WO2019193626A1 - Refrigeration appliance - Google Patents

Abstract

This refrigeration appliance has a box-shaped body having a storage chamber, double doors that cover an opening in the box-shaped body, a partition plate that blocks infiltration of outside air into the storage chamber when the double doors are closed, an outside-air temperature sensor that detects the temperature of the outside air, an outside-air humidity sensor that detects the humidity of the outside air, a refrigeration-chamber temperature sensor that detects the temperature inside the storage chamber as the temperature of a refrigeration chamber, a heater that prevents condensation on the partition plate, and a heater control means that controls transmission of electricity to the heater on the basis of a reference electricity transmission ratio calculated from the temperature of the outside air and the humidity of the outside air. The heater control means calculates an electricity transmission coefficient from the temperature of the outside air, the temperature of the refrigeration chamber, and a target temperature of the refrigeration chamber, and controls the heater using a corrected electricity transmission ratio obtained by multiplying the calculated electricity transmission coefficient by the reference electricity transmission ratio.

Description

Freezer refrigerator

The present invention relates to a refrigerator with a double door.

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

In the state that the door of the refrigerator compartment is closed, the partition plate is in close contact with the gasket of the door of the refrigerator compartment to block the refrigerator compartment from the outside air. Since a partition plate is cooled from the surface inside a store | warehouse | chamber, the surface temperature outside a store | warehouse | chamber falls by heat conduction, and the surface outside a store | warehouse will dew condensation. In many refrigerators, a heater is provided inside the partition plate in order to prevent condensation on the outer surface of the refrigerator.

When the heater heats the partition plate, if the amount of power supplied to the heater is increased only for dew condensation measures, the power consumption of the refrigerator increases and the electricity cost increases. In addition, qualitatively, the heat that moves from the partition plate to the refrigerator compartment increases, which may interfere with cooling of the refrigerator compartment.

As an example of energization control of the heater provided in the partition plate, the input power P to the heater is calculated by the equation P = α × Δt with respect to the temperature difference Δt between the outside air temperature and the inside temperature of the refrigerator compartment. The refrigerator to control is known (for example, refer to patent documents 1).

An example of a refrigerator that performs another heater energization control is disclosed in Patent Document 2. In the refrigerator of Patent Document 2, when 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 the outside air humidity is higher than the reference humidity, the heater energization rate is set higher than the reference energization rate. When the humidity is lower than the reference humidity, the heater energization rate is set lower than the reference energization rate.

JP 2004-353972 A JP 2013-72595 A

The refrigerator disclosed in Patent Document 1 is based on the premise that the temperature of the refrigerator compartment is stable at the set temperature, and if the temperature of the refrigerator compartment is close to the outside air temperature, there is a risk of consuming power wastefully. There is. Examples of cases where the temperature of the refrigerator compartment becomes higher as the outside air temperature is higher are, 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 refrigerator compartment is close to the set temperature, and when the temperature of the refrigerator compartment is higher as it is closer to the outside air temperature, the refrigerator compartment is cooled to the preset temperature. In the transition period until it is done, there is a risk of consuming power wastefully.

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

The refrigerator-freezer according to the present invention includes a box having a storage room, a double door that covers the opening of the box, and a partition plate that prevents the outside air from entering the storage room in a state where the double door is closed, An outside air temperature sensor for detecting outside air temperature, an outside air humidity sensor for detecting outside air humidity, a refrigerating room temperature sensor for detecting a temperature in the storage room as a refrigerating room temperature, a heater for preventing dew condensation on the partition plate, Heater control means for controlling energization to the heater based on a reference energization ratio calculated from the outside air temperature and the outside air humidity, and the heater control means includes the outside air temperature, the refrigerating room temperature, and the refrigerating room. An energization coefficient is calculated from a target temperature, and the heater is controlled using a corrected energization rate obtained by multiplying the calculated energization coefficient by the reference energization rate.

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

It is an external appearance front view which shows the example of 1 structure of the refrigerator-freezer which concerns on Embodiment 1 of this invention. It is a refrigerant circuit diagram of the refrigerator-freezer shown in FIG. FIG. 2 is a cross-sectional view taken along line AA shown in FIG. FIG. 3 is a functional block diagram of a control unit shown in FIG. 2. It is a graph which shows the calculation formula which calculates | requires a reference | standard energization rate from external temperature and relative humidity. It is a graph which shows the calculation formula which calculates | requires a reference | standard energization rate from external temperature and relative humidity. It is a model figure which shows the heat transfer from the outside air to the refrigerator compartment shown in FIG. It is a figure which shows the flow-velocity distribution of the whole cold air inside the refrigerator compartment shown in FIG. It is an enlarged view which shows the flow velocity distribution of the cold air in the uppermost shelf among the inside of the refrigerator compartment shown in FIG. It is a flowchart which shows an example of the procedure of the heater energization control which the heater control means shown in FIG. 4 performs. In heater energization control concerning Embodiment 1 of the present invention, when outside temperature is 30 ° C and relative humidity is 75% RH, it is a graph which shows temperature change from a power-on start. In the heater energization control of a comparative example, it is a graph which shows the temperature change from power-on start, when outside temperature is 30 degreeC and relative humidity is 75% RH. In heater energization control concerning Embodiment 1 of the present invention, it is a figure showing time change of refrigerator temperature, energization coefficient, standard energization rate, and correction energization rate. In heater energization control concerning Embodiment 1 of the present invention, when outside temperature is 30 ° C and relative humidity is 55% RH, it is a graph which shows a temperature change from power-on start. In heater energization control of a comparative example, it is a figure which shows each temperature waveform at the time of power activation in the case of 30 degreeC outside temperature and 55% RH outside temperature. 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. In the refrigerator-freezer which concerns on Embodiment 3 of this invention, it is a figure which shows the time transition of the electricity supply rate of a heater.

Embodiment 1 FIG.
The structure of the refrigerator-freezer of this Embodiment 1 is demonstrated. FIG. 1 is an external front view showing a configuration example of a refrigerator-freezer according to Embodiment 1 of the present invention. FIG. 2 is a refrigerant circuit diagram of the refrigerator-freezer shown in FIG.

As shown in FIG. 1, the refrigerator-freezer 100 includes a box 100A, and has a refrigerator room 1, an ice making room 2, a small freezer room 3, a freezer room 4, and a vegetable room 5 as storage rooms. In the configuration example shown in FIG. 1, the refrigerator compartment 1 is provided at the top of the main body of the refrigerator 100, and the ice making chamber 2 and the small refrigerator compartment 3 are provided in parallel below the refrigerator compartment 1 (in the direction opposite to the Z-axis arrow). It has been. A freezer room 4 is arranged under the ice making room 2 and the small freezer room 3, and a vegetable room 5 is arranged under the freezer room 4. In this Embodiment 1, the case where a storage room is the refrigerator compartment 1 among the boxes 100A which have a some storage room is demonstrated.

The refrigerator-freezer 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 refrigerator compartment 1 is provided with a partition plate 9 that prevents intrusion of outside air when the double door is closed. The length in the vertical direction (Z-axis arrow direction) of the partition plate 9 is equal to the length in the vertical direction of the refrigerator compartment 1 shown in FIG. The refrigerator-freezer 100 should just have a double door, and arrangement | positioning of these store rooms is not limited to the structure 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 refrigerant piping, and the refrigerant circuit 57 in which a refrigerant circulates is comprised.

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 releases it to the outside of the refrigerator-freezer 100. The condensation pipe is provided on the side surface of the refrigerator 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 warehouse. The fan 55 supplies air cooled by exchanging heat with the refrigerant in the evaporator 54 to the refrigerator compartment 1 and the freezer compartment 4. The fan 55 is, for example, a propeller fan. The damper device 56 adjusts the amount of cold air supplied to the refrigerator compartment 1 and the freezer compartment 4 by changing the opening of the baffle. The heater 18 is provided on the partition plate 9 shown in FIG. 1 and prevents the surface of the partition plate 9 from condensing.

Moreover, the refrigerator-freezer 100 has a plurality of sensors for temperature control of the refrigerator compartment 1 and the freezer compartment 4 and the like and for energization control of the heater 18. Specifically, the refrigerator-freezer 100 includes a freezer temperature sensor 71, a refrigerator temperature sensor 72, an outside air temperature sensor 73, and an outside air humidity sensor 74. The freezer compartment temperature sensor 71 is provided in the freezer compartment 4 and detects the freezer compartment temperature Tf. The refrigerator compartment temperature sensor 72 is provided in the refrigerator compartment 1 and detects the refrigerator compartment temperature Ti. The outside air temperature sensor 73 detects the outside air temperature To as the surrounding environment of the refrigerator-freezer 100. The outside air humidity sensor 74 detects the outside air humidity Mo as the surrounding environment of the refrigerator-freezer 100. The outside air temperature sensor 73 and the outside air humidity sensor 74 are provided, for example, in an upper hinge portion (not shown) of the left door 7. The refrigerator compartment temperature sensor 72 serves not only for temperature management of the refrigerator compartment 1 but also for temperature compensation of the surface of the partition plate 9 for optimally energizing the heater 18.

The freezer temperature sensor 71 is not limited as long as it is a position that can detect the temperature of the frozen storage room. The refrigerating room temperature sensor 72 may be a position where the temperature of the refrigerating object can be detected, and the installation position is not limited. As long as the outside air temperature sensor 73 can detect the outside air temperature To as an ambient environment, the installation location is not limited. As long as the outside air humidity sensor 74 can detect the outside air humidity Mo as an ambient environment, the installation location is not limited.

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

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

When the double door of the refrigerator compartment 1 is in a closed state, 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 Z-axis arrow direction).

The partition plate 9 includes 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 to the inner side is attached to the outer surface of the partition plate 9. A heater 18 is disposed inside 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, a heat insulating material 19 is arranged on the inner side than 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 cabinet. The back surface (surface in the direction of the Y-axis arrow) and the side surface (surface in the direction of the X-axis arrow and surface in the direction opposite to the X-axis arrow) of the heat insulating material 19 are covered with the internal resin member 20. Then, the outside 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 inside resin member 20.

The left door gasket 22 is fitted in the groove portion 24 of the left door inner plate 10. A right door gasket 23 is fitted in the groove 24 of the right door inner plate 11. As shown in FIG. 3, each of the left door gasket 22 and the right door gasket 23 includes a magnet 25 at a position facing the sheet metal member 17 of the partition plate 9 when the double door of the refrigerator compartment 1 is closed. When the double door of the refrigerator compartment 1 is closed, the sheet metal member 17 is attracted to the magnet 25 by 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 refrigeration is performed from outside the refrigerator. Block the outside air from entering the chamber 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 protrudes inside the cabinet so as to follow 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 projection of the guide component installed on the top surface of the refrigerator compartment 1 is hooked on the partition plate 9 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 projection of the guide component installed on the top surface of the refrigerator compartment 1 is hooked on the partition plate 9 in the groove shape provided at the upper end of the partition plate 9. Therefore, the partition plate 9 rotates clockwise about 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 refrigerator compartment 1 from between the left door 7 and the right door 8 of the refrigerator compartment 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 illustrated in FIG. 2, the control unit 60 includes a memory 61 that stores a program, and a CPU (Central Processing Unit) 62 that executes 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 refrigeration cycle control means 65 and the heater control means 66 are configured in the refrigeration refrigerator 100.

The refrigeration cycle control means 65 controls the refrigeration cycle of the refrigerant circuit 57 based on the freezer compartment temperature Tf, the refrigerator compartment temperature Ti, the freezer compartment target temperature, and the refrigerator compartment target temperature Ts. Specifically, the refrigeration cycle control means 65 controls the rotation speed of the compressor 51 so that the freezer compartment temperature Tf matches the freezer compartment target temperature. The refrigeration 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 refrigerator compartment temperature Ti matches the refrigerator compartment target temperature Ts. The refrigerator compartment 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 the time during which the heater 18 is energized with the rated current. For example, the energization rate when energizing for 5 seconds out of the time 10 seconds is (5 [s] / 10 [s]) × 100% = 50%. The reference energization rate DRref is an energization rate at which the surface of the partition plate 9 is not dewed. The reference energization rate DRref is calculated from the outside air temperature To and the outside air relative humidity Mrh using a 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 air diagram. An equation for calculating the relative humidity Mrh from the outside air temperature To and the outside air humidity Mo is registered in a program stored in the memory 61.

The reference energization rate DRref will be described. 5 and 6 are graphs showing calculation formulas for obtaining the reference energization rate from the outside air temperature and the relative humidity. For example, as shown in FIG. 5, calculation formulas PF1 to PF3 using the outside air temperature To as a parameter are set for the reference energization rate DRref. The example shown in FIG. 5 shows the case of three temperature zones where the outside air temperature To ≦ 20 ° C. or less, 20 ° C. <outside air temperature To ≦ 30 ° C., and 30 <outside air temperature To ≦ 40 ° C. The reference energization rate DRref increases linearly as the relative humidity Mrh increases according to the calculation formulas PF1 to PF3.

FIG. 6 is a graph showing another calculation formula for the reference energization rate DRref. As shown in FIG. 6, the calculation ratios LF1 to LF3 using the outside air temperature To as a parameter are set for the reference energization rate DRref. FIG. 6 also shows a case where there are three temperature zones, as in FIG. The reference energization rate DRref increases logarithmically as the relative humidity Mrh increases according to the 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. The calculation formula for 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. It is determined by the rated wattage of the heater 18 and the set temperature in the cabinet. The reference energization rate DRref is calculated by substituting the relative humidity Mrh calculated from the outside air temperature To and the outside air humidity Mo into a calculation formula determined depending on 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 A and B are set for each temperature zone of the outside air temperature To. In addition, the calculation formulas LF1 to LF3 shown in FIG. 6 are expressed by the reference energization rate DRref = C × lnMrh + D when the natural logarithm is represented by the symbol ln. The coefficients of C and D are set for each temperature range of the outside air temperature To. These coefficients are determined in advance by a development test or the like and registered in a program stored in the memory 61.

In the first embodiment, as shown in FIG. 5 and FIG. 6, the case where there are three temperature zones for determining the calculation formula has been described, but the temperature zone is not limited to three. In the first embodiment, the case where the temperature zone width is 10 ° C. or more has been described. However, the temperature zone width is not limited to 10 ° C., and the temperature zone is set to a value such as 5 ° C. smaller than 10 ° C. The width may be subdivided.

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

Before explaining the energization coefficient kt in the equation (1), heat input from the outside to the inside through the partition plate 9 will be explained. FIG. 7 is a model diagram showing heat transfer from the outside air into the refrigerator compartment shown in FIG. In FIG. 7, αo is the outside heat transfer coefficient [W / (m ² · K)], and αi is the inside heat transfer coefficient [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 from the heat transfer shown in FIG. Calculated. In the equation (2), the unit of the outside air temperature To and the refrigerator compartment temperature Ti is Kelvin [K].

Of the right side of Equation (2), the previous 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 internal resin member 20. Here, the partition plate 9 is simply treated as one member, and the thermal conductivity of the partition plate 9 is λ.

In addition, when the heat input model is strictly considered three-dimensionally, it is necessary to consider the influence of a heat bridge that goes into the refrigerator compartment 1 from the outside of the side surface of the partition plate 9. In this Embodiment 1, since the side surface of the partition plate 9 is covered with resin, it is considered that the heat transfer amount due to the influence of the heat bridge outside 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. 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 internal resin member 20. Therefore, the thermal conductivity λ does not change due to the influence of the operation of the refrigerator / freezer 100, for example, the thermal influence due to the condensation pipe and the thermal influence when the heater 18 is energized.

The heat transfer coefficient αo on the outside of the box is assumed to depend on the air flow rate on the surface of the partition plate 9, but it is assumed that the wind speed in the environment where the refrigerator-freezer 100 is installed is small. In addition, although a part of the surface of the partition plate 9 is exposed to the outside air, the partition plate 9 is disposed in the back of the narrow gap between the left door 7 and the right door 8. Less susceptible to ambient wind speeds. 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 natural convection caused by the temperature difference is generated. is assumed. However, even when the air flow generated by energizing the heater 18 is taken into consideration, the heat transfer coefficient αo is as small as about 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 conductivity αo can be considered as a fixed value.

In addition, regarding the heat transfer coefficient αi inside the refrigerator, it is considered that the wind speed in the refrigerator compartment 1 changes depending on the rotation speed of the fan 55. However, normally, the wind speed at the outlet of the refrigerator compartment 1 is about 3 [m / s] at the maximum, although it depends on the cool air outlet and the shape of the outlet. When the double door is closed, the standing walls 15 and 16 are arranged on the side surface of the partition plate 9 in the refrigerator compartment 1. Therefore, it is assumed that the standing walls 15 and 16 become obstacles to cool air from the outlet, and the wind against the partition plate 9 is weakened. 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 cool air from the outlet, and the air contact with the partition plate 9 is further weakened. Therefore, the wind speed to the partition plate 9 inside the warehouse becomes a value approximated to 0 [m / s].

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

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

8 and 9, the left side of the figure (in the direction opposite to the Y-axis arrow) is the front side of the refrigerator-freezer 100, and the right side of the figure (in the direction of the Y-axis arrow) is the back side of the refrigerator-freezer 100. 8 and 9, the left end of the figure is located on the back surface (side surface in the Y-axis arrow direction) of the partition plate 9 shown in FIG. FIG. 8 and FIG. 9 depict the magnitude of the flow velocity as a wind speed contour line as an analysis result of the flow velocity distribution inside the refrigerator compartment 1.

8 and 9, in the refrigerator 100, the shelves 13 and the door pockets 12 are indicated by broken lines, and the wind speed contour lines 35 to 38 are indicated by solid lines. The wind speed of the wind speed contour line 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]. The wind speed contour line 38 shown in FIG. 9 has a portion where the wind speed is larger than 0.4 [m / s]. In FIG. 9, the wind speed contour line larger than 0.4 [m / s] is shown. Omitted.

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

Referring to Table 1, out of the outlets 30 to 34, the outlet 30 has the highest wind speed. The reason will be explained. The uppermost shelf 13 of the refrigerator compartment 1 tends to rise in temperature compared to the other shelves 13 due to heat leakage from the uppermost surface of the refrigerator 100. In order to make the temperature distribution in each storage room divided by the plurality of shelves 13 uniform, the cross-sectional area of the air outlet 30 is increased so that the air volume at the uppermost shelf 13 is increased. Bigger than. Further, since the blowout port 30 is located near the end of the blowout air passage 39, cold air that is folded back at the end of the blowout air passage 39 is also added, and thus the wind speed tends to increase.

From the analysis results, it can be seen that the wind speed in the vicinity of the rear surface of the partition plate 9 shown at the left end of FIGS. 8 and 9 is a value approximate to 0 [m / s] at any height in the refrigerator compartment 1. Therefore, in equation (2), the thermal conductivity αi inside the warehouse is considered to be as small as about 3 to 4 [W / (m ² · K)], similarly to the thermal conductivity αo outside the warehouse. Further, it is considered that the thermal conductivity αi inside the refrigerator hardly changes even when the operation state of the refrigerator-freezer 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 passage coefficient in the equation (2) is fixed during the operation of the refrigerator 100. It is considered 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 compartment and the refrigerator compartment temperature Ti inside the compartment.

In order to prevent dew on the surface of the partition plate 9, the surface temperature may be set to a dew point or higher. 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 It can be seen in principle that the temperature is kept at a temperature that does not condense. That is, the energization coefficient kt in 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 Equation (3), the numerator is the temperature difference ΔT between the outside air temperature To and the refrigerator compartment temperature Ti, and the denominator is the temperature difference between the outside air temperature To and the refrigerator compartment target temperature Ts. The refrigerator compartment target temperature Ts is a fixed value set as 3 ° C., for example. The heater control means 66 sets the energization coefficient kt according to equation (3).

When the refrigerator compartment temperature Ti is high, for example, immediately after the refrigerator-freezer 100 is installed and immediately after the power is turned on, the refrigerator compartment 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 room temperature Ti is also detected as 30 ° C., the heat flux q passing through the partition plate 9 is also 0, so heating of the partition plate 9 by the heater 18 is unnecessary. It becomes. In this case, in Equation (3), the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature Ti is 0, and the heater control unit 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 supply to the freezer 100 is turned on, the refrigerator temperature 100 gradually decreases as the refrigerator 100 is operated. When the refrigerator compartment temperature Ti reaches the refrigerator compartment target temperature Ts, the value of the numerator and the value of the denominator 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 equation (1), the corrected energization rate DRa becomes the same as the reference energization rate DRref, and the heater control unit 66 calculates the reference energization rate DRref as the corrected energization rate DRa.

Thereafter, the refrigerator compartment temperature Ti may become lower than the refrigerator compartment target temperature Ts. In this case, the energization coefficient kt is greater than 1, and the corrected energization rate DRa is greater 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. Thereby, it is possible to prevent the heater 18 from being energized more than necessary.

As shown in Equation (3), the energization coefficient kt is a function of the temperature difference ΔT between the outside air temperature To and the refrigerator temperature Ti. Therefore, when the heater control means 66 calculates and updates the temperature difference ΔT at a constant cycle, the ambient environment is stabilized, and the refrigerator compartment temperature Ti decreases linearly from the power-on, the linearity is reduced. 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 refrigerator compartment temperature Ti.

Also, even in a situation where the surrounding environment is not stable, as shown in Expression (3), the energization coefficient kt also changes in accordance with the surrounding environment, so that the corrected energization rate DRa also changes corresponding to the change in the energization coefficient kt. Therefore, the energization rate of the heater 18 can be optimally controlled with respect to changes in the surrounding environment.

Next, the heater energization control procedure executed by the heater control means 66 will be described. FIG. 10 is a flowchart showing an example of a heater energization control procedure 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 controller 66 determines a calculation formula for calculating the reference energization rate DRref based on the outside air temperature To (step S2). In FIG. 10, the calculation formulas PF1 to PF3 shown in FIG. 5 are shown as calculation formula options. However, 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 FIG. When the heater control means 66 determines the calculation formula 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 Mrh calculated from the outside air temperature To and the outside air humidity Mo (step S5).

Subsequently, when the heater control means 66 acquires the refrigeration room temperature Ti from the refrigeration room temperature sensor 72 (step S6), the heater control means 66 uses the equation (3) and the outside air temperature To, the refrigeration room temperature Ti, and the refrigeration room target temperature Ts. The energization coefficient kt is calculated (step S7). The heater control means 66 calculates the corrected energization rate DRa by multiplying the energization coefficient kt by the reference energization rate DRref 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).

FIG. 10 shows a case where the refrigerator compartment temperature Ti is acquired in step S6 and the energization coefficient kt is calculated in step S7. However, the acquisition timing of the refrigerator compartment temperature Ti and the calculation timing of the energization coefficient kt are illustrated in FIG. It is not limited to the case shown in FIG. The acquisition timing of the refrigerator compartment temperature Ti and the calculation timing of the energization coefficient kt may be any timing as long as it is from the acquisition of the outside air temperature To to the calculation of the corrected energization rate DRa. Further, if the control cycle shown in the procedure of FIG. 10 is too long, a change and deviation of the surrounding environment may occur. For example, the cycle is preferably within 1 minute.

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 output to the heater 18. To calculate. Since the energization coefficient kt increases in accordance with the decrease in the refrigerator compartment temperature Ti, the energization rate to the heater 18 is suppressed from becoming larger than necessary. As a result, the power consumption of the refrigerator-freezer 100 can be reduced.

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

Explain the conditions for this test. The outside air temperature was constant at 30 ° C., and the relative humidity was constant at 75% RH. In the test, a refrigerator-freezer having an overall rated internal volume of 517 liters and a refrigerator compartment 1 having a rated internal volume of 277 liters was used. A heater having a power of 11.1 W was used as the heater 18. There is no food in the cabinet, and the doors of each storage room are not opened or closed. Moreover, the temperature mass made from brass was installed in the shelf 13 of the refrigerator compartment 1, and the temperature mass was installed also in the freezer compartment 4.

In this test, in order to compare the transient state of the refrigerator compartment temperature Ti in the two heater energization controls, the power supply to the refrigerator-freezer was turned on with the temperature mass and the surface temperature of the partition plate 9 being 30 ° C., 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, a constant reference energization rate is energized to the heater from the start of power-on of the refrigerator-freezer.

FIG. 11 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 according to Embodiment 1 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 FIG. 11 and FIG. 12, the power consumption is not marked.

In FIG. 11, a waveform 201 indicates a time change of power consumption of the refrigerator-freezer. In the period TP1 of the waveform 201, since it is an initial stage from the start of power-on, the rotation speed of the compressor 51 and the fan 55 is increased so that the refrigeration cycle control means 65 cools the interior 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 refrigerator compartment temperature 203, the refrigerator compartment temperature 204, and the refrigerator compartment temperature 205 are Each temperature decreases with time. When the internal temperature 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. Thereafter, over a period TP3 to TP5, the compressor 51 and the fan 55 stably operate at a low rotation speed, and the temperatures of the refrigerator compartment temperature 203, the refrigerator compartment temperature 204, and the freezer compartment mass 205 are stabilized.

Thus, each temperature of the refrigerator compartment temperature 203, the refrigerator compartment temperature 204, and the freezer compartment temperature 205 changes transiently from the start of power-on to the refrigerator-freezer during the period TP1, and during periods TP3 to TP5. Then it will be stable. Referring to the comparative example in FIG. 12, a waveform 301 indicating a time change in power consumption of the refrigerator-freezer shows the same change as the waveform 201. Further, the temperature changes of the refrigerator compartment temperature 303, the refrigerator compartment mass 304, and the refrigerator compartment mass 305 shown in FIG. 12 are the temperature changes of the refrigerator compartment temperature 203, the temperature 204, and the temperature 205 shown in FIG. There is a similar trend.

Referring to the graph shown in FIG. 11, comparing the refrigerator compartment temperature 203 with the refrigerator compartment temperature 204, the refrigerator compartment 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 side of the refrigerating room 1 (in the Y-axis arrow direction shown in FIG. 8) does not directly hit, whereas the refrigerating room mass Because it hits directly. Since these temperature differences are small, it can be seen that the refrigerator temperature sensor 72 can detect the temperature of the storage compartment of the refrigerator compartment 1 more accurately.

Referring to FIG. 11 and FIG. 12, the surface temperature of the partition plate 9 is compared in the period TP1 in which the temperature in the storage changes transiently. In FIG. 11, the surface temperature 202 of the partition plate 9 is constant around 35 ° C. On the other hand, in the comparative example of FIG. 12, the surface temperature 302 of the partition plate rises 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 when the refrigerator compartment is not sufficiently cooled as in the period TP1. The broken lines shown in FIGS. 11 and 12 indicate that the temperature is 35 ° C.

In the heater energization control according to the first embodiment, as the energization rate to the heater 18, 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 refrigerator temperature Ti. Is used. Therefore, the energization rate gradually increases from the start of power-on 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 is compared with the broken line, the surface temperature 202 changes from the initial stage of the period TP1 at a temperature that is not different from the stable period of the periods TP3 to TP5. Yes. Further, since the dew point temperature when the outside air temperature is 30 ° C. and the relative humidity is 75% RH is about 25 ° C., the surface of the partition plate 9 is also dewed by the heater energization control of the first embodiment. It never happened.

Here, with respect to 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 refrigerator temperature 203 shown in FIG. 11 will be described. FIG. 13 is a diagram showing temporal changes in the refrigerator temperature, the energization coefficient, the reference energization rate, and the corrected energization rate in the heater energization control according to Embodiment 1 of the present invention. In FIG. 13, the power consumption and the energization rate are not marked.

As shown in FIG. 13, the temperature difference ΔT between the outside air temperature To and the refrigerating room temperature 203 increases from 0 as the refrigerating room temperature 203 decreases since the power supply to the refrigerator 100 is turned on. It grows upward from the time the power is turned on. 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 period TP1 to TP5.

Since the corrected energization rate DRa is obtained by multiplying the energization factor kt by the reference energization rate DRref, it rises linearly in the period TP1. Since the refrigerator compartment temperature 203 reaches the refrigerator compartment target temperature Ts at the end of the period TP1, the reference energization rate DRref and the corrected energization rate DRa become the same value, and the energization rate to the heater 18 becomes the reference energization rate DRref. Will continue.

Next, the test results of the heater energization control of the first embodiment and the heater energization control of the comparative example will be described for the power consumption of the refrigerator-freezer. Table 2 is a table | surface which shows the power consumption and power consumption of a refrigerator-freezer in the period TP1 shown to FIG. 11 and FIG.

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

Further, referring to FIG. 11 and FIG. 12, when comparing the cooling speed of the temperature 204 and 304 of the refrigerator compartment, for example, the time until the temperature reaches 30 ° C. to 3 ° C., the first embodiment is compared. Compared to the example, an improvement of about 3 minutes was observed.

Next, test results comparing the heater energization control of the first embodiment and the heater energization control of the comparative example when the outside air temperature is 30 ° C. and the relative humidity is 55% RH will be described. Other test conditions are the same as those described with reference to FIGS. 11 and 12, and thus detailed description thereof is 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 Embodiment 1 of the present invention. FIG. 15 is a diagram showing each temperature waveform at power-on in the case of the heater energization control of the comparative example when the outside air temperature is 30 ° C. and the outside air humidity is 55% RH.

FIG. 14 shows temporal changes in the power consumption waveform 211 of the refrigerator-freezer of Embodiment 1, the surface temperature 212 of the partition plate 9, the refrigerator compartment temperature 213, the refrigerator compartment temperature 214, and the refrigerator compartment temperature 215. . FIG. 15 shows temporal changes in the power consumption waveform 311, the partition plate surface temperature 312, the refrigerator compartment temperature 313, the refrigerator compartment temperature 314, and the refrigerator compartment temperature 315 of the comparative refrigerator-freezer. The broken lines shown in FIGS. 14 and 15 are lines indicating a temperature of about 24 ° C.

14 and 15, pay attention 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 decreases. Also in the subsequent period TP2, the surface temperature 312 of the partition plate slightly rises and falls. On the other hand, in the heater energization control according to 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. It becomes the same temperature as when it is stable. Further, although the dew point under the conditions of this test is about 20 ° C., in the heater energization control of the first embodiment, no dew was found on the surface of the partition plate 9. Also in this test, the reduction effect comparable to the test result demonstrated with reference to FIG. 11 and FIG. 12 about the power consumption of heater energization control of this Embodiment 1 has been confirmed.

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 when the double door is closed. Further, at least one of the left door gasket 22 and the right door gasket 23 may be provided with a heater 18. Even in these cases, the heater energization control of the first embodiment can be applied, and the same effect as the first embodiment can be obtained.

There are three timings for turning on the power to the refrigerator-freezer: (a) turning on power at the initial stage of installation by replacement, (b) turning on power again when power supply resumes after a power failure, and (c) turning on power for the convenience of the user. is assumed. The user's convenience is, for example, the movement of the refrigerator-freezer and the repair response in the event of failure. It will be described that the heater energization control according to the first embodiment is effective in any of the assumed situations.

In the assumed situation (a), since the temperature of the refrigerator compartment is close to room temperature 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 increase in the refrigerator compartment is not large, so the corrected energization rate DRa is equal 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 increase in the temperature of the refrigerating room increases, so the corrected energization rate DRa becomes a value smaller than the reference energization rate DRref. Along with this, the reference energization rate DRref approaches. In the assumed situation (c), when the energization of the heater 18 is resumed, the temperature of the refrigerating room temperature becomes closer to room temperature as the time during which power is not supplied is longer, 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 no power is supplied. By controlling the energization rate according to these assumed situations, it is possible to reduce the power consumption.

In addition, with reference to FIG. 13, the case where the energization coefficient kt calculated by Expression (3) is used for the period TP <b> 1 from when the power is turned on until the refrigerator temperature reaches the refrigerator temperature target temperature has been described. Expression (3) may be applied for a predetermined time from the start. In this case, the energization coefficient kt is set to a constant value of 1 after a predetermined time has elapsed. For example, when a user purchases a refrigerator-freezer, when a food whose temperature has increased to near room temperature is put into a new refrigerator-freezer, the food whose temperature has increased may be placed near the refrigerator compartment temperature sensor 72. Moreover, a user may put the pan containing the cooked food in the refrigerator compartment 1 with high temperature. In such a case, it is conceivable that the temperature detected by the refrigerating room temperature sensor 72 is less likely to decrease than the average temperature of the refrigerating room 1.

Therefore, the memory 61 stores, as a predetermined time, several hours until the object to be cooled is stored in the refrigerating room and reaches the refrigerating target temperature from a state where the temperature of the refrigerating room is high. The predetermined time may be registered in the memory 61 in advance, 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) until a predetermined time elapses after the temperature of the refrigerator compartment is high, and sets the energization coefficient kt to a constant value 1 after the elapse of the predetermined time. . It is assumed that the memory 61 stores a reference temperature for determining whether or not the temperature of the refrigerator compartment is high.

Next, the heater energization control according to the first embodiment is not limited to the case of replacing the refrigerator / freezer and the case where a high-temperature cooling object is stored in the refrigerator compartment, but also when the door opening time of the refrigerator compartment 1 is long. Explain that is valid.

Depending on which one of the left and right doors of the refrigerator compartment is opened, there is a difference in the surface temperature of the partition plate. However, if the refrigerator door 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 increase. On the other hand, in this Embodiment 1, the left door 7 or the right door 8 of the refrigerator compartment 1 is opened for a long time by taking in and out food, and the refrigerator compartment temperature sensor 72 is higher than the stable refrigerator compartment temperature. When the temperature is detected, the energization coefficient kt becomes a smaller value than when it is stable. Therefore, the corrected energization rate DRa shown in Expression (1) is 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, let us consider a case where the left door 7 is closed and the right door 8 is opened in a configuration in which the partition plate 9 is attached to the left door 7. If the door of the refrigerator compartment 1 is opened for a long time, even if cold air is supplied to the refrigerator compartment 1, it becomes useless, so the refrigeration cycle control means 65 may stop the rotation of the fan 55. Moreover, the temperature in a store | warehouse | chamber rises by the natural convection by the temperature difference of the cool air in a store | chamber, and external air. As a result, the surface temperature of the back surface of the partition plate 9 increases. Conventionally, as described above, since the energization rate to the heater remains the reference energization rate and does not change, the surface temperature of the partition plate further increases. On the other hand, in the heater energization control according to the first embodiment, the energization coefficient kt decreases as the temperature of the refrigerator compartment increases, so that the corrected energization rate DRa decreases. As a result, the power consumption of the refrigerator / freezer is improved compared to the conventional case.

On the other hand, when the right door 8 is closed and the left door 7 is opened, as described with reference to FIG. 3, the partition plate 9 rotates and becomes along the standing wall 15. Most are exposed to the open air. Therefore, it is considered that the surface temperature of the partition plate 9 increases when the left door 7 is opened compared to when the right door 8 is opened. In this case, since the cold air in the refrigerator compartment 1 is exchanged with the outside air, the refrigerator compartment temperature also rises, and in the heater energization control of the first embodiment, the corrected energization rate DRa is set in accordance with the rise of the refrigerator compartment temperature. descend. As a result, similarly to the case where the right door 8 is opened, the power consumption of the refrigerator-freezer is improved as compared with the conventional case. Even when both the left door 7 and the right door 8 are opened, the refrigerator temperature 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 refrigerator compartment door is about several minutes, even if the heater control means 66 changes the energization coefficient kt with the change of the refrigerator compartment temperature, the power consumption is as large as when the power is turned on. It is thought that the reduction effect cannot be obtained. Therefore, when the refrigerator compartment temperature reaches the refrigerator compartment target temperature after the power supply to the refrigerator-freezer body is turned on, the refrigerator compartment temperature is stabilized without greatly fluctuating thereafter, so the energization coefficient kt is set to a constant value of 1. Also good. This will be described 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 elapse of the period TP1. kt may be set to 1. After the elapse 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 refrigerator compartment 1. The opening time of the door of the refrigerator compartment 1 is set as a threshold value, for example, the time for the refrigerator compartment temperature Ti to rise about 10 ° C. The threshold is, for example, 10 minutes. A sensor for detecting the open / closed state of the door of the refrigerator compartment 1 is provided in the refrigerator 100, and the heater control means 66 has a timer function. When the door opening time is equal to or greater than the threshold, the heater control unit 66 uses the energization coefficient kt calculated by Equation (3). When the door opening time is less than the threshold, the heater control means 66 sets the energization coefficient kt to a constant value. Set to 1. When 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 refrigerator compartment temperature Ti when the door is opened depends on the outside air temperature To, the threshold value does not correspond to any outside air temperature To. Therefore, when the door opening time exceeds the threshold, the forced time for forcibly using the energization coefficient kt calculated by Equation (3) is set in consideration of the amplitude of the outside air temperature To. Good. When the opening time of the door is equal to or greater than the threshold, the heater control unit 66 uses the energization coefficient kt calculated by Expression (3) until the forced time elapses after the door is closed, and after the forced time has elapsed, The energization coefficient kt is set to a constant value of 1. After the forced time has elapsed, the heater control means 66 energizes the heater 18 at the reference energization rate DRref.

Further, the heater energization control may be performed by setting a threshold value for the refrigerating room temperature Ti, without being limited to setting the threshold value for the door opening time. The threshold value is 10 ° C., for example. In this case, the heater control means 66 uses the energization coefficient kt calculated by Equation (3) when the refrigerator compartment temperature Ti rises above the threshold, and when the refrigerator compartment temperature Ti falls to a value below the threshold, the energization coefficient. Set kt to 1. When the refrigerator compartment 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 becomes long, the surface of the partition plate 9 can be prevented from condensing and the power consumption of the heater 18 can be reduced. As a result, energy saving of the refrigerator-freezer 100 can be achieved.

Note that the refrigerating room target temperature Ts is not limited to the temperature set by the user, and the user may select one temperature setting value from a plurality of temperature setting values. For example, a temperature operation panel (not shown) is provided in the refrigerator-freezer 100, and the user operates the temperature operation panel to set one temperature from three types of temperature setting values of weak, medium and strong as the refrigerator compartment target temperature Ts. A set value may be selected.

In the heater energization control according to the first embodiment, the minimum energization rate DRmin may be set. For example, when a high-temperature object to be cooled such as a pan containing a heat-treated object is placed in the vicinity of the refrigerator compartment temperature sensor 72, the temperature difference ΔT between the outside air temperature To and the refrigerator compartment temperature Ti becomes small. The corrected energization rate DRa calculated from (1) and equation (3) is reduced. In this case, the surface temperature of the partition plate 9 may be lowered to a temperature lower than the dew condensation temperature. Therefore, assuming that the refrigerator compartment temperature Ti rises rapidly, the minimum energization rate DRmin is set. The memory 61 stores the minimum energization rate DRmin. For example, the minimum energization rate DRmin is set to a value of about 10 to 20% of the reference energization rate DRref. The heater control means 66 energizes the heater 18 at the minimum energization rate DRmin when the energization rate DR calculated from the equations (1) and (3) becomes smaller than the minimum energization rate DRmin. As a result, the surface temperature of the partition plate 9 can be prevented from dropping to a temperature lower than the dew condensation temperature.

The refrigerator-freezer 100 according to the first embodiment calculates a conduction coefficient kt from the outside air temperature To, the refrigeration room temperature Ti, and the refrigeration room target temperature Ts, and a corrected conduction ratio DRa obtained by multiplying the conduction ratio kt by the reference conduction ratio DRref. The heater 18 of the partition plate 9 is energized.

According to the first embodiment, the corrected energization rate DRa reflecting the outside air temperature To, the refrigerating room temperature Ti, and the refrigerating room target temperature Ts is used for the heater energization control, so that the surface temperature of the partition plate 9 is lower than the dew condensation preventing temperature. Is also suppressed from becoming unnecessarily large. Therefore, it is possible to prevent the partition plate 9 from being dewed, to suppress unnecessary power consumption of the heater 18, and to reduce the power consumption of the refrigerator-freezer 100. As a result, energy saving of the refrigerator-freezer 100 can be achieved.

In the first embodiment, the heater control means 66 uses Equation (3) for calculating the energization coefficient kt in Equation (1). Since the energization coefficient kt increases in accordance with the decrease in the refrigerator compartment temperature Ti, the energization rate to the heater 18 is suppressed from becoming larger than necessary. As a result, the power consumption of the refrigerator-freezer 100 can be reduced.

Embodiment 2. FIG.
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, differences from the refrigerator-freezer described in the first embodiment will be described in detail, and a detailed description of the same configuration and operation as in 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 Expression (4), the correction energization rate DRa of the second embodiment is obtained by multiplying the right side of the calculation expression shown in Expression (1) by the correction coefficient kv.

As shown in FIG. 1, the partition plate 9 is long in the vertical direction (Z-axis arrow direction) of the left door 7 and the right door 8 of the refrigerator compartment 1, and the heater 18 is provided therein. It is conceivable that the surface temperature is not uniform. As a factor that the surface temperature of the partition plate 9 does not become uniform, for example, the depth of the refrigerator compartment 1 is considered to be small. As another factor, it is conceivable that a fan that circulates the air inside the refrigerator compartment 1 is attached to the refrigerator compartment 1 separately from the fan 55.

When the depth of the refrigerator compartment 1 is small, the temperature near the center where the cold air supplied from the back of the refrigerator compartment 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. Tend to be higher. When a fan that circulates the air inside the refrigerator compartment 1 is attached to the refrigerator compartment 1, the temperature of the part of the partition plate 9 where the cold air sent out by the fan directly hits tends to be lower than the temperature of the other parts. .

In such a configuration, the heater control means 66 increases the correction energization rate DRa by multiplying the reference energization rate DRref of Expression (1) by a correction coefficient kv having a value greater 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 refrigerator 100 has been described. However, the heater control unit 66 selects the correction coefficient kv depending on the outside air temperature To. Also 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 at the correction energization rate 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 factor kv and an energization factor kt larger than 1 as the energization rate of the heater 18. is there. According to the second embodiment, when the surface temperature of the partition plate 9 is not uniform, the correction coefficient kv having a value greater than 1 is multiplied by the reference energization rate DRref, so that the average over the entire surface of the partition plate 9 is obtained. The temperature lower than the temperature is suppressed from becoming lower than the dew condensation temperature. As a result, condensation on the surface of the partition plate 9 can be prevented.

Embodiment 3 FIG.
In the third embodiment, heater energization control is performed according to a set temperature selected by the user from a plurality of set temperatures as the refrigerating room target temperature Ts. In this Embodiment 3, a different point from the refrigerator-freezer demonstrated in Embodiment 1 is demonstrated in detail, and the detailed description about the structure and operation | movement similar to Embodiment 1 is abbreviate | omitted.

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

In the third embodiment, when the user selects one temperature setting rank from a plurality of temperature setting ranks, the refrigeration cycle control means 65 sets the refrigerator compartment target temperature to the refrigerator compartment target temperature corresponding to the temperature setting rank selected by the user. The temperature Ts is set to control the refrigeration cycle. Moreover, the heater control means 66 calculates the energization coefficient kt from Formula (5) according to the temperature setting rank selected by the user. The fixed value is, for example, a temperature difference between the strongly set refrigerator compartment target temperature Ts and the weakly set refrigerator compartment target temperature Ts. Here, the fixed value is 6.

In the first embodiment, the denominator term of the energization coefficient kt is “outside air temperature To−refrigeration room target temperature Ts”, whereas in the third embodiment, the user can set 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). In the third embodiment, the heater control means 66 uses the energization coefficient kt calculated by the equation (5) even if the refrigerator compartment temperature Ti reaches the refrigerator compartment 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 refrigerator compartment target temperature Ts is 0 ° C.

When the heater performs the heater energization control using the energization coefficient kt calculated by the equation (3), the heater control unit 66 performs the energization in the equation (1) when the user performs an operation of selecting the temperature setting rank. The coefficient kt may be changed to the energization coefficient kt calculated by Expression (5).

FIG. 17 is a diagram showing a time transition of the energization rate of the heater in the refrigerator-freezer according to Embodiment 3 of the present invention. The horizontal axis in FIG. 17 is time t, and the vertical axis is the corrected energization rate DRa. A time t0 shown in FIG. 17 is a time when the refrigerator-freezer 100 is started to be turned on. Time t1 is the time when the refrigerator compartment temperature Ti reaches the refrigerator compartment target temperature Ts.

As shown in FIG. 17, for each temperature setting rank, the energization coefficient kt shown in the equation (5) changes with time from time t0. The slope of the corrected energization rate DRa from time t0 to time t1 varies depending on the temperature setting rank from time t0. The lower the refrigerator compartment target temperature Ts, the greater the slope from time t0 to time t1. This is because the denominator of equation (5) becomes smaller as the refrigerator compartment target temperature Ts is lower.

After the time t1 when the refrigerating room temperature Ti reaches the refrigerating room target temperature Ts at time t1, the energization coefficient kt becomes a constant value, and the corrected energization rate DRa becomes constant. Referring to FIG. 17, in any temperature setting rank, the corrected energization rate DRa after time t1 is represented by a straight line with a slope = 0. When the corrected energization rate DRa is compared between the temperature setting ranks after the time t1, the strongly set corrected energization rate DRa is the largest and the weakly set corrected energization rate DRa is the smallest. The corrected energization rate DRa after the temperature of the refrigerator compartment temperature Ti is stabilized differs for each temperature setting rank. FIG. 17 shows that when the refrigeration room temperature Ti becomes stable in accordance with the refrigeration room target temperature Ts, the energization rate is constant in any temperature setting rank, but the energization rate differs for each temperature setting rank. .

Here, the reason why the energization rate differs for each temperature setting rank after the refrigerator compartment temperature Ti has reached the refrigerator compartment target temperature Ts will be described. After the refrigerating room temperature Ti reaches the refrigerating room target temperature Ts, the numerator and the denominator of the formula (5) are the same in the case of medium setting. That is, in the case of the medium setting, the corrected energization rate DRa becomes the reference energization rate DRref after 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 is larger than the reference energization rate DRref. Further, in the case of weak setting, since the denominator is larger than the numerator in the equation (5) after the time t1, the corrected energization rate DRa becomes a value smaller than the reference energization rate DRref.

Although the third embodiment has been described based on the first embodiment, the second embodiment may be applied to the third embodiment.

The refrigerator-freezer 100 according to the third embodiment uses the energization coefficient kt calculated by the equation (5) as the corrected energization rate DRa of the heater 18. According to the third embodiment, the lower the refrigerating room target temperature Ts, the larger the inclination of the energization rate until the refrigerating room temperature Ti becomes stable. It can be maintained at a large value. Even if the refrigerating room temperature Ti rapidly decreases, the inclination of the energization rate of the heater 18 is large, so that it is possible to prevent condensation on the surface of the partition plate 9. Even if the refrigerator compartment temperature Ti is set to a low temperature, since the energization rate of the heater 18 is large, it is possible to prevent condensation on the surface of the partition plate 9 when the user opens and closes the door of the refrigerator compartment 1. .

1 cold room, 2 ice making room, 3 small freezer room, 4 freezer room, 5 vegetable room, 7 left door, 8 right door, 9 partition plate, 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 insulation, 20 Inside resin member, 22 Left door gasket, 23 Right door gasket, 24 Groove, 25 Magnet, 28 Outside resin member , 29 packing, 30-34 outlet, 35-38 wind speed contour, 39 outlet, 40 return port, 51 compressor, 52 condenser, 53 decompressor, 54 evaporator, 55 fan, 56 damper device, 57 refrigerant Circuit, 60 control unit, 61 memory, 62 CPU, 65 refrigeration cycle control means, 66 heater control means, 71 freezer temperature sensor, 2 refrigerating compartment temperature sensor, 73 outside air temperature sensor, 74 outdoor air humidity sensor, 80 temperature control panel 100 refrigerator, 100A box, 201, 211 waveforms 301, 311 waveform.

Claims (6)

1. A box having a storage room;
   A double door that covers the opening of the box,
   A partition plate that prevents intrusion of outside air into the storage chamber with the double door closed;
   An outside temperature sensor for detecting the outside temperature;
   An outside air humidity sensor for detecting outside air humidity;
   A refrigerator temperature sensor for detecting the temperature in the storage chamber as a refrigerator temperature;
   A heater for preventing condensation of the partition plate;
   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 includes
   A refrigerator-freezer that calculates an energization coefficient from the outside air temperature, the refrigerating room temperature, and a refrigerating room target temperature, and controls the heater using a corrected energization ratio obtained by multiplying the calculated energization coefficient by the reference energization ratio.
2. The heater control means includes
   The refrigerator-freezer according to claim 1, wherein the heater is energized at the reference energization rate when the refrigerator compartment temperature is the refrigerator compartment target temperature.
3. The heater control means includes
   The heater is energized at the corrected energization rate when the refrigerator temperature is equal to or higher than a threshold value, and the heater is energized at the reference energization rate when the refrigerator temperature falls from the threshold value to less than the threshold value. The refrigerator-freezer according to 1 or 2.
4. The heater control means includes
   The refrigerator-freezer according to any one of claims 1 to 3, wherein the heater is energized with a value obtained by multiplying the reference energization ratio by a correction coefficient greater than 1 and the energization coefficient as the correction energization ratio.
5. The heater control means includes
   Energization coefficient = (outside air temperature-refrigerator compartment temperature) / (outside air temperature-refrigerator compartment target temperature)
   The refrigerator-freezer according to any one of claims 1 to 4, wherein the corrected energization rate is calculated using a calculation formula represented by:
6. The heater control means includes
   Energization coefficient = (outside air temperature-refrigerator compartment temperature) / {outside air temperature-(fixed value-refrigerator compartment target temperature)}
   The refrigerator-freezer according to any one of claims 1 to 4, wherein the corrected energization rate is calculated using a calculation formula represented by:

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