CN110131958A - refrigerator - Google Patents

Abstract

The present invention provides a refrigerator in which the space of a machine room is reduced and noise is suppressed. The refrigerator has a refrigerating temperature zone chamber, a freezing temperature zone chamber, an adiabatic partition wall separating the refrigerating temperature zone chamber and a freezing temperature zone chamber, a compressor for ejecting refrigerant, and a radiator for dissipating the heat of the refrigerant to the outside air, and It is equipped with a first evaporator that absorbs heat from the room in the refrigeration temperature zone, a first gas-liquid separator that prevents liquid refrigerant in the refrigerant flowing out of the first evaporator from flowing into the compressor, and a second gas-liquid separator that absorbs heat in the room from the freezing temperature zone. The second evaporator, the second gas-liquid separator that prevents the liquid refrigerant in the refrigerant flowing out of the second evaporator from flowing into the compressor, and the refrigerant from the first gas-liquid separator and the refrigerant from the second gas-liquid separator The refrigerant confluence part of the refrigerant of the device is buried in the heat insulating material so that the refrigerant flows from the second gas-liquid separator to the refrigerant confluence part side and does not flow from the refrigerant confluence part to the second gas-liquid separator side. check valve.

Description

refrigerator

technical field

The present invention relates to refrigerators.

Background technique

At present, as a structure of the freezing cycle of a refrigerator, there is a refrigerator in which a refrigerating evaporator for cooling a storage room in a refrigerating temperature zone and a freezing evaporator for cooling a storage room including a freezing temperature zone are connected in parallel in time series. Alternately cool the pantry. In such a refrigerator, generally, the pressure of the evaporator for freezing (for example -25°C) is lower than the pressure of the evaporator for refrigeration (for example -10°C), so the refrigerant is likely to evaporate toward the refrigerating evaporator from the relationship of pressure. Device reverse flow. Therefore, the backflow of the refrigerant is prevented by providing a check valve in the refrigeration cycle on the side of the refrigeration evaporator. For example, in Patent Document 1, the installation position of the check valve is provided in the machine room outside the heat insulating box.

prior art literature

Patent Document 1: Japanese Patent No. 3696064

However, if it is installed in the machine room as described above, if the check valve is not installed vertically, the effect will be small, and there is a problem that the space of the machine room will increase due to this characteristic. In addition, since a part of the check valve is formed with a small diameter, there is a problem that sound is emitted from the check valve.

Contents of the invention

An object of the present invention is to provide a refrigerator in which noise is suppressed while realizing space saving of a machine room.

The refrigerator of the present invention made in view of the above-mentioned problems has a refrigerating temperature zone chamber, a freezing temperature zone chamber, an insulating partition wall separating the refrigerating temperature zone chamber and the freezing temperature zone chamber, and a compressor for discharging refrigerant. , and a radiator that dissipates the heat of the refrigerant to the outside air. The above-mentioned refrigerator is also equipped with: a first capillary tube that decompresses the refrigerant; a first evaporator that absorbs heat from the above-mentioned refrigeration temperature zone; The refrigerant flowing out of the device returns to the first suction pipe of the above-mentioned compressor; the first gas-liquid separator that prevents the liquid refrigerant in the refrigerant flowing out of the above-mentioned first evaporator from flowing into the above-mentioned compressor; the device that decompresses the refrigerant The second capillary tube; the second evaporator that absorbs heat from the above-mentioned freezing temperature zone; the second suction pipe that returns the refrigerant flowing out of the above-mentioned second evaporator to the above-mentioned compressor; prevents the refrigerant flowing out of the above-mentioned second evaporator The liquid refrigerant in the above-mentioned compressor flows into the second gas-liquid separator; and the refrigerant confluence part connecting the refrigerant from the first gas-liquid separator and the refrigerant from the second gas-liquid separator, in In the above-mentioned refrigerator, a check valve is embedded in the heat insulating material, and the check valve allows the refrigerant to flow from the second gas-liquid separator to the side of the refrigerant junction and prevents the refrigerant from flowing from the refrigerant junction to the side of the refrigerant junction. The above-mentioned second gas-liquid separator side flow.

The effects of the invention are as follows.

According to the present invention, it is possible to provide a refrigerator in which noise is suppressed while realizing space saving of a machine room.

Description of drawings

Fig. 1 is a front view of the refrigerator of the embodiment.

Fig. 2 is a cross-sectional view along line A-A of Fig. 1 .

Fig. 3 is a B-B sectional view of Fig. 2 .

Fig. 4 is a schematic diagram showing a refrigeration cycle structure in the refrigerator of the embodiment.

Fig. 5 is a C-C sectional view of Fig. 2 .

Fig. 6 is an example of the temperature of the straw in the refrigerator of the embodiment.

Explanation of symbols

1—refrigerator, 2—refrigerator, 2a, 2b—refrigerator door, 3—ice maker, 4—upper freezer, 5—lower freezer, 3a, 4a, 5a—freezer door, 6—vegetable room, 6a—vegetable compartment door, 7—freezer compartment (collectively referred to as 3, 4, and 5), 8a—R evaporator chamber (evaporator chamber for refrigeration), 8b—F evaporator chamber (evaporator chamber for freezing), 9a— R fan (refrigerating fan), 9b—F fan (refrigerating fan), 10—insulated box, 10a—outer box, 10b—inner box, 11—refrigerating room air duct, 11a—refrigerating room outlet, 12— Freezer air duct, 12a—jet outlet of freezer, 14a—R evaporator (evaporator for refrigeration), 14b—F evaporator (evaporator for freezing), 15a, 15b—return port of refrigerator, 16—door hinge cover , 17—refrigerator return port, 18—vegetable room return air path, 18a—vegetable room return port, 21—radiant heater, 22a, 22b—drain outlet, 23a, 23b—launder, 24—compressor, 27a— R drain pipe, 27b—F drain pipe, 28, 29, 30—insulation partition wall, 31—control substrate, 32—evaporating dish, 35—chilled room, 39—mechanical room, 40a—R evaporator temperature sensor, 40b —F evaporator temperature sensor, 41—refrigerator temperature sensor, 42—freezer temperature sensor, 43—vegetable room temperature sensor, 45—launder temperature sensor, 50a, 50b—radiator, 51—dryer, 52—three Through valve (refrigerant control mechanism), 53a—capillary tube for refrigeration (decompression mechanism), 53b—capillary tube for freezing (decompression mechanism), 54a—gas-liquid separator for refrigeration, 54b—gas-liquid separator for freezing, 55a —Suction pipe for refrigeration, 55b —Suction pipe for freezing, 56—Check valve, 57—Refrigerant confluence section, 58—Cooling air passage for vegetable compartment, 59a, 59b—Heat exchange section, 101—Heater in trough section, 102— Drain pipe upper heater, 103—drain pipe lower heater.

Detailed ways

Hereinafter, the refrigerator which implements this invention is demonstrated. Fig. 1 is a front view of the refrigerator of the embodiment, Fig. 2 is a sectional view along A-A of Fig. 1 , and Fig. 3 is a sectional view along B-B of Fig. 2 . The cabinet 10 of the refrigerator 1 has storage compartments in this order from above, including a refrigerating compartment 2 , an ice making compartment 3 arranged side by side, an upper freezer compartment 4 , a lower freezer compartment 5 , and a vegetable compartment 6 . Refrigerator 1 includes doors for opening and closing the openings of the respective storage compartments. These doors are left and right divided rotary refrigerator compartment doors 2a, 2b for opening and closing the opening of the refrigerator compartment 2, and drawers for opening and closing the openings of the ice making compartment 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6, respectively. Type ice-making compartment door 3a, upper freezer compartment door 4a, lower freezer compartment door 5a, vegetable compartment door 6a. Hereinafter, ice making compartment 3 , upper freezer compartment 4 , and lower freezer compartment 5 are collectively referred to as freezer compartment 7 .

The freezer compartment 7 is basically a storage room where the inside of the box is set to a freezing temperature zone (less than 0°C), for example, an average of about -18°C, and the refrigerator compartment 2 and the vegetable compartment are set to a freezer temperature zone (above 0°C). For example, the refrigerator room 2 is a storage room with an average temperature of about 4°C, and the vegetable room is a storage room with an average temperature of about 7°C.

The door 2a is provided with an operation unit 26 for operating the temperature setting in the box. In order to fix the refrigerator 1 and the doors 2a and 2b, door hinges (not shown) are provided on the upper and lower parts of the refrigerator compartment 2, and the upper door hinges are covered by a door hinge cover 16.

As shown in FIG. 2 , a foam insulation material (such as foamed polyurethane) is filled between the outer box 10 a and the inner box 10 b to form a box body 10 , and the box body 10 is used to separate the outside and the inside of the refrigerator 1 . In the box body 10, a plurality of vacuum heat insulating materials 25 are attached between the outer box 10a made of steel plate and the inner box 10b made of synthetic resin in addition to the foam heat insulating material. The upper freezer compartment 4 and the ice making compartment 3 are separated from the refrigerating compartment 2 by an insulating partition wall 28 , and the lower freezer compartment 5 and the vegetable compartment 6 are separated by a thermally insulating partition wall 29 . In addition, an insulating partition wall 30 is provided on the front side of each storage compartment of the ice-making compartment 3, the upper freezer compartment 4, and the lower freezer compartment 5, so as to prevent the air in the freezer compartment 7 from entering the compartment through the gaps of the doors 3a, 4a, and 5a. The outside leaks out, and the air outside the box invades into each storage room.

A plurality of door shelves 33a, 33b, 33c and a plurality of shelves 34a, 34b, 34c, 34d are provided on the inner sides of the doors 2a, 2b of the refrigerator compartment 2 to divide into a plurality of storage spaces. The freezer compartment 7 and the vegetable compartment 6 are equipped with an ice maker container (not shown) that is pulled out integrally with the doors 3a, 4a, 5a, and 6a, an upper freezer compartment container 4b, a lower freezer compartment container 5b, and a vegetable compartment. Container 6b.

Above the heat-insulating partition wall 28, a chilled compartment 35 set to a temperature range lower than that of the refrigerator compartment 2 is provided. The chilled compartment can be switched to a refrigerated temperature range of, for example, about 0 to 3° C. by controlling the R evaporator 14 a and R fan 9 a described later, and a heater (not shown) installed in the heat insulating partition wall 28 . The model of the model and the model of the freezing temperature zone, such as about -3 ~ 0 ℃.

The R evaporator 14a serving as an evaporator for refrigeration is provided in the R evaporator chamber 8a serving as an evaporator chamber for refrigeration provided substantially at the back of the refrigerator compartment 2 . The air that exchanges heat with the R evaporator 14a and becomes low temperature is sent to the refrigerating room 2 through the refrigerating room air duct 11 and the refrigerating room outlet 11a by the R fan 9a as a refrigerating fan installed above the R evaporator 14a. The inside of the refrigerator compartment 2 is cooled. The air sent to the refrigerator compartment 2 returns to the R evaporator chamber 8a from the refrigerator compartment return ports 15a and 15b (see FIG. 3 ), and is cooled by the R evaporator 14a again.

The F evaporator 14b which is an evaporator for freezing is provided in the F evaporator chamber 8b which is an evaporator chamber for freezing which is provided in the substantially back part of the freezer compartment 7 . The air that exchanges heat with the F evaporator 14b and becomes low-temperature is sent to the freezer compartment 7 through the freezer compartment air duct 12 and the freezer compartment discharge port 12a by the F fan 9b as a cooling fan located above the F evaporator 14b, The inside of the freezer compartment 7 is cooled. The air sent to the freezer compartment 7 returns to the F evaporator chamber 8b from the freezer compartment return port 17, and is cooled by the F evaporator 14b again.

In the refrigerator 1 of the present embodiment, the vegetable compartment 6 is also cooled by the air that has become low temperature in the F evaporator 14b. In the F evaporator 14b, the air in the F evaporator chamber 8b of low temperature is sent to the vegetable chamber 6 by the F fan 9b through the vegetable chamber air path (not shown), the vegetable chamber damper (not shown), and the vegetable chamber 6 cooling inside. When the vegetable compartment 6 is at a low temperature, cooling of the vegetable compartment 6 is suppressed by closing the vegetable compartment damper. In addition, the air sent to the vegetable compartment 6 is returned to the lower part of the F evaporator compartment 8b through the vegetable compartment cool air return duct 18 from the cold air return portion 18a provided on the lower front side of the heat insulating partition wall 29 on the side of the vegetable compartment.

The refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, and the vegetable compartment temperature sensor 43 are respectively provided on the back side of the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, and the R evaporator is provided on the top of the R evaporator 14a. F evaporator temperature sensor 40a, F evaporator temperature sensor 40b is provided on the top of F evaporator 14b, utilizes above-mentioned sensor to detect the temperature of refrigerator compartment 2, freezer compartment 7, vegetable compartment 6, R evaporator 14a, and F evaporator 14b . Furthermore, an outside air temperature sensor 37 for detecting the temperature and humidity of outside air (outside air) is provided inside the door hinge cover 16 on the top of the refrigerator 1 . As other sensors, there are door sensors (not shown) for detecting the open and closed states of the doors 2a, 2b, 3a, 4a, 5a, and 6a, and a partition temperature sensor 100 as a partition temperature detection mechanism described later. .

As shown in FIGS. 2 and 3 , a defrosting heater 21 for heating the F evaporator 14 b is provided in the lower portion of the F evaporator chamber 8 b. The defrosting heater 21 is, for example, an electric heater of 50W to 200W, and is a radiant heater of 150W in this embodiment. The defrosting water (melted water) generated during the defrosting of the F evaporator 14b falls to the flow tank 23b provided at the lower part of the F evaporator chamber 8b, and then flows to the compressor 24 through the drain port 22b and the F drain pipe 27b. The upper evaporating dish 32 is drained.

In addition, the defrosted water generated during the defrosting of the R evaporator 14a falls to the flow tank 23a provided at the lower part of the R evaporator chamber 8a, and flows to the upper part of the compressor 24 through the drain port 22a and the R drain pipe 27a. The evaporating pan 32 is discharged, and the defrosting method of the R evaporator 14a will be described below using FIG. 3 .

As shown in FIG. 3 , the launder heater 101 that melts the defrosting water when the defrosting water at the launder 23 a freezes is provided in the launder 23 a. The R drain pipe 27a is provided with a drain pipe upper heater 102 and a drain pipe lower heater 103 . In addition, a launder temperature sensor 45 for detecting the presence or absence of residual water is embedded in the final water collection part of the launder 23a and inside the heat insulating material. The launder sensor 45 is embedded in the foamed polyurethane heat insulating material, and thus is configured to avoid a reduction in durability due to dripping of water. Furthermore, the launder sensor 45 is arranged at the final water collection part of the launder 23a, and is configured to react to a small amount of residual water. Control of residual water is described below. The energization of the launder heater 101, the water distribution pipe upper heater 102, or the water distribution lower heater 103 is controlled. In addition, each heater 101, 102, 103 is, for example, an electric heater whose power consumption is 20 W or less and which is lower than that of the defrosting heater 21. In this embodiment, the launder heater 101 is The 6W heater, the drainpipe upper heater 102 is a 3W heater, and the drainpipe lower heater 103 is a 1W heater.

Fig. 4 is a diagram showing the structure of the R drain pipe 27a. 201 and 202 in the figure show the same height positions as 201 and 202 shown in FIG. 3 , the range 201 represents the height range of the freezing chamber 7 and the F evaporator chamber 8b, and the range 202 represents the distance from the heat insulating partition wall 28 to the heat insulating partition wall The height range up to the lower end of 29.

The upper part of the R drain pipe 27a is provided to be away from the freezer compartment 7 and the evaporator chamber 8 for freezing, and is inclined outward and downward from the drain port 22a toward the outer case 10a side, and a drain pipe upper heater 102 is provided in this section. . Its lower part is provided substantially in the vicinity of the outer case 10a, and the drainpipe lower heater 103 is provided up to the lower end of the heat insulating partition wall 29 in this section. The R drain pipe 27 a at its lower portion (lower than the heat insulating partition wall 29 ) is inclined inward so as to discharge the defrosted water to the evaporating pan 32 . In addition, in this embodiment, both the drain pipe upper heater 102 and the drain pipe lower heater 103 are fixed to the R drain pipe 27a by using aluminum seals with high thermal conductivity, so The parts are also configured to be heated by heat conduction generated by the aluminum seal.

By arranging the upper drain heater 102 and the lower drain heater 103 as described above, the upper ends of the upper drain heater 102 and the lower drain heater 103 are set to a position higher than the upper end of the range 201, and the lower end Set to a position lower than the lower end of the range 201 . Since the R drain pipe 27a in the range 201 is cooled by the freezer chamber 7 and the F evaporator chamber 8b in the freezing temperature range, the temperature in the R drain pipe 27a becomes subzero, and the defrosted water may freeze in the R drain pipe 27a. On the other hand, by providing the drain pipe upper heater 102 and the drain pipe lower heater 103 in the area 201, even if the water freezes in the drain pipe, it can be melted. (Refer to Figure 3) Drain.

In addition, the upper end of the drainpipe upper heater 102 is set at a position equal to or higher than the upper end of the range 202, and the lower end of the drainpipe lower heater 103 is set at a position equal to or higher than the lower end of the range 202. low position. The heat-insulating partition wall 28 and the heat-insulating partition wall 29 are in contact with the freezer compartment 7 and the F evaporator compartment 8b in the freezing temperature zone, and at least a part thereof has a subzero temperature. Therefore, the temperature in the R drain pipe 27a in the height range of the heat-insulating partition wall 28 and the heat-insulating partition wall 29 may become subzero. Therefore, it is possible to more reliably drain water from the R drain pipe 27a to the evaporating pan 32 (see FIG. 3 ). In addition, the part inside the heat-insulating partition wall 28 in the R drain pipe 27a is easily cooled directly by the heat-insulating partition wall 28 to become low temperature, and it is effective to provide the drain pipe upper heater 102 especially at this part.

Here, as shown in FIG. 2 and FIG. 3 , when the R fan 9a is driven in the flow tank 23a, return air returning from the refrigerator compartment 2 to the refrigerator compartment evaporator 14a flows. Since the R fan 9a is driven during the defrosting operation of the R evaporator 14a to be described later, the flow tank 23a can be heated by the return air at the above-zero temperature. Thereby, freezing of the defrosted water in the launder 23a can be suppressed, and even if it is frozen, the heating amount of the launder heater 101 required for melting can be suppressed, and energy-saving performance can be improved.

And the lower part of the drain pipe 27a (where the drain pipe lower heater 103 is provided) is closer to the outer case 10a than the freezer compartment 7 and the F evaporator compartment 8b. Thereby, especially when the outside air is high temperature, it is possible to heat the outside air through the outer case 10a, thereby suppressing the freezing of the lower part of the drain pipe 27a, and even if it freezes, it is also possible to suppress the heating of the drain pipe lower part heater. 103 heating capacity, which can improve energy-saving performance. On the other hand, when the outside air is low temperature, the drain pipe lower heater 103 can be heated to reliably discharge the defrosted water. In addition, since the R drain pipe 27a flows defrosting water at about 0°C, the outer case 10a close to the R drain pipe 27a is cooled by the defrosting water and may become a temperature lower than the dew point temperature, but by The drain pipe lower heater 103 is provided, and when the outside air is high-humidity, the drain pipe lower heater 103 is energized during the R first defrosting operation and the R second defrosting operation described later to suppress the leakage of the outer case 10a. The temperature is lowered, and dew condensation on the outer case 10a can be suppressed.

On the upper part of the refrigerator 1 (see FIG. 2 ), a control board 31 on which a memory such as a CPU, ROM or RAM, an interface circuit, etc. are mounted as a part of the control device is arranged. The control board 31 is connected to the refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, the vegetable compartment temperature sensor 43, the evaporator temperature sensors 40a, 40b, etc., and the above-mentioned CPU is based on their output values, the setting of the operation part 26, and the pre-recorded The programs in the above-mentioned ROM control the compressor 24, the R fan 9a, the cooling fan 9b, the above-mentioned heaters 21, 101, 102, and 103, and the refrigerant control valve 52 described later.

Fig. 4 is a refrigerating cycle (refrigerant flow path) of the refrigerator of the embodiment. In the refrigerator 1 of the present embodiment, the compressor 24, the external radiator 50a and the wall surface heat dissipation piping 50b as a heat dissipation mechanism for heat dissipation of the refrigerant are provided, and the dew condensation on the front parts of the heat insulating partition walls 28, 29, 30 is suppressed. The anti-condensation piping 50c, the capillary tube 53a for refrigeration and the capillary tube 53b for freezing as a decompression mechanism for decompressing the refrigerant, and the R evaporator 14a for exchanging heat between the refrigerant and the air in the box to absorb the heat in the box F evaporator 14b, refrigeration suction pipe 55a for exchanging heat with refrigeration capillary 53a, and freezing suction pipe 55b for freezing heat exchange with capillary 53b to cool the inside of the box. In addition, it includes a drier 51 for removing moisture in the refrigeration cycle, gas-liquid separators 54a and 54b for preventing liquid refrigerant from flowing into the compressor 24, and a three-way valve 52 and a check valve for controlling the refrigerant flow path. 56 and the refrigerant confluence part 57 connected to the flow of the refrigerant, and a refrigeration cycle is constituted by connecting the above-mentioned components with refrigerant piping. In addition, isobutane which is a flammable refrigerant is used for the refrigerant|coolant of the refrigerator 1 of this Example. In addition, the compressor 24 of this embodiment can be equipped with an inverter to change the rotational speed. The capillary 53a for refrigeration and the suction pipe 55a for refrigeration are brazed or soldered to form a heat exchange portion 59a capable of exchanging heat with each other, and the capillary 53b for freezing and the suction pipe 55b for freezing also form a heat exchange portion 59a capable of exchanging heat with each other. Heat section 59b.

The three-way valve 52 is a member provided with two outlets indicated by 52a and 52b, and has a refrigeration mode in which the refrigerant flows to the outlet 52a side and a freezing mode in which the refrigerant flows to the outlet 52b side, and can switch between the two. model. In addition, the three-way valve 52 of this embodiment also has a fully closed mode in which neither the refrigerant flows into the outflow port 52a nor the outflow port 52b, or a fully open mode in which the refrigerant both flows, and can be switched between these two modes.

In the refrigerator 1 of the present embodiment, the refrigerant flows as follows. The refrigerant discharged from the compressor 24 flows through the external radiator 50 a, the external radiator 50 b, the condensation prevention piping 50 c, and the dryer 51 in order, and then reaches the three-way valve 52 . The outflow port 52a of the three-way valve 52 is connected to the refrigerating capillary tube 53a via the refrigerant pipe, and the outflow port 52b is connected to the refrigerating capillary tube 53b via the refrigerant pipe.

If the refrigerant flows toward the outlet 52a side, the refrigerant flowing out from the outlet 52a flows sequentially to the capillary tube 53a for refrigeration, the R evaporator 14a, the gas-liquid separator 54a, the suction pipe 55a for refrigeration, and the refrigerant confluence part 57, and then returns to compressor 24. The low-pressure and low-temperature refrigerant in the capillary tube 53a for refrigeration flows through the R evaporator 14a, and the R evaporator 14a becomes low-temperature, thereby cooling the air in the R evaporator chamber 8a, that is, cooling the refrigerator compartment 2 .

And, when the three-way valve 52 is set so that the refrigerant flows toward the outlet 52b side, the refrigerant flowing out from the outlet 52b flows sequentially through the capillary tube 53b for freezing, the F evaporator 14b, the gas-liquid separator 54b, and the refrigerant for refrigeration. The suction pipe 55 a , the check valve 56 , the refrigerant junction 57 , and then returns to the compressor 24 . The check valve 56 is arranged so that the refrigerant flows from the gas-liquid separator 54 b to the refrigerant junction 55 side, but does not flow from the refrigerant junction 55 to the gas-liquid separator 54 b side. The low-pressure and low-temperature refrigerant in the freezing capillary tube 53b flows through the F evaporator 14b, and the F evaporator 14b becomes low-temperature to cool the air in the R evaporator chamber 8a, that is, to cool the freezing chamber 7.

Fig. 5 is a C-C sectional view of Fig. 1, showing the positional relationship between the suction pipes 55a, 55b, the check valve 56 and the insulating partition walls 28, 29 of the refrigerator of the embodiment. The suction pipe 55a for refrigeration is arrange|positioned so that the effective heat exchange length may increase substantially in the horizontal direction on the back surface of the R evaporator 14a, and it penetrates the heat insulation partition wall 28. As shown in FIG. Here, in this embodiment, the arrangement of the rear surface of the heat-insulating partition wall 28 is minimized, but if there is no interference with the thickness of the heat-insulating partition wall 28 and the structure of the heat-insulating partition wall 28, it is preferable that the temperature difference with the suction pipe is small. The refrigerating room 2 and the back of the heat-insulating partition wall 28 increase the effective heat exchange length (extended path) substantially along the horizontal direction. Thereafter, the back surface of the freezer compartment 7 to the heat insulating partition wall 29 and the back surface of the vegetable compartment 6 are arranged approximately vertically. For the disposition of the back side of the freezer compartment 7, the temperature difference between the suction pipe 55a for refrigeration and the freezer compartment 7 is relatively large, which causes the reduction of the heat exchange performance of the straw and the heating of the freezer compartment 7, thereby minimizing (not extending the path) )It's effective. In this embodiment, the effective heat exchange length (extended path) is increased on the back side of the vegetable compartment 6 where the temperature difference with the straw is small, but it may be extended (extended path) on the back side of the heat insulating partition wall 29 . In particular, the closer to the downstream of the suction pipe, the higher the temperature is, and the heating capacity increases, so that an effective effect can be obtained if it is arranged in a place where the temperature is to be raised. The suction pipe 55b for freezing preferentially increases the heat exchange length as much as possible (extends the path). However, the downstream portion of the suction pipe which becomes high temperature is arranged on the back surface of the heat insulating partition wall 29 . Thereafter, it passes through the check valve 56 and reaches the refrigerant confluence portion 57 .

Here, by accommodating the check valve 56 inside the foamed polyurethane heat insulating material, the assembly of the refrigerant piping in the machine room 39 is simplified, and the space saving in the height direction of the machine room can be realized, and the work can be improved. sex. Furthermore, it is also possible to suppress valve opening and closing sounds and the like generated by the check valve 56 . In order to suppress the sound of the check valve 56, measures such as providing a cushioning material so that the check valve 56 does not come into contact with the wall surface are also effective. The check valve 56 may fail due to the influence of heat at the time of manufacture, but as long as the heat load is paid attention to, the failure will not occur. Furthermore, since it is extremely rare that a failure occurs during use by a customer, it is difficult to consider that priority maintenance is a major advantage in manufacturing. In addition, since the check valve 56 of this embodiment has a cylindrical shape, it is hardly deformed even if it receives foaming pressure by accommodating it in the foamed polyurethane heat insulating material.

FIG. 6 shows the relationship between the relative lengths of the suction pipes 55a, 55b (the length from the evaporator outlet/the total length from the evaporator outlet to the compressor) and the temperature of the suction pipes 55a, 55b. In addition, the operation condition of the refrigerator of FIG. 6 is a no-load state, and the external air temperature is 30 degreeC. The temperature of the suction pipes 55a, 55b rises as it flows downstream from the outlet of the evaporator due to heat exchange with the capillary pipes 53a, 53b, and when it reaches the refrigerant confluence part 57, it becomes close to the inlet temperature of the capillary pipes 53a, 53b, that is, the outside air temperature. temperature zone. Therefore, it is effective to avoid the back of the freezer compartment 7, especially the back of the F evaporator 14b, by dissipating heat from the suction pipes 55a and 55b embedded in the heat insulating material to the cooled refrigerator 1. On the other hand, if such an arrangement is intended, the heat exchange length of the suction pipes 55a, 55b (the length of the heat exchange parts 59a, 59b where the suction pipes 55a, 55b exchange heat with the capillary tubes 53a, 53b) cannot be obtained sufficiently, and sometimes Impairs cooling power and leads to deterioration of energy saving. Therefore, by obtaining the lengths of the suction pipes 55a and 55b on the back side of the heat insulating partition walls 28 and 29, the performance of the refrigerator and the suction pipes can be effectively improved. In addition, the performance of the refrigerator refers to cooling capacity and energy-saving performance, and the performance of the straw refers to the ratio of the heat exchange capacity in a completely adiabatic state to the actual heat exchange capacity.

As shown in Fig. 5, for the suction pipe 55a for refrigeration, since the temperature of the R evaporator 14a (for example -10°C) is higher than the temperature of the F evaporator 14b (for example -25°C), the suction pipe 55a from the inlet to the outlet It is effective to avoid the low temperature part at all parts. On the other hand, in the heat exchange parts 59a, 59b from the evaporators 14a, 14b to the compressor 24, on the side closer to the compressor 24 than the middle position of the entire length, the temperature of the suction pipes 55a, 55b is as high as about 15°C. Therefore, it is effective to configure to avoid the back of the freezer compartment and the back of the F evaporator 14b as much as possible. In particular, on the side closer to the compressor 24 than the middle of the entire length of the heat exchange part 59a from the evaporator 14a to the compressor 24, the length passing through the back surface of the freezing temperature zone chamber passes through the heat insulating partition wall. The length of the back side and the back side of the refrigerated temperature belt compartment is longer, resulting in a higher effect. In addition, the high temperature part can also be used to suppress freezing of the drain pipe by embedding it in the back surface of the flow tank 23b and the F drain pipe 27b of the defrosted water discharged from the F evaporator 14b to always heat it.

Moreover, in this Example, the vegetable compartment 6 is cooled by the F evaporator 14b, and the wall surface of the inner case 10b of the vegetable compartment 6 is temporarily cooled. In this case, dew condensation may generate|occur|produce by the temperature difference between the vegetable compartment 6 and room temperature (for example, 6 degreeC). As shown in this embodiment, by adopting the structure of the vegetable compartment cooling air duct 58, the suction pipes 55a, 55b, and the refrigerant confluence part 57, the suction pipe can be used to heat the wall surface, and dew condensation can be suppressed. As for the temperature downstream of the check valve 56, since the temperature rises independently of the freezer cooling operation and the refrigerator cooling operation, it is effective to dispose the downstream side of the check valve 56 as the wall surface on the back side of the vegetable compartment 6. of. But, because the suction pipe 55a, 55b heats the wall surface of the vegetable compartment 6 cooled by the F drain pipe 27b or the vegetable compartment cooling air passage 58, the performance of the suction pipe decreases, and if the temperature of the suction pipe in the machine room is too low than the outside air temperature, Then, the probability of occurrence of dew condensation on the tube increases, and therefore it is necessary to adjust according to the heat exchange length of the suction tube and the like.

In addition, in this embodiment, the check valve 56 is not embedded in the back surface of the F evaporator 14b, and the length of the piping (heat exchange part 59b) from the outlet of the F evaporator 14b to the check valve 56 is also longer than that from the check valve. 56 The length of the piping (heat exchange part 59b) leading to the compressor 24 is long, so that the influence of heat on the inside of the tank can be suppressed to a minimum.

The above is an example showing an example of this embodiment. In addition, this invention is not limited to the said Example, Various modification examples are included. For example, the above-mentioned embodiments have been described in detail to explain the present invention in an easy-to-understand manner, and are not limited to having all the configurations described. In addition, addition, deletion, and replacement of other configurations can be performed on a part of the configurations of the embodiments.

Claims (10)

1. a kind of refrigerator, there is refrigerating temperature zone room, cryogenic temperature band room, by above-mentioned refrigerating temperature zone room and above-mentioned cryogenic temperature With the insulation partition wall separated between room, sprays the compressor of refrigerant and the heat of refrigerant is made to be dispersed into external sky The radiator of gas,

Above-mentioned refrigerator is also equipped with:

The first capillary for depressurizing refrigerant；

The first evaporator to absorb heat out of above-mentioned refrigerating temperature zone room；

The refrigerant flowed out from above-mentioned first evaporator is set to be back to the first suction pipe of above-mentioned compressor；

The first gas-liquid for preventing the liquid refrigerant from the refrigerant that above-mentioned first evaporator flows out from flowing into above-mentioned compressor Separator；

The second capillary for depressurizing refrigerant；

The second evaporator to absorb heat out of above-mentioned cryogenic temperature band room；

The refrigerant flowed out from above-mentioned second evaporator is set to be back to the second suction pipe of above-mentioned compressor；

The second gas-liquid for preventing the liquid refrigerant from the refrigerant that above-mentioned second evaporator flows out from flowing into above-mentioned compressor Separator；And

Connect the refrigeration of the refrigerant from above-mentioned first gas-liquid separator and the refrigerant from above-mentioned second gas-liquid separator Agent merging part,

Above-mentioned refrigerator is characterized in that,

Check-valves is embedded in heat-insulating material, which makes refrigerant from above-mentioned second gas-liquid separator to above-mentioned refrigerant The flowing of merging part side, and flow refrigerant from above-mentioned refrigerant merging part to above-mentioned second gas-liquid separator side.

2. refrigerator according to claim 1, which is characterized in that

Piping length from above-mentioned second evaporator to above-mentioned check-valves is than matching pipe range from above-mentioned check-valves to above-mentioned compressor Degree length.

3. refrigerator according to claim 1, which is characterized in that

Above-mentioned check-valves is not buried at the back side of above-mentioned second evaporator.

4. refrigerator according to any one of claims 1 to 3, which is characterized in that

The above-mentioned cylindrical shape of check-valves.

5. refrigerator according to any one of claims 1 to 4, which is characterized in that

For above-mentioned second evaporator not only to freezing chamber cool-air feed, the vegetable compartment supply also to the lower section for being located at above-mentioned freezing chamber is cold Gas, the piping from above-mentioned check-valves to above-mentioned compressor are located at the back side of above-mentioned vegetable compartment.

6. a kind of refrigerator, there is refrigerating temperature zone room, cryogenic temperature band room, by above-mentioned refrigerating temperature zone room and above-mentioned cryogenic temperature With the insulation partition wall separated between room, sprays the compressor of refrigerant and the heat of refrigerant is made to be dispersed into external sky The radiator of gas,

Above-mentioned refrigerator is also equipped with:

The first capillary for depressurizing refrigerant；

The first evaporator to absorb heat out of above-mentioned refrigerating temperature zone room；

The refrigerant flowed out from above-mentioned first evaporator is set to be back to the first suction pipe of above-mentioned compressor；

The second capillary for depressurizing refrigerant；

The second evaporator to absorb heat out of above-mentioned cryogenic temperature band room；And

The refrigerant flowed out from above-mentioned second evaporator is set to be back to the second suction pipe of above-mentioned compressor,

Above-mentioned refrigerator is characterized in that,

It is more closer than the middle position of its overall length in the heat exchanging part for making above-mentioned first capillary and above-mentioned first suction pipe exchange heat The side of above-mentioned compressor extends path at the back side of above-mentioned insulation partition wall or above-mentioned refrigerating temperature zone room.

7. refrigerator according to claim 6, which is characterized in that

Above-mentioned heat exchanging part does not extend path at the back side of above-mentioned cryogenic temperature band room.

8. a kind of refrigerator, there is refrigerating temperature zone room, cryogenic temperature band room, by above-mentioned refrigerating temperature zone room and above-mentioned cryogenic temperature With the insulation partition wall separated between room, sprays the compressor of refrigerant and the heat of refrigerant is made to be dispersed into external sky The radiator of gas,

Above-mentioned refrigerator is also equipped with:

The first capillary for depressurizing refrigerant；

The first evaporator to absorb heat out of above-mentioned refrigerating temperature zone room；

The refrigerant flowed out from above-mentioned first evaporator is set to be back to the first suction pipe of above-mentioned compressor；

The second capillary for depressurizing refrigerant；

The second evaporator to absorb heat out of above-mentioned cryogenic temperature band room；And

The refrigerant flowed out from above-mentioned second evaporator is set to be back to the second suction pipe of above-mentioned compressor,

Above-mentioned refrigerator is characterized in that,

It is more closer than the middle position of its overall length in the heat exchanging part for making above-mentioned first capillary and above-mentioned first suction pipe exchange heat Only prolong generally in a horizontal direction at the back side of above-mentioned insulation partition wall or above-mentioned refrigerating temperature zone room the side of above-mentioned compressor It is long.

9. a kind of refrigerator, there is refrigerating temperature zone room, cryogenic temperature band room, by above-mentioned refrigerating temperature zone room and above-mentioned cryogenic temperature With the insulation partition wall separated between room, sprays the compressor of refrigerant and the heat of refrigerant is made to be dispersed into external sky The radiator of gas,

Above-mentioned refrigerator is also equipped with:

The first capillary for depressurizing refrigerant；

The first evaporator to absorb heat out of above-mentioned refrigerating temperature zone room；

The refrigerant flowed out from above-mentioned first evaporator is set to be back to the first suction pipe of above-mentioned compressor；

The second capillary for depressurizing refrigerant；

The second evaporator to absorb heat out of above-mentioned cryogenic temperature band room；And

The refrigerant flowed out from above-mentioned second evaporator is set to be back to the second suction pipe of above-mentioned compressor,

Above-mentioned refrigerator is characterized in that,

It is more closer than the middle position of its overall length in the heat exchanging part for making above-mentioned first capillary and above-mentioned first suction pipe exchange heat The side of above-mentioned compressor is passed through above-mentioned by above-mentioned insulation partition wall or the length ratio at the back side of above-mentioned refrigerating temperature zone room The length at the back side of cryogenic temperature band room is long.

10. according to refrigerator described in any one of claim 6~9, which is characterized in that

Successively have from upper using above-mentioned first evaporator carry out cooling refrigerating chamber, using above-mentioned second evaporator carry out it is cold But freezing chamber and cooling vegetable compartment is carried out using above-mentioned second evaporator, above-mentioned heat exchanging part is embedded in discharge above-mentioned the The back part of the chute of the defrosted water of two evaporators.