JP4406275B2 - refrigerator - Google Patents

Description

  The present invention relates to a refrigerator provided with a two-stage compressor having a ball joint structure.

Conventionally, a refrigerator using a hermetic reciprocating compressor that performs two-stage compression in a refrigeration cycle having evaporators with different evaporation temperatures has been considered (see, for example, Patent Document 1).
In this case, the refrigerant discharged from one evaporator is evaporated to the first compressor 112a of the compressor 110 via the first suction pipe 114 as shown in FIG. 4 which is a schematic diagram of the compressor. The refrigerant discharged from the container flows through the second suction pipe 116 to the second compression portion 112b of the compressor 110.

  In the compressor 110, a first compression part 112a and a second compression part 112b face each other in a sealed case 111 and are connected in a connected state by a ball joint structure, and these compression parts drive the same motor 113. As a source.

  Specifically, pistons 131a and 131b are housed in cylinders 130a and 130b in a reciprocating manner, and connecting rods 133a and 131b are connected to rotating shafts that are eccentric with respect to the central axis of the motor 113. It is connected to 133b. In this connection structure, ball portions 134a and 134b are provided at the tips of connecting rods 133a and 133b, and the ball portions 134a and 132b are formed by caulking after the ball portions 134a and 134b are inserted into the pistons 131a and 131b. The ball portions 134a and 134b are held and are engaged with each other.

  When the refrigerant gas suction process is performed by the low pressure compression unit, for example, the first compression unit 112a, the compression process for compressing and discharging the refrigerant gas by the intermediate pressure compression unit, for example, the second compression unit 112b, is performed. The compression units 112a and 112b perform the reverse operation. The refrigerant gas from the first evaporator is sucked into the first compression part 112a through the first suction pipe 114, and the first stage compression is performed. This refrigerant gas is discharged into the sealed case 111 from the discharge pipe 115 in the case.

In the sealed case 111, the refrigerant gas discharged from the in-case discharge pipe 115 and the refrigerant gas introduced from the second suction pipe 116 are mixed, and the second compression unit 112b is connected via the in-case suction pipe 117. To be introduced. In the second compression unit 112b, the second-stage compression is performed and discharged from the second discharge pipe 118 to the refrigeration cycle outside the compressor 110.
JP 2003-239854 A

  In the refrigerator using the ball joint structure compressor that performs such two-stage compression, the ball portions 132a and 134b push the pistons 131a and 131b in the compression direction in the compression step, and thus the load is applied to the ball receiving portion 132a. However, in the suction process, since the pistons 131a and 131b are pulled back in the suction direction, particularly immediately after the start of the suction, the ball portions 134a and 134b press the ball receiving portions 132a and 132b, and a large load (for example, 10 kg or more).

  In addition, since the refrigerant gas compressed by the first compression unit 112a is discharged into the case 111, and the inside of the case is held at an intermediate pressure, the pressure inside the case 111 is greater in the cylinder during the suction process. For example, the pressure is higher by about 0.05 to 0.2 MPa than the internal pressure of 130a and 130b. For this reason, piston 131a, 131b is pressed by the compression direction, and the load which ball receiving part 132a, 132b receives becomes large.

  In this case, generally, the load described above is based on the moving speed of the ball portions 134a and 134b, the pressure difference between the case 111 and the cylinders 130a and 130b (for example, 0.05 to 0.2 MPa), and the like. It is conceivable to design the strength of the ball receiving portions 132a and 132b so that it can withstand.

  However, depending on the cooling operation method, the pressure difference between the assumed case 111 and the cylinders 130a and 130b may be higher. In this case, as shown in FIG. Since the load received by the ball becomes larger than the assumed load, the caulking portions of the ball receiving portions 132a and 132b may be loosened and the ball portions 134a and 134b may come off.

  In particular, when there is a slight gap between the ball portions 134a and 134b and the ball receiving portions 132a and 132b, the springback of the caulking portion is unavoidable and the impact is repeatedly applied to the crimping portion. As a result, the gap is enlarged and the above-described breakage occurs.

  Therefore, in consideration of the above problems, the present invention provides a two-stage compressor having a ball joint structure that prevents the pressure difference between the case and the cylinder from becoming higher than a predetermined value and eliminates damage to the compression portion. It aims at providing the refrigerator provided.

In order to solve the above-described problems, a refrigerator according to the present invention includes a refrigerator body having a freezer compartment and a refrigerator compartment filled with a heat insulating material between an outer box and an inner box, and a different evaporation temperature provided in the refrigerator body. A freezer compartment evaporator and a refrigerator compartment evaporator, a flow rate adjusting device for changing a flow rate of refrigerant flowing through the freezer compartment evaporator or the refrigerator compartment evaporator, and a first compressor and a second compressor in the case The first compression unit compresses the refrigerant gas evaporated in the freezer evaporator and discharges it into the case, and the second compression unit evaporates in the refrigerator evaporator and the case The refrigerant gas sucked in and the refrigerant gas discharged from the first compression part are compressed and discharged out of the case, and the compression of the first compression part and the second compression part is connected by a ball joint structure. each piston is the axis of rotation In conjunction with the rolling and a compressor which performs a reciprocating motion, the refrigerator compartment evaporator and the freezer compartment evaporator is connected in parallel via the flow rate control device, the way flow of the refrigerant by the flow rate switching device Has at least a full-open mode in which a refrigerant flows through the freezer compartment evaporator and the refrigerator compartment evaporator, and an F cooling mode in which the refrigerant flows only through the freezer compartment evaporator. It is characterized by not having the R cooling mode in which the refrigerant flows only to the evaporator.

  According to the above invention, there is provided a refrigerator provided with a two-stage compressor having a ball joint structure that prevents the pressure in the case from being higher than the pressure in each cylinder by a predetermined value or more and eliminates breakage of the compression portion. can do.

  An embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 2 which is a longitudinal sectional view of the refrigerator according to the present invention, the refrigerator main body 1 has a rectangular box-shaped heat insulation box 2 filled with a heat insulating material 2c between the outer box 2a and the inner box 2b. In order from the top, it has a refrigerator compartment 3, a vegetable compartment 4, a switching chamber 5, and a freezer compartment 6. Although not shown in particular, an ice making chamber is provided with the switching chamber 5. The front opening of the main body 1 is provided with doors 7 to 10 that sequentially close the storage chambers 3 to 6 in an openable manner.

  The refrigerator compartment 3 and the vegetable compartment 4 are maintained in a temperature range of approximately 1 to 5 degrees, and each is partitioned by a partition plate 11. On the back of the vegetable compartment 4, a refrigerator 27 (hereinafter referred to as "R EVA"), which is a second evaporator, is provided, and in the upper part thereof, a refrigerator compartment fan 28 (hereinafter referred to as "R fan"). Provided). When the R fan 28 is operated, the cold air generated by the R evaporator 27 is supplied to the refrigerator compartment 3 and the vegetable compartment 4 to cool each chamber, and the cooled cold air is returned to the R evaporator 27 again. It is designed to exchange heat.

  On the other hand, the freezer compartment 6 and the switching chamber 5 are each partitioned by a heat insulating partition wall 16, the freezer compartment 6 is maintained in a temperature range of −18 to −25 degrees, and the switching chamber 5 has various set temperatures. It is controlled to be held in the belt. On the back surfaces of the switching chamber 5 and the freezer compartment 6, there is provided a freezer compartment cooler 32 (hereinafter referred to as F evaporator), which is a first evaporator whose evaporation temperature is set lower than that of the R evaporator 27, and the upper part thereof. A freezer compartment fan 33 (hereinafter referred to as F fan) is provided.

When the F fan 33 is operated, the cold air generated by the F EVA 32 is supplied to the switching chamber 5 and the freezing chamber 6 to cool each chamber, and the cooled cold air is again heat-exchanged by the F EVA 32. It has become so.

  A machine room 36 is provided at the bottom of the back surface of the main body 1, and a compressor 40 and a heat radiating fan 38 (hereinafter referred to as a C fan) for radiating heat from the compressor 40 are provided therein.

  In the refrigeration cycle according to the present invention, as shown in FIG. 3 which is a schematic diagram, a condenser 37 is connected to the discharge side of the compressor 40, and the first capillary tube 34 ( (Hereinafter referred to as F capillary tube), a pipe connecting F evaporator 32 and accumulator 35 in order, and a pipe connecting second capillary tube 29 (hereinafter referred to as R capillary tube) and R evaporator 27 are connected in parallel. Yes.

  As will be described later, the outlet side of the F evaporator 32 and the accumulator 35 is connected to the first compression portion 42a of the compressor 40 via the first suction pipe 55, and the outlet side of the R evaporator 27 is connected to the compressor via the second suction pipe 56. 40 cases 41 are connected to each other.

  The flow rate adjusting device 39 can change the valve opening by the rotation of the stepping motor to adjust the flow rate of the refrigerant flowing through the F-evaluator 32 and the R-evaluator 27, and can also change the flow path, be fully closed, and fully open. ing. The flow rate adjusting device 39 is not limited to the above configuration, and various changes such as a configuration using a solenoid can be made.

  Next, a specific configuration of the compressor will be described. As shown in FIG. 1, which is a schematic diagram of the compressor, 41 is a vertical sealing case, and a frame 41a is attached and fixed to the side wall of the case 41 at a substantially middle portion in the vertical direction in the sealing case 41. . The compression part 42 is mounted on the upper side of the frame 41a, and the electric mechanism part 43 is provided on the lower side.

  Here, the compression unit 42 employs a so-called reciprocating compressor, and includes a first compression unit 42 a located on the right side of the drawing and a second compression 42 b located on the left side.

  A pivot hole is provided at the center of the frame 41a, and a rotation shaft 44 is rotatably provided in the pivot hole. The upper end portion of the rotating shaft 44 is integrally provided with a flange portion 44a mounted on the upper surface of the frame 41a, and the upper portion of the flange portion 44a has a central axis that is eccentric from the central axis of the rotating shaft 44 by a predetermined amount. The eccentric shaft portion 44b is integrally formed.

  When the rotating shaft 44 is driven to rotate, the flange portion 44a rotates in a sliding contact with the upper surface of the frame 41a, and the eccentric shaft portion 44b rotates eccentrically with respect to the center of the rotating shaft 44.

  The first compression part 42a and the second compression part 42b are placed on the upper surface of the frame 41a. Each compression part 42a, 42b is arrange | positioned in the position which opposes substantially 180 degrees via the said eccentric shaft part 44b, and is provided with cylinder 45a, 45b each arrange | positioned horizontally with respect to the axial direction.

  Inside the cylinders 45a and 45b are compression chambers 47a and 47b in which pistons 46a and 46b are reciprocally accommodated. One ends of connecting rods 48a and 48b are connected to the pistons 46a and 46b, respectively, and the pistons 46a and 46b are connected to the eccentric shaft portion 44b via the connecting rods 48a and 48b.

  Ball joints k are formed at the tips of the connecting rods 48a and 48b, and a ball joint type connection that engages and holds the ball k by a ball receiving portion m formed by caulking inside the pistons 46a and 46b. is doing. In addition, the sphere part k and the sphere receiving part m may be provided opposite to the connecting rods 48a and 48b and the pistons 46a and 46b, respectively.

  The other ends of the connecting rods 48a and 48b form end portions 49a and 49b that are rotatably fitted to the eccentric shaft portion 44b, and have a double-fitting structure with respect to the eccentric shaft portion 44b.

  A first suction port 50 a that sucks the refrigerant gas evaporated and vaporized by the F-evapor 32 is provided on the right wall of the first compression portion 42 a and is connected to the first suction pipe 55. A first discharge port 51a for discharging the refrigerant gas compressed by the compression unit 42a is provided in the case 41.

  On the other hand, the second suction pipe 56 is directly connected to the case 41, and the inside of the case 41 becomes a mixed gas of the refrigerant gas from the R-eva 27 and the refrigerant gas compressed by the first compression part 42a. The left wall of 42b is provided with a second suction port 50b for sucking the mixed gas and a discharge port 51b for discharging the refrigerant gas compressed by the compression unit 42b to the condenser 37 side.

  With respect to such a compression part 42, the electric mechanism part 43 has a rotor 52 fitted in a portion that discharges downward from the frame 41 a of the rotating shaft 44, and a narrow gap from the peripheral surface of the rotor 52. The stator 53 has an inner peripheral surface and is suspended and fixed from the frame 41a by appropriate means.

  Next, the compression operation of the compressor 40 in a state (full open mode) in which the refrigerant flows through both the evaporators 32 and 27 by the operation of the flow control device 39 will be described. When the electric mechanism portion 43 is energized to rotate the rotation shaft 44, the eccentric shaft portion 44b rotates eccentrically, and the pistons 46a, 46b of the first compression portion 42a and the second compression portion 42b respond to this rotation. Reciprocate in the same direction.

  Since each compression part 42a, 42b is arrange | positioned in the position which opposes 180 degrees, each piston 46a, 46b makes a mutually reverse process in each compression chamber 47a, 47b.

For example, when the first compression unit 42a performs the suction stroke of sucking the refrigerant gas into the compression chamber 47a in the compression chamber 47a, the second compression unit 42b performs the discharge stroke of discharging the compressed and high pressure gas.

Refrigerant gas (for example, 0.06 MPa) from the F-evapor 32 is sucked into the first compression part 42a, is increased in pressure by the compression stroke, and is discharged into the case 41. On the other hand, the refrigerant gas (for example, 0.14 MPa) from the R evaporator 27 is sucked into the case 41 via the second suction port 56 and is mixed with the high-pressure refrigerant gas (hereinafter referred to as mixed gas). The inside of the case 41 has an intermediate pressure (for example, 0.14 MPa) that is substantially the same pressure as the refrigerant gas from the R-eva 27. The intermediate-pressure refrigerant gas is sucked into the second compression portion 42b and is increased in pressure by the compression stroke (for example, 0. 0.
5 MPa) and discharged to the condenser 37 side to circulate the refrigeration cycle.

  According to such a configuration, in the suction process, the refrigerant gas from the F EVA 32 is introduced into the first compression unit 42a, and the mixed gas is introduced into the second compression unit 42b. The pressure difference between 45b and the inside of the case 41 is maintained at a substantially predetermined value, for example, 0.2 MPa or less, and a large load is not applied to the ball receiving portion m that is a connecting portion, so that the ball portion k is removed. Breakage can be prevented.

  However, in the cooling operation method, in addition to the above-described full-open mode in which the refrigerant is caused to flow to both the evaporators 32 and 27 by the flow rate control valve 29, the refrigerant flowing in the refrigerator having two or more evaporators is, for example, The refrigerant is supplied to both the evaporators 32 and 27, such as the F cooling mode in which the refrigerant is supplied only to the F-evapor 32 and the freezer is cooled, the R cooling mode in which the refrigerant is supplied only to the R-eve 27 and the refrigerator is cooled. Since there is a fully closed mode in which the compressor 42 is operated for a certain period of time, each cooling mode is also verified.

  In the F cooling mode, the refrigerant gas is sucked into the suction case 41 in the first compression section 42a, so that the pressure in the suction process in the cylinder 45a is equal to or less than the pressure in the case 41, and the ball receiver No great load is applied to the part m. On the other hand, in the 2nd compression part 42b, since the refrigerant gas in case 41 is further compressed, it does not become lower than the pressure in case 41. FIG. Therefore, there is no possibility that the ball joint is damaged in the F cooling mode.

  In the R cooling mode, the refrigerant gas does not flow into the first compression portion 42a. Therefore, when the compression and suction strokes are repeated, the pressure in the cylinder 45a decreases and eventually becomes a vacuum state. Since the intermediate pressure refrigerant gas that has cooled the R-eva 27 is sucked into the case 41, the pressure difference between the cylinder 45a and the case 41 becomes large, especially after the defrosting of the R-eva 27 and when the power is turned on. In some cases, the refrigerant gas temperature from the R-eva 27 is high, so the pressure difference may become a predetermined value (for example, 0.2 MPa) or more. In this case, during the suction process in which the load is most applied to the ball receiving portion m, the cylinder 45a is pressed in the direction opposite to the suction direction due to the pressure in the case 41 that is larger than usual, so that the ball receiving portion m continues. As a result, a great load is applied, and the ball joint is likely to be broken due to the loosening of the ball k and the ball part k coming off.

  On the other hand, since the refrigerant gas in the case 41 is compressed in the second compression part 42b, it does not become lower than the pressure in the case 41. Therefore, in the R cooling mode, the first compression portion 42a may be damaged.

  In the fully closed mode, the refrigerant gas does not flow into the first compression part 42a, the case 41, and the second compression part 42b. 41 is in a vacuum state, there is no pressure difference.

  Therefore, in the cooling operation of the refrigerator, the cooling operation in which the refrigerant is sucked only into the case 41 without sucking the refrigerant into the first compression portion 42a by the flow rate adjusting device 39, and the R cooling mode is not performed in this embodiment. By doing so, it is possible to prevent the pressure in the case 41 and the compression parts 42a and 42b from becoming higher than a predetermined value, so that a great load is not applied to the ball receiving part m, and the connection part of the ball joint structure The damage problem can be solved.

  Even if the R cooling mode is not performed, since the refrigerator compartment 3 is cooled in the fully open mode, it can be kept at an appropriate temperature, and when only the refrigerator compartment 3 is rapidly increased in temperature, for example, the compressor 42 Even if the temperature of the freezer compartment 6 is lowered below the target temperature by operating at a maximum rotational speed, the preservation of the food stored in the freezer compartment 6 is not affected at all. In this case, by adjusting the flow path control valve 39, the flow rate to the F-evapor 32 can be reduced to suppress the cooling of the freezer compartment 6 so that the power saving operation can be performed.

  On the other hand, when only the freezer compartment 6 rises in temperature, only the freezer compartment 6 can be cooled using the F cooling mode, so that the food in the refrigerator compartment 3 is unnecessarily lowered to freeze food. In addition, the frost attached to the R-evaporator 27 is melted by rotating the R fan 28 and exchanging heat between the R-evaporator 27 and the room air during the F-cooling mode. The indoor humidity can be maintained and the defrosting operation can be performed.

  Next, another embodiment of the present invention will be described. As described above, in the normal state of the fully open mode, the pressure in the case 41 and the compression parts 42a and 42b does not exceed a predetermined value. For example, a high-load food is thrown into the summertime or the refrigerator compartment 3. Then, the internal temperature rises and heat exchange of the R-eva 27 is promoted, so that the refrigerant gas temperature sucked into the case 41 rises. In this case, since the pressure of the refrigerant gas increases with this temperature rise, the pressure in the case 41 and the first compression part 42a may become a predetermined value (for example, 0.2 MPa) or more.

  Therefore, when the pressure difference between the inside of the case 41 and the first compressor 42a is larger than a predetermined value, the R fan 28 that blows the cold air generated by the R evaporator 27 that is the second evaporator into the room is stopped or rotated. By reducing the pressure, the heat exchange of the R-eva 27 can be suppressed, the temperature of the refrigerant gas sucked into the case 41 can be lowered, and the pressure in the cylinder 45a can be lowered. It can prevent becoming higher than the pressure of the 1st compression part 42a.

  In addition, as a method of detecting the pressure difference, it may be detected by providing a pressure sensor or a temperature sensor in the case 41 and the first compression part 42a. However, due to the structure, the pressure sensor is provided in the first compression part 42a. Since it is difficult to attach, it is easy to attach a temperature sensor or pressure sensor to the inlet or outlet piping of the F-evaluator 32 or R-evaluator 27, so that the evaporating temperature is detected or discharged from each evaporator. It is preferable to detect by the pressure of the refrigerant. Further, when the temperature of the evaporative refrigerator compartment 3 reaches a predetermined value, for example, 5 ° C. or more, it is determined that the load in the room is large and the evaporation temperature is high, and the pressure difference is regarded as being equal to or greater than the predetermined value. May be.

  In addition to stopping the R fan 27 and reducing the number of rotations, switching from the fully open mode to the F cooling mode blocks the suction of refrigerant gas from the R evaporator 27 and prevents the pressure inside the case 41 from rising. May be.

  On the other hand, when the heat exchange of the F EVA 32 is not promoted, for example, in winter, the temperature of the refrigerant gas sucked into the first compression portion 42a is lowered, and the pressure in the cylinder 45a is lowered. Further, since the pressure of the refrigerant gas discharged into the case 41 is substantially constant, even if the pressure of the refrigerant gas in the cylinder 45a is reduced, the pressure in the case 41 does not change. There is a possibility that the pressure difference in the compression part 42a becomes a predetermined value (for example, 0.2 MPa) or more.

  Therefore, when the pressure difference between the case 41 and the first compressor 42a is larger than a predetermined value, the F fan 33 that blows the cold air generated by the F evaporator 32 serving as the first evaporator into the room is operated or rotated. By increasing the temperature of the refrigerant gas sucked into the first compression part 42a by promoting the heat exchange of the F EVA 33, so that the pressure in the cylinder 45a can be increased. The pressure difference between 42a and the case 41 can be kept below a predetermined value.

  In this embodiment, in addition to the above-described method for detecting the pressure difference, when the freezer compartment 6 temperature reaches a predetermined value, for example, −25 ° C. or less, it is determined that the pressure difference is equal to or greater than the predetermined value. May be.

  Next, still another embodiment of the present invention will be described. In general, when the freezer compartment 6 is opened, the rotation of the F fan 33 is stopped in order to prevent cold air leakage to the outside of the refrigerator, but when the rotation of the F fan 33 is stopped, the heat exchange of the F EVA 32 is performed. Is not performed, the refrigerant gas temperature from the F-evapor 32 is lowered, and the pressure in the cylinder 45a is lowered. In this case, as described above, the pressure difference between the case 41 and the first compression portion 42a may be a predetermined value or more.

  Therefore, when the rotation of the F fan 33 is stopped for a predetermined time or more, for example, for 3 minutes or more, or when the F fan 33 is operated at a low speed, the pressure difference between the first compression portion 42a and the case 41 is a predetermined value or more. As a result, the F fan 33 is forcibly rotated or the number of rotations is increased, thereby promoting the heat exchange of the F EVA 32 and the refrigerant gas sucked into the first compression section 42a. The pressure can be increased. Accordingly, since the pressure difference between the case 41 and the first compression portion 42a can be maintained at a predetermined value or less, it is possible to prevent the ball joint from being damaged such as the ball portion k coming off.

  In addition to the rotation of the F fan 33 as described above, the fully open mode may be switched to the F cooling mode.

  In the present embodiment, the predetermined value is set to 0.2 MPa as one embodiment, but it is needless to say that the predetermined value can be appropriately changed depending on the strength of the ball receiving portion m.

  The present invention can prevent the pressure difference between the case and each cylinder from becoming higher than a predetermined value, eliminate the breakage of the compression section, and various types of two-stage compressors having a ball joint structure. Applicable to refrigerator.

It is a longitudinal cross-sectional view which shows the compressor of this invention. It is a longitudinal cross-sectional view which shows the refrigerator of this invention. It is the schematic which shows the refrigerating cycle of this invention. It is a longitudinal cross-sectional view which shows the compressor of the conventional refrigerator. It is a longitudinal cross-sectional view which shows the ball joint structure of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Refrigerator main body 3 ... Refrigeration room 6 ... Freezer room 27 ... R Eva 28 ... R fan 32 ... F Eva 33 ... F Fan 39 ... Flow control device 40 ... Compressor 41 ... Case 42 ... Compression part 42a ... 1st compression part 42b ... 2nd compression part 45a, b ... Cylinder 46a, b ... Piston 48a, b ... Connecting rod k ... Ball part m ... Ball receiving part

Claims (4)

A refrigerator body having a freezing room and a refrigeration room filled with a heat insulating material between an outer box and an inner box, an evaporator for a freezing room and an evaporator for a refrigeration room disposed in the refrigerator body and having different evaporation temperatures, A flow rate adjusting device that varies a flow rate of refrigerant flowing in the freezer compartment evaporator or the refrigerator compartment evaporator; and a first compression portion and a second compression portion in the case, wherein the first compression portion is the freezer compartment The refrigerant gas evaporated by the evaporator is compressed and discharged into the case, and the second compression part is evaporated from the refrigerator gas evaporator and sucked into the case from the first compression part. The discharged refrigerant gas is compressed and discharged out of the case, and the compression of the first compression part and the second compression part is performed in conjunction with the rotation of the rotation shaft of each piston connected by a ball joint structure. With a reciprocating compressor,
The freezer compartment evaporator and the refrigerator compartment evaporator are connected in parallel via the flow rate control device,
The flow rate of the refrigerant by the flow rate switching device includes at least a full-open mode in which the refrigerant flows to the freezer evaporator and the refrigerator refrigerator, and an F cooling mode in which the refrigerant flows only to the freezer evaporator. However, the refrigerator does not have an R cooling mode in which a refrigerant is allowed to flow only through the refrigerator-use evaporator.   When the pressure difference between the case and the first compression unit is larger than a predetermined value, the refrigerator for cooling room that blows cold air generated by the evaporator for the refrigerator into the room is stopped or the number of rotations is reduced. The refrigerator according to claim 1.   When the pressure difference between the case and the first compression unit is greater than a predetermined value, the freezer compartment fan that blows cool air generated by the freezer evaporator into the room is operated or the number of rotations is increased. The refrigerator according to claim 1.   2. The refrigerator according to claim 1, wherein when the pressure difference between the case and the first compression unit is larger than a predetermined value, the F cooling mode in which the refrigerant is allowed to flow only to the freezer evaporator is performed.

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