AU2015268480B2

AU2015268480B2 - Refrigerator

Info

Publication number: AU2015268480B2
Application number: AU2015268480A
Authority: AU
Inventors: Masao Araki; Masashi Fujitsuka; Go Maeda; Komei NAKAJIMA; Yusuke Tashiro
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2014-05-28
Filing date: 2015-05-28
Publication date: 2017-07-20
Anticipated expiration: 2035-05-28
Also published as: WO2015182698A1; AU2015268480A1; JPWO2015182698A1; SG11201609295YA; CN106415165A; JP6223564B2; CN106415165B

Abstract

The purpose of the present invention is to provide a refrigerator which has one evaporator and one internal fan, and which can reduce power consumption while suppressing temperature variation in the storage compartments. In this refrigerator (100), if the internal load is less than or equal to a prescribed value, the amount of cold air supplied to a refrigeration compartment (22) is controlled by controlling the duration that a supply port (2) is open during a control time (CT); if the internal load is greater than a prescribed value, then, when the load in the freezer compartment (21) is greater than a prescribed value, a refrigeration compartment damper (23) is controlled such that the supply port (2) is completely closed during the control time (CT); and, when the load in a storage compartment other than the freezer compartment (21) is greater than a prescribed value, the refrigeration compartment damper (23) is controlled such that the supply port (2) is completely open during the control time (CT).

Description

1001621906

DESCRIPTION

Title of Invention REFRIGERATOR Technical Field 5 [0001]

The present invention relates to a refrigerator, and particularly, to a refrigerator including a freezing chamber and a storage chamber different from the freezing chamber (a storage chamber such as a refrigerating chamber having a temperature zone different from that of the freezing chamber). 10 Background Art [0002]

Hitherto, refrigerators including a freezing chamber and a storage chamber different from the freezing chamber (a storage chamber such as a refrigerating chamber having a temperature zone different from that of the freezing chamber) 15 have been known. In such conventional refrigerators, an evaporator (cooler) and an internal fan of a refrigeration cycle are installed at an air passage communicating to each storage chamber, and each storage chamber is cooled with one evaporator and one internal fan. Specifically, when the temperature of a freezing chamber gets higher than a setting temperature, a compressor and an 20 internal fan of a refrigeration cycle are driven. Furthermore, when the temperature of a storage chamber different from the freezing chamber gets higher than the setting temperature, control is performed such that a damper provided at a cold air supply port of the storage chamber is opened to reduce the temperature of the storage chamber to a temperature lower than or equal to the 25 setting temperature and the damper is then closed. Thus, a conventional refrigerator including a freezing chamber and a storage chamber different from the freezing chamber has a problem that, even with a low internal load, when the damper is opened, the amount of cold air supplied to the freezing chamber is reduced, variations in the temperature of the freezing chamber are thus 1 1001621906 increased, and therefore, reducing the temperature of the freezing chamber increases the driving time of a compressor and thus increases power consumption.

[0003] A conventional refrigerator provided with a freezing chamber and a storage chamber different from the freezing chamber, to achieve suppression of variations in the temperature of the freezing chamber and other chambers, "including a main body, a refrigerating chamber formed at the main body and refrigerating foods, a cooler arranged within a cooling chamber formed on a rear side of the main body, the cooler cooling air flowing in the cooling chamber and generating cold air, a duct unit to send cold air from a back side of the refrigerating chamber into the refrigerating chamber, an air-blowing fan conveying cold air to the duct unit, a refrigerating chamber damper device adjusting the amount of cold air flowing from the cooling chamber to the duct unit, an outside air temperature detector detecting outside air temperature, a refrigerating chamber temperature detector detecting the temperature inside the refrigerating chamber, and a controller operating the air-blowing fan and performing opening degree control of the refrigerating chamber damper device, the controller setting a specific opening degree for the opening degree of the refrigerating chamber damper device, based on a measured outside air temperature, which is the outside air temperature detected by the outside air temperature detector, comparing, in a state in which the air-blowing fan is being driven, a measured refrigerating chamber temperature, which is the temperature inside the refrigerating chamber detected by the refrigerating chamber temperature detector with a predetermined first refrigerating chamber setting temperature, allowing the opening degree of the refrigerating chamber damper device to be in a fully-opened state when, based on a result of the comparison, the measured refrigerating chamber temperature is higher than the first refrigerating chamber setting temperature, comparing, in a state in which the air- 2 1001622809 2015268480 03 Nov 2016 blowing fan is being driven, the measured refrigerating chamber temperature with a predetermined second refrigerating chamber setting temperature that is smaller than the first refrigerating chamber setting temperature, and allowing the opening degree of the refrigerating chamber damper device to be in a state of the specific 5 opening degree when, based on a result of the comparison, the measured refrigerating chamber temperature is lower than the second refrigerating chamber setting temperature" has been suggested (see, for example, Patent Literature 1).

Citation List 10 Patent Literature [0004]

Patent Literature 1: Japanese Patent No. 5631284 [0004A]

Reference to any prior art in the specification is not, and should not be 15 taken as, an acknowledgment or any form of suggestion that this prior art forms part of the common general knowledge in any jurisdiction or that this prior art could reasonably be expected to be understood, regarded as relevant and/or combined with other pieces of prior art by a person skilled in the art.

Summary 20 [0004B]

As used herein, except where the context requires otherwise, the term "comprise" and variations of the term, such as "comprising", "comprises" and "comprised", are not intended to exclude further additives, components, integers or steps. 25 [0005]

However, the refrigerator described in Patent Literature 1 adjusts the degree of opening of the damper device to adjust the amount of air to the refrigerating chamber. That is, the refrigerator described in Patent Literature 1 3 1001622809 2015268480 03 Nov 2016 causes the damper device to operate as resistance of an air passage of the refrigerating chamber to suppress the amount of air to the refrigerating chamber. As a result, for example, to reduce the amount of air to the refrigerating chamber, the refrigerator described in Patent Literature 1 reduces the degree of opening of 5 the damper device, that is, increases the air passage resistance, and therefore, a region that cold air does not reach is generated at each position within the refrigerating chamber. Accordingly, the refrigerator described in Patent Literature 1 has a problem that temperature distribution is generated within the refrigerating chamber, and, especially, a pocket shelf part at a door of the 10 refrigerating chamber is not thus cooled enough.

[0006] 3a 1001622809 2015268480 03 Nov 2016

The present invention has been designed in the light of the problems described above. Disclosed within the following is a refrigerator including an evaporator and an internal fan, the refrigerator being able to reduce the amount of power consumption while suppressing variations in the temperature of each 5 storage chamber.

[0007] A refrigerator according to an embodiment of the present invention includes a freezing chamber and at least one storage chamber different from the freezing chamber; a refrigeration cycle including a compressor, a condenser, an 10 expansion mechanism, and an evaporator; an air passage communicating to the freezing chamber and the storage chamber different from the freezing chamber, the evaporator being arranged at the air passage; an internal fan provided at the air passage and configured to supply air cooled by the evaporator to the freezing chamber and the storage chamber different from the freezing chamber; a damper 15 provided at a supply port of the storage chamber different from the freezing chamber in the air passage and configured to open and close the supply port; and a controller configured to control, based on an internal load, at least the damper, the controller including an internal load recognizing unit configured to recognize the internal load, an opening time acquisition unit configured to acquire 20 an opening time during which the supply port is opened within a specified time serving as a control interval for the damper in a case where the internal load is less than or equal to a specified value, a determination unit configured to determine whether or not a load of the freezing chamber and a load of the storage chamber different from the freezing chamber are greater than the 25 specified value, and a damper control unit configured to control, in a case where the internal load is less than or equal to the specified value, the damper to open the supply port for the opening time within the specified time, and control, in a case where the internal load is greater than the specified value and the internal 4 1001622809 2015268480 03 Nov 2016 load is the load of the freezing chamber, the damper to fully close the supply port for the specified time, and in a case where the internal load is greater than the specified value and the internal load is the load of the storage chamber different from the freezing chamber, the damper to fully open the supply port for the 5 specified time.

[0007A]

According to a second aspect of the invention there is provided a refrigerator comprising: a freezing chamber and at least one storage chamber different from the freezing chamber; a refrigeration cycle including a compressor, 10 a condenser, an expansion mechanism, and an evaporator; an air passage communicating to the freezing chamber and the storage chamber different from the freezing chamber, the evaporator being arranged at the air passage; an internal fan provided at the air passage and configured to supply air cooled by the evaporator to the freezing chamber and the storage chamber different from 15 the freezing chamber; a damper provided at a supply port of the storage chamber different from the freezing chamber in the air passage and configured to adjust an opening ratio of the supply port; and a controller configured to control, based on an internal load, at least the damper, the controller being configured to control, in a case where the internal load is less than or equal to a specified value, the 20 damper not to fully close or fully open the supply port to control, a temperature of the storage chamber different from the freezing chamber toward the setting temperature, and control, in a case where the internal load is greater than the specified value and the internal load is the load of the freezing chamber, the damper to fully close the supply port, and in a case where the internal load is 25 greater than the specified value and the internal load is the load of the storage chamber different from the freezing chamber, the damper to fully open the supply port. 5 1001622809 2015268480 03 Nov 2016 [0008]

According to a refrigerator disclosed within the following, in a case where an internal load is less than or equal to a specified value (in a case where the internal load is low), by adjusting the time during which a supply port is opened 5 within a specified time as a control interval for a damper, the temperature of a storage chamber different from a freezing chamber is maintained at a setting temperature, That is, only an amount of air that keeps the temperature of the storage chamber different from the freezing chamber constant is conveyed to the storage chamber within the specified time, and variations in the temperature of 10 the storage chamber is thus suppressed. Therefore, in a case where the internal load is low, the amount of cold air supplied to the freezing chamber within the specified time may be increased compared to a conventional refrigerator. Accordingly, the cooling capacity for the freezing chamber may be increased. Thus, the driving time of a compressor may be reduced compared to a 15 conventional refrigerator, and power consumption may further be reduced compared to a conventional refrigerator. At this time, in reducing the amount of air to the storage chamber different from the freezing chamber, the time during which the supply port is opened within the specified time may be reduced. Therefore, in reducing the amount of air to the storage chamber different from the 20 freezing chamber, the air passage resistance is not increased. Accordingly, a region that cold air does not 5 a 1001622809 2015268480 03 Nov 2016 reach may be prevented from being generated in the storage chamber different from the freezing chamber. Furthermore, temperature distribution may be prevented from being generated within the storage chamber different from the freezing chamber. 5 [0009]

Furthermore, in a case where the internal load is greater than the specified value (in a case where the internal load is high), the damper is controlled to fully close the supply port for the specified time when the load of the freezing chamber is greater than the specified value and to fully open the supply port for the 10 specified time when the load of the storage chamber different from the freezing chamber is greater than the specified value. Therefore, even in a case where the internal load is greater than the specified value, variations in the temperature of each storage chamber may be suppressed (stabilization and cooling capacity may be maintained). 15 Brief Description of Drawings [0010] [Fig. 1] Fig. 1 is a diagram explaining a configuration of a refrigeration cycle of a refrigerator 100 according to Embodiment of the present invention.

[Fig. 2] Fig. 2 is a diagram illustrating a cold air circuit of the refrigerator 20 100 according to Embodiment of the present invention.

[Fig. 3] Fig. 3 is a diagram explaining a specified time CT of a refrigerating chamber damper 23 of the refrigerator 100 according to Embodiment of the present invention.

[Fig. 4] Fig. 4 is a flowchart illustrating a flow until opening time control for 25 the refrigerating chamber damper 23 of the refrigerator 100 according to Embodiment of the present invention within the specified time is executed. Description of Embodiments [0011] 6 1001621906

Hereinafter, a refrigerator according to Embodiment of the present invention will be described with reference to drawings. The present invention is not intended to be limited to Embodiment described below. In the drawings provided below including Fig. 1, the size relationship of individual component members may differ from the actual size relationship.

[0012]

Embodiment.

Fig. 1 is a diagram explaining a configuration of a refrigeration cycle of a refrigerator 100 according to Embodiment of the present invention. The configuration of the refrigeration cycle of the refrigerator 100 will be described below with reference to Fig. 1.

The refrigerator 100 cools inside the refrigerator 100 to a setting temperature by using a vapor-compression refrigeration cycle. Such a refrigeration cycle is configured such that a compressor 11, a condensing pipe 14, which serves as a condenser, a dew condensation prevention pipe 15, a drier 16, a capillary tube 17, which is a pressure-reducing mechanism, and an evaporator 18, which is a cooler, are connected by pipes. Furthermore, at the refrigeration cycle of the refrigerator 100, a heat exchange part 19 that allows heat exchange between refrigerant flowing in the capillary tube 17 and refrigerant flowing in a pipe (suction pipe) provided between the evaporator 18 and the compressor 11 is provided. Furthermore, at the refrigeration cycle, a temperature sensor 18a, such as a thermistor, for measuring the temperature of refrigerant on an inlet side of the evaporator 18 and a temperature sensor 18b, such as a thermistor, for measuring the temperature of refrigerant on an outlet side of the evaporator 18 are provided.

[0013]

The compressor 11 is, for example, arranged inside a machine chamber provided in a lower part of a rear surface of the refrigerator 100. The compressor 11 compresses refrigerant into high-temperature and high-pressure 7 1001621906 refrigerant and is driven by an inverter, and the operation capacity is controlled in accordance with conditions.

[0014]

The condensing pipe 14 represents a condensing pipe buried on a top surface, a side surface, a rear surface, or other surfaces of the refrigerator 100 via an insulating material. Furthermore, the condensing pipe 14 also includes a hot pipe for drain evaporation.

[0015]

The dew condensation prevention pipe 15 is connected between the condensing pipe 14 and the drier 16. The dew condensation prevention pipe 15 is provided for prevention of dew attachment to a front surface of the main body of the refrigerator 100.

[0016]

The drier 16 is connected between the dew condensation prevention pipe 15 and the capillary tube 17. The drier 16 includes a filter for preventing dust, metal powder, or other materials within the refrigeration cycle of the refrigerator 100 from flowing into the compressor 11, an adsorption member that adsorbs moisture within the refrigeration cycle, and other components.

[0017]

The capillary tube 17 is connected between the drier 16 and the evaporator 18. The capillary tube 17 operates as a pressure-reducing mechanism for reducing the pressure of refrigerant flowing through the drier 16.

[0018]

The evaporator 18 is connected between the capillary tube 17 and a suction pipe side of the heat exchange part 19. The evaporator 18 cools inside air, for example, at an evaporator installation chamber provided on the rear surface side of the refrigerator 100. Above the evaporator 18, an internal fan 20 is provided. By the internal fan 20, cold air is supplied from the evaporator 18, and cold air is conveyed to each storage chamber. 8 1001621906 [0019]

The heat exchange part 19 is a part that allows heat exchange between refrigerant flowing in the capillary tube 17 and refrigerant sucked into the compressor 11.

[0020]

Furthermore, for example, in an upper part of the rear surface of the refrigerator 100, the controller 10 including a microcomputer or other devices for controlling the operation of the refrigerator 100 is provided. Furthermore, the controller 10 includes an internal load recognizing unit 10a, an opening time acquisition unit 10b, a determination unit 10c, and a damper control unit 10d.

The internal load recognizing unit 10a recognizes whether or not the internal load of the refrigerator 100 is less than or equal to a specified value. The opening time acquisition unit 10b acquires, when the internal load is less than or equal to the specified value, an opening time during which a supply port 2 of a refrigerating chamber 22 is opened within a specified time, which is a control interval for a refrigerating chamber damper 23. The refrigerating chamber damper 23 and the supply port 2 of the refrigerating chamber 22 will be described later with reference to Fig. 2. The determination unit 10c determines whether or not the load of a freezing chamber 21 and the load of the refrigerating chamber 22 (a storage chamber different from the freezing rom 21) is greater than the specified value. The damper control unit 10d controls the refrigerating chamber damper 23.

[0021]

In the refrigerator 100 configured as described above, the refrigerant that has turned into high-temperature and high-pressure refrigerant at the compressor 11 transfers heat to the outside air through the condensing pipe 14 and the dew condensation prevention pipe 15 (or part of the refrigerant remains in the refrigerator). The refrigerant whose heat has been sufficiently transferred is decompressed into low-temperature and low-pressure refrigerant at the capillary 9 1001621906 tube 17, receives heat at the evaporator 18 from air returning from each storage chamber, and is compressed into high-temperature and high-pressure refrigerant again at the compressor 11.

[0022] 5 Fig. 2 is a diagram illustrating a cold air circuit of the refrigerator 100 according to Embodiment of the present invention.

The refrigerator 100 includes the freezing chamber 21 and the refrigerating chamber 22 as a storage chamber different from the freezing chamber 21. In Fig. 2, only two storage chambers, that is, the freezing chamber 21 and the 10 refrigerating chamber 22, are illustrated. However, in addition to the above storage chambers, an ice-making chamber, a vegetable chamber, a switching chamber, and other chambers may be installed in parallel to the freezing chamber 21 and the refrigerating chamber 22 or in series to the refrigerating chamber 22 (not illustrated in Fig. 2). In Fig. 2, the refrigerating chamber 22, 15 which is a storage chamber having the largest capacity in the refrigerator 100, and the freezing chamber 21, which has the lowest temperature zone, are illustrated.

[0023]

An air passage 1 at which the evaporator 18 and the internal fan 20 are 20 provided connects the above storage chambers via supply ports. That is, cold air cooled by the evaporator 18 (cooled air) is conveyed by the internal fan 20 to each storage chamber. More particularly, the flow of cold air from the internal fan 20 is caused to branch off into individual storage chambers. One part of the entire amount of air is supplied to the freezing chamber 21, and the other part is 25 supplied to the refrigerating chamber 22. Then, the air returns to the evaporator 18 again.

[0024]

At the supply port 2 of the refrigerating chamber 22 in the air passage 1, the refrigerating chamber damper 23 for opening and closing the supply port 2 is 10 1001621906 provided. The refrigerating chamber damper 23 is configured such that time control is performed on opening and closing of the refrigerating chamber damper 23 by the controller 10. That is, the controller 10 may adjust (control) the opening time during which the supply port 2 is opened within a specified time CT 5 by controlling the opening time of the refrigerating chamber damper 23. That is, for the refrigerating chamber 22, the amount of cold air within the specified time CT is adjusted and the temperature of the refrigerating chamber is thus adjusted by the control of the opening time of the refrigerating chamber damper 23. The temperature of the refrigerating chamber 22 is measured by a temperature 10 sensor 22b, such as a thermistor, provided at the refrigerating chamber 22.

Then, the opening time acquisition unit 10b of the controller 10 acquires (predicts) a necessary opening time within the specified time CT of the refrigerating chamber damper 23, based on the measured temperature. That is, the opening time acquisition unit 10b acquires (predicts) how long within the 15 specified time CT the supply port 2 needs to be opened so that the temperature of the refrigerating chamber 22 may be kept constant. Furthermore, the damper control unit 10d of the controller 10 controls the refrigerating chamber damper 23 such that the supply port 2 is opened only for the necessary opening time within the specified time CT. The above necessary opening time is predicted, for 20 example, by a prediction technique such as PI control (proportional-integral control). During the opening time, the opening ratio of the supply port 2 by the refrigerating chamber damper 23 is set such that a region that cold air does not reach is not generated within the refrigerating chamber 22 due to a large air passage resistance. The opening ratio of the supply port 2 by the refrigerating 25 chamber damper 23 is set, for example, to be fully open.

[0025]

Specifically, in Embodiment, the necessary opening time within the specified time CT of the refrigerating chamber damper 23 is obtained using equation (1). 11 1001621906 MV= Kp X [1+{1/(TlxS)}] X EV ·· (1)

In equation (1), MV represents the amount of operation, and is an opening time within the specified time CT of the refrigerating chamber damper 23. EV represents a control deviation, which is a difference between a setting 5 temperature of the refrigerating chamber 22 and a measured value of the temperature sensor 22b provided at the refrigerating chamber 22. Furthermore, Kp represents a proportional gain, Tl represents an integration time, and S represents a Laplace operator.

[0026] 10 Furthermore, the temperature of the freezing chamber 21 is measured by a temperature sensor 21 b, such as a thermistor, provided at the freezing chamber 21.

In the case where a damper is provided at a supply port of the freezing chamber 21 in the air passage 1, advantages of the present invention may be 15 attained.

[0027]

Next, the specified time CT will be described. The specified time CT is the shortest control interval at which the controller 10 controls the refrigerating chamber damper 23. The controllability improves as the specified time CT 20 decreases. However, the specified time CT may be set in a desired manner.

[0028]

Fig. 3 is a diagram explaining the specified time CT for the refrigerating chamber damper 23 in the refrigerator 100 according to Embodiment of the present invention. The horizontal axis of Fig. 3 represents the specified time 25 CT, and a more right position on the horizontal axis represents a larger specified time CT. The vertical axis of Fig. 3 represents input (input power), and an upper position on the vertical axis represents a larger input.

[0029] 12 1001621906

As illustrated in Fig. 3, the number of times of driving the refrigerating chamber damper 23 increases as the specified time CT decreases (that is, the control interval decreases), and therefore, the amount of input necessary for opening and closing the refrigerating chamber damper 23 (damper input in Fig. 5 3) increases. In contrast, the shorter the specified time CT, the more the variations in the temperature of each storage chamber may be suppressed, and the more the amount of air to the freezing chamber 21 becomes, as described later. Therefore, the average input of the compressor 11 (compressor input in Fig. 3) decreases. Thus, as shown in Fig. 3, the entire input of the refrigerator 10 100, which is the total sum of input of a driving device such as the refrigerating chamber damper 23, input of the compressor 11, and other inputs has a minimum value. That is, by operating the refrigerating chamber damper 23 for the specified time CT, for which the entire input is at the minimum, the power consumption of the refrigerator 100 may further be reduced. Therefore, in 15 Embodiment, the specified time CT by which the entire input is minimum is adopted. The specified time CT differs according to the operation conditions, internal capacity, and insulating structure of the refrigerator 100. Taking into consideration the number of times of driving the refrigerating chamber damper 23, the specified time CT is desirably set to about five minutes. 20 [0030]

Next, the opening time of the supply port 2 within the specified time CT at a stable state of the refrigerator 100 will be described. The stable state of the refrigerator 100 refers to a state in which the internal load, which will be described later, is less than or equal to a specified value, that is, the internal load 25 is lower than a reference value.

[0031]

The controller 10 of the refrigerator 100 starts the compressor 11 when the temperature of the freezing chamber 21 reaches a setting temperature or above, and stops the compressor 11 when the temperature of the freezing chamber 21 13 1001621906 drops to the setting temperature or below. The compressor 11, which occupies most of the entire input, needs to be stopped to reduce the amount of power consumption by the refrigerator 100. Thus, by increasing the cooling capacity for the freezing chamber 21, that is, by increasing the amount of air supplied to 5 the freezing chamber 21 as much as possible, the freezing chamber 21 is set to the setting temperature or below in a short time, and the operation time of the compressor 11 is reduced.

[0032]

With a conventional refrigerator, in opening and closing of the refrigerating 10 chamber damper 23, the amount Qra of air is supplied to the refrigerating chamber 22 to reduce the temperature of the refrigerating chamber 22 at the time when the refrigerating chamber damper 23 is opened. At this time, the amount Qfa of cold air, which is obtained by subtracting Qra from the entire amount Q of air, is supplied to the freezing chamber 21 (i.e. Qfa = Q- Qra). Therefore, the 15 temperature of the freezing chamber 21 is constant or increases.

[0033]

After the refrigerating chamber 22 is cooled to the setting temperature, the refrigerating chamber damper 23 is closed, and the entire amount Q of air is conveyed to the freezing chamber 21. Therefore, the freezing chamber 21 is 20 cooled to the setting temperature, and then the compressor 11 stops.

[0034]

In contrast, with the refrigerator 100 according to Embodiment, the controller 10 controls the refrigerating chamber damper 23 to control the opening time during which the supply port 2 is opened within the specified time CT. That 25 is, the refrigerator 100 according to Embodiment supplies the amount Qrb of cold air, which corresponds to an amount that keeps the temperature of the refrigerating chamber 22 constant, to the refrigerating chamber 22 for the specified time CT. As is clear from the amount of reduction in the temperature of the refrigerating chamber 22, Qrb is smaller than Qra. Consequently, in 14 1001621906

Embodiment, the amount of air conveyed to the freezing chamber 21 is represented by Qfb = Q - Qrb, where Qfb is larger than Qfa. Therefore, the temperature of the freezing chamber 21 rapidly decreases compared to variations in the temperature of the conventional freezing chamber 21. Thus, inventors have obtained a result that the refrigerator 100 according to Embodiment achieves an improved operation ratio, which represents the ratio of operation to stoppage of the compressor 11, compared to a conventional refrigerator. Such a reduction ratio differs according to the operation conditions, internal capacity, and insulating structure of the refrigerator 100.

[0035]

With the refrigerator 100 according to Embodiment, in reducing the amount of cold air (amount of air) supplied to the refrigerating chamber 22, the time during which the supply port 2 is opened within the specified time CT may be reduced. Therefore, with the refrigerator 100 according to Embodiment, in reducing the amount of air to the refrigerating chamber 22, the air passage resistance is not increased, and therefore, a region that cold air does not reach may be prevented from being generated in the refrigerating chamber 22, and temperature distribution may be prevented from being caused in the refrigerating chamber 22.

[0036]

As described above, the shorter the specified time CT, the more the temperature constant control for the refrigerating chamber 22 may be achieved. However, the number of operation times of the refrigerating chamber damper 23 increases. Therefore, driving input of the refrigerating chamber damper 23 increases, and the possibility that the refrigerating chamber damper 23 is broken down due to its lifetime and other reasons increases. Furthermore, as the number of operation times of the refrigerating chamber damper 23 increases, the amount of heat generation of a motor for causing the refrigerating chamber damper 23 to operate also increases and serves as an internal load, and the 15 1001621906 amount of power consumption by the refrigerator 100 increases. Therefore, by adopting the specified time CT by which the entire input of the refrigerator 100 is minimum, a further reduction in the amount of power consumption may be achieved. Furthermore, inventors have achieved a further improvement by performing similar control for a storage chamber different from the refrigerating chamber 22.

[0037]

As described above, by controlling the opening time during which the supply port 2 is open within the specified time CT for each of the storage chambers including the refrigerating chamber 22 but not including the freezing chamber 21 at a stable state to increase the amount of air to the freezing chamber 21, a reduction in the amount of power consumption may be achieved.

[0038]

Although damper control for the refrigerating chamber 22 has been described above, in the case where the damper control is performed for a plurality of storage chambers at the same time, the storage chambers may mutually receive disturbance at the time of damper control, and therefore, controllability of the temperature of the storage chambers may be degraded. Thus, control is desirably started in order from a damper provided at a supply port (cold air supply port) of a storage chamber with a high setting temperature. This is because for a storage chamber with a higher setting temperature, the temperature of air flowing into the evaporator 18 (cooler) increases, the influence exerted on the temperature of cold air supplied by the evaporator 18 (cooler) increases, and more disturbance tends to occur.

[0039]

At this time, since the refrigerating chamber 22 is a storage chamber having the largest capacity, control for the refrigerating chamber damper 23 provided at the supply port 2 of the refrigerating chamber 22 may be started first, and then, control may be performed in order from a damper provided at a supply 16 1001621906 port (cold air supply port) of a storage chamber with a high setting temperature. For a refrigerator including the refrigerating chamber 22, an ice-making chamber, a switching chamber, the freezing chamber 21, and a vegetable chamber, as an example, the order in which control is to be performed will be described below. 5 In general, a vegetable chamber is a storage chamber with the highest setting temperature, and the refrigerating chamber 22 is a storage chamber having the largest capacity. Therefore, the refrigerating chamber 22 is provided with the highest priority. The vegetable chamber, which has the highest setting temperature, is provided with the second highest priority. The ice-making 10 chamber and the switching chamber may have any setting temperature set by a user. Therefore, the order is determined by the setting temperature. In general, the ice-making chamber is set to have a temperature substantially close to the freezing chamber, and therefore is given a low priority.

[0040] 15 Next, examples of detection of the internal load of the refrigerator 100 will be explained.

[0041] (1-1) Detection of internal load based on operation conditions of compressor Operation/stoppage of the compressor 11 according to Embodiment is 20 controlled based on the temperature detected by the temperature sensor 21 b of the freezing chamber 21, and during operation, the rotation speed of the compressor 11 is controlled in accordance with the state of a deviation between the temperature of the freezing chamber 21 and a setting temperature, and the operation time. Therefore, the operation conditions of the compressor 11 may 25 be represented as one of indicators indicating the entire cooling load of the refrigeration cycle of the refrigerator 100, that is, the internal load. Thus, as the internal load, the rotation speed f of the compressor 11 or the input power W to the compressor 11 may be used. In the case where the rotation speed f of the compressor 11 is higher than a predetermined threshold (in the case where the 17 1001621906 input power W is large), the internal load is high. In the case where the rotation speed of the compressor 11 is lower than the predetermined threshold (in the case where the input power W is small), the internal load is low. The controller 10 determines whether or not the internal load is less than or equal to a threshold Qa (specified value) by acquiring the rotation speed f or the input power W, which is acquired when controlling the operation of the compressor 11, and comparing the acquired value with a threshold stored in advance in a microcomputer. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) is performed by the internal load recognizing unit 10a.

[0042] (1-2) Detection of internal load based on difference in temperature between outlet and inlet of evaporator A state in which the temperature of air flowing into the evaporator 18 according to Embodiment represents a state in which the internal load is high.

In this case, a temperature difference ATe occurs between refrigerant on the outlet side of the evaporator 18 and refrigerant on the inlet side of the evaporator 18. Therefore, the temperature difference ATe between the outlet side and the inlet side of the evaporator 18 may be regarded as one of indicators indicating the entire cooling load of the refrigeration cycle of the refrigerator 100, that is, the internal load. Thus, as the internal load, the temperature difference ATe between the outlet side and the inlet side of the evaporator 18 may be used.

The controller 10 determines whether or not the internal load is less than or equal to the threshold Qa by acquiring output from the temperature sensor 18a, which is provided on the inlet side of the evaporator 18, and output from the temperature sensor 18b, which is provided on the outlet side of the evaporator 18, and comparing the temperature difference ATe with a threshold stored in advance in a microcomputer. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the 18 1001621906 temperature sensors 18a and 18b is performed by the internal load recognizing unit 10a.

[0043] (1-3) Detection of internal load based on number Rr of times of opening and 5 closing door of refrigerating chamber.

By opening a door 22a of the refrigerating chamber 22, outside air flows into the refrigerating chamber 22, and cold air flows to the outside. Therefore, the temperature of the refrigerating chamber 22 increases, and the cooling load increases. The refrigerating chamber 22 is a region with the largest capacity in 10 the refrigerator 100, and a large amount of cold air is necessary for cooling the refrigerating chamber 22 to a predetermined temperature. Therefore, the number Rr of times of opening and closing the door of the refrigerating chamber 22 may be regarded as one of indicators indicating the entire cooling load of the refrigeration cycle of the refrigerator 100, that is, the internal load. Thus, as the 15 internal load, the number Rr of times of opening and closing the door per unit time may be used. The controller 10 determines whether or not the internal load is less than or equal to the threshold Qa by counting the number Rr of times of opening and closing the door per unit time based on output from a door opening and closing sensor 22c of the refrigerating chamber 22 and comparing a 20 predetermined threshold stored in advance in a microcomputer with the number Rr of times of opening and closing the door. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the door opening and closing sensor 22c of the refrigerating chamber 22 is performed by the internal load recognizing unit 10a. 25 [0044] (1-4) Detection of internal load based on number Rf of times of opening and closing door of freezing chamber

Similarly, the number Rf of times of opening and closing a door 21a of the freezing chamber 21 may be regarded as one of indicators indicating the entire 19 1001621906 cooling load of the refrigeration cycle of the refrigerator 100, that is, the internal load. That is, as described above, operation and stoppage of the compressor 11 according to Embodiment is controlled based on the temperature detected by the temperature sensor 21b of the freezing chamber 21. Thus, similarly to the 5 number Rr of times of opening and closing the door of the refrigerating chamber 22, as the internal load, the number Rf of times of opening and closing the door per unit time may be used. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using a door opening and closing sensor 21c provided at the freezing chamber 21 is 10 performed by the internal load recognizing unit 10a.

[0045] (1-5) Detection of internal load based on time xr during which door of refrigerating chamber is opened

As described above, by opening the door 22a of the refrigerating chamber 15 22, the temperature of the refrigerating chamber 22 increases, and therefore, the cooling load increases. Thus, the time xr during which the door of the refrigerating chamber 22 is opened (cumulative of time during which the door 22a is opened per unit time) may be regarded as one of indicators indicating the entire cooing load of the refrigeration cycle of the refrigerator 100, that is, the 20 internal load. Accordingly, as the internal load, the time xr during which the door of the refrigerating chamber 22 is opened may be used. The controller 10 counts and accumulates times during which the door 22a is opened, based on output from the door opening and closing sensor 22c. Then, the controller 10 determines whether or not the internal load is less than or equal to the threshold 25 Qa by comparing the time xr during which the door is opened per unit time with a predetermined threshold stored in advance in a microcomputer. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the door opening and closing sensor 22c 20 1001621906 provided at the refrigerating chamber 22 is performed by the internal load recognizing unit 10a.

[0046] (1-6) Detection of internal load based on time if during which door of freezing chamber is opened

Similarly, the time tf during which the door 21a of the freezing chamber 21 is opened may also be regarded as one of indicators indicating the entire cooing load of the refrigeration cycle of the refrigerator 100, that is, the internal load. Thus, similarly to the time xr during which the door of the refrigerating chamber 22 is opened, as the internal load, the time if during which the door is opened per unit time may be used. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the door opening and closing sensor 21c provided at the freezing chamber 21 is performed by the internal load recognizing unit 10a.

[0047] (1-7) Detection of internal load based on temperature Tr of refrigerating chamber It can be said that the higher the temperature detected by the temperature sensor 22b provided at the refrigerating chamber 22, the higher the internal load of the refrigerating chamber 22. Thus, as the internal load, the temperature Tr of the refrigerating chamber may be used. The controller 10 determines whether or not the internal load is less than or equal to the threshold Qa by comparing, based on output from the temperature sensor 22b of the refrigerating chamber 22, the temperature Tr of the refrigerating chamber with a predetermined threshold stored in advance in a microcomputer. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the temperature sensor 22b provided at the refrigerating chamber 22 is performed by the internal load recognizing unit 10a.

[0048] 21 1001621906 (1-8) Detection of internal load based on amount of reduction in temperature of freezing chamber

In the case where a large food having a relatively high temperature is placed in the freezing chamber 21, the speed of reduction in the temperature of 5 the freezing chamber 21 tends to be slow. In such a case, it may be said that the cooling load in the freezing chamber 21 is high. Thus, as the internal load, the amount of reduction in the temperature of the freezing chamber 21 per unit time may be used. The controller 10 determines whether or not the internal load is less than or equal to the threshold Qa by calculating the amount of reduction in 10 the temperature per unit time, based on output from the temperature sensor 21 b of the freezing chamber 21, and comparing the amount of reduction in the temperature with a predetermined threshold stored in advance in a microcomputer. The determination as to whether or not the internal load is less than or equal to the threshold Qa (specified value) using the temperature sensor 15 21b provided at the freezing chamber 21 is performed by the internal load recognizing unit 10a.

[0049]

Each of the above-described examples of an internal load detector may be implemented without providing an additional component, and the number of 20 components of the refrigerator 100 does not need to be increased.

[0050]

Next, control for the refrigerating chamber damper 23 in a state in which the above internal load is more than the threshold Qa (specified value) will be described. When the state in which the internal load is more than the threshold 25 Qa (specified value) is detected, the controller 10 of the refrigerator 100 controls the refrigerating chamber damper 23 in accordance with a flow illustrated in a flowchart of Fig. 4. Fig. 4 is a flowchart illustrating a flow up to the point where opening time control within the specified time CT of the refrigerating chamber damper 23 at the stable state of the refrigerator 100 according to Embodiment of 22 1001621906 the present invention is executed. By performing a similar determination for a storage chamber different from the refrigerating chamber, opening time control at the stable state of the refrigerator 100 according to Embodiment may be attained.

[0051]

In the case where the internal load is more than the threshold Qa (specified value) (step S1), the controller 10 compares the temperature Tr of the refrigerating chamber of the refrigerating chamber 22 with a setting temperature Trm (step S2). This comparison is performed by the determination unit 10c of the controller 10. When Tr is less than or equal to Trm, the internal load is of the freezing chamber 21 not the refrigerating chamber 22, that is, the load of the freezing chamber 21 is greater than the specified value. Therefore, the damper control unit 10d of the controller 10 controls the refrigerating chamber damper 23 to constantly close (fully close) the supply port 2 for the specified time CT (step S3). Accordingly, substantially the entire amount of air from the internal fan 20 of the refrigerator 100 may be supplied to the freezing chamber 21, and the load may be rapidly handled. Thus, the freezing chamber 21 may be cooled to the setting temperature. At this time, the rotation speed of at least one of the internal fan 20 and the compressor 11 may be increased at the same time, so that the cooling speed may be increased (from No in step S4 to step S5).

[0052]

After the freezing chamber 21 is cooled to the setting temperature (Yes in step S4), the damper control unit 10d of the controller 10 performs control equivalent to the stable state for the refrigerating chamber damper 23 (step S6).

[0053]

In contrast, when Tr is greater than Trm in step S2, the internal load is of the refrigerating chamber 22, that is, the load of the refrigerating chamber 22 is greater than the specified value. Therefore, the damper control unit 10d of the controller 10 controls the refrigerating chamber damper 23 to constantly fully open the supply port 2 for the specified time CT (step S11). Accordingly, the 23 1001621906 load of the refrigerating chamber 22 is handled, and the refrigerating chamber 22 is cooled to the setting temperature. At this time, the rotation speed of at least one of the internal fan 20 and the compressor 11 may be increased at the same time, so that the cooling speed may be increased (from No in step S12 to step S13). After the freezing chamber 21 is cooled to the setting temperature (Yes in step S12), the damper control unit 10d of the controller 10 performs control equivalent to the stable state for the refrigerating chamber damper 23 (step S14).

[0054]

As described above, with the refrigerator 100 according to Embodiment, in the case where the internal load is less than or equal to the specified value (in the case where the internal load is low), by adjusting the time during which the supply port is opened within the specified time, which is a control interval for the damper, the temperature of a storage chamber different from the freezing chamber 21 is maintained at the setting temperature, in a manner different from a conventional structure in which the supply port of the storage chamber different from the freezing chamber 21 is opened or closed according to the setting temperature. That is, with the refrigerator 100 according to Embodiment, only an amount of cold air that keeps the temperature of the storage chamber different from the freezing chamber 21 constant is conveyed to the storage chamber for the specified time CT, and thus variations in the temperature of the storage chamber is suppressed. Therefore, in the case where the internal load is low, the refrigerator 100 according to Embodiment may increase the amount of cold air supplied to the freezing chamber 21 compared to a conventional refrigerator. Thus, variations in the temperature of the freezing chamber 21 may be suppressed. Accordingly, the driving time of the compressor 11 may be reduced compared to a conventional refrigerator, and therefore a further reduction in the power consumption may be achieved compared to a conventional refrigerator.

[0055] 24 1001621906

At this time, with the refrigerator 100 according to Embodiment, in reducing the amount of air to the storage chamber different from the freezing chamber 21, the time during which the supply port is opened within the specified time CT may be reduced. Therefore, with the refrigerator 100 according to Embodiment, in reducing the amount of air to the storage chamber different from the freezing chamber 21, the air passage resistance is not increased. Therefore, a region that cold air does not reach may be prevented from being generated in the storage chamber different from the freezing chamber 21. Furthermore, temperature distribution may be prevented from being caused in the storage chamber different from the freezing chamber 21.

[0056]

Furthermore, with the refrigerator 100 according to Embodiment, in the case where the internal load is greater than the specified value (in the case where the internal load is high), the damper is controlled to fully close the supply port for the specified time when the load of the freezing chamber 21 is greater than the specified value and to fully open the supply port for the specified time when the load of the storage chamber different from the freezing chamber 21 is greater than the specified value. Therefore, with the refrigerator 100 according to Embodiment, even in the case where the internal load is greater than the specified value, variations in the temperature of each storage chamber may be suppressed (stabilization and cooling capacity may be maintained).

Reference Signs List [0057] 1 air passage, 2 supply port, 10 controller, 10a internal load recognizing unit, 10b opening time acquisition unit, 10c determination unit, 10d damper control unit, 11 compressor, 14 condensing pipe, 15 dew condensation prevention pipe, 16 drier, 17 capillary tube, 18 evaporator, 18a temperature sensor, 18b temperature sensor, 19 heat exchange part, 20 internal fan, 21 freezing chamber, 21a door, 21b temperature sensor, 21c door opening and 25 1001621906 closing sensor, 22 refrigerating chamber, 22a door, 22b temperature sensor, 22c door opening and closing sensor, 23 refrigerating chamber damper, 100 refrigerator 26

Claims

CLAIMS [Claim 1] A refrigerator comprising: a freezing chamber and at least one storage chamber different from the freezing chamber; a refrigeration cycle including a compressor, a condenser, an expansion mechanism, and an evaporator; an air passage communicating to the freezing chamber and the storage chamber different from the freezing chamber, the evaporator being arranged at the air passage; an internal fan provided at the air passage and configured to supply air cooled by the evaporator to the freezing chamber and the storage chamber different from the freezing chamber; a damper provided at a supply port of the storage chamber different from the freezing chamber in the air passage and configured to open and close the supply port; and a controller configured to control, based on an internal load, at least the damper, the controller including an internal load recognizing unit configured to recognize the internal load, an opening time acquisition unit configured to acquire an opening time during which the supply port is opened within a specified time serving as a control interval for the damper in a case where the internal load is less than or equal to a specified value, a determination unit configured to determine whether or not a load of the freezing chamber and a load of the storage chamber different from the freezing chamber are greater than the specified value, and a damper control unit configured to control, in a case where the internal load is less than or equal to the specified value, the damper to open the supply port for the opening time within the specified time, and control, in a case where the internal load is greater than the specified value and the internal load is the load of the freezing chamber, the damper to fully close the supply port for the specified time, and in a case where the internal load is greater than the specified value and the internal load is the load of the storage chamber different from the freezing chamber, the damper to fully open the supply port for the specified time. [Claim
2] The refrigerator of claim 1, wherein the specified time is a time for which an entire input of the refrigerator is minimum. [Claim
3] The refrigerator of claim 1 or 2, wherein the storage chamber different from the freezing chamber includes a plurality of storage chambers, and the damper includes a plurality of dampers, the storage chambers different from the freezing chamber include a refrigerating chamber and at least one storage chamber different from the refrigerating chamber, and the damper control unit is configured to start control for the damper provided at the supply port of the refrigerating chamber and then start control for the damper provided at the supply port of the storage chamber different from the refrigerating chamber. [Claim
4] The refrigerator of claim 3, wherein the storage chamber different from the refrigerating chamber incudes a plurality of storage chambers, and in controlling the damper provided at the supply port of each of the storage chambers different from the refrigerating chamber, the damper control unit is configured to start control in order from the damper corresponding to a storage chamber having a high setting temperature. [Claim
5] The refrigerator of claim 1 or 2, wherein the storage chamber different from the freezing chamber includes a plurality of storage chambers, and the damper includes a plurality of dampers, and the damper control unit is configured to start control in order from the damper provided at the supply port of a storage chamber having a high setting temperature. [Claim
6] The refrigerator of any one of claims 1 to 5, further comprising: a temperature sensor configured to detect a temperature of the storage chamber different from the freezing chamber, wherein the determination unit is configured to compare, in a state in which the internal load is greater than the specified value, the temperature detected by the temperature sensor with a specified value, determine, in a case where the temperature detected by the temperature sensor is less than or equal to the specified value, that the load of the freezing chamber is greater than the specified value, and determine, in a case where the temperature detected by the temperature sensor is greater than the specified value, that the load of the storage chamber different from the freezing chamber is greater than the specified value. [Claim
7] The refrigerator of any one of claims 1 to 6, wherein the internal load recognizing unit is configured to recognize the internal load, based on a rotation speed of the compressor or input power of the compressor. [Claim
8] The refrigerator of any one of claims 1 to 6, further comprising: a temperature sensor configured to measure a temperature of refrigerant on an inlet side of the evaporator; and a temperature sensor configured to measure a temperature of refrigerant on an outlet side of the evaporator, wherein the internal load recognizing unit is configured to recognize the internal load, based on a difference in the temperature between the refrigerant on the outlet side of the evaporator and the refrigerant on the inlet side of the evaporator. [Claim
9] The refrigerator of any one of claims 1 to 6, further comprising: a door opening and closing sensor configured to detect an opening and closing state of a door of the storage chamber, wherein the internal load recognizing unit is configured to recognize the internal load, based on a number of times of opening and closing the door per unit time. [Claim
10] The refrigerator of any one of claims 1 to 6, further comprising: a door opening and closing sensor configured to detect an opening and closing state of a door of the storage chamber, wherein the internal load recognizing unit is configured to recognize the internal load, based on a cumulative opening time of the door per unit time. [Claim
11] The refrigerator of any one of claims 1 to 6, further comprising: a temperature sensor configured to detect a temperature of the storage chamber different from the freezing chamber, wherein the internal load recognizing unit is configured to recognize the internal load, based on the temperature of the storage chamber. [Claim
12] The refrigerator of any one of claims 1 to 6, further comprising: a freezing chamber temperature sensor configured to detect a temperature of the freezing chamber, wherein the internal load recognizing unit is configured to recognize the internal load, based on an amount of reduction in the temperature of the freezing chamber per unit time. [Claim
13] The refrigerator of any one of claims 1 to 12, wherein in a case where the internal load is greater than the specified value, the controller is configured to increase a rotation speed of at least one of the compressor and the internal fan. [Claim
14] A refrigerator comprising: a freezing chamber and at least one storage chamber different from the freezing chamber; a refrigeration cycle including a compressor, a condenser, an expansion mechanism, and an evaporator; an air passage communicating to the freezing chamber and the storage chamber different from the freezing chamber, the evaporator being arranged at the air passage; an internal fan provided at the air passage and configured to supply air cooled by the evaporator to the freezing chamber and the storage chamber different from the freezing chamber; a damper provided at a supply port of the storage chamber different from the freezing chamber in the air passage and configured to adjust an opening ratio of the supply port; and a controller configured to control, based on an internal load, at least the damper, the controller being configured to control, in a ease where the internal load is less than or equal to a specified value, the damper not to fully close or fully open the supply port to control, a temperature of the storage chamber different from the freezing chamber toward the setting temperature, and control, in a case where the internal load is greater than the specified value and the internal load is the load of the freezing chamber, the damper to fully close the supply port, and in a case where the internal load is greater than the specified value and the internal load is the load of the storage chamber different from the freezing chamber, the damper to fully open the supply port.