TW201530069A - Refrigerator - Google Patents

Abstract

The control device of this refrigerator has: a setting table that associates and stores the flow resistance of a decompression device differing for each outside air temperature; a driving condition setting means that selects a flow resistance from the setting table on the basis of the outside air temperature detected by an outside air temperature sensor; and a refrigeration cycle control means that sets the driving time at the flow resistance selected by the driving condition setting means and controls a refrigeration cycle in a manner so as to perform a power-saving driving by means of the flow resistance (Rf) and driving time.

Description

refrigerator

The present invention relates to a refrigerator having a condensation prevention tube for preventing condensation.

In general, the refrigerator includes a box portion of the heat insulating box that is open at the front portion, a partition portion that divides the inner space of the box portion into a plurality of storage chambers, and a front opening portion that closes each storage chamber by freely opening and closing. Insulated door piece. In such a refrigerator, cold air convects between the box portion and the partition portion and the heat insulating door piece, so that the surface temperature of the front opening edge in the box portion becomes low. Moreover, the surface temperature becomes lower than the outside air temperature, and dew condensation occurs below the dew point temperature. Therefore, a dew condensation prevention pipe through which the high-pressure refrigerant flows is provided in the tank portion of the opening portion of the refrigerator storage compartment and the front side edge of the partition portion, and the front side of the tank portion and the partition portion is heated by the condensation heat of the refrigerant flowing through the dew condensation prevention tube. Thereby suppressing the occurrence of condensation.

On the other hand, when the condensation preventing tube is excessively heated, a part of the heat of condensation is intruded into the storage chamber from the condensation preventing tube, and the cooling load in the refrigerator is increased. Therefore, there has been known a refrigerator which regulates the flow rate of the refrigerant flowing into the condensation prevention tube or the temperature of the refrigerant to prevent dew condensation while avoiding excessive heating of the condensation prevention tube (see, for example, Patent Documents 1, 2).

Patent Document 1 discloses a refrigerator in which a refrigerant flow distribution device is disposed between an exothermic condenser and a dew condensation prevention condenser, and a refrigerant flow distribution device is installed. The distribution of the refrigerant to the condensation prevention condenser and the bypass pipe is performed in accordance with the temperature difference between the ambient temperature and the condensation prevention condenser. Patent Document 2 discloses a refrigerator in which a condensation tube is respectively disposed at a front portion and a rear portion of a condenser, and an adjustable expansion valve is disposed between the condenser and a condensation prevention tube at a rear stage, and the expansion valve is adjusted to dew condensation into the rear portion. Prevent the temperature of the refrigerant in the tube from being adjusted to the most appropriate temperature.

Advanced technical literature Patent literature

Patent Document 1: Japanese Laid-Open Patent Publication No. Hei 8-285426 (Fig. 1)

Patent Document 2: Japanese Laid-Open Patent Publication No. 54-21660 (Fig. 5)

However, in the refrigerator of Patent Document 1, in order to change the flow rate of the refrigerant flowing into the condensation prevention tube and to set the temperature of the refrigerant flowing into the condensation prevention tube to the target temperature, it is necessary to accurately detect the flow rate or pressure of the refrigerant flowing into the dew condensation prevention tube. Flow regulating device and pressure detecting device. As a result, an increase in cost is caused, and an additional compressor input is required, so that the amount of consumed power is also increased. Further, in the refrigerator of Patent Document 2, it is necessary to dispose the condensation prevention tube at a position corresponding to the temperature of the opening edge of the storage chamber having different temperature settings, and the attachment and arrangement structure of the condensation prevention tube is complicated.

The present invention has been made to solve the above problems, and a main object thereof is to provide a refrigerator capable of preventing an increase in a cooling load in a refrigerator due to heat of a condensation preventing tube with an inexpensive and simple configuration.

A refrigerator according to the present invention includes: a box portion having an internal space; a partition portion partitioning the inner space of the box portion into a plurality of storage compartments; and a refrigeration cycle housed in the box portion, and depending on the compressor and the condensation tube a pressure reducing device, a condensation preventing tube, and a capillary tube are sequentially connected in series; an external gas temperature detector is disposed outside the tank portion to detect an outside air temperature; and a control device for controlling the operation of the refrigeration cycle; the control device The method includes: a setting table that memorizes a flow impedance of the decompression device different in relation to each external gas temperature; and an operation condition setting means based on the external gas temperature detected by the external gas temperature detector, from the setting The table selects the flow impedance and sets the operating time of the selected flow impedance; the refrigeration cycle control means controls the refrigeration cycle to perform the flow impedance and the operation time set according to the operating condition setting means Running.

According to the refrigerator of the present invention, the flow impedance of the decompression device and the operation time thereof are automatically set in accordance with the temperature of the outside air, whereby the pressure detecting device or the bypass pipe can be provided as in the past, and the inexpensive and simple configuration can be used. It suppresses the increase in power consumption due to the heat of the condensation preventing tube, while preventing the occurrence of condensation.

1‧‧‧Box Department

2‧‧‧Departure

3‧‧‧Refrigerator

4‧‧‧ Ice making room

5‧‧‧Switching room

6‧‧‧Freezer

7‧‧ ‧ vegetable room

8‧‧‧Operating device

9a‧‧‧External gas temperature detector

9b‧‧‧Humidity detector

10‧‧‧Control device

10A‧‧‧Setting Table

10B‧‧‧ Operating conditions setting means

10C‧‧‧ refrigeration cycle control

11‧‧‧Outer box

12‧‧‧ inner box

13‧‧‧ Back wall

14‧‧‧ Wind Road

15‧‧‧cooler room

16‧‧‧Circular fan

20‧‧‧Refrigeration cycle

21‧‧‧Compressor

22‧‧‧Condensation tube

23‧‧‧Filter

24‧‧‧Reducing device

25‧‧‧Condenation prevention tube

26‧‧‧Dryer

27‧‧‧ Capillary

28‧‧‧cooler

29‧‧‧Refrigerant Heat Exchange Department

31, 41, 51, 61, 71‧‧‧

32, 42, 52, 62, 72‧‧‧ blown out

100‧‧‧ refrigerator

HA‧‧‧ Humidity

Rf‧‧‧ flow impedance

Rf0‧‧‧ minimum flow impedance

Rf1‧‧‧1st flow impedance

Rf2‧‧‧2nd flow impedance

Rf3‧‧‧3rd flow impedance

t, t0, t1, t2, t3‧‧‧ running time

TA‧‧‧ outside gas temperature

TAref1‧‧‧1st temperature threshold

TAref2‧‧‧2nd temperature threshold

Td‧‧‧ dew point temperature

Tmp0, Tmp1, Tmp2, Tmp3‧‧‧ The temperature of the refrigerant

Fig. 1A is a front elevational view showing a preferred embodiment of the refrigerator of the present invention.

Fig. 1B is a side cross-sectional view showing a preferred embodiment of the refrigerator of the present invention.

Fig. 1C is a front elevational view showing a state in which the door piece is removed in the preferred embodiment of the refrigerator of the present invention.

Fig. 2 is a refrigerant circuit diagram showing an example of a refrigeration cycle in the refrigerator of Fig. 1.

Fig. 3 is a plan view showing an example of a dew condensation prevention tube incorporated in the box portion of Fig. 1.

Fig. 4 is a functional block diagram showing an example of a control device in the refrigerator of Fig. 1.

Fig. 5 is a view showing an example of a setting table in the control device of Fig. 4.

Fig. 6 is a view showing a state in which the opening degree of the pressure reducing device is controlled during the operation of the refrigeration cycle of Fig. 2.

Fig. 7 is a flow chart showing an operation example of the refrigerator of Fig. 1.

Embodiments of the refrigerator of the present invention will be described below with reference to the drawings. Furthermore, the present invention is not limited to the embodiments described below. In addition, in the first drawing, the relationship of the dimensions of the respective constituent members in the respective drawings to be described later may be different from the actual object. 1A is a front elevational view showing a preferred embodiment of the refrigerator of the present invention, FIG. 1B is a side cross-sectional view showing a preferred embodiment of the refrigerator of the present invention, and FIG. 1C is a view showing a preferred embodiment of the refrigerator of the present invention. Front view of the state after the door. The refrigerator 100 of FIGS. 1A to 1C includes a box portion 1 and a partition portion (partition wall) 2 constituting a refrigerator body.

The box portion 1 is a box-shaped object that is open on the front side, has an outer box 11 that forms an outer profile, and an inner box 12 that forms an inner wall, and a polyurethane such as polyurethane is disposed between the outer box 11 and the inner box 12. A heat insulating material such as an ester. The partition portion 2 is an object that cuts the internal space of the box portion 1 into a plurality of storage chambers, and partitions the internal space of the box portion 1 into, for example, the refrigerating chamber 3, the ice making chamber 4, the switching chamber 5, the freezing chamber 6, and the vegetables. Storage room of room 7, etc.

The refrigerating compartment 3 is provided at the uppermost portion of the refrigerator 100, and its front surface is covered by a split-type door piece 31 having a heat insulating structure in a freely switchable manner. The ice making compartment 4 and the switching compartment 5 are arranged side by side on the left and right sides of the refrigerator compartment 3, and the front faces thereof are respectively covered by a drawer type door piece 41 having a heat insulating structure and a door piece 51 so as to be freely switchable. The freezing compartment 6 is provided on the lower side of the ice making compartment 4 and the switching compartment 5, and the front surface thereof is covered by a drawer type door piece 61 having a heat insulating structure so as to be freely switchable. The vegetable compartment 7 is provided on the lower side of the freezing compartment 6, and at the lowermost portion of the refrigerator 100, and the front surface thereof is covered by a drawer type door panel 71 having a heat insulating structure so as to be freely switchable. Further, a door opening and closing detector (not shown) that detects an open/close state is provided on each of the door sheets of each of the storage compartments 3 to 7.

Each of the storage compartments 3 to 7 is distinguished by a settable temperature zone (set temperature zone). For example, the refrigerator compartment 3 can be set to about 0 ° C to 4 ° C, and the vegetable compartment 7 can be set to about 3 ° C to 10 ° C. The ice chamber 4 can be set to about -18 ° C, and the freezer chamber 6 can be set to about -16 ° C to -22 ° C. In addition, the switching chamber 5 can be switched to a temperature zone such as cooling (about 0 ° C) or weak freezing (about -7 ° C). Thus, the set temperature bands of the refrigerating compartment 3 and the vegetable compartment 7 are set to be higher than the temperature zones of the ice making compartment 4, the switching compartment 5, and the freezing compartment 6. Furthermore, the set temperature of each of the storage compartments 3 to 7 is not limited thereto, and the setting may be appropriately changed depending on the installation location and the contents. Further, an internal temperature detector (not shown) for detecting the temperature of each storage compartment is provided in each of the storage compartments 3 to 7. Further, a damper (not shown) is provided on the air passage 14 side of each of the air outlets 32, 42, 52, 62, and 72.

The box portion 1 has a rear wall 13 on the back side of each of the storage chambers 3 to 7. An air path 14 and a cooler chamber 15 are formed between the inner box 12 and the back surface of the back wall 13. The air passage 14 is a cold air supply air passage for supplying cold air to each storage compartment, and is provided, for example, in a range opposed to the back surface of each of the storage compartments 3 to 7. The cooler chamber 15 is disposed at For example, in a range opposed to the back surface of the freezing compartment 6, it houses the cooler 28 of the refrigeration cycle 20. Further, cold air which has been heat-exchanged by the cooler 28 is supplied from the cooler chamber 15 to the air passage 14.

The air outlets for blowing the cold air flowing through the air passages 14 into the respective storage chambers 3 to 7 are respectively opened to the back surfaces of the storage chambers 3 to 7 in the tank portion 1. Specifically, the air outlet 32 is opened in the refrigerating chamber 3, the air outlet 42 is opened in the ice making chamber 4, the air outlet 52 is opened in the switching chamber 5, the air outlet 62 is opened in the freezing chamber 6, and the air outlet 72 is opened in the vegetable compartment 7. Further, a damper (not shown) is provided in each of the air outlets 32, 42, 52, 62, and 72, and the temperature of each of the storage rooms 3 to 7 is managed by a switch of the damper.

The refrigeration cycle 20 is disposed on the back side of the tank portion 1 and is a device that uses a vapor compression refrigeration cycle 20 to generate cold air in the refrigerator 100. Fig. 2 is a refrigerant circuit diagram showing an example of a refrigeration cycle in the refrigerators of Figs. 1A to 1C. In the refrigeration cycle 20 of the refrigerator 100 of Fig. 2, the apparatus is connected in series by a pipe, such as a compressor 21, a condensing pipe 22, a filter 23, a decompression device 24, a dew condensation prevention pipe 25, a dryer 26, and a capillary tube 27. Cooler 28.

The compressor 21 is disposed, for example, in a machine room provided at a lower portion of the back surface of the refrigerator 100. The compressor 21 compresses the refrigerant to a high temperature. The high-pressure refrigerant device is driven by the inverter circuit and controls the operating capacity in response to the situation. The condensing duct 22 is a device that performs heat exchange between the refrigerant discharged from the compressor 21 and the outside air, and is embedded in, for example, a heat pipe for condensing evaporation or an air condensing device placed in an installation space of the compressor 21. A heat insulating material pipe or the like is formed on the side or the back of the refrigerator 100. The filter 23 is composed of a filter or the like that removes impurities and metal powder flowing out of the condensation tube 22 from the refrigerant.

The pressure reducing device 24 is configured to flow from the condensation tube 22 through the filter 23 The device for decompressing and expanding the refrigerant to be introduced is configured such that the opening degree of the electronic expansion valve or the like can be controlled and changed. Further, the condensation prevention tube 25 is connected in series with the decompression device 24, and the refrigerant flow that has flowed into the decompression device 24 from the condensation tube 22 and the filter 23 flows into the dew condensation prevention tube 25 without being branched.

The dew condensation prevention tube 25 is connected in series with the condensation tube 22 through the decompression device 24, and has a function as a condenser as in the condensation tube 22, and has a function of preventing dew condensation of the tank portion 1 and the partition portion 2. Here, Fig. 3 is a plan view showing an example of the condensation preventing tube 25 housed in the box portion 1 of Fig. 1. The condensation preventing tube 25 is housed in a peripheral portion of the opening of the front surface of the box portion 1 and an edge of the front side of the partition portion 2 in a bent manner. The condensation prevention tube 25 is provided in the case portion 1 and the partition portion 2 through an elastic member having a large heat capacity such as butyl rubber. Further, the refrigerant flows in the condensation prevention tube 25, whereby condensation can be prevented from occurring in the front portion of the main body of the refrigerator 100.

In the third embodiment, the condensation prevention tube 25 is disposed on the edge of the front side of one of the box portion 1 and the partition portion 2, but the arrangement of the condensation prevention tube 25 is not limited thereto. It can be disposed at any position that can suppress condensation caused by leakage of cold air to the outside. For example, the condensation prevention tube 25 may be disposed on the edge of the entire front side of the box portion 1 and the partition portion 2. Alternatively, the condensation prevention tube 25 may be disposed only on the edge of the front side of the tank portion 1 and the partition portion 2 adjacent to the ice making chamber 4, the switching chamber 5, and the freezing chamber 6, (the region where the cold air in the freezing temperature zone may leak). In this case, it is possible to prevent the processing and arrangement of the condensation prevention tube 25 from becoming complicated.

The dryer 26 of Fig. 2 is composed of a filter for preventing impurities, metal powder, or the like contained in the refrigerant flowing from the dew condensation preventing pipe 25, and a suction member that adsorbs moisture in the refrigeration cycle. . Capillary 27 It is made of a capillary tube made of, for example, copper, and is a decompression device that depressurizes the refrigerant flowing through the dryer 26 and flows out to the cooler 28 side.

The cooler 28 is connected between the capillary 27 and the suction pipe side of the inter-refrigerant heat exchange portion 29. The cooler 28 is disposed in the cooler chamber 15, and is a device that cools the inside of the cooler chamber 15 to generate cold air. A circulation fan 16 is disposed above the cooler 28, and the circulation fan 16 supplies air to the cooler 28, and cool air cooled around the cooler 28 is blown to each of the storage compartments 3-7.

Further, in the refrigeration cycle 20, a refrigerant heat exchange unit 29 is provided between the refrigerant flowing through the capillary 27 and the refrigerant flowing in the pipe (suction pipe) between the cooler 28 and the compressor 21. Perform heat exchange. The inter-refrigerant heat exchange unit 29 exchanges heat between the refrigerant flowing through the capillary 27 and the refrigerant sucked into the compressor 21.

As described above, in the refrigeration cycle 20, the condensation prevention tube 25 is connected in series with the condensation tube 22 through the pressure reducing device 24, and has a function of a condenser and a function of preventing condensation. For example, in the case where the necessary cooling capacity is large, the amount of heat release in the condensation tube 22 and the condensation prevention tube 25 must also be large. When the load in the reservoir is small and the necessary cooling capacity is also small, the condensing pipe 22 and the condensation preventing pipe 25 may have a small heat release amount. When the refrigerant flowing through the condensation prevention tube 25 causes the tank portion 1 and the partition portion 2 to be excessively heated, the heat from the condensation prevention tube 25 enters each of the storage chambers 3 to 7, so that the heat is consumed in order to cool the respective storage chambers 3 to 7. Electricity is increasing. Therefore, when the load in the reservoir is small, the opening degree of the decompression device 24 is controlled so that the temperature of the refrigerant flowing into the condensation prevention tube 25 becomes lower.

On the other hand, in the case of prevention of condensation, in the tank portion 1 or the partition portion 2, dew condensation may occur when the surface temperature is below the dew point temperature. Therefore, it is necessary to maintain the surface temperature of the tank portion 1 and the partition portion 2 at a temperature higher than the dew point temperature of the outside air by reducing the refrigerant pressure of the condensation preventing tube 25 and increasing the temperature of the refrigerant to condense heat of the refrigerant.

Therefore, the refrigerator 100 has a function of suppressing the throttle mode (power saving mode) for consuming power according to the user's input or the like, and is capable of switching between the plurality of throttlings in response to the temperature of the outside air in the setting environment of the refrigerator 100. The function of the mode.

Fig. 4 is a functional block diagram showing an example of the control device 10 of Figs. 1A to 1C. The refrigerator 100 of FIGS. 1A to 1C and 4 includes an operation device 8, an external air temperature detector 9a, a humidity detector 9b, and a control device 10. The operation device 8 is a device that receives various inputs from the user, and is provided, for example, on the surface of the door piece 31 of the refrigerating chamber 3. The operation device 8 is constituted by an operation switch for adjusting the temperature of each of the storage chambers 3 to 7, and a liquid crystal display device for displaying the temperatures of the respective storage chambers 3 to 7. Further, in the operation device 8, for example, an operation switch for selecting a throttle mode is provided, and the user can operate the operation device 8 to select any one of the plurality of throttle modes.

The external air temperature detector 9a is a device that detects the outside air temperature TA in which the installation environment of the refrigerator 100 is installed. Further, the humidity detector 9b is a device that detects the humidity HA of the outside air in the installation environment in which the refrigerator 100 is installed. The outside air temperature detector 9a and the humidity detector 9b are provided, for example, at the operating device 8. Further, the outside air temperature detector 9a and the humidity detector 9b may be provided at a position other than the operation device 8 (for example, the periphery of the connection portion between the door piece 31 of the refrigerator compartment 3 and the case portion 1).

The control device 10 of FIGS. 1A to 1C is for controlling the refrigeration cycle 20 The apparatus for operating the entire refrigerator 100 is constituted by a microcomputer or the like and is provided on the upper portion of the back surface of the refrigerator 100. Further, the control device 10 controls the operation of the refrigeration cycle 20 and the operation of the damper switch so that, for example, the detected temperature of the interior temperature of each of the storage compartments 3 to 7 is a set temperature. Further, the control device 10 detects the opening and closing state of each of the door pieces based on the output of each of the door opening and closing detectors, and controls, for example, when the door piece is not closed for a long time, so that the operation device 8 or the sound output device controls the operation. The situation is reported to the user.

In particular, the control device 10 controls the opening degree (flow resistance) of the decompression device 24 in response to the input of the operation device 8, thereby adjusting the refrigerant pressure in the condensation prevention tube 25. Specifically, the control device 10 includes a setting table 10A, an operating condition setting means 10B, and a freezing cycle control means 10C.

Fig. 5 is a view showing an example of the setting table 10A of Fig. 4. As shown in FIGS. 4 and 5, the setting table 10A stores the different flow impedances Rf0 to Rf3 in association with the respective outside air temperatures TA (throttle modes 1 to 3). Further, the operating condition setting means 10B selects any one of the throttle modes 1 to 3 from the setting table 10A based on the outside air temperature TA detected by the outside air temperature detector 9a. In addition, in the fifth diagram, the three-stage throttling modes 1 to 3 are exemplified, and the different flow resistances Rf0 to Rf3 are stored in association with each of the outside air temperatures TA as the throttling modes 1 to 3. Specifically, when the outside air temperature TA is equal to or higher than the first temperature threshold TAref1 (throttle mode 1), and the outside air temperature TA is lower than the first temperature threshold TAref1 and higher than the second temperature threshold TAref2 (throttle Mode 2) When the outside air temperature TA is equal to or lower than the second temperature threshold TAref2 (throttle mode 3).

Further, the operating condition setting means 10B selects the decompression device from the setting table 10A based on the outside air temperature TA and the respective temperature threshold values TAref1, TAref2. Set the flow resistance Rf of 24. In Fig. 5, the first flow impedance Rf1 is larger than the minimum flow impedance (full open state) Rf0 (Rf1 > Rf0), the second flow impedance Rf2 is larger than the first flow resistance Rf1 (Rf1 > Rf2), and the third flow impedance Rf3 is larger than 2 Flow resistance Rf2 (Rf3>Rf2). Further, as the opening degree of the decompression device 24 is larger, the flow resistance Rf is smaller, and the smaller the flow resistance Rf is, the higher the temperature of the refrigerant flowing through the condensation prevention tube 25 is.

In particular, in the setting table 10A, each of the outside air temperatures TA (throttle modes 1 to 3) is associated with a plurality of different flow resistances Rf0 to Rf3. For example, the combination of the throttle mode 1 and the minimum flow resistance Rf0 and the first flow resistance Rf1, the combination of the throttle mode 2 and the minimum flow impedance Rf0 and the second flow impedance Rf2, the throttle mode 3 and the minimum flow impedance Rf0 and the 3 Combination of flow resistance Rf3.

Further, after the operation condition setting means 10B selects the flow resistance Rf, the operation time t is set for each of the different flow impedances Rf. Specifically, in the setting table 10A, the temperatures Tmp0 to Tmp3 of the refrigerant flowing into the respective condensation preventing tubes 25 are memorized in advance for the respective flow impedances Rf0 to Rf3. In the operating condition setting means 10B, as shown in the following formula (1), the operating times t0 and t1 are calculated so that the temperature of the refrigerant flowing into the dew condensation preventing pipe 25 is equal to or higher than the dew point temperature Td and equal to or less than the outside air temperature TA. In the following formula (1), the case where the combination of the minimum flow resistance Rf0 and the first flow resistance Rf1 is selected in the case of the throttle mode 1 is exemplified.

The dew point temperature Td in the equation (1) is calculated based on the outside air temperature TA detected by the outside air temperature detector 9a and the humidity HA detected by the humidity detector 9b by the operating condition setting means 10B, and the calculation method thereof is calculated. can To use a variety of known techniques.

That is, the equation (1) indicates that the flow resistance Rf of the decompression device 24 is adjusted so as to flow through the condensation prevention tube 25 by changing the ratio of the operation time t0 of the minimum flow resistance Rf0 to the operation time t1 of the first flow resistance Rf1. The time average of the temperature of the refrigerant is equal to or higher than the dew point temperature Td and equal to or less than the outside air temperature TA. The ratio of the operation time t0 and t1 changes depending on the installation environment in which the temperature or the humidity is different. For example, the higher the dew point temperature Td is, the operation time t0 of the minimum flow resistance Rf0 is shorter than the operation time t1 of the first flow resistance Rf1.

Further, the operating condition setting means 10B is exemplified by calculating the dew point temperature Td and calculating the operation time t using the above formula (1). However, the present invention is not limited thereto, and is controlled so that the temperature of the refrigerant is higher than the dew point temperature Td. can. For example, the operating condition setting means 10B can calculate the respective operating times t0 and t1 such that the average temperature of the refrigerant flowing through the condensation preventing pipe 25 is the outside air temperature TA or only a predetermined temperature (for example, 5 ° C) lower than the outside air temperature TA. In this way, the humidity detector 9b for calculating the dew point temperature Td is not required, and the occurrence of dew condensation can be surely prevented, and the power consumption in the refrigerator 100 due to the heat of the condensation prevention tube 25 can be suppressed with an inexpensive configuration.

In addition, although the operation time t0 and t1 are calculated using the formula (1), the operation time t0 to t3 of each of the flow impedances Rf0 to Rf3 is stored in the setting table 10A in advance, and is then stored in response to the external air temperature TA. The setting of the flow resistance Rf and the operation time t in the setting table 10A may be used.

When the user selects three stages of the throttle modes 1 to 3 through the operation device 8, the operation condition setting means 10B has the flow resistance Rf selected to match the throttle mode 1 to 3 selected by the user from the setting table 10A. function. Like this In this way, not only in the automatic migration to the throttling mode, but also in the user's will to manually perform condensation prevention measures. In this case, the operation time t may be a value calculated by the equation (1), or may be stored in advance in the value in the setting table 10A.

The refrigeration cycle control means 10C controls the refrigeration cycle 20 to execute a throttle mode (power saving operation) in accordance with the throttle modes 1 to 3 (flow resistance Rf and operation time t) set by the operation condition setting means 10B. Specifically, the refrigeration cycle control means 10C starts the driving of the compressor 21, and controls the refrigeration cycle 20 to be the respective flow impedances Rf0, Rf1 of the decompression device 24 and their operation times t0, t1.

Fig. 6 is a view showing a state in which the opening degree of the pressure reducing device 24 is controlled when the refrigeration cycle 20 of Fig. 2 is operated. As shown in Fig. 6, the refrigeration cycle control means 10C controls the decompression device 24 so that the operation time t0 of the minimum flow resistance Rf0 and the operation time t1 of the first flow resistance Rf1 are switched with each other. In this way, during the operation time t0 of the minimum flow resistance Rf0, the temperature of the refrigerant flowing through the condensation prevention tube 25 is Tmp0, and during the operation time t0 of the first flow resistance Rf1, the temperature of the refrigerant is Tmp1 ( <Tmp0). In addition, the time average value of the temperature of the refrigerant flowing into the condensation prevention tube 25 during the period (t0+t1) is as described in the above formula (1).

Further, the refrigeration cycle control means 10C can forcibly cancel the throttle mode 1 to 3 in response to the load in the store. For example, when the load in the library is equal to or greater than a predetermined threshold, the refrigeration cycle control means 10C cancels the execution of the throttle mode in order to prevent the shortage of cooling, or controls so that the throttle mode cannot be set.

Fig. 7 is a flow chart showing an operation example of the refrigerator in the first to third embodiments, and an operation example of the refrigerator 100 will be described with reference to Fig. 7 from Fig. 1A to Fig. 1C. again In the initial state, the refrigerator 100 is not set to any of the throttle modes, and is set to a state in which the pressure reducing device 24 does not adjust the refrigerant pressure to a fully open state, that is, a state in which the amount of refrigerant pressure loss in the pressure reducing device 24 is minimized.

First, whether or not the operation device 8 is to be moved to the throttle mode 1 to 3 by the user's operation (step ST1). When the content input to the operation device 8 is not to the throttle mode 1 to 3, the decompression device 24 is set to the fully open state (minimum flow resistance Rf0) in the refrigeration cycle control means 10C (step ST2). In this way, the operation is performed in a state where the cooling capacity of the refrigerator 100 is the largest (step ST8).

On the other hand, if the content input by the operation device 8 is transferable to the throttle mode 1 to 3, it is determined whether or not the operation of the throttle mode 1 to 3 is automatically input from the operation device 8 by the operation condition setting means 10B. Instruction (step ST3). When the command to automatically select the throttle modes 1 to 3 is input from the operation device 8, the outside air temperature TA detected by the outside air temperature detector 9a is acquired by the operation condition setting means 10B (step ST4). Then, in the operation condition setting means 10B, the throttle modes 1 to 3 (flow resistance Rf) are selected from the setting table 10A based on the outside air temperature TA (step ST5). Further, the operation time t of each of the flow impedances Rf is set in accordance with the equation (1) or the like (step ST6). Then, the operation of the compressor 21 is started (step ST8), and the driving of the decompression device 24 is controlled in accordance with the set flow resistance Rf and the operation time. Thereby, the refrigerant temperature (refrigerant pressure) of the condensation prevention tube 25 is controlled to be equal to or higher than the dew point temperature Td and equal to or lower than the outside air temperature (see FIG. 6).

On the other hand, when the operation device 8 is directly input by the user without automatically selecting any throttle mode, the flow impedance associated with the throttle modes 1 to 3 of the input operation device 8 is set in the operation condition setting means 10B. Rf (step ST7), and set the operation time t. At this time, the setting of the operation time t is as described above, and can be calculated by the equation (1), or the operation time t associated with the flow impedance Rf stored in advance can be used. Then, the operation of the compressor 21 is started (step ST8).

As described above, according to the present embodiment, when the power saving operation of the refrigerator 100 is executed, the flow resistance Rf is set using the setting table 10A, and the operation time t is set in accordance with the set flow resistance Rf, whereby the flow of the condensation prevention tube 25 can be ensured. The temperature of the refrigerant is above the dew point temperature Td. Therefore, in the case where the outside air is high humidity (for example, RH 90% or more) and low humidity (for example, RH 50% or more), in the case of a high-temperature external gas (for example, 30 ° C) or a low-temperature external gas (for example, 15 ° C) Any external gas temperature TA such as this can suppress the occurrence of dew condensation regardless of the external gas environment while suppressing the consumption of electric power.

In particular, since the temperature of the refrigerant flowing through the condensation prevention tube 25 is controlled by using the setting table 10A, it is not necessary to monitor the state of the refrigerant flowing through the refrigeration cycle 20 as in the past, and accordingly, the change of the pressure reducing device 24 is performed. Degree control. In this manner, by changing the temperature of the refrigerant flowing through the condensation prevention tube 25 in response to the flow resistances Rf0 to Rf3, the refrigerant temperature can be controlled to a predetermined refrigerant temperature. Therefore, it is not necessary to provide a refrigerant temperature detector, a refrigerant pressure detector, or the like and monitor the state of the refrigerant, and it is possible to inexpensively execute the dew condensation prevention mechanism in accordance with the installation environment.

Further, when the control device 10 receives the throttling modes 1 to 3 when the content of the operation device 8 is that the input of the throttling mode is possible, the control device 10 may, for example, enter the throttling mode when the load in the library is high. The decompression preventing device 24 is fully opened and the condensation preventing tube 25 is used as a condenser, so that the refrigerant can be condensed in the condensation tube 22 and the condensation prevention tube 25, so that the cooling can be continued while ensuring the necessary heat of condensation.

Further, when the operation time t0 to t3 is set for each of the flow impedances Rf0 to Rf3 corresponding to the selected throttle modes 1 to 3, high-precision refrigerant temperature control can be performed regardless of the setting environment. , can definitely prevent the occurrence of condensation.

The embodiment of the present invention is not limited to the above embodiment. For example, in the fourth drawing, the case where the outside air temperature TA is classified into three regions is exemplified, but two or more temperature thresholds TAref1 and Tref2 may be defined and divided into a plurality of classifications. Further, in the setting table 10A of Fig. 4, the case where the combination of the minimum flow resistance Rf0 and the respective flow impedances Rf1 to Rf3 is stored is illustrated, but the combination is not limited thereto, and any of the flow resistances Rf0 to Rf3 is memorized. Combination can be. In addition, not only a combination of two flow impedances, but also one flow resistance can be memorized, and a combination of three or more different flow impedances can be memorized.

8‧‧‧Operating device

9a‧‧‧External gas temperature detector

9b‧‧‧Humidity detector

10‧‧‧Control device

10A‧‧‧Setting Table

10B‧‧‧ Operating conditions setting means

10C‧‧‧ refrigeration cycle control

21‧‧‧Compressor

24‧‧‧Reducing device

16‧‧‧Circular fan

Claims (10)

A refrigerator comprising: a box portion having an internal space; partitioning an internal space of the box portion into a partition portion of a plurality of storage compartments; and a refrigeration cycle, which is housed in the box portion, and is compressed by a compressor, a condensation tube, or a The pressure device, the condensation prevention tube, and the capillary are sequentially connected in series; the external gas temperature detector is disposed outside the box portion to detect the temperature of the external air; and the control device for controlling the operation of the refrigeration cycle; the control device includes: a setting table for storing a flow impedance of the decompression device different in relation to each external gas temperature; and an operation condition setting means for selecting from the setting table based on the external gas temperature detected by the external gas temperature detector The flow impedance is set to the selected operation time of the flow impedance, and the refrigeration cycle control means controls the refrigeration cycle to perform the operation according to the flow impedance set in the operating condition setting means and the operation time. The refrigerator according to claim 1, further comprising an operation device capable of accepting the flow resistance adjustment, the control device performing the refrigeration cycle when the operation device receives an input executable to indicate the flow resistance The choice of the flow impedance and the setting of the operating time. According to the refrigerator of claim 2, the operating device includes an operation opening Off, it is used to directly input the selection of the flow impedance from the setting table, and the operating condition setting means has a function of selecting the flow impedance input from the operating device. The refrigerator according to claim 1, wherein the setting table has a plurality of the flow impedances different for each external gas temperature, and the operating condition setting means sets the operation time for each of the different flow impedances. According to the refrigerator of the fourth aspect of the invention, in the setting table, the temperature of the refrigerant flowing into the condensation prevention tube is previously stored for each of the flow impedances, and the operation condition setting means sets the operation for each of the different flow impedances. The time is such that the average temperature of the refrigerant flowing into the condensation prevention tube is higher than the dew point temperature. The refrigerator according to claim 5, wherein the refrigeration cycle control means sets the operation time for each of the different flow impedances so that the average temperature of the refrigerant flowing into the condensation prevention pipe is the outside air temperature. The refrigerator according to claim 5, wherein the refrigeration cycle control means sets the operation time for each of the different flow impedances so that the average temperature of the refrigerant flowing into the condensation prevention tube is lower than the temperature of the external gas. temperature. The refrigerator according to claim 5, further comprising a humidity detector that detects the humidity of the external air, the refrigeration cycle control means calculating the humidity detected by the humidity detector and the temperature of the outside air Dew point temperature, and set the operation time for each of the different flow impedances so that the condensation prevention tube The temperature of the flowing refrigerant is higher than the dew point temperature. The refrigerator according to claim 1, wherein the outside air temperature is classified into three categories in the setting table. The refrigerator according to claim 1, wherein the condensation preventing tube is housed in at least a portion of an edge of the box portion and the front side of the partition portion.