant pipe.
Is fixed above. Behind the cooler 12, a cool air guide duct 13 is provided in an arc shape along the back wall of the machine room unit 1 from the back wall 5a of the cooler room 5 to the back wall 6a of the compressor room 6. A centrifugal cold air blowing fan 14 is provided in the unit. The cool air blower fan 14 is driven by a motor (not shown) provided in the back wall 5 a of the cooler room 5, sucks cool air in the cooler room 5 through the bell mouth 15, and blows air into the cool air guide duct 13. It is supposed to.

On the other hand, below the cooler 12, first and second two defrost heaters 16 and 17 each composed of a glass tube heater are provided between the partition wall 8 and the right and left sides in a direction orthogonal to the air flow direction. It is provided to extend in the direction. The first defrost heater 16 is
The second defrost heater 17 is located below the center of the cooler 12 below the front edge of the cooler 12 near the air inlet 11 into the cooler chamber 5. Further, an arc-shaped heat reflection plate 18 is provided below the first defrost heater 16 so that the first
The radiant heat of the defrost heater 16 can be intensively guided to the front corner of the inner surface of the cooler chamber 5 where frost is particularly likely to occur and the front half of the cooler 12 as shown by the broken line in FIG. I have to. Further, below the second defrost heater 17, there is provided a heat reflection plate 19 which is also curved in an arc shape, thereby dissipating radiant heat of the second defrost heater 17 as shown by a broken line in FIG. Cooler 12
Can be intensively guided to the rear half of the vehicle and the vicinity of the bell mouth 15 of the cool air guide duct 13.

As shown in FIG. 3, the bottom of the cooler chamber 5 has a gentle slope which becomes lower toward the center, and a circular drain hole 20 for discharging defrost water is provided at the bottom. A drain passage 21 formed and connected to the adjacent compressor chamber 6 is connected to the drain hole 20 in an inclined manner with the compressor chamber 6 slightly lowered. The drainage channel 21 is composed of a circular water receiving portion 21a and a gutter-like portion 21b following the circular water receiving portion 21a.
2 are stored. The porous water absorbing body 22 is formed, for example, in a state where hydrophilic synthetic fibers are bundled.
As shown in the figure, the drainage channel 21 has a shape following the shape of the drainage channel 21, and is housed in the drainage channel 21 so as to be in contact with the drainage port 20 and close the inside thereof. Above the drain hole 20, a heat shielding plate 23 for shielding radiant heat from the defrost heaters 16 and 17 is provided as necessary.

(2) Compressor Room 6 Next, the configuration of the compressor room 6 will be described.

Inside the outer wall 4 is a condenser 2
4. The compressor 25 and the cooling fan 26 are arranged in the front-back direction. The cooling fan 26 is of a centrifugal type, and a bell mouth 27a of a casing 27 covering the cooling fan 26 faces the compressor 25, and a discharge port 27b is formed at the upper right side of the compressor chamber 6. An exhaust duct 28 is connected to the discharge port 27b, extends forward along the inner surface of the outer wall 4 on the right side, extends from here to the left, and is connected to an exhaust grill 29 provided on the upper front surface of the outer wall 4.

As shown in FIG. 7, an exhaust grill 29 is provided on the front surface of the outer wall 4.
In addition, an intake grill 30 is also provided. The intake grill 30 is provided at a lower portion on the right side of the front surface of the outer wall 4 corresponding to the compressor room 6, so that outside air can be sucked into the compressor room 6. As shown in FIG. 8, each of the vanes 30a of the intake grill 30 has a front side facing downward, so that the outside air for cooling in the compressor chamber 6 is sucked from below. On the other hand, the exhaust grill 29
Is formed so as to extend over both the cooler room 5 and the compressor room 6 in the upper part of the front surface of the outer wall 4 from the viewpoint of design, but the hot air discharged from the exhaust grill 29 is again supplied to the intake grill 30. In order to prevent the air from being sucked as much as possible, a closed portion 29a is formed in the right half of the portion overlapping with the intake grill 30, and each vane 29b has a front side facing upward as shown in FIG. Is discharged upward. Further, in the exhaust grill 29, as shown in FIG. 1, a wind guide plate 29c is provided so as to guide the hot air in a leftward direction which is a direction different from that of the intake grill 30.

As shown in FIG. 9, the condenser 24 has a configuration in which a number of radiating fins 31 are combined with a meandering refrigerant pipe 32, and the air passage between the radiating fins 31 extends in the front-rear direction. It is located behind. As shown in FIGS. 10 and 11, a large number of columnar spacer protrusions 33 are formed on
A water absorption plate 34, which is a porous water absorption body, is provided in the rear half (windward side) between 31. Each of these water absorption plates 34
For example, a non-woven fabric of polyester fiber is impregnated with a small amount of a phenol resin to perform a hydrophilic treatment, and then punched and formed by a press so as to form a notch or the like for allowing the refrigerant pipe 32 to pass therethrough. As shown in the drawing, the lower end reaches the inside of the evaporating dish 35 arranged below the condenser 24, and the upper part projects backward from the evaporating dish 35.

In order to manufacture the condenser 24, as shown in FIG. 13, a U-shaped bent refrigerant pipe 32 is passed through the pipe through hole 31a of the radiation fin 31, and thereafter, as shown in FIG. The refrigerant pipe 31 is bent in a meandering shape. At this time, before bending the refrigerant pipe 32 in a meandering shape, if each water absorbing plate 34 is inserted so as to be pressed between the spacer protrusions 33 of the heat radiation fin 31, the water absorption plate 34 group and the heat radiation fin 31 group can be connected. It can be handled integrally, and the manufacture of the capacitor 24 is simplified.

(3) Control operation unit The above-described cooler 12, condenser 24, compressor 25 and the like arranged in the machine room unit 1 are connected by a refrigerant pipe (not shown). It cools and liquefies in the condenser 24, vaporizes it in the cooler 12 to perform a cooling action, and then configures a well-known compression refrigeration cycle in which the gasified refrigerant is returned to the compressor 25 and compressed again. . Also, although not shown, the compressor 25 is driven by an inverter device having a variable frequency output, and is operated when the temperature in any of the heat insulation chamber units 2 exceeds a maintenance temperature set by a user. As the number of the adiabatic chamber units 2 exceeding the set maintenance temperature increases, the inverter device outputs a higher frequency and sets the compressor 25 to the high capacity operation. For this purpose, a temperature sensor for detecting the temperature in the storage room is provided in each of the heat insulation chamber units 2, and a control circuit and a motor drive circuit for receiving a temperature signal from the temperature sensor are provided at a lower front portion inside the machine room unit 1. Embedded circuit board 36
(See FIG. 2), and an operation panel 36a for the user to operate is also provided at the lower front of the machine room unit 1 (see FIG. 7).

(4) Duct Structure As described above, the return duct 10 is provided on the back wall 5a of the cooler room 5 made of a heat insulating material, and the cool air guide duct 13 extending in an arc shape to the back wall 6a of the compressor room 6. Are provided in a buried state. Each of the ducts 10 and 13 extends downward and opens in an oval shape at the rear edge of the lower surface of the outer wall 4. As shown in FIG. 15, the duct opening 37 has a stepped shape in which a first opening 37a and a second opening 37b having a smaller opening are connected vertically.

<III> Heat Insulation Room Unit 2 Each heat insulation room unit 2 is configured by pivotally supporting a heat insulation door 39 rotatably on a heat insulation box 38 having an open front surface.
At 38a, a cool air guide duct 40 and a return duct 41 are provided at positions corresponding to the cool air guide duct 13 and the return duct 10 of the machine room unit 1 vertically (see FIG. 5). Duct openings 37 having the same structure as that of the machine room unit 1 are provided at the upper and lower ends of each of the ducts 40 and 41, and as shown in FIG. It is connected to a duct and a return duct. As a result, as shown in FIG. 5, the cool air guide duct 13 and the return duct 10 of the machine room unit 2 are vertically communicated with the cool air guide duct 40 and the return duct 41 of each heat insulating room unit 2 to supply the cool air and return the cool air. The two ducts for the two. The above-described duct connector 42 is provided with an inner periphery 43 fitted into the first opening 37a on the inner periphery side of the duct opening 37.
And an outer cylinder 44 fitted into the second opening 37b on the outer peripheral side of the duct opening 37.
The outer cylinder 44 is formed of a soft compressive heat insulating material such as a sponge.

In addition, a heat insulating plug 45 shown in FIG. 16 is fitted in the duct opening 37 below the heat insulating chamber unit 2 located at the lowermost stage. The heat insulating plug 45 is fitted into the second opening 37b of the duct opening 37 and fixed by a screw 46, for example.
And a sealing cylinder 45b integrated with the substrate 45a and fitted into the first opening 37a, and a plug body 45c located on the inner periphery of the sealing cylinder 45b and entering the duct. The seal cylinder 45b is made of a soft compressive heat insulating material such as sponge, and the plug body 45c is made of a hard heat insulating material such as urethane foam.

On the other hand, a cool air discharge port 47 communicating with the cool air guide duct 40 is formed in an upper portion of an inner surface of the back wall portion 38a of the heat insulating box 38 of the heat insulating chamber unit 2, and a cool air inlet 48 communicating with the return duct 41 is formed in a lower portion of the inner surface. Are formed. The cool air discharge port 47 is provided with, for example, an electric damper 49 for driving a pulse motor (not shown) so as to open the damper plate 49a from a fully closed state to a predetermined maximum opening angle. Cold air outlet 47 and electric damper of each heat insulation room unit 2
Regardless of the type, the common shape of the parts is achieved in any type, but the set maximum opening angle of the electric damper 49 differs depending on the type of the heat insulation chamber unit 2. As a result, the insulated room unit 2 in which the maintenance temperatures set as in the freezing room unit 2a and the refrigerating room unit 2b greatly differ.
Parts can be shared between the two. Further, a ceiling cover 50 is attached to an upper portion of the inner surface of the heat insulating box 38 so as to cover the cool air discharge port 47 and the electric damper 49, and a cool air blowing grill 51 for blowing cool air obliquely downward is formed on the ceiling cover 50. Have been.

The cold air inlet 48 is provided with a cool air suction grill 52 at the lower portion of the inner surface of the heat insulating box 38 as shown in FIG. The cool air suction grill 52 includes a baffle plate 52a that rises substantially vertically from the bottom surface so as to prevent the cool air in the storage room from naturally flowing into the return duct 41 when the cool air blowing fan 14 is stopped. I have.

At the front corners of the upper and lower surfaces of the heat insulating box 38, a concave portion 53 is formed as shown in FIG. 19 (only the upper surface is shown), and a pair of hinge members 54 are fixed so as to be embedded therein. . The hinge member 54 has a hinge pin 5 attached to the mounting plate 54a.
4b is integrated with hinge pins 54b located above and below
By fitting the hinge hole of the heat insulating door 39 to the heat insulating door 39, the heat insulating door 39 can be opened and closed. Also, insulation box 38
The upper surface of the door switch is also formed with a recess 55 as shown in FIG.
56 are installed. And, although not shown, the insulation box
At the front end of the lower surface of 38, a heat insulation unit 2 located below
An escape recess 57 for allowing the upper half of the door switch 56 to escape is formed.

<IV> Bottom unit 3 An outline of the bottom unit 3 is shown in FIG. The heat insulating chamber unit 2 can be stacked on the upper surface thereof, and casters 58 are attached to the four corners of the lower surface.

<V> Regarding the operation and effect of the embodiment The internal temperature rises in any of the heat-insulating chamber units 2 that are desirably combined, and when this exceeds the set maintenance temperature, the compressor 25 is operated to cool the refrigerant. It vaporizes in the vessel 12 and exhibits a cooling action. At the same time,
Since the cool air blower fan 14 is operated, the cool air generated by the cooler 12 is sent out into the cool air guide duct 13 by the cool air blower fan 14. Further, the cool air is supplied to the cool air guide duct 4 formed on the back wall 38a of the heat insulating box 38 of the heat insulating chamber unit 2.
0, which passes through the cool air discharge port 47 opened by the electric damper 49, and cools the outlet grill of the ceiling cover 50.
It flows into the storage room from 51 and cools the stored items. The air used for cooling the storage in the storage room is sucked into the return duct 41 from the lower part of the storage room through the cool air inlet 48 formed in the back wall, and the return of the machine room unit 1 is performed through the return duct 41. It is returned from the duct 10 into the cooler room 5. Then, when the storage room is cooled so as to be lower than the set maintenance temperature and this is detected by the temperature sensor, the opening degree of the electric damper 49 is gradually reduced to restrict the inflow of cool air, and all the heat insulation chamber units When the inside is sufficiently cooled, the compressor 25 is stopped. According to this configuration, since the cooler 12 is disposed horizontally in the cooler chamber 5, the vertical dimension can be reduced. Further, a cool air guide duct 13 and a return duct 10 are provided along the back wall surface of the machine room unit 1, and
Since the centrifugal-type cool air blower fan 14 that can secure a sufficient amount of air flow even if the axial size is short is arranged inside the starting end, the horizontal size can also be reduced. Thus, the entire machine room unit 1 can be reduced in size, and the entire refrigerator can be reduced in size.

Now, when the cooling operation is repeated, frost develops in the cooler room 5. Therefore, in this embodiment, the compressor 25
When the operation time reaches a predetermined time, the compressor 25 is stopped and the electric dampers 49 of the heat insulation chamber units 2 are closed, and the defrost heaters 16 and 17 are energized to perform defrost in the cooler chamber 5. Do. At this time, the cool air blowing fan 14 is rotated in the direction opposite to the normal cool air blowing operation. Thereby, since all the electric dampers 49 of the heat insulation chamber units 2 are closed, the air circulates weakly in the cooler room 5 and the air temperature in the cooler room 5 becomes uniform.

By the way, the amount of frost generated in the cooler room 5 tends to be particularly large in the vicinity of the suction port 11 from which the air from the heat insulation room unit 2 returns, that is, in the front part of the cooler room 5. In view of this point, in the present embodiment, the rod-shaped first defrost heater 16 is disposed near the air inlet 11 of the air into the cooler chamber 5 and extends in a direction perpendicular to the air flow direction. Therefore, the frosted portion can be heated particularly well, and defrosting in the cooler room 5 can be effectively performed. Moreover, in the present embodiment, the heat reflecting plate 18 is provided, and the front edge of the heat reflecting plate 18 is curved in an arc shape. Therefore, the radiant heat of the first defrost heater 16 is indicated by a broken line in FIG. As shown in the figure, the inner surface of the cooler room 5 can be guided intensively to the front corner where frost is particularly likely to occur and the front half of the cooler 12, so that defrosting can be performed more efficiently. In particular, in the present embodiment, in consideration of the fact that the cooler 12 is relatively long in the front and back, a second defrost heater 17 is provided below the center of the cooler 12 and the second defrost heater 17 is provided. The sub-reflector 19 whose front is curved in an arc shape is provided below the radiator, so that the radiant heat of the second defrost heater 17 is transferred to the rear half of the cooler 12 and the vicinity of the bell mouth 15 of the cool air guide duct 13. It is possible to guide, and eventually, it becomes possible to uniformly defrost the inside of the cooler room 5.

When the above-described defrosting operation is performed, the frozen porous water absorbing body 22 near the drain port 20 is defrosted by the heat of the defrost heaters 16 and 17, and the frozen portion is thawed and defrosting caused by melting of frost is performed. The frost flows from the drain hole 20 into the water receiving portion 21a of the drain channel 21,
Here, water is absorbed by the porous water absorbing body 22, penetrates the inside thereof by capillary action, and is stored in the evaporating dish 35 in the compressor chamber 6. As described above, the defrost water is sent to the evaporating dish 35 by utilizing the capillary phenomenon of the porous water absorbing body 22, so that the defrost water is reliably sent to the evaporating dish 35 even if the inclination of the drainage channel 21 is gentle. In this case, the vertical dimension of the machine room unit 1 can be reduced. In addition, after the defrosting operation is completed, a considerable amount of defrost water is accumulated in the porous water absorbing body 22, so that the volume of the evaporating dish 35 can be reduced accordingly, and the mechanical This contributes to downsizing of the room unit 1. Further, since the porous water absorbing body 22 is housed so as to close the inside of the drainage channel 21 and the drainage port 20, it is possible to prevent the high temperature air in the compressor room 6 from entering the cooler room 5 and to prevent the air seal from being released. It also works.

The defrost water flowing into the evaporating dish 35 is sucked up by a water absorbing plate 34 provided between the radiation fins 31 of the condenser 24 by capillary action. And the water absorption plate is formed by the radiation fins 31.
Since the cooling air flows between the heat radiation fins 31 and the cooling fins 31, the defrost water contained in the water absorbing plate 34 evaporates quickly, and the defrost water is sucked up from the evaporating dish 35 one after another and evaporated. In this case, since each radiation fin 31 is provided with a spacer projection 33 to secure an air passage between the radiation fin 31 and the water absorbing plate 4, it is possible to improve the evaporation efficiency of the defrost water as well as the original radiation fin.
The effect of 31 can also be fully exhibited.

Further, during the operation of the compressor 25, the cooling fan 26 is operated, the outside air is sucked from the intake grill 30 to cool the inside of the compressor room 6, and the hot air that has cooled the inside of the compressor room 6 is discharged forward from the exhaust grill 29. You. In this case, the hot air that has cooled the inside of the compressor chamber 6 is guided by the wind guide plate 29c of the exhaust grill 29 in a direction different from that of the intake grill 30, so that the hot air is sucked into the compressor chamber 6 again from the intake grill 30. Short circuit can be prevented. Moreover, each vane of the intake grill 30
30a so that the front side faces downward, and exhaust grill 2
Closed part 29a in the right half of the part that overlaps with the intake grill 30 of 9
Is formed, and the front side of each vane 29b is directed upward, so that the short circuit can be more reliably prevented.

In this embodiment, the heat insulation box of the heat insulation chamber unit 2 is particularly used.
A suction grille 52 is provided at the cold air suction opening 48 of the 38, and a baffle plate 52a that rises substantially vertically from the bottom surface is provided on the cooling suction grille 52, so that cool air in the storage room naturally flows into the return duct 41. This can prevent the cooling efficiency from being lowered. Further, since this baffle plate portion 52a is in close contact with the heat insulating plug 45 as shown in FIG. 16,
It also works effectively with air seals.

Further, in this embodiment, the duct connector 42 is formed in a double cylindrical shape from the inner cylinder 43 and the outer cylinder 44, and the inner cylinder 43 is formed of a hard heat insulating material, and the outer cylinder 44 is formed of a soft compressive heat insulating material. Therefore, the inner cylinder 43 is mainly responsible for heat insulation, and the outer cylinder 44 is mainly responsible for air seals, so that both heat insulation and air seals can be effectively achieved by one component.

The present invention is not limited to the embodiment described above and shown in the drawings. For example, modifications can be made without departing from the scope as follows.

(B) In the defrosting water drainage channel, the cross-sectional area of the gutter part is made larger than the cross-sectional area of the water receiving part.
It may be shaped as shown in FIG. Thus, the water supply capacity is increased and the water storage capacity is increased, so that the size of the evaporating dish can be reduced accordingly.

(B) The operation panel 36a of the control unit may be provided not only in the machine room unit 1 but also in the heat insulation room unit 2 as shown in FIG. In the case of this structure, the circuit board 36 in the machine room unit 1 and the operation panel 36a may be connected by the connector 60.

(C) A cool air intake grill provided in the heat insulation room unit 2
As shown in FIG. 23, if the two baffle portions 61a and 61b are provided so as to extend from above and below, as shown in FIG. 23, when the cool air blower fan stops, cool air in the storage room naturally flows into the return duct 41. Can be more reliably prevented.

(D) If the water absorbing plate 34 provided between the heat radiation fins 31 of the capacitor 24 is made of porous ceramic, the durability is further improved.

(E) The heat reflection plate 18 disposed at the bottom of the cooling chamber 5 may be provided so as to cover the entire upper surface of the partition wall 8.

(F) The cool air guide duct and the return duct may be provided on the side wall of each unit. If these two ducts are provided so as to be parallel in the same heat insulating wall,
It is possible to reduce the thickness of the heat insulating wall not provided with the heat insulating wall.

(G) As a defrost heater, even if it is not a glass tube heater,
A pipe heater disposed around the cooler may be used.

In addition, the present invention can be variously modified without departing from the gist, for example, the bottom unit is not necessarily required and may be omitted.

[Effects of the Invention] As described above, according to the refrigerator of the present invention, the machine room unit is made as compact as possible while the machine room unit and the heat insulation room unit are combined to form a compact type. This has the effect of enabling the conversion.

Further, according to the second aspect of the present invention, frost formation in the cooler room can be effectively performed in accordance with the fact that the frost is likely to be generated in the vicinity of the air inlet into the cooler room. Item 3
According to the invention, the defrost water is efficiently guided by the porous water absorbing body in the drainage channel, and it is possible to prevent the high-temperature air in the compressor room from flowing back into the cooler room during the normal operation.

Further, according to the invention of claim 4, the heat generated in the condenser can be used for evaporation of the defrost water, and the passage of the evaporating wind can be secured, so that the evaporation of the defrost water can be more effectively performed. According to the fifth aspect of the present invention, a short circuit in which hot air is sucked again from the intake grill into the compressor chamber can be prevented as much as possible.

[Brief description of the drawings]

1 to 20 show an embodiment of the present invention. FIG. 1 is a cross-sectional view of a machine room, FIG. 2 is a vertical side view, FIG. 3 is a vertical front view, and FIG. FIG. 5 is a schematic longitudinal sectional front view for explaining a configuration of a duct, FIG. 6 is a perspective view of a porous water absorbing body, and FIG. 7 is a front view of a machine room. , FIG. 8 is a partial sectional view taken along the line VIII-VIII in FIG. 7, FIG. 9 is a perspective view of the capacitor, FIG. 10 is a partial side view of the same, FIG. Is a longitudinal side view of the cooler and the evaporating dish, FIG. 13 is a plan view of the cooler during the manufacturing process, FIG. 14 is a plan view of the completed cooler, FIG.
FIG. 15 is a partial longitudinal sectional view showing the structure of the connecting portion of the duct, and FIG.
The figure is a partial longitudinal sectional view showing the state where the heat insulating plug is attached, FIG.
FIG. 18 is a longitudinal sectional view of the heat insulating chamber unit showing the cool air discharge port, FIG. 18 is a vertical sectional view of the heat insulating chamber unit showing the cool air suction port, and FIG. FIG. 20 is a perspective view of the bottom unit. 21st
The figure is a perspective view showing a modified example of the porous water absorbing body, FIG. 22 is a front view showing a modified example in which an operation panel is provided in a heat insulating chamber unit,
FIG. 23 is an enlarged vertical sectional view showing a modification of the cool air suction grille. In the drawing, 1 is a machine room unit, 2 is a heat insulation room unit, 5
Is a cooler room, 6 is a compressor room, 10 is a return duct, 12 is a cooler, 13 is a cool air guide duct, 16 and 17 are defrost heaters, 20 is a drain hole, 21 is a drain passage, and 22 is a porous water absorbing body. ,twenty four
Is a condenser, 25 is a compressor, 26 is a cooling fan, 29
Is an exhaust grill, 29c is a wind guide plate, 30 is an intake grill, 31 is a radiation fin, 33 is a spacer projection, 34 is a water absorbing plate (porous water absorbing body), 35 is an evaporating dish, 36 is a circuit board, 36a is an operation panel , 42 is a duct connected body, 43 is an inner cylinder, 44 is an outer cylinder, 45 is a heat insulating plug, 47 is a cool air outlet, 48 is a cool air inlet, 49 is an electric damper, 52 is a cool air intake grill, and 52a is a baffle plate , 55 is a recess, 56 is a door switch, and 57 is an escape recess.

──────────────────────────────────────────────────続 き Continuation of the front page (51) Int.Cl. ⁶ Identification code Agency reference number FI Technical display location F25D 21/14 F25D 21/14 S 23/00 304 23/00 304

Claims (5)

(57) [Claims] 1. A machine room unit having a compressor room accommodating a compressor and a cooler room in which the periphery is insulated and a cooler is accommodated, and a storage room for accommodating foods and the like, and is independent of the machine room unit. An insulation room unit configured as a separate unit, wherein the machine room unit and the insulation room unit are combined so as to be able to function as a refrigerator. A cooler guide duct for guiding cool air from the cooler room to the storage room of the heat insulation room unit and a return duct for returning the air of the storage room to the cooler room are arranged in the machine room unit. A combination refrigerator provided along a wall surface, wherein a centrifugal fan for cooling air is disposed inside a start end of the cooling air guide duct. 2. A defrost heater for heating a cooler disposed in a cooler room is provided, and the defrost heater is disposed at least near a suction port of air into the cooler room. The combination refrigerator according to claim 1, wherein: 3. A drainage channel is provided at the bottom of the cooler chamber to guide defrost water generated in the cooler chamber to an evaporating dish provided in the compressor chamber. 3. The combination refrigerator according to claim 1, wherein a water absorber is stored. 4. A porous water absorber is arranged between a plurality of cooling fins constituting a condenser, and the cooling fin is in contact with the porous water absorber and wind between the cooling fin and the porous water absorber. 4. The combination refrigerator according to claim 1, further comprising a spacer projection for securing a passage. 5. An intake grill for taking in outside air for cooling the compressor room, on a front surface of the machine room unit.
An exhaust grill for discharging hot air cooled in the compressor chamber is provided, and the exhaust grill is provided with a wind guide plate for guiding the hot air in a direction different from that of the intake grill. 4. The combination refrigerator according to any one of 4.