JP6972310B2 - Freezer refrigerator - Google Patents

Description

The present invention relates to a freezer / refrigerator provided with a double door.

Conventionally, a worktop type refrigerator having a refrigerator compartment at the top is known. Some such refrigerators are provided with a double door in the refrigerator compartment and a partition plate to prevent outside air from entering the refrigerator compartment through the gap between the left door and the right door.

With the door of the refrigerator closed, the partition plate is in close contact with the gasket of the door of the refrigerator to shield the refrigerator from the outside air. Since the partition plate is cooled from the inner surface of the refrigerator, the surface temperature of the outer side of the partition plate is lowered by heat conduction, and the surface of the outer side of the refrigerator is condensed. Many refrigerators are provided with a heater inside the partition plate to prevent condensation on the outer surface of the refrigerator.

When the heater heats the partition plate, if the amount of electric power supplied to the heater is increased only as a measure against dew condensation, the amount of electric power consumed by the refrigerator becomes large and the electricity bill becomes high. In addition, qualitatively, the amount of heat transferred from the partition plate to the refrigerating chamber also increases, which may hinder the cooling of the refrigerating chamber.

As an example of energization control of the heater provided on the partition plate, the input power P to the heater is calculated by the formula P = α × Δt with respect to the temperature difference Δt between the outside air temperature and the temperature inside the refrigerator compartment. A controlled refrigerator is known (see, for example, Patent Document 1).

Another example of a refrigerator that controls the energization of a heater is disclosed in Patent Document 2. In the refrigerator of Patent Document 2, the reference energization rate and the reference humidity at which the partition plate does not condense are set in advance according to the outside air temperature, and when the outside air humidity is higher than the reference humidity, the heater energization rate is made higher than the reference energization rate and the outside air If the humidity is lower than the standard humidity, the heater energization rate is set to be lower than the standard energization rate.

Japanese Unexamined Patent Publication No. 2004-353792 Japanese Unexamined Patent Publication No. 2013-72595

The refrigerator disclosed in Patent Document 1 is based on the premise that the temperature of the refrigerating chamber is stable at a set temperature, and if the temperature of the refrigerating chamber is close to the outside air temperature, there is a risk of wasteful power consumption. There is. When the temperature of the refrigerator compartment becomes higher as it gets closer to the outside air temperature, for example, when the power is turned on after the refrigerator is installed, when the power is restored from a long power failure, or when the door is opened for a long time. ..

The refrigerator disclosed in Patent Document 2 also does not consider whether or not the temperature of the refrigerating chamber is close to the set temperature, and when the temperature of the refrigerating chamber is higher as it is closer to the outside air temperature, the refrigerating chamber is cooled to the set temperature. In the transitional period until it is done, there is a risk of wasting power.

The present invention has been made to solve the above-mentioned problems, and provides a freezer / refrigerator capable of reducing power consumption.

The refrigerator / freezer according to the present invention includes a box body having a storage chamber, a double door that covers the opening of the box body, and a partition plate that prevents outside air from entering the storage room with the double door closed. An outside air temperature sensor that detects the outside air temperature, an outside air humidity sensor that detects the outside air humidity, a refrigerating room temperature sensor that detects the temperature in the storage room as the refrigerating room temperature, a heater that prevents dew condensation on the partition plate, and the above. It has a heater control means for controlling energization to the heater based on an outside air temperature and a reference energization rate calculated from the outside air humidity, and the heater control means includes the outside air temperature, the refrigerating room temperature, and the refrigerating room. calculating a power factor from the target temperature, the calculated power factor using a correction duty ratio obtained by multiplying the reference duty ratio to control the heater energization factor = (outside air temperature - the refrigerating compartment temperature) / (the outside air temperature - refrigerated The corrected energization rate is calculated using the calculation formula expressed by the room target temperature) .

According to the present invention, since the corrected energization rate reflecting the outside air temperature, the refrigerating chamber temperature and the refrigerating chamber target temperature is used for the heater energization control, the surface temperature of the partition plate may be higher than necessary than the dew condensation prevention temperature. It is suppressed. Therefore, wasteful power consumption of the heater can be suppressed, and the power consumption of the freezer / refrigerator can be reduced.

It is an external front view which shows one structural example of the freezer and refrigerator which concerns on Embodiment 1 of this invention. It is a refrigerant circuit diagram of the freezer / refrigerator shown in FIG. It is sectional drawing of the line AA shown in FIG. It is a functional block diagram of the control part shown in FIG. It is a graph which shows the calculation formula which calculates the reference energization rate from the outside air temperature and the relative humidity. It is a graph which shows the calculation formula which calculates the reference energization rate from the outside air temperature and the relative humidity. It is a model diagram which shows the heat transfer from the outside air to the refrigerating room shown in FIG. It is a figure which shows the flow velocity distribution of the whole cold air in the refrigerating room shown in FIG. It is an enlarged view which shows the flow velocity distribution of the cold air in the uppermost shelf in the refrigerating room part shown in FIG. It is a flowchart which shows an example of the procedure of the heater energization control executed by the heater control means shown in FIG. It is a graph which shows the temperature change from the start of power-on when the outside air temperature is 30 degreeC, and the relative humidity is 75% RH in the heater energization control which concerns on Embodiment 1 of this invention. It is a graph which shows the temperature change from the start of power-on when the outside air temperature is 30 degreeC, and the relative humidity is 75% RH in the heater energization control of the comparative example. It is a figure which shows the time change of the refrigerating room temperature, the energization coefficient, the reference energization rate and the correction energization rate in the heater energization control which concerns on Embodiment 1 of this invention. It is a graph which shows the temperature change from the start of power-on when the outside air temperature is 30 degreeC, and the relative humidity is 55% RH in the heater energization control which concerns on Embodiment 1 of this invention. It is a figure which shows each temperature waveform at the time of power-on when the outside air temperature is 30 degreeC, and the outside air humidity is 55% RH in the heater energization control of the comparative example. It is a functional block diagram which shows the structural example of the control part of the refrigerator-freezer which concerns on Embodiment 3 of this invention. It is a figure which shows the time transition of the energization rate of a heater in the freezing refrigerator which concerns on Embodiment 3 of this invention.

Embodiment 1.
The configuration of the freezer / refrigerator of the first embodiment will be described. FIG. 1 is an external front view showing a configuration example of a freezer / refrigerator according to the first embodiment of the present invention. FIG. 2 is a refrigerant circuit diagram of the freezer / refrigerator shown in FIG.

As shown in FIG. 1, the freezer / refrigerator 100 includes a box body 100A, and has a refrigerating room 1, an ice making room 2, a small freezing room 3, a freezing room 4, and a vegetable room 5 as storage rooms. In the configuration example shown in FIG. 1, the refrigerating chamber 1 is provided at the uppermost part of the main body of the freezer / refrigerator 100, and the ice making chamber 2 and the small freezing chamber 3 are provided in parallel below the refrigerating chamber 1 (in the direction opposite to the Z-axis arrow). Has been done. A freezing room 4 is arranged under the ice making room 2 and a small freezing room 3, and a vegetable room 5 is arranged under the freezing room 4. In the first embodiment, a case where the storage chamber is the refrigerating chamber 1 in the box body 100A having a plurality of storage chambers will be described.

The freezer / refrigerator 100 has a double door that covers the opening of the refrigerator compartment 1. The double door is composed of a left door 7 and a right door 8 that open and close the opening of the refrigerator compartment 1. The refrigerating room 1 is provided with a partition plate 9 for preventing the intrusion of outside air when the double doors are closed. The length of the partition plate 9 in the vertical direction (Z-axis arrow direction) is equivalent to the length in the vertical direction of the refrigerating chamber 1 shown in FIG. The freezer / refrigerator 100 may have double doors, and the arrangement of these storage chambers is not limited to the configuration shown in FIG.

As shown in FIG. 2, the refrigerator-freezer 100 includes a heater 18, a compressor 51, a condenser 52, a decompression device 53, an evaporator 54, a fan 55, a damper device 56, and a control unit 60. The compressor 51, the condenser 52, the decompression device 53, and the evaporator 54 are connected by a refrigerant pipe to form a refrigerant circuit 57 through which the refrigerant circulates.

The compressor 51 compresses and discharges the refrigerant, and circulates the refrigerant in the refrigerant circuit 57. The compressor 51 is, for example, an inverter type compressor whose capacity can be varied. The condenser 52 is a heat exchanger that causes the refrigerant to exchange heat with the outside air. The condenser 52 is, for example, a condensing pipe that takes heat from the refrigerant and discharges it to the outside of the freezer / refrigerator 100. The condensation pipe is provided on the side surface of the housing of the freezer / refrigerator 100. The decompression device 53 decompresses and expands the refrigerant. The decompression device 53 is, for example, a capillary tube. The evaporator 54 is a heat exchanger that causes the refrigerant to exchange heat with the air in the refrigerator. The fan 55 supplies the cooled air to the refrigerating chamber 1, the freezing chamber 4, and the like by exchanging heat with the refrigerant in the evaporator 54. The fan 55 is, for example, a propeller fan. The damper device 56 adjusts the supply amount of cold air supplied to the refrigerating chamber 1, the freezing chamber 4, and the like by changing the opening degree of the baffle. The heater 18 is provided on the partition plate 9 shown in FIG. 1 to prevent dew condensation on the surface of the partition plate 9.

Further, the freezer / refrigerator 100 has a plurality of sensors for temperature control of the refrigerating chamber 1 and the freezing chamber 4, and energization control of the heater 18. Specifically, the refrigerator-freezer 100 has a freezer room temperature sensor 71, a refrigerating room temperature sensor 72, an outside air temperature sensor 73, and an outside air humidity sensor 74. The freezing room temperature sensor 71 is provided in the freezing room 4 and detects the freezing room temperature Tf. The refrigerating room temperature sensor 72 is provided in the refrigerating room 1 and detects the refrigerating room temperature Ti. The outside air temperature sensor 73 detects the outside air temperature To as the ambient environment of the freezer / refrigerator 100. The outside air humidity sensor 74 detects the outside air humidity Mo as the ambient environment of the freezer / refrigerator 100. The outside air temperature sensor 73 and the outside air humidity sensor 74 are provided, for example, on the upper hinge portion of the left door 7 (not shown in the drawing). The refrigerating chamber temperature sensor 72 serves not only to control the temperature of the refrigerating chamber 1 but also to compensate the temperature of the surface of the partition plate 9 for optimally energizing the heater 18.

The freezing room temperature sensor 71 may be installed at any position as long as it can detect the temperature of the freezing room temperature sensor. The refrigerating room temperature sensor 72 may be installed at any position as long as it can detect the temperature of the refrigerated object. The installation location of the outside air temperature sensor 73 is not limited as long as it can detect the outside air temperature To as the ambient environment. The installation location of the outside air humidity sensor 74 is not limited as long as it can detect the outside air humidity Mo as the surrounding environment.

However, it is desirable that the outside air temperature sensor 73 and the outside air humidity sensor 74 are installed in a place that is not affected by the operation of the freezer / refrigerator 100. For example, since the temperature of the condensed pipe (not shown) fixed to the side surface of the housing becomes high while the refrigerator / freezer 100 is in operation, the outside air temperature sensor 73 and the outside air humidity sensor 74 are not affected by heat radiation from the condensed pipe. It is desirable to install it in a position. For example, when the outside air temperature sensor 73 and the outside air humidity sensor 74 are installed at the upper hinge portion of the left door 7 or the right door 8, they are not affected by the heat of the condensed pipe (not shown).

FIG. 3 is a cross-sectional view taken along the line AA shown in FIG. With the partition plate 9 as a boundary, the upper side of FIG. 3 (in the direction of the Y-axis arrow) is the inside of the refrigerator, and the lower side of FIG. 3 (the direction opposite to the Y-axis arrow) is the outside of the refrigerator. The partition plate 9 is a rectangular parallelepiped having a rectangular cross section on a horizontal plane (XY plane). The left door inner plate 10 is provided inside the left door 7 shown in FIG. 1, and the right door inner plate 11 is provided inside the right door 8. The left door inner plate 10 is provided with a standing wall 15 inside the refrigerator. The right door inner plate 11 is provided with a standing wall 16 inside the refrigerator.

When the double doors of the refrigerator compartment 1 are closed, the partition plate 9 is located between the standing wall 15 and the standing wall 16 as shown in FIG. The partition plate 9 is attached to the left door 7 by a hinge mechanism (not shown). The partition plate 9 is configured to be rotatable with respect to the axis of the hinge mechanism (parallel to the direction of the Z-axis arrow).

The partition plate 9 has a sheet metal member 17, a heater 18, and a heat insulating material 19. As shown in FIG. 3, a sheet metal member 17 having both ends bent inward is attached to the outer surface of the partition plate 9. A heater 18 is arranged inside the chamber of the sheet metal member 17. Since the aluminum foil 14 covers the heater 18 and is glued or attached to the sheet metal member 17 with double-sided tape, the heater 18 is fixed to the sheet metal member 17.

Further, in the partition plate 9, the heat insulating material 19 is arranged inside the refrigerator with respect to the sheet metal member 17 and the heater 18. The heat insulating material 19 suppresses the heat of the heater 18 from being conducted to the inside of the refrigerator. The back surface (the surface in the direction of the Y-axis arrow) and the side surface (the surface in the direction of the X-axis arrow and the surface in the direction opposite to the X-axis arrow) of the heat insulating material 19 are covered with the resin member 20 inside the refrigerator. The outer side resin member 28 fitted between the sheet metal member 17 and the heat insulating material 19 covers a part of the side surface of the inner side resin member 20.

The left door gasket 22 is fitted in the groove 24 of the left door inner plate 10. The right door gasket 23 is fitted in the groove 24 of the right door inner plate 11. As shown in FIG. 3, with the double doors of the refrigerating chamber 1 closed, each of the left door gasket 22 and the right door gasket 23 is provided with a magnet 25 at a position facing the sheet metal member 17 of the partition plate 9. When the double door of the refrigerating chamber 1 is closed, the sheet metal member 17 is attracted to the magnet 25 by a magnetic force, so that the left door gasket 22 and the right door gasket 23 are in close contact with the sheet metal member 17 of the partition plate 9 and refrigerated from outside the refrigerator. Block the intrusion of outside air into room 1.

Further, a packing 29 is provided on the partition plate 9 side of the left door inner plate 10. On the partition plate 9 side of the right door inner plate 11, a part of the right door gasket 23 projects inward along the standing wall 16. The protruding portions of the packing 29 and the right door gasket 23 suppress heat leakage from the heater 18 to the periphery of the partition plate 9.

When the user opens the left door 7, the partition plate 9 is hooked by the protrusion of the guide component installed on the top surface of the refrigerating chamber 1 in the groove shape provided at the upper end of the partition plate 9. Therefore, the partition plate 9 rotates counterclockwise around the axis of the hinge mechanism (not shown) of the left door 7 and is integrated with the standing wall 15 along the standing wall 15. On the other hand, when the user closes the left door 7, the partition plate 9 is caught by the protrusion of the guide component installed on the top surface of the refrigerating chamber 1 in the groove shape provided at the upper end of the partition plate 9. Therefore, the partition plate 9 rotates clockwise around the axis of the hinge mechanism (not shown) of the left door 7 so as to be separated from the standing wall 15. As a result, the partition plate 9, the left door inner plate 10 and the right door inner plate 11 are in the state shown in FIG. In this way, the partition plate 9 serves to prevent outside air from entering the refrigerating room 1 from between the left door 7 and the right door 8 of the refrigerating room 1 when the double doors are closed.

Next, the configuration of the control unit 60 will be described. FIG. 4 is a functional block diagram of the control unit shown in FIG. The control unit 60 is, for example, a microcomputer. As shown in FIG. 2, the control unit 60 has a memory 61 for storing a program and a CPU (Central Processing Unit) 62 for executing processing according to the program. As shown in FIG. 4, the control unit 60 includes a refrigeration cycle control means 65 and a heater control means 66. When the CPU 62 executes the program, the freezing cycle control means 65 and the heater control means 66 are configured in the freezer / refrigerator 100.

The refrigerating cycle control means 65 controls the refrigerating cycle of the refrigerant circuit 57 based on the refrigerating chamber temperature Tf, the refrigerating chamber temperature Ti, the refrigerating chamber target temperature, and the refrigerating chamber target temperature Ts. Specifically, the freezing cycle control means 65 controls the rotation speed of the compressor 51 so that the freezing room temperature Tf matches the freezing room target temperature. Further, the refrigerating cycle control means 65 controls the rotation speed of the fan 55 and the opening degree of the baffle of the damper device 56 so that the refrigerating chamber temperature Ti matches the refrigerating chamber target temperature Ts. The refrigerating room target temperature Ts is stored in the memory 61.

The heater control means 66 controls the energization rate to the heater 18 based on the reference energization rate DRref calculated from the outside air temperature To and the outside air humidity Mo. The energization rate indicates the ratio of time for energizing the heater 18 at the rated current. For example, the energization rate when energizing for 5 seconds out of 10 seconds is (5 [s] / 10 [s]) × 100% = 50%. The reference energization rate DRref is an energization rate at which dew does not adhere to the surface of the partition plate 9. The reference energization rate DRref is calculated from the outside air temperature To and the relative humidity Mr. of the outside air by using the calculation formula described later. The relative humidity Mrh is obtained from the outside air temperature To and the outside air humidity Mo based on the determined psychrometric chart. The formula for calculating the relative humidity Mr from the outside air temperature To and the outside air humidity Mo is registered in the program stored in the memory 61.

The reference energization rate DRref will be described. 5 and 6 are graphs showing a calculation formula for obtaining a reference energization rate from the outside air temperature and relative humidity. As the reference energization rate DRref, for example, as shown in FIG. 5, calculation formulas PF1 to PF3 having the outside air temperature To as a parameter are set. In the example shown in FIG. 5, the case of three temperature zones of outside air temperature To ≦ 20 ° C. or lower, 20 ° C. <outside air temperature To ≦ 30 ° C., and 30 <outside air temperature To ≦ 40 ° C. is shown. The reference energization rate DRref increases linearly as the relative humidity Mr increases according to the respective calculation formulas PF1 to PF3.

Further, FIG. 6 is a graph showing another calculation formula for the reference energization rate DRref. As shown in FIG. 6, the reference energization rate DRref is set to the calculation formulas LF1 to LF3 with the outside air temperature To as a parameter. Similar to FIG. 5, FIG. 6 also shows a case where there are three temperature zones. The reference energization rate DRref increases logarithmically as the relative humidity Mrh increases according to the respective calculation formulas LF1 to LF3.

The calculation formulas PF1 to PF3 shown in FIG. 5 and LF1 to LF3 shown in FIG. 6 are examples, and the calculation formula of the reference energization rate DRref is a structure such as the thermal conductivity of the material of the partition plate 9 and the thickness of the partition plate 9. , Determined by the rated wattage of the heater 18 and the set temperature inside the refrigerator. The reference energization rate DRref is calculated by substituting the relative humidity Mr. calculated from the outside air temperature To and the outside air humidity Mo into the calculation formula determined by which temperature zone the detected outside air temperature To belongs to. .. Which calculation formula is optimal under which condition is determined in advance by a development test or the like, and the calculation formula determination procedure is registered in a program stored in the memory 61.

For example, the calculation formulas PF1 to PF3 shown in FIG. 5 are represented by the reference energization rate DRref = A × Mrh + B. In this equation, the coefficients of A and B are set for each temperature zone of the outside air temperature To. Further, the calculation formulas LF1 to LF3 shown in FIG. 6 are represented by the reference energization rate DRref = C × lnMhr + D when the natural logarithm is represented by the symbol of ln. The coefficients C and D are set for each temperature zone of the outside air temperature To. These coefficients are determined in advance by a development test or the like, and are registered in a program stored in the memory 61.

In the first embodiment, as shown in FIGS. 5 and 6, the case where the temperature zone for determining the calculation formula is three has been described, but the temperature zone is not limited to three. Further, in the first embodiment, the case where the width of the temperature zone is 10 ° C. or higher has been described, but the width of the temperature zone is not limited to 10 ° C. The width of may be subdivided.

In the first embodiment, the heater control means 66 calculates the reference energization rate DRrer as described above, and then uses the corrected energization rate DRa to be output to the heater 18 as the reference energization rate as shown in the equation (1). Calculated by multiplying DRref by the energization coefficient kt.

Before explaining the energization coefficient kt in the formula (1), the heat input from the outside to the inside of the refrigerator through the partition plate 9 will be described. FIG. 7 is a model diagram showing heat transfer from the outside air to the refrigerating room shown in FIG. In FIG. 7, αo is the heat transfer coefficient outside the refrigerator [W / (m ² · K)], and αi is the heat transfer coefficient inside the refrigerator [W / (m ² · K)]. λ is the thermal conductivity [W / (m · K)] of the partition plate 9, and d is the thickness [m] of the partition plate 9. Here, the heat input model is simply considered, and the heat transfer amount (heat flux) q [W / m ² ] per unit area passing through the partition plate 9 is calculated by the equation (2) from the heat transfer shown in FIG. It is calculated. In the formula (2), the unit of the outside air temperature To and the refrigerating room temperature Ti is Kelvin [K].

Of the right side of the equation (2), the preceding term of the (To-Ti) term is called the heat transfer coefficient. The thermal conductivity of the partition plate 9 is originally calculated from the thermal conductivity of the sheet metal member 17 shown in FIG. 3, the thermal conductivity of the heat insulating material 19, and the thermal conductivity of the resin member 20 inside the refrigerator. Here, the partition plate 9 is simply treated as one member, and the thermal conductivity of the partition plate 9 is λ.

Further, when considering the heat input model strictly three-dimensionally, it is necessary to consider the influence of the heat bridge that wraps around the refrigerating chamber 1 from the outside of the side surface of the partition plate 9. In the first embodiment, since the side surface of the partition plate 9 is covered with the resin, it is considered that the heat transfer amount due to the influence of the heat bridge on the outside of the side surface of the partition plate 9 is smaller than the heat transfer amount q. Therefore, here, the heat input model is simply considered as a two-dimensional heat transfer. Further, the thermal conductivity λ can be regarded as a physical property value determined by the material of each member such as the sheet metal member 17, the heat insulating material 19, and the resin member 20 inside the refrigerator. Therefore, the thermal conductivity λ does not change due to the influence of the operation of the refrigerator / freezer 100, for example, the heat influence of the condensed pipe and the heat influence when the heater 18 is energized.

It is presumed that the heat transfer coefficient αo on the outside of the refrigerator depends on the air flow velocity on the surface of the partition plate 9, but it is assumed that the wind speed in the environment where the freezer / refrigerator 100 is installed is small. Further, although a part of the surface of the partition plate 9 is exposed to the outside air, the partition plate 9 is arranged in the back of a narrow gap between the left door 7 and the right door 8, so that the refrigerator / freezer 100 has a freezer / refrigerator 100. It is not easily affected by the surrounding wind speed. On the other hand, when the air near the surface of the partition plate 9 is warmed due to the heat generated by the heater 18, a temperature difference occurs between the air near the surface of the partition plate 9 and the outside air, and the air flow due to the natural convection generated by the temperature difference occurs. is assumed. However, even considering the air flow generated by the energization of the heater 18, the heat transfer coefficient αo is ^{as small as 3 to 4 [W / (m 2} · K)], and the refrigerator / freezer 100 is in operation. However, since the change in the heat transfer coefficient αo is small, the heat transfer coefficient αo can be considered to be a fixed value.

Further, regarding the heat transfer coefficient αi inside the refrigerator, it is considered that the wind speed in the refrigerating chamber 1 changes depending on the rotation speed of the fan 55. However, usually, the wind speed of the outlet of the refrigerating chamber 1 is about 3 [m / s] at the maximum, although it depends on the outlet air passage and the outlet shape of the cold air. Further, when the double doors are closed, the standing walls 15 and 16 are arranged on the side surfaces of the partition plate 9 in the refrigerating room 1. Therefore, it is assumed that the standing walls 15 and 16 become obstacles to the cold air from the outlet, and the wind blow to the partition plate 9 becomes weak. Further, when food or the like is placed on the shelf of the refrigerator compartment 1, it is assumed that the food becomes an obstacle to the cold air from the outlet and the wind blow to the partition plate 9 is further weakened. Therefore, the wind speed to the partition plate 9 inside the refrigerator is a value close to 0 [m / s].

From these assumptions, the heat input model in the partition plate 9 is similar to the equation (2).

Next, the analysis result of the wind speed distribution of the refrigerating chamber in the freezer / refrigerator 100 of the first embodiment will be described. The internal volume of the refrigerator compartment 1 used in the analysis is 271 liters. The diameter of the fan 55 is φ120 mm, and the rotation speed of the fan 55 is 2000 rpm. FIG. 8 is a diagram showing the flow velocity distribution of the entire cold air inside the refrigerating chamber shown in FIG. FIG. 9 is an enlarged view showing the flow velocity distribution of cold air in the uppermost shelf in the refrigerating room inside shown in FIG.

In FIGS. 8 and 9, the left side of the figure (direction opposite to the Y-axis arrow) is the front side of the freezer / refrigerator 100, and the right side of the figure (direction of the Y-axis arrow) is the back side of the freezer / refrigerator 100. In FIGS. 8 and 9, the left end of the figure is located on the back surface (side surface in the direction of the Y-axis arrow) of the partition plate 9 shown in FIG. 8 and 9 show the magnitude of the flow velocity drawn by wind speed contour lines as the analysis result of the flow velocity distribution inside the refrigerating chamber 1.

In FIGS. 8 and 9, in the refrigerator / freezer 100, the shelves 13 and the door pockets 12 are shown by broken lines, and the wind speed contour lines 35 to 38 are shown by solid lines. The wind speed of the wind speed contour lines 35 shown in FIGS. 8 and 9 is 0.1 [m / s]. In FIG. 9, the wind speed of the wind speed contour line 36 is 0.2 [m / s], the wind speed of the wind speed contour line 37 is 0.3 [m / s], and the wind speed of the wind speed contour line 38 is 0.4 [m / s]. s]. Inside the wind speed contour line 38 shown in FIG. 9, there is a place where the wind speed is higher than 0.4 [m / s], but in FIG. 9, it is shown that the wind speed contour line is higher than the wind speed 0.4 [m / s]. It is omitted.

As shown by a broken line in FIG. 8, on the back side of the refrigerating chamber 1, there are an outlet air passage 39 through which cold air flows, a plurality of outlets 30 to 34 arranged on a plurality of shelves 13 of the refrigerating chamber 1, and refrigeration. A return port 40 is provided so that the cold air flowing through the chamber 1 returns to the evaporator 54. The cold air cooled by the evaporator 54 functioning as a cooler flows from the evaporator 54 into the refrigerating chamber 1 from the outlets 30 to 34 via the outlet air passage 39 by the fan 55. Table 1 shows the numerical analysis results of the wind speeds of the outlets 30 to 34. In Table 1, the rotation speed of the fan 55 is 2000 rpm.

Referring to Table 1, the wind speed of the outlet 30 is the highest among the outlets 30 to 34. Explain the reason. The temperature of the uppermost shelf 13 of the refrigerator compartment 1 tends to rise more easily than the other shelves 13 due to heat leakage from the uppermost surface of the freezer / refrigerator 100. In order to equalize the temperature distribution of each storage chamber divided by the plurality of shelves 13, the cross-sectional area of the outlet 30 is the cross-sectional area of the other outlets 31 to 34 so that the air volume in the uppermost shelf 13 is large. Greater than. Further, since the outlet 30 is located near the end of the outlet air passage 39, the cold air folded back at the end of the outlet air passage 39 is also added, so that the wind speed tends to increase.

From the analysis results, it can be seen that the wind speed near the back surface of the partition plate 9 shown at the left end of FIGS. 8 and 9 is a value close to 0 [m / s] at any height in the refrigerating chamber 1. Therefore, in the formula (2), the thermal conductivity αi inside the refrigerator is also considered to be as small as about ^{3 to 4 [W / (m 2 · K)] like the thermal conductivity αo outside the refrigerator.} Further, it is considered that the thermal conductivity αi inside the refrigerator hardly changes even if the operating state of the freezer / refrigerator 100, for example, the rotation speed of the fan 55 changes.

From the above, if the ambient environment including the outside air temperature To and the outside air humidity Mo is stable and the energization rate of the heater 18 does not change, the heat transfer coefficient in the formula (2) is fixed during the operation of the freezer / refrigerator 100. It is considered to be a value or a value that hardly changes. As a result, the heat flux q passing through the partition plate 9 is proportional to the temperature difference ΔT between the outside air temperature To outside the refrigerator and the refrigerating chamber temperature Ti inside the refrigerator.

In order to prevent dew from adhering to the surface of the partition plate 9, the surface temperature may be set above the dew point. Since the heat flux q passing through the partition plate 9 is proportional to the temperature difference ΔT between the outside air temperature To and the refrigerating chamber temperature Ti, if the energization to the heater 18 is controlled in proportion to the temperature difference ΔT, the surface of the partition plate 9 can be controlled. It can be seen in principle that the temperature is maintained at a temperature that does not cause dew condensation. That is, the energization coefficient kt in the equation (1) may be set to a value proportional to the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti. In the first embodiment, the heater control means 66 calculates the energization coefficient kt according to the equation (3).

In the formula (3), the numerator is the temperature difference ΔT between the outside air temperature To and the refrigerating chamber temperature Ti, and the denominator is the temperature difference between the outside air temperature To and the refrigerating chamber target temperature Ts. The refrigerating room target temperature Ts is a fixed value set as, for example, 3 ° C. The heater control means 66 sets the energization coefficient kt according to the equation (3).

When the refrigerating room temperature Ti is high, for example, after the refrigerator / freezer 100 is installed and immediately after the power is turned on, the refrigerating room temperature Ti is the same as the outside air temperature To. For example, when the outside air temperature To is detected as 30 ° C. and the refrigerating chamber temperature Ti is also detected as 30 ° C., the heat flux q passing through the partition plate 9 is also 0, so that the heater 18 does not need to heat the partition plate 9. It becomes. In this case, in the formula (3), the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti becomes 0, and the heater control means 66 calculates the energization coefficient kt as 0. As a result, the heater control means 66 calculates the corrected energization rate DRa as 0% from the equation (1).

After the power is turned on to the freezer / refrigerator 100, the freezer / refrigerator 100 is operated, so that the refrigerating room temperature Ti gradually decreases. When the refrigerating chamber temperature Ti reaches the refrigerating chamber target temperature Ts, the numerator value and the denominator value on the right side of the equation (3) become the same, and the heater control means 66 calculates the energization coefficient kt as 1. As a result, in the formula (1), the corrected energization rate DRa becomes the same as the reference energization rate DRref, and the heater control means 66 calculates the reference energization rate DRref as the corrected energization rate DRa.

After that, the refrigerating chamber temperature Ti may become lower than the refrigerating chamber target temperature Ts. In this case, the energization coefficient kt becomes larger than 1, and the corrected energization rate DRa becomes larger than the reference energization rate DRref. Therefore, the reference energization rate DRref is set as the upper limit value of the corrected energization rate DRa. This makes it possible to prevent the heater 18 from being energized more than necessary.

As shown in the equation (3), the energization coefficient kt is a function of the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti. Therefore, when the heater control means 66 calculates and updates the temperature difference ΔT at regular intervals, the surrounding environment is stable and the refrigerating room temperature Ti drops linearly from the power-on, linearly. The corrected energization rate DRa changes. Therefore, the energization rate of the heater 18 can be optimally controlled with respect to the change in the refrigerating chamber temperature Ti.

Further, even in a situation where the surrounding environment is not stable, as shown in the equation (3), the energization coefficient kt also changes according to the surrounding environment, so that the corrected energization rate DRa also changes in response to the change in the energization coefficient kt. Therefore, the energization rate of the heater 18 can be optimally controlled in response to changes in the surrounding environment.

Next, the procedure of the heater energization control executed by the heater control means 66 will be described. FIG. 10 is a flowchart showing an example of the procedure of heater energization control executed by the heater control means shown in FIG.

When the heater control means 66 acquires the outside air temperature To from the outside air temperature sensor 73 (step S1), the heater control means 66 determines a calculation formula for calculating the reference energization rate DRref based on the outside air temperature To (step S2). FIG. 10 shows the case of the calculation formulas PF1 to PF3 shown in FIG. 5 as the calculation formula options, but the calculation formula options are not limited to the calculation formulas PF1 to PF3 shown in FIG. The calculation formulas LF1 to LF3 shown in the above may be used. When the calculation formula is determined in step S3, the heater control means 66 acquires the outside air humidity Mo from the outside air humidity sensor 74 (step S4). Then, the heater control means 66 calculates the reference energization rate DRref using the calculation formula determined in step S3 and the relative humidity Mr calculated from the outside air temperature To and the outside air humidity Mo (step S5).

Subsequently, when the heater control means 66 acquires the refrigerating room temperature Ti from the refrigerating room temperature sensor 72 (step S6), the heater control means 66 uses the formula (3), the outside air temperature To, the refrigerating room temperature Ti, and the refrigerating room target temperature Ts. To calculate the energization coefficient kt (step S7). The heater control means 66 calculates the corrected energization rate DRa by multiplying the reference energization rate DRref by the energization coefficient kt according to the equation (1) (step S8). The heater control means 66 energizes the heater 18 according to the calculated corrected energization rate DRa (step S9).

Note that FIG. 10 shows a case where the refrigerating room temperature Ti is acquired in step S6 and the energization coefficient kt is calculated in step S7. It is not limited to the case shown in 10. The acquisition timing of the refrigerating room temperature Ti and the calculation timing of the energization coefficient kt may be any timing as long as it is between the acquisition of the outside air temperature To and the calculation of the corrected energization rate DRa. Further, if the control cycle shown in the procedure of FIG. 10 is too long, changes and deviations in the surrounding environment may occur. Therefore, for example, a cycle of 1 minute or less is desirable.

In the first embodiment, the heater control means 66 calculates the reference energization rate DRrer according to the procedure shown in FIG. 10, and then multiplies the reference energization rate DRref by the energization coefficient kt as the energization rate to be output to the heater 18. And calculate. Since the energization coefficient kt increases as the refrigerating chamber temperature Ti decreases, it is possible to prevent the energization rate of the heater 18 from becoming unnecessarily large. As a result, the power consumption of the freezer / refrigerator 100 can be reduced.

Next, the result of the test comparing the heater energization control of the first embodiment and the heater energization control of the comparative example will be described.

The conditions of this test will be explained. The outside air temperature was constant at 30 ° C. and the relative humidity was constant at 75% RH. For the test, a freezer / refrigerator having an overall rated internal volume of 517 liters and a refrigerating chamber 1 having a rated internal volume of 277 liters was used. A heater having an electric power of 11.1 W was used as the heater 18. No food is placed in the refrigerator, and the doors of each storage room are not opened or closed. Further, a brass temperature mass was installed on the shelf 13 of the refrigerating room 1, and a temperature mass was also installed in the freezing room 4.

In this test, in order to compare the transient state of the refrigerating room temperature Ti in the two heater energization controls, the power is turned on to the refrigerator / freezer with the surface temperature of the temperature mass and the partition plate 9 being 30 ° C, which is the same as the outside air temperature. , The temperature measurement was started when the power was turned on. In this test, 54% calculated from an outside air temperature of 30 ° C. and a relative humidity of 75% RH was used as the reference energization rate. In the comparative example, the heater is energized with a reference energization rate of a certain value from the start of turning on the power of the refrigerator / freezer.

FIG. 11 is a graph showing a temperature change from the start of turning on the power when the outside air temperature is 30 ° C. and the relative humidity is 75% RH in the heater energization control according to the first embodiment of the present invention. FIG. 12 is a graph showing a temperature change from the start of power-on when the outside air temperature is 30 ° C. and the relative humidity is 75% RH in the heater energization control of the comparative example. In FIGS. 11 and 12, it is omitted to add a scale to the power consumption.

In FIG. 11, the waveform 201 shows the time change of the power consumption of the freezer / refrigerator. In the period TP1 of the waveform 201, since the initial stage is from the start of turning on the power, the refrigerating cycle control means 65 increases the rotation speeds of the compressor 51 and the fan 55 in order to cool the inside of the refrigerator quickly. In the period TP1, since the refrigerator / freezer operates the compressor 51 and the fan 55 to perform the cooling operation after the power is turned on, the refrigerating chamber temperature 203, the refrigerating chamber mass temperature 204, and the refrigerating chamber mass temperature 205 Each temperature decreases with the passage of time. When the temperature inside the refrigerator drops to the target temperature, the compressor 51 and the fan 55 temporarily stop operating. During the period TP2, the compressor 51 and the fan 55 resume operation, and the waveform of each temperature is disturbed. After that, from the period TP3 to TP5, the compressor 51 and the fan 55 operate stably at a low rotation speed, and the temperatures of the refrigerating chamber temperature 203, the refrigerating chamber mass temperature 204, and the freezing chamber mass temperature 205 are stabilized.

As described above, the temperatures of the refrigerating chamber temperature 203, the refrigerating chamber mass temperature 204, and the freezing chamber mass temperature 205 are transiently changed in the period TP1 from the start of turning on the power to the refrigerator / freezer, and the periods TP3 to TP5. Then it will be stable. Referring to the comparative example of FIG. 12, the waveform 301 showing the time change of the power consumption of the freezer / refrigerator shows the same change as the waveform 201. Further, the temperature changes of the refrigerating chamber temperature 303, the refrigerating chamber mass temperature 304, and the freezing chamber mass temperature 305 shown in FIG. 12 are the same as the temperature changes of the refrigerating chamber temperature 203, the temperature 204, and the temperature 205 shown in FIG. There is a similar tendency.

Comparing the refrigerating room temperature 203 and the refrigerating room mass temperature 204 with reference to the graph shown in FIG. 11, the refrigerating room temperature 203 is slightly higher than the temperature 204 in the period TP1. This is because the refrigerating room temperature sensor 72 is installed at a position where the cold air blown out from the back side of the refrigerating room 1 (in the direction of the Y-axis arrow shown in FIG. 8) does not directly hit, whereas the refrigerating room mass is cold air. Is because it hits directly. Since these temperature differences are small, it can be seen that the refrigerating chamber temperature sensor 72 can more accurately detect the temperature of the storage chamber of the refrigerating chamber 1.

With reference to FIGS. 11 and 12, let us compare the surface temperature of the partition plate 9 during the period TP1 in which the temperature inside the refrigerator changes transiently. In FIG. 11, the surface temperature 202 of the partition plate 9 is constant at around 35 ° C. On the other hand, in the comparative example of FIG. 12, the surface temperature 302 of the partition plate has risen to 47.8 ° C. This is because, in the comparative example, the heater is energized at a reference energization rate of a constant value as the energization rate even in a state where the refrigerating chamber is not sufficiently cooled as in the period TP1. The dashed lines shown in FIGS. 11 and 12 indicate that the temperature is 35 ° C.

In the heater energization control of the first embodiment, the corrected energization rate DRa obtained by multiplying the reference energization rate DRref by the energization coefficient Kt reflecting the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti as the energization rate to the heater 18. Is used. Therefore, the energization rate gradually increases from the start of turning on the power of the refrigerator / freezer 100, and as described above, the heater 18 is energized at an energization rate proportional to the temperature difference ΔT. As a result, as shown in FIG. 11, when the surface temperature 202 of the partition plate 9 and the broken line are compared, the surface temperature 202 changes from the initial stage of the period TP1 to the same temperature as when the periods TP3 to TP5 are stable. There is. Further, since the dew point temperature is about 25 ° C. when the outside air temperature is 30 ° C. and the relative humidity is 75% RH, dew is attached to the surface of the partition plate 9 even in the heater energization control of the first embodiment. It never happened.

Here, regarding the heater energization control of the first embodiment, changes in the energization coefficient kt, the reference energization rate DRref, and the corrected energization rate DRa with respect to the change in the refrigerating chamber temperature 203 shown in FIG. 11 will be described. FIG. 13 is a diagram showing time changes of the refrigerating chamber temperature, energization coefficient, reference energization rate, and corrected energization rate in the heater energization control according to the first embodiment of the present invention. In FIG. 13, it is omitted to add a scale to the power consumption and the energization rate.

As shown in FIG. 13, as the refrigerating room temperature 203 decreases from the power-on to the refrigerator-freezer 100, the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature 203 increases from 0, so that the energization coefficient kt is From the time the power is turned on, it grows to the right. On the other hand, since the reference energization rate DRref is determined by the outside air temperature To and the outside air humidity Mo, it is stable at a constant value during the periods TP1 to TP5.

Since the corrected energization rate DRa is obtained by multiplying the reference energization rate DRref by the energization coefficient kt, it linearly rises upward in the period TP1. At the end of the period TP1, the refrigerating chamber temperature 203 reaches the refrigerating chamber target temperature Ts, so that the reference energization rate DRref and the corrected energization rate DRa become the same value, and the energization rate to the heater 18 is the reference energization rate DRref. Continued at.

Next, regarding the power consumption of the freezer / refrigerator, the test results of the heater energization control of the first embodiment and the heater energization control of the comparative example will be described. Table 2 is a table showing the power consumption and the electric energy consumption of the refrigerator / freezer in the period TP1 shown in FIGS. 11 and 12.

Focusing on the power consumption in Table 2, it can be seen that the first embodiment is improved by about 2% as compared with the comparative example. This is due to the reduction of the energization rate to the heater 18 as can be seen from the waveform of the corrected energization rate DRa of the period TP1 in FIG.

Further, when comparing the cooling speeds of the temperatures 204 and 304 of the refrigerating chamber mass, for example, the time until the temperature reaches 3 ° C. from 30 ° C. with reference to FIGS. 11 and 12, the first embodiment is compared. Compared to the example, an improvement of about 3 minutes was seen.

Next, in the case where the outside air temperature is 30 ° C. and the relative humidity is 55% RH, a test result comparing the heater energization control of the first embodiment and the heater energization control of the comparative example will be described. Since the other test conditions are the same as those described with reference to FIGS. 11 and 12, detailed description thereof will be omitted. In this test, the reference energization rate was calculated to be 22% from the outside air temperature of 30 ° C. and the relative humidity of 55% RH.

FIG. 14 is a graph showing a temperature change from the start of power-on when the outside air temperature is 30 ° C. and the relative humidity is 55% RH in the heater energization control according to the first embodiment of the present invention. FIG. 15 is a diagram showing each temperature waveform at the time of turning on the power when the outside air temperature is 30 ° C. and the outside air humidity is 55% RH in the heater energization control of the comparative example.

FIG. 14 shows the time variation of the power consumption waveform 211 of the refrigerator / freezer of the first embodiment, the surface temperature 212 of the partition plate 9, the refrigerating chamber temperature 213, the refrigerating chamber mass temperature 214, and the freezing chamber mass temperature 215. .. FIG. 15 shows the time variation of the power consumption waveform 311 of the refrigerator / freezer of the comparative example, the surface temperature 312 of the partition plate, the refrigerating chamber temperature 313, the refrigerating chamber mass temperature 314, and the freezing chamber mass temperature 315. The broken line shown in FIGS. 14 and 15 is a line indicating a temperature of about 24 ° C.

In FIGS. 14 and 15, attention is paid to the period TP1. As shown in FIG. 14, in the heater energization control of the comparative example, the surface temperature 312 of the partition plate rises to 36.3 ° C. and then falls. Even in the subsequent period TP2, the surface temperature 312 of the partition plate fluctuates slightly. On the other hand, in the heater energization control of the first embodiment, the surface temperature 212 of the partition plate 9 temporarily exceeds 30 ° C. after the power is turned on, but gradually decreases, and the period TP2 includes the period TP3 or later. The temperature will be the same as when the temperature is stable. Further, although the dew point under the conditions of this test was about 20 ° C., no dew was observed on the surface of the partition plate 9 in the heater energization control of the first embodiment. In this test as well, it was confirmed that the power consumption of the heater energization control of the first embodiment was reduced to the same extent as the test results described with reference to FIGS. 11 and 12.

In the first embodiment, the structure of the partition plate 9 has been described with reference to FIGS. 1 and 3, but the structure of the partition plate 9 is not limited to the structure described in the first embodiment. The heater 18 may not be provided inside the partition plate 9. For example, the heater 18 may be provided on at least one of the surfaces facing the left door 7 and the right door 8 with the double door closed. Further, the heater 18 may be provided on at least one of the left door gasket 22 and the right door gasket 23. Even in these cases, the heater energization control of the first embodiment can be applied, and the same effect as that of the first embodiment can be obtained.

There are three timings for turning on the power to the refrigerator / freezer: (a) turning on the power at the initial stage of installation due to replacement by purchase, (b) turning on the power again when the power supply is restarted from a power failure, and (c) turning on the power again at the convenience of the user. is assumed. The convenience of the user is, for example, moving the refrigerator / freezer and repairing the refrigerator in case of failure. It will be described that the heater energization control of the first embodiment is effective in any of these assumed situations.

In the case of the assumed situation (a), since the refrigerating room temperature is high near room temperature even before the power is turned on, the corrected energization rate DRa is smaller than the reference energization rate DRref. In the case of the assumed situation (b), if the power failure time is short, the temperature of the refrigerator compartment does not rise significantly, so that the corrected energization rate DRa is equivalent to the reference energization rate DRref. On the other hand, in the case of the assumed situation (b), if the power failure time is long, the temperature of the refrigerating room rises significantly. Along with this, the reference energization rate DRref approaches. In the case of the assumed situation (c), when the heating of the heater 18 is restarted, the refrigerating room temperature becomes closer to room temperature as the power is not supplied for a longer time, similar to the power failure time in the assumed situation (b). Therefore, the corrected energization rate DRa in the assumed situation (c) is controlled in the same manner as in the assumed situation (b) according to the length of time during which the power is not supplied. By controlling the energization rate according to these assumed conditions, it is possible to reduce the amount of power consumption.

Further, with reference to FIG. 13, the case where the energization coefficient kt calculated by the equation (3) is used for the period TP1 from the power-on to the refrigerating room temperature reaching the refrigerating room target temperature has been described. Equation (3) may be applied for a predetermined time from the start. In this case, after the lapse of a predetermined time, the energization coefficient kt is set to a constant value of 1. For example, when a user buys a new refrigerator / freezer and puts food having a temperature near room temperature into a new refrigerator / freezer, the food with a high temperature may be placed near the refrigerator compartment temperature sensor 72. In addition, the user may put the pot containing the cooked food into the refrigerating room 1 at a high temperature. In such a case, it is conceivable that the temperature detected by the refrigerating room temperature sensor 72 is less likely to drop than the average temperature of the refrigerating room 1.

Therefore, the memory 61 stores several hours from the state where the temperature of the refrigerating chamber is high to the time when the target refrigerating temperature is reached, including the time when the object to be cooled is stored in the refrigerating chamber, as a predetermined time. The predetermined time may be registered in advance in the memory 61, or the predetermined time stored in the memory 61 may be updated. The heater control means 66 uses the energization coefficient kt calculated by the equation (3) from the state where the temperature of the refrigerating chamber is high until a predetermined time elapses, and after the elapse of the predetermined time, the energization coefficient kt is set to a constant value of 1. .. It is assumed that the memory 61 stores the reference temperature for determining whether or not the temperature of the refrigerating chamber is high.

Next, the heater energization control of the first embodiment is not limited to the case where the refrigerator / freezer is replaced or the high-temperature object to be cooled is stored in the refrigerating room, but also when the door of the refrigerating room 1 is opened for a long time. Explain that is valid.

There is a difference in the change in the surface temperature of the partition plate depending on which of the left and right doors of the refrigerator compartment is opened, but when the door of the refrigerator compartment is opened for a long time, the conventional heater is energized. Since the control energizes the heater at a constant reference energization rate, the surface temperature of the partition plate tends to rise. On the other hand, in the first embodiment, the left door 7 or the right door 8 of the refrigerating chamber 1 is opened for a long time due to food loading / unloading, etc., and the refrigerating chamber temperature sensor 72 is higher than the refrigerating chamber temperature at the time of stability. When the temperature is detected, the energization coefficient kt becomes a value smaller than that at the time of stability. Therefore, the corrected energization rate DRa represented by the equation (1) becomes a value smaller than the reference energization rate DRref. As a result, the power consumption of the refrigerator / freezer can be reduced, and energy saving can be achieved.

For example, as described with reference to FIG. 3, in a configuration in which the partition plate 9 is attached to the left door 7, the case where the left door 7 is closed and the right door 8 is opened is considered. If the door of the refrigerating chamber 1 is opened for a long time, even if cold air is supplied to the refrigerating chamber 1, it is useless, so that the refrigerating cycle control means 65 may stop the rotation of the fan 55. In addition, the temperature inside the refrigerator rises due to natural convection due to the temperature difference between the cold air inside the refrigerator and the outside air. As a result, the surface temperature of the back surface of the partition plate 9 rises. Conventionally, as described above, since the energization rate to the heater does not change at the reference energization rate, the surface temperature of the partition plate further rises. On the other hand, in the heater energization control of the first embodiment, the energization coefficient kt decreases as the refrigerating chamber temperature rises, so that the corrected energization rate DRa decreases. As a result, the power consumption of the freezer / refrigerator is improved as compared with the conventional case.

On the other hand, when the right door 8 is closed and the left door 7 is open, the partition plate 9 rotates along the standing wall 15 as described with reference to FIG. 3, but the partition plate 9 Most are exposed to the outside air. Therefore, it is considered that the surface temperature of the partition plate 9 rises when the left door 7 is opened as compared with the case where the right door 8 is opened. In this case, since the cold air in the refrigerating chamber 1 is replaced with the outside air, the temperature of the refrigerating chamber also rises, and in the heater energization control of the first embodiment, the corrected energization rate DRa is increased according to the rise in the refrigerating chamber temperature. descend. As a result, the power consumption of the freezer / refrigerator is improved as compared with the conventional case, as in the case where the right door 8 is opened. Even when both the left door 7 and the right door 8 are opened, the temperature of the refrigerator compartment rises and the corrected energization rate DRa decreases, so that the power consumption of the refrigerator / freezer is improved as compared with the conventional case.

However, when the opening time of the door of the refrigerating room is about several minutes, even if the heater control means 66 changes the energization coefficient kt with the change of the refrigerating room temperature, the power consumption is as large as when the power is turned on. It is considered that the reduction effect cannot be obtained. Therefore, when the refrigerating room temperature reaches the refrigerating room target temperature after the power is turned on to the refrigerator / freezer body, the refrigerating room temperature does not fluctuate significantly and stabilizes. Therefore, the energization coefficient kt is set to 1 which is a constant value. May be good. Explaining this with reference to FIG. 13, the heater control means 66 calculates the energization coefficient kt for the equation (1) using the equation (3) in the period TP1, and the energization coefficient after the lapse of the period TP1. You may set kt to 1. After the lapse of the period TP1, the heater control means 66 energizes the heater 18 at the reference energization rate DRref.

Further, the heater energization control of the first embodiment may be performed by setting a threshold value for the opening time of the door of the refrigerating room 1. The opening time of the door of the refrigerating chamber 1, for example, the time during which the refrigerating chamber temperature Ti rises by about 10 ° C. is set as a threshold value. The threshold is, for example, 10 minutes. The refrigerator / freezer 100 is provided with a sensor for detecting the open / closed state of the door of the refrigerator compartment 1, and the heater control means 66 has a timer function. The heater control means 66 uses the energization coefficient kt calculated by the equation (3) when the door opening time is equal to or longer than the threshold value, and sets the energization coefficient kt to a constant value when the door opening time is less than the threshold value. Set to 1. If the door opening time is less than the threshold value, the heater control means 66 energizes the heater 18 at the reference energization rate DRref.

However, since the time change of the refrigerating room temperature Ti when the door is opened also depends on the outside air temperature To, the threshold value does not correspond to any outside air temperature To. Therefore, even if the forced time for forcibly using the energization coefficient kt calculated by the equation (3) is set in consideration of the swing range of the outside air temperature To when the door opening time exceeds the threshold value. good. When the door opening time is equal to or longer than the threshold value, the heater control means 66 uses the energization coefficient kt calculated by the equation (3) from the closing of the door until the forced time elapses, and after the forced time elapses, The energization coefficient kt is set to a constant value of 1. After the forced time elapses, the heater control means 66 energizes the heater 18 at the reference energization rate DRref.

Further, not only when the threshold value is set for the door opening time, the heater energization control may be performed by setting the threshold value for the refrigerating room temperature Ti. The threshold is, for example, 10 ° C. In this case, the heater control means 66 uses the energization coefficient kt calculated by the equation (3) when the refrigerating chamber temperature Ti rises above the threshold value, and when the refrigerating chamber temperature Ti falls below the threshold value, the energizing coefficient Set kt to 1. When the refrigerating chamber temperature Ti becomes lower than the threshold value, the heater control means 66 energizes the heater 18 at the reference energization rate DRref. Even if the opening time of the door is long, it is possible to prevent the surface of the partition plate 9 from condensing and to reduce the power consumption of the heater 18. As a result, energy saving of the freezer / refrigerator 100 can be achieved.

The refrigerating room target temperature Ts is not limited to the temperature set by the user, and the user may be able to select one temperature set value from a plurality of temperature set values. For example, a temperature control panel (not shown in the figure) is provided in the freezer / refrigerator 100, and the user operates the temperature control panel to set the refrigerating room target temperature Ts to one temperature from three types of temperature setting values of weak, medium, and strong. You may select the set value.

Further, in the heater energization control of the first embodiment, the minimum energization rate DRmin may be set. For example, when a high-temperature object to be cooled, such as a pot containing a heat-treated object, is placed near the refrigerating room temperature sensor 72, the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti becomes small. The corrected energization rate DRa calculated from (1) and the equation (3) is lowered. In this case, the surface temperature of the partition plate 9 may drop to a temperature lower than the condensation temperature. Therefore, assuming a case where the refrigerating room temperature Ti rises sharply, the minimum energization rate DRmin is set. The memory 61 stores the minimum energization rate DRmin. The minimum energization rate DRmin is set to, for example, a value of about 10 to 20% of the reference energization rate DRref. When the energization rate DR calculated from the equations (1) and (3) becomes smaller than the minimum energization rate DRmin, the heater control means 66 energizes the heater 18 at the minimum energization rate DRmin. As a result, it is possible to prevent the surface temperature of the partition plate 9 from dropping to a temperature lower than the condensation temperature.

In the refrigerator / freezer 100 of the first embodiment, the current-carrying coefficient kt is calculated from the outside air temperature To, the refrigerating room temperature Ti, and the refrigerating room target temperature Ts, and the current-carrying coefficient kt is multiplied by the reference current-carrying rate DRref to obtain a corrected current-carrying rate DRa. The heater 18 of the partition plate 9 is energized.

According to the first embodiment, since the corrected energization rate DRa reflecting the outside air temperature To, the refrigerating chamber temperature Ti, and the refrigerating chamber target temperature Ts is used for the heater energization control, the surface temperature of the partition plate 9 is higher than the dew condensation prevention temperature. Is suppressed from becoming larger than necessary. Therefore, it is possible to prevent dew from adhering to the partition plate 9, suppress unnecessary power consumption of the heater 18, and reduce the power consumption of the freezer / refrigerator 100. As a result, energy saving of the freezer / refrigerator 100 can be achieved.

In the first embodiment, the heater control means 66 uses the formula (3) for calculating the energization coefficient kt in the formula (1). Since the energization coefficient kt increases as the refrigerating chamber temperature Ti decreases, it is possible to prevent the energization rate of the heater 18 from becoming unnecessarily large. As a result, the power consumption of the freezer / refrigerator 100 can be reduced.

Embodiment 2.
In the second embodiment, a correction coefficient is added to the calculation of the corrected energization rate DRa described in the first embodiment. In the second embodiment, the differences from the freezer / refrigerator described in the first embodiment will be described in detail, and the detailed description of the configuration and operation similar to the first embodiment will be omitted.

The heater control means 66 of the second embodiment calculates the corrected energization rate DRa from the equation (4). As shown in the formula (4), the corrected energization rate DRa of the second embodiment is obtained by multiplying the right side of the calculation formula shown in the formula (1) by the correction coefficient kv.

As shown in FIG. 1, the partition plate 9 has a long length in the vertical direction (Z-axis arrow direction) of the left door 7 and the right door 8 of the refrigerating chamber 1, even if the heater 18 is provided inside. It is possible that the surface temperature is not uniform. As a factor that the surface temperature of the partition plate 9 is not uniform, for example, it is considered that the length of the depth of the refrigerating chamber 1 is small. Further, as another factor, it is conceivable that a fan for circulating the air inside the refrigerating chamber 1 is attached to the refrigerating chamber 1 in addition to the fan 55.

When the length of the depth of the refrigerating chamber 1 is small, the temperature near the center where the cold air supplied from the back surface of the refrigerating chamber 1 directly hits the partition plate 9 is lowered, and the temperatures at the upper end and the lower end are higher than those near the center. Tends to be high. When a fan that circulates the air inside the refrigerating chamber 1 is attached to the refrigerating chamber 1, the temperature of the portion of the partition plate 9 to which the cold air sent out by the fan directly hits tends to be lower than the temperature of the other portions. ..

In such a configuration, the heater control means 66 increases the corrected energization rate DRa by multiplying the reference energization rate DRref of the equation (1) by the correction coefficient kv having a value larger than 1. The memory 61 stores a correction coefficient kv at which the minimum temperature at the surface temperature of the partition plate 9 is equal to or higher than the dew point temperature.

In the second embodiment, the case where the correction coefficient kv is set depending on the configuration of the freezer / refrigerator 100 has been described, but the heater control means 66 selects the correction coefficient kv depending on the outside air temperature To. May be good. For example, the memory 61 stores information in which the outside air temperature To is grouped into a plurality of temperature zones and a plurality of correction coefficients kv are set corresponding to the plurality of temperature zones. The heater control means 66 selects a correction coefficient kv corresponding to the outside air temperature To from a plurality of correction coefficients kv, and energizes the heater 18 with the correction energization factor DRa calculated from the equation (4).

The refrigerator / freezer 100 of the second embodiment energizes the heater 18 with a correction energization rate DRa obtained by multiplying the reference energization rate DRref by a correction coefficient kv larger than 1 and an energization coefficient kt as the energization rate to the heater 18. be. According to the second embodiment, when the surface temperature of the partition plate 9 is not uniform, the correction coefficient kv having a value larger than 1 is multiplied by the reference energization rate DRref, so that the average is averaged over the entire surface of the partition plate 9. It is suppressed that the portion lower than the temperature becomes lower than the dew condensation temperature. As a result, it is possible to prevent the surface of the partition plate 9 from condensing.

Embodiment 3.
In the third embodiment, the heater energization control is performed according to the set temperature selected by the user from a plurality of set temperatures as the refrigerating room target temperature Ts. In the third embodiment, the differences from the freezer / refrigerator described in the first embodiment will be described in detail, and the detailed description of the configuration and operation similar to the first embodiment will be omitted.

FIG. 16 is a functional block diagram showing an example of a control unit of a freezer / refrigerator according to a third embodiment of the present invention. The refrigerator-freezer 100 of the third embodiment is provided with a temperature control panel 80 used when a user sets a refrigerating room target temperature Ts. The user can operate the temperature control panel 80 to select one temperature setting rank from a plurality of temperature setting ranks for the refrigerating room target temperature Ts. As the temperature setting ranks that can be selected by the user, for example, a strong setting of the refrigerating room target temperature Ts = 0 ° C., a medium setting of the refrigerating room target temperature Ts = 3 ° C., and a weak setting of the refrigerating room target temperature Ts = 6 ° C. be.

In the third embodiment, when the user selects one temperature setting rank from a plurality of temperature setting ranks, the refrigerating cycle control means 65 sets the refrigerating room target temperature to the refrigerating room target corresponding to the temperature setting rank selected by the user. The refrigeration cycle is controlled by setting the temperature Ts. Further, the heater control means 66 calculates the energization coefficient kt from the equation (5) according to the temperature setting rank selected by the user. The fixed value is, for example, the temperature difference between the strong setting refrigerating room target temperature Ts and the weak setting refrigerating room target temperature Ts. Here, the fixed value is 6.

In the first embodiment, the term of the denominator of the energization coefficient kt is "outside air temperature To-target temperature Ts of the refrigerating room", whereas in the third embodiment, the user sets one temperature from a plurality of temperature setting ranks. When the rank is selected, the energization coefficient kt is determined according to the equation (5). Further, in the third embodiment, the heater control means 66 uses the energization coefficient kt calculated by the equation (5) even when the refrigerating chamber temperature Ti reaches the refrigerating chamber target temperature Ts. In this case, even after the refrigerating room temperature Ti reaches the refrigerating room target temperature Ts, the corrected energization rate DRa is the refrigerating room target temperature indicated by the temperature setting rank selected by the user according to the equations (1) and (5). Ts is set as a parameter. For example, when the selected temperature setting rank is a strong setting, the refrigerating room target temperature Ts is 0 ° C.

When the heater control means 66 performs an operation of selecting a temperature setting rank while performing heater energization control using the energization coefficient kt calculated by the equation (3), the energization in the equation (1) is performed. The coefficient kt may be changed to the energization coefficient kt calculated by the equation (5).

FIG. 17 is a diagram showing the time transition of the energization rate of the heater in the freezer / refrigerator according to the third embodiment of the present invention. The horizontal axis of FIG. 17 is the time t, and the vertical axis is the corrected energization rate DRa. The time t0 shown in FIG. 17 is the time when the power is turned on to the refrigerator / freezer 100. The time t1 is the time when the refrigerating chamber temperature Ti reaches the refrigerating chamber target temperature Ts.

As shown in FIG. 17, the energization coefficient kt represented by the equation (5) changes with the passage of time from time t0 for each temperature setting rank. The slope of the corrected energization rate DRa from the time t0 to the time t1 differs depending on the temperature setting rank from the time t0. The lower the refrigerating room target temperature Ts, the larger the slope from time t0 to time t1. This is because the lower the refrigerating chamber target temperature Ts, the smaller the denominator of the equation (5).

After the time t1 when the refrigerating room temperature Ti reaches the refrigerating room target temperature Ts at the time t1, the energization coefficient kt becomes a constant value and the corrected energization rate DRa becomes constant. Referring to FIG. 17, in each temperature setting rank, the corrected energization rate DRa after the time t1 is represented by a straight line having a slope = 0. When the corrected energization rate DRa is compared between the temperature setting ranks after the time t1, the corrected energization rate DRa at the strong setting is the largest and the corrected energization rate DRa at the weak setting is the smallest. The corrected energization rate DRa after the temperature of the refrigerating chamber temperature Ti becomes stable is different for each temperature setting rank. FIG. 17 shows that when the refrigerating chamber temperature Ti becomes stable in accordance with the refrigerating chamber target temperature Ts, the energization rate becomes constant in all temperature setting ranks, but the energizing rate differs for each temperature setting rank. ..

Here, the reason why the energization rate is different for each temperature setting rank after the refrigerating chamber temperature Ti reaches the refrigerating chamber target temperature Ts will be described. After the refrigerating chamber temperature Ti reaches the refrigerating chamber target temperature Ts, the numerator and denominator of the formula (5) become the same in the case of the medium setting. That is, in the case of the medium setting, the corrected energization rate DRa becomes the reference energization rate DRref after the time t1. On the other hand, in the case of the strong setting, since the numerator is larger than the denominator in the equation (5) after the time t1, the corrected energization rate DRa becomes a value larger than the reference energization rate DRref. Further, in the case of a weak setting, since the denominator is larger than the numerator in the formula (5) after the time t1, the corrected energization rate DRa becomes a value smaller than the reference energization rate DRref.

Although the description of the third embodiment is based on the first embodiment, the second embodiment may be applied to the third embodiment.

In the freezer / refrigerator 100 of the third embodiment, the energization coefficient kt calculated by the equation (5) is used for the corrected energization rate DRa of the heater 18. According to the third embodiment, the lower the refrigerating chamber target temperature Ts, the larger the slope of the energization rate until the refrigerating chamber temperature Ti stabilizes, and the energizing rate can be increased even after the refrigerating chamber temperature Ti stabilizes. It can be maintained at a large value. Even if the refrigerating chamber temperature Ti drops sharply, the inclination of the energization rate of the heater 18 is large, so that it is possible to prevent dew condensation from forming on the surface of the partition plate 9. Even if the refrigerating chamber temperature Ti is set to a low temperature, the energization rate of the heater 18 is large, so that it is possible to prevent dew condensation from forming on the surface of the partition plate 9 when the user opens and closes the door of the refrigerating chamber 1. ..

1 Refrigerator room, 2 Ice making room, 3 Small freezer room, 4 Freezer room, 5 Vegetable room, 7 Left door, 8 Right door, 9 Damper, 10 Left door inner plate, 11 Right door inner plate, 12 Door pocket, 13 Shelf, 14 aluminum foil, 15, 16 standing wall, 17 sheet metal member, 18 heater, 19 heat insulating material, 20 refrigerator inner resin member, 22 left door gasket, 23 right door refrigerant, 24 groove, 25 magnet, 28 refrigerator outer resin member , 29 packing, 30-34 outlet, 35-38 wind velocity contour, 39 outlet, 40 return, 51 compressor, 52 condenser, 53 decompressor, 54 evaporator, 55 fan, 56 damper device, 57 refrigerant Circuit, 60 Control unit, 61 Memory, 62 CPU, 65 Refrigerator cycle control means, 66 Heater control means, 71 Refrigerator room temperature sensor, 72 Refrigerator room temperature sensor, 73 Outside air temperature sensor, 74 Outside air humidity sensor, 80 Temperature control panel, 100 refrigerator / freezer, 100A box body, 201, 211 waveform, 301, 311 waveform.

Claims (5)

A box with a storage room and
A double door that covers the opening of the box,
A partition plate that prevents outside air from entering the storage chamber when the double door is closed.
An outside air temperature sensor that detects the outside air temperature, and
An outside air humidity sensor that detects outside air humidity, and an outside air humidity sensor
A refrigerating room temperature sensor that detects the temperature in the storage room as the refrigerating room temperature, and
A heater that prevents condensation on the partition plate and
It has a heater control means for controlling energization to the heater based on a reference energization rate calculated from the outside air temperature and the outside air humidity.
The heater control means
The energization coefficient was calculated from the outside air temperature, the refrigerating room temperature, and the refrigerating room target temperature, and the heater was controlled using the corrected energizing rate obtained by multiplying the calculated energizing coefficient by the reference energizing rate.
Energization coefficient = (outside air temperature-refrigerator room temperature) / (outside air temperature-refrigerator room target temperature)
A freezer / refrigerator that calculates the corrected energization rate using the calculation formula represented by. A box with a storage room and
A double door that covers the opening of the box,
A partition plate that prevents outside air from entering the storage chamber when the double door is closed.
An outside air temperature sensor that detects the outside air temperature, and
An outside air humidity sensor that detects outside air humidity, and an outside air humidity sensor
A refrigerating room temperature sensor that detects the temperature in the storage room as the refrigerating room temperature, and
A heater that prevents condensation on the partition plate and
It has a heater control means for controlling energization to the heater based on a reference energization rate calculated from the outside air temperature and the outside air humidity.
The heater control means
The energization coefficient was calculated from the outside air temperature, the refrigerating room temperature, and the refrigerating room target temperature, and the heater was controlled using the corrected energizing rate obtained by multiplying the calculated energizing coefficient by the reference energizing rate.
Energization coefficient = (outside air temperature-refrigerator room temperature) / {outside air temperature- (fixed value-refrigerator room target temperature)}
A freezer / refrigerator that calculates the corrected energization rate using the calculation formula represented by. The heater control means
The freezer / refrigerator according to claim 1, wherein the heater is energized at the reference energization rate when the refrigerating room temperature is the refrigerating room target temperature. The heater control means
The heater is energized at the corrected energization rate when the temperature of the refrigerating chamber is equal to or higher than the threshold value, and when the temperature of the refrigerating chamber drops from the threshold value or higher to less than the threshold value, the heater is energized at the reference energization rate. The refrigerator / freezer according to any one of 1 to 3. The heater control means
The freezer / refrigerator according to any one of claims 1 to 4, wherein the heater is energized with a value obtained by multiplying the reference energization coefficient by a correction coefficient larger than 1 and the energization coefficient as the correction energization rate.

Images