JP7444580B2 - refrigerator - Google Patents

Description

The present invention relates to a refrigerator.

Regarding heat dissipation of equipment provided in the machine room of a refrigerator, for example, a technique described in Patent Document 1 is known. In other words, Patent Document 1 states, ``Tightly wound coiled capacitors are arranged concentrically around the outer periphery of the fan. A refrigerator is described.

Japanese Patent Application Publication No. 7-305939

However, in the technique described in Patent Document 1, since a closely wound coiled capacitor is provided around the outer periphery of the fan, the volume of the machine room increases, resulting in an increase in the size of the refrigerator. Therefore, in order to make the refrigerator more compact, for example, if the tightly wound coiled condenser is made smaller, the heat of the refrigerant discharged from the compressor may not be sufficiently radiated, which may lead to a decrease in the performance of the refrigerator.

Therefore, an object of the present invention is to provide a refrigerator that appropriately radiates heat from refrigerant from a compressor.

In order to solve the above problems, a refrigerator according to the present invention includes a refrigerant circuit in which refrigerant circulates through a compressor, a condenser, a throttle mechanism, and an evaporator in sequence, and at least the compressor and the blower The condenser includes an outer condenser installed outside the machine room in the housing, and from the discharge side of the compressor to the outer condenser. At least a part of the connecting piping included in the refrigerant path is a grooved pipe having a groove in its inner wall, and the axial blower is fitted into a constricted part formed by recessing the wall surface of the machine room inward. The internal space of the constriction part is included in the machine room, the blower is installed in the internal space of the constriction part, and the at least part of the connecting pipe has a leeward side of the blower. The air blower is characterized in that it includes a portion disposed radially outward from the motor of the blower.

According to the present invention, it is possible to provide a refrigerator that appropriately radiates heat from refrigerant from a compressor.

1 is a front view of a refrigerator according to a first embodiment of the present invention. FIG. 2 is a sectional view taken along the line II-II in FIG. 1 of the refrigerator according to the first embodiment of the present invention. FIG. 3 is a sectional view taken along line III-III in FIG. 2 of the refrigerator according to the first embodiment of the present invention. FIG. 1 is a configuration diagram including a refrigerant circuit of a refrigerator according to a first embodiment of the present invention. It is an explanatory view showing arrangement of a second radiator and a third radiator of the refrigerator according to the first embodiment of the present invention. It is a perspective view of the first radiator with which the refrigerator concerning a 1st embodiment of the present invention is provided. FIG. 2 is an explanatory diagram regarding the arrangement of various devices in the machine room of the refrigerator according to the first embodiment of the present invention. It is a sectional view of connection piping with which the refrigerator concerning a 1st embodiment of the present invention is provided. FIG. 2 is a perspective view of a first radiator, a machine room blower, and connection piping included in the refrigerator according to the first embodiment of the present invention. It is a back view of the first radiator, the machine room blower, and the connection piping with which the refrigerator based on 1st Embodiment of this invention is equipped. 11 is a view taken along the line IV-IV in region U of FIG. 10 in the refrigerator according to the first embodiment of the present invention. FIG. It is an explanatory view showing a temperature change of a refrigerant in connection piping, a first radiator, a second radiator, and a third radiator with which the refrigerator according to the first embodiment of the present invention is provided. It is an explanatory view showing changes in the heat transfer coefficient of refrigerant in connection piping, a first radiator, a second radiator, and a third radiator with which the refrigerator according to the first embodiment of the present invention is provided. FIG. 2 is an explanatory diagram showing changes in the thermal resistance of air and the thermal resistance of a refrigerant in a first radiator included in the refrigerator according to the first embodiment of the present invention. It is a sectional view of a heat exchanger tube of a first radiator with which a refrigerator concerning a modification of a 1st embodiment of the present invention is provided, and a heat exchanger tube of a first evaporator. It is a Mollier diagram of a refrigerator concerning a modification of a 1st embodiment of the present invention, and a comparative example. It is an explanatory view about arrangement of each device in the machinery room of the refrigerator concerning a 2nd embodiment of the present invention. It is an explanatory view showing a temperature change of a refrigerant in connection piping, a second radiator, and a third radiator with which a refrigerator concerning a 2nd embodiment of the present invention is provided. It is an explanatory view about arrangement of each device in the machinery room of a refrigerator concerning a 3rd embodiment of the present invention. It is an explanatory view about arrangement of each device in the machinery room of a refrigerator concerning a 4th embodiment of the present invention.

≪First embodiment≫
FIG. 1 is a front view of a refrigerator 100 according to the first embodiment.
The refrigerator 100 is a device that cools food and the like, and includes a housing M in which a refrigerator compartment R1 and the like are provided. In the example of FIG. 1, inside the refrigerator 100, in order from the top, there are provided a refrigerator compartment R1, an ice making compartment R2 and an upper freezer compartment R3 lined up on the left and right, a lower freezer compartment R4, and a vegetable compartment R5. There is. The casing of the refrigerator 100 is constructed by the insulating box 20 (see FIG. 2) having a shape that partitions each of the rooms described above, and each door (refrigerator door 11a, 11b, etc.) installed in the insulating box 20. A body M is constructed. In addition, the ice making compartment R2, the upper freezing compartment R3, and the lower freezing compartment R4 are collectively referred to as the freezing compartment Rs.

The refrigerator 100 includes French-type (so-called double-door type) refrigerator compartment doors 11a and 11b that form a refrigerator compartment R1 together with the heat insulating box 20 (see FIG. 2). Further, the refrigerator 100 includes a door 12 of the ice making compartment R2, a door 13 of the upper freezer compartment R3, a door 14 of the lower freezer compartment R4, and a door 15 of the vegetable compartment R5 as pull-out doors. The inside of each of these doors is filled with urethane foam, which is a heat insulating material.

FIG. 2 is a sectional view taken along the line II--II in FIG.
In addition, in FIG. 2, the flow of air is shown by solid line arrows. The inside and outside of the refrigerator 100 shown in FIG. 2 are separated by a casing M filled with foamed heat insulating material. In addition to the foamed heat insulating material described above, a vacuum heat insulating material 21 (see also FIG. 3) is provided on the back and side surfaces of the casing M. These vacuum insulation materials 21 are constructed by wrapping a core material such as glass wool or urethane with an outer wrapping material.

As shown in FIG. 2, the refrigerator compartment R1 and the upper freezer compartment R3 are separated by a heat insulating partition wall 22a (the same applies to the refrigerator compartment R1 and the ice making compartment R2: see FIG. 1). Further, the lower freezer compartment R4 and the vegetable compartment R5 are separated by a heat insulating partition wall 22b. Between the ice making compartment R2 (see Fig. 1), the upper freezing compartment R3, and the lower freezing compartment R4, air is not allowed to flow inside or outside the refrigerator through the gaps between the doors 12, 13, and 14. A heat insulating partition wall 22c is provided near its front end. A plurality of door pockets J1 and a plurality of shelves J2 are provided on the inside of the refrigerator compartment doors 11a and 11b.

In addition to an ice-making compartment container (not shown) that is pulled out integrally with the door 12 (see FIG. 1), an upper freezer compartment container J3 and a lower freezer container J4 are installed in the freezer compartment Rs. Moreover, a vegetable compartment container J5 that is pulled out integrally with the door 15 is installed in the vegetable compartment R5.

A chilled compartment R1a is provided above the heat insulating partition wall 22a, and the temperature range is set lower than that of the refrigerator compartment R1. In addition to the first evaporator 36a and first blower Fa, which will be described later, the temperature of the chilled room R1a is changed to a predetermined value by a heater (not shown) provided inside the heat insulating partition wall 22a. . Note that the remaining configurations in FIG. 2 will be described later.

FIG. 3 is a sectional view taken along the line III--III in FIG. 2 (see also FIG. 2 as appropriate).
In addition, in FIG. 3, the flow of air is shown by a white arrow.
The first evaporator 36a shown in FIG. 3 is a cross-fin tube type heat exchanger for cooling the refrigerator compartment R1, and is provided in the evaporator compartment R1b (see also FIG. 2) on the back side of the refrigerator compartment R1. There is. The air, which has become low temperature through heat exchange with the first evaporator 36a, is guided to the refrigerator compartment R1 by the first blower Fa above the first evaporator 36a, sequentially through the outlet air passage ha and the outlet hb. It will be destroyed. The air thus led to the refrigerator compartment R1 is again led to the first evaporator 36a via the return port hc (see FIG. 2).

Furthermore, a tub 23a is provided below the first evaporator 36a to receive water dripping from the first evaporator 36a. A heater 24a is installed on the surface of this tub 23a. Even if the water accumulated in the tub 23a freezes, the ice is melted by energizing the heater 24a. Note that the water accompanying the above-mentioned melting flows down to the evaporation tray 25 above the compressor 31 via the drain pipe ra.

The second evaporator 36b shown in FIG. 3 is a cross-fin tube type heat exchanger for cooling the freezing compartment Rs, and is installed in the evaporator compartment Rt (see also FIG. 2) on the back side of the freezing compartment Rs. There is. The air, which has become low temperature through heat exchange with the second evaporator 36b, is transferred to the outlet air passage hd (see FIG. 2) and the outlet he by the second blower Fb (see also FIG. 2) above the second evaporator 36b. (see FIG. 2), and is led to the freezer compartment Rs. The air thus led to the freezing compartment Rs is again led to the second evaporator 36b via the return port hf (see FIG. 2).

Moreover, in the example of FIG. 3, the air that has become low temperature through heat exchange with the second evaporator 36b is also guided to the vegetable compartment R5. That is, the air that has become low temperature through heat exchange with the second evaporator 36b is guided to the vegetable compartment R5 via a vegetable compartment air path (not shown) and a vegetable compartment damper (not shown) in sequence. Note that when the vegetable compartment R5 is at a low temperature, the vegetable compartment damper (not shown) described above is closed, and cooling of the vegetable compartment R5 is suppressed. The air led to the vegetable compartment R5 is returned to the freezer compartment Rs via the return port hg (see FIG. 2) and the return air passage hi (see FIG. 2) provided at the front of the heat insulating partition wall 22b. be guided.

As shown in FIG. 3, a heater 24b is provided below the second evaporator 36b. During a predetermined defrosting operation, the heater 24b is energized to melt the frost on the surface of the second evaporator 36b. Melt water generated by the defrosting operation falls into the gutter 23b provided at the lower part of the evaporator chamber Rt, and flows down into the evaporation tray 25 described above via the drain pipe rb.

Further, a temperature/humidity sensor 27 (see FIG. 2) that detects the temperature and humidity of the outside air is installed in a cover 26 (see FIG. 2) installed on the top surface of the housing M of the refrigerator 100. Further, a control board 28 is installed on the upper rear side of the refrigerator 100. By executing a predetermined control program in a control circuit mounted on the control board 28, various devices such as a compressor 31, which will be described next, are controlled.

FIG. 4 is a configuration diagram including a refrigerant circuit Q of the refrigerator 100 according to the first embodiment.
As shown in FIG. 4, the refrigerator 100 includes a compressor 31, a first radiator 32a (machine room condenser), a second radiator 32b (outer condenser), and a third radiator 32c (outer condenser). ), a dryer 33, capillary tubes 34a, 34b (throttle mechanism), and a three-way valve 35. In addition to the above-described configuration, the refrigerator 100 also includes a first evaporator 36a (evaporator), a second evaporator 36b (evaporator), gas-liquid separators 37a, 37b, and a check valve 38. A refrigerant merging section 39 is provided. Furthermore, the refrigerator 100 includes a machine room blower Fm (air blower), a first blower Fa, and a second blower Fb.

The compressor 31 is a device that compresses gas refrigerant, and is installed in a machine room R6 provided at the lower rear of the housing M (see FIGS. 2 and 3). As such a compressor 31, a rotary compressor, a scroll compressor, a reciprocating compressor, etc. are used. As shown in FIG. 4, from the compressor 31 toward the downstream side of the refrigerant flow, a first radiator 32a (machine room condenser), a second radiator 32b (outer condenser), and a third radiator 32c. (outer condensers) are connected in sequence.

The first heat radiator 32a is a heat exchanger that radiates (condenses) the refrigerant flowing through the heat transfer tube by exchanging heat with air, and is installed in the machine room R6 of the housing M (see FIG. 3).
The machine room blower Fm is a blower that allows air to flow through the machine room R6 of the housing M (see FIG. 3), and is installed in the machine room R6.

The second radiator 32b and the third radiator 32c are heat exchangers that radiate (condense) the refrigerant flowing through the heat transfer tubes by exchanging heat with air, and are buried in the side surface of the housing M (see FIG. 5). has been done.
The dryer 33 is a filter that removes moisture and foreign matter mixed in the refrigerant, and is provided downstream of the third radiator 32c.
The capillary tubes 34a and 34b are capillary tubes with a relatively small diameter, and have a function of reducing the pressure of the refrigerant.

The three-way valve 35 determines whether the refrigerant radiated by the third radiator 32c is guided to the first evaporator 36a via the capillary tube 34a or to the second evaporator 36b via the other capillary tube 34b. It is a switching valve. The three-way valve 35 includes an outflow port pa that leads the refrigerant to the capillary tube 34a, and an outflow port pb that leads the refrigerant to the other capillary tube 34b.

The first evaporator 36a is a heat exchanger that cools air by exchanging heat with the refrigerant flowing through the heat transfer tube, and is installed in the evaporator chamber R1b (see FIG. 2) described above. The refrigerant that has undergone heat exchange in the first evaporator 36a is guided to the refrigerant confluence section 39 via the gas-liquid separator 37a.
The gas-liquid separator 37a is a shell-like member that separates the refrigerant into gas and liquid in order to prevent liquid compression in the compressor 31. The first blower Fa is a blower that sends air into the refrigerator compartment R1.

The second evaporator 36b is a heat exchanger that cools the air by exchanging heat with the refrigerant flowing through the heat transfer tube, and is installed in the freezing compartment Rs. The refrigerant that has undergone heat exchange in the second evaporator 36b is led to the refrigerant confluence section 39 via the gas-liquid separator 37a and the check valve 38 in sequence. The refrigerant thus guided to the refrigerant merging section 39 heads toward the suction side of the compressor 31.

The gas-liquid separator 37b is a shell-like member that separates the refrigerant into gas and liquid in order to prevent liquid compression in the compressor 31. Further, the check valve 38 is a valve that allows the refrigerant to flow from the gas-liquid separator 37b toward the refrigerant confluence section 39, and prohibits the flow in the opposite direction. The second blower Fb is a blower that sends air into the freezer compartment Rs.

For example, in the refrigeration mode, the three-way valve 35 is switched in a predetermined manner, and the compressor 31, first radiator 32a, second radiator 32b, third radiator 32c, capillary tube 34a, and first evaporator 36a are sequentially activated. A refrigerant circulates through it. This cools the food and the like in the refrigerator compartment R1.

On the other hand, in the freezing mode, the three-way valve 35 is switched to a predetermined value, and the compressor 31, first radiator 32a, second radiator 32b, third radiator 32c, capillary tube 34b, and second evaporator 36b are sequentially activated. A refrigerant circulates through it. This cools the food and the like in the freezer compartment Rs.

In this way, the refrigerator 100 includes a refrigerant circuit Q in which refrigerant circulates sequentially through the compressor 31, a "condenser," a "throttle mechanism," and an "evaporator." The above-mentioned "condenser" includes a first radiator 32a installed in the machine room R6 of the casing M (see FIG. 3), and a second radiator 32a installed outside the machine room R6 in the casing M. Also included is a heat radiator 32b and a third heat radiator 32c.

FIG. 5 is an explanatory diagram showing the arrangement of the second radiator 32b and the third radiator 32c of the refrigerator 100. Although not shown in FIG. 5, the first radiator 32a is installed in the machine room R6 as described above (see FIG. 3).
The second heat radiator 32b shown in FIG. 5 is a heat exchanger tube embedded in the side surface of the housing M, etc.
The third heat radiator 32c shown in FIG. 5 is a heat exchanger tube buried near the front ends of the heat insulating partition walls 22a, 22b, and 22c (see also FIG. 2). As a result, the vicinity of the front ends of the heat insulating partition walls 22a, 22b, 22c is maintained at a temperature above the dew point, so that dew condensation can be suppressed.

The refrigerant flowing through these second radiators 32b and third radiators 32c radiates heat by natural convection. Therefore, compared to the first radiator 32a (see Fig. 3) that radiates heat from the refrigerant through forced convection of the machine room fan Fm (see Fig. 3), there is no need to provide fins (not shown), so space can be saved. can be achieved. Next, the first radiator 32a and the like installed in the machine room R6 will be explained.

FIG. 6 is a perspective view of the first radiator 32a included in the refrigerator.
Note that the solid arrow shown in FIG. 6 indicates the direction in which the refrigerant flows. The first radiator 32a shown in FIG. 6 is a cross-fin tube heat exchanger installed in the machine room R6 (see FIG. 3). The first radiator 32a includes a plurality of fins 321a arranged at predetermined intervals, and a heat transfer tube 322a that passes through the fins 321a and guides the refrigerant in a predetermined meandering manner. In this way, by using a cross-fin tube type heat exchanger as the first heat radiator 32a, the efficiency of heat radiation per unit length of the heat exchanger tube 322a can be increased.

FIG. 7 is an explanatory diagram regarding the arrangement of each device in the machine room R6 of the refrigerator.
Note that FIG. 7 shows the arrangement when viewed from the back side of the refrigerator 100 (see FIG. 3).
In the example of FIG. 7, the first radiator 32a, the machine room blower Fm, and the compressor 31 are sequentially arranged at a predetermined interval toward the downstream side of the air flow. In addition, the housing M (see FIG. 3) of the refrigerator 100 has a plurality of holes (not shown) for guiding air into the machine room R6 as well as a plurality of holes (not shown) for letting air escape from the machine room R6. It is provided.

The refrigerator 100 (see FIG. 3) includes a connection pipe ka in addition to the compressor 31, the first radiator 32a, and the machine room blower Fm described above. This connection pipe ka is a pipe that connects the discharge pipe kv of the compressor 31 and the heat transfer tube 322a (see also FIG. 6) of the first radiator 32a. As shown in FIG. 7, the upstream end of the connection pipe ka is connected to the discharge side of the compressor 31 (that is, the discharge pipe kv).

Note that the welding point between the discharge pipe kv of the compressor 31 and the connecting pipe ka is referred to as a welding point wa. Moreover, the welding point between the connection pipe ka and the upstream end of the heat exchanger tube 322a of the first radiator 32a is referred to as a welding point wb. Moreover, the welding point between the downstream end of the heat exchanger tube 322a of the first radiator 32a and the connecting pipe kb is referred to as a welding point wc. Note that the connection pipe kb is a pipe that guides the refrigerant heat radiated by the first radiator 32a to the second radiator 32b (see FIG. 4).

In the first embodiment, grooved pipes (see FIG. 8) are used as the connection piping ka and the heat transfer tube 322a in the range S1 from the welding point wa to the welding point wc, and heat is radiated from the refrigerant by forced convection of the machine room blower Fm. That's what I do. On the other hand, in the range S2 downstream of the welding point wc, smooth tubes without grooves are used as the heat transfer tubes of the connection pipe kb, the second radiator 32b (see FIG. 4), and the third radiator 32c (see FIG. 4). That's what I do. Note that a smooth pipe is a pipe whose inner circumferential surface is smooth.

Although details will be described later, the gas refrigerant discharged from the compressor 31 has a higher thermal resistance than a gas-liquid two-phase refrigerant, so it is difficult to radiate heat to the air. If the gas refrigerant discharged from the compressor 31 flows into the first radiator 32a without radiating almost any heat, the heat transfer function of the fins 321a (see FIG. 6) of the first radiator 32a will not be fully utilized. This makes it difficult for heat to dissipate from the refrigerant to the air. Therefore, in the first embodiment, as described above, the connecting pipe ka and the heat transfer tube 322a of the first radiator 32a are made of grooved tubes to promote heat radiation from the refrigerant to the air. . This is one of the main features of the first embodiment. Such a grooved tube will be explained using FIG. 8.

FIG. 8 is a sectional view of the connecting pipe ka provided in the refrigerator.
As shown in FIG. 8, a plurality of grooves ma recessed outward in the radial direction are provided on the inner wall of the connecting pipe ka at approximately equal intervals in the circumferential direction. These grooves ma may be provided along the extending direction of the connecting pipe ka, or may be provided obliquely (that is, in a spiral shape) with respect to the above-mentioned extending direction. . Note that the cross section of the heat exchanger tube 322a (see FIG. 6) of the first radiator 32a is also similar to that in FIG. 8.

Furthermore, in general, regarding a fluid (eg, a gas refrigerant) flowing through a predetermined pipe, a boundary layer is formed near the inner circumferential surface of the pipe, where the velocity of the fluid is relatively low due to the viscosity of the fluid. Therefore, when the connecting pipe ka, which is a grooved pipe, has minute irregularities, the connecting pipe ka is It is desirable to have a turbulent flow of gas refrigerant flowing through it.

Specifically, regarding the rotational speed N of the compressor 31 (see FIG. 7), it is preferable that the following equation (1) is satisfied. Here, N included in equation (1) is the rotation speed [rotations/s] of the compressor 31, π is pi, and D is the average inner diameter of the grooved pipe (for example, connecting pipe ka). [mm], and Vst is the stroke volume of the compressor 31 [cm ³ ]. Further, η _v included in equation (1) is the average volumetric efficiency [-] of the compressor 31, and ν _d is the average kinematic viscosity of the gas refrigerant on the high pressure side (discharge side) of the compressor 31 [m ² /s ], ρ _d is the density [kg/m ³ ] of the gas refrigerant on the high pressure side of the compressor 31, and ρ _s is the density [kg/m ³ ] of the gas refrigerant on the low pressure side (suction side) of the compressor 31. ].

Equation (1) is a mathematical expression derived from a predetermined characteristic expression of the compressor 31 and a defining expression of Reynolds number. If this formula (1) is satisfied, the gas refrigerant flowing through the connection pipe ka becomes turbulent. Therefore, the effect of increasing the heat transfer area by using the grooved pipe as the connecting pipe ka is fully exhibited. Note that the compressor 31 may be driven at a rotation speed of 800 [revolutions/min] or more, for example, so that the flow of the refrigerant becomes turbulent.

FIG. 9 is a perspective view of the first radiator 32a, the machine room blower Fm, and the connecting pipe ka included in the refrigerator.
As shown in FIG. 9, the machine room blower Fm is, for example, an axial propeller fan, and includes a motor Fma as a drive source, a blade Fmb that rotates integrally with the rotor of the motor Fma, and a frame Fmc. , is equipped with. The first radiator 32a and the machine room fan Fm are spaced apart from each other by a predetermined distance so that the plurality of fins 321a of the first radiator 32a and the central axis of the motor Fma of the machine room fan Fm are approximately parallel. It is located.

Further, the connecting pipe ka is bent in a predetermined manner from the welding point wa to the welding point wb. As a result, the length of the connecting pipe ka becomes relatively long, and in combination with the fact that the connecting pipe ka is a grooved pipe, a sufficient heat transfer area can be ensured.

FIG. 10 is a rear view of the first radiator 32a, the machine room blower Fm, and the connecting pipe ka included in the refrigerator.
As the machine room blower Fm is driven, air flows in a predetermined manner in the machine room R6, as shown by the solid arrow in FIG. Thereby, the heat of the refrigerant flowing through the connection pipe ka and the first radiator 32a is radiated to the air. Moreover, the frame body Fmc of the machine room blower Fm is fitted into the wall surface of the machine room R6. Therefore, the air that has passed through the gaps between the fins 321a of the first radiator 32a is concentrated toward the blades Fmb of the machine room blower Fm, and the wind speed increases. The air accelerated in this manner is mainly blown out to a region outside the motor Fma of the machine room blower Fm in the radial direction.

FIG. 11 is a view taken along the line IV-IV in region U of FIG. 10.
Note that the circular broken line in FIG. 11 indicates the installation area Sm of the motor Fma.
As shown in FIG. 11, on the outlet side of the machine room blower Fm, the connecting pipe ka is bent in a predetermined manner, and most of the connecting pipe ka is installed radially outward than the motor Fma. As a result, the accelerated air heads toward the connection pipe ka, so that heat radiation from the refrigerant flowing through the connection pipe ka to the air is promoted. Incidentally, in the area where the installation area Sm of the motor Fma is projected on the blowing side in the axial direction, the wind speed of the air is not so high.

In addition, as shown in FIG. 11, in the connecting pipe ka, a portion of the machine room blower Fm that is arranged radially outward from the motor Fma is an area of 180° or more in the circumferential direction with respect to the rotation axis of the motor Fma. (area of angle range θ) is preferably included. In the example of FIG. 11, when viewed from the outlet side of the machine room blower Fm, the area around the area where the connection pipe ka is located is based on the intersection of the periphery (circular broken line) of the installation area Sm of the motor Fma and the connection pipe ka. The angle range θ in the direction is 180° or more. As a result, the temperature efficiency in heat radiation from the refrigerant to the air is improved compared to arranging the connecting pipes ka in a concentrated manner at a predetermined location in the machine room R6. Therefore, in combination with making the connection pipe ka a grooved pipe, heat radiation from the refrigerant flowing through the connection pipe ka to the air is promoted.

<Action/Effect>
FIG. 12 is an explanatory diagram showing temperature changes of the refrigerant in the connection pipe ka, the first radiator 32a, the second radiator 32b, and the third radiator 32c (see FIGS. 4 and 7 as appropriate).
Note that the horizontal axis in FIG. 12 indicates piping and the like through which the refrigerant flows. That is, the symbols of the connection pipe ka, the first radiator 32a, the second radiator 32b, and the third radiator 32c are sequentially written so that the right side of the page of FIG. 12 is the downstream side of the flow of the refrigerant. . On the other hand, the vertical axis in FIG. 12 indicates the temperature of the refrigerant flowing through the pipes and the like. Moreover, the solid line in FIG. 12 shows the temperature change of the refrigerant in the first embodiment. On the other hand, the broken line in FIG. 12 shows a comparative example in which the connecting pipe ka and the heat exchanger tube 322a are not grooved pipes but smooth pipes.

The high temperature gas refrigerant discharged from the compressor 31 (see FIG. 7) exchanges heat with the air in the machine room R6 while flowing through the connection pipe ka, and its temperature decreases. The refrigerant that has flowed into the first radiator 32a via the connecting pipe ka exchanges heat with the air in the machine room R6 while flowing through the first radiator 32a, changing from a gas refrigerant to a gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows sequentially through the second radiator 32b and the third radiator 32c while maintaining the predetermined condensing temperature. Then, on the downstream side of the third radiator 32c, the state of the refrigerant changes from a gas-liquid two-phase refrigerant to a liquid refrigerant, and the temperature of the refrigerant decreases with the amount of heat radiated.

As described above, in the first embodiment, since grooved pipes are used as the connection pipes ka and the heat transfer tubes 322a (see FIG. 6) of the first radiator 32a, the refrigerant flowing through the connection pipes ka, etc. It promotes heat dissipation into the air. As a result, as shown in FIG. 12, the temperature of the gas refrigerant in the connecting pipe ka and the first radiator 32a decreases at a steeper gradient in the first embodiment (solid line) than in the comparative example (broken line). . As described above, according to the first embodiment, it is possible to provide the refrigerator 100 that appropriately radiates heat from the refrigerant from the compressor 31.

FIG. 13 is an explanatory diagram showing changes in the heat transfer coefficient of the refrigerant in the connection pipe ka, the first radiator 32a, the second radiator 32b, and the third radiator 32c. (See Figures 4 and 7 as appropriate)
Note that the horizontal axis in FIG. 13 is the same as the horizontal axis in FIG. 12. The vertical axis in FIG. 13 indicates the heat transfer coefficient of the refrigerant. Moreover, the solid line in FIG. 13 shows the change in the heat transfer coefficient of the refrigerant flowing through each pipe in the first embodiment. On the other hand, the broken line in FIG. 13 shows a comparative example in which the connection pipe ka and the heat exchanger tube 322a (see FIG. 6) of the first radiator 32a are made of smooth pipes.

In general, gas refrigerants have low heat transfer coefficients, while gas-liquid two-phase refrigerants tend to have significantly higher heat transfer coefficients. However, in the first embodiment (solid line in FIG. 13), By using a grooved tube for the first radiator 32a, the heat transfer coefficient of the gas refrigerant is made higher than in the comparative example (broken line). Therefore, the high temperature gas refrigerant immediately after being discharged from the compressor 31 sufficiently radiates heat while flowing through the connection pipe ka and the first radiator 32a, so that the gas refrigerant is removed from the gas refrigerant near the entrance of the first radiator 32a. Changes to a gas-liquid two-phase refrigerant.

As a result, it is possible to suppress the gas refrigerant having a low heat transfer coefficient from flowing into the second radiator 32b (see FIG. 4), and to lower the condensation temperature of the refrigerant flowing into the second radiator 32b. Moreover, since the amount of heat transfer (cooling load) from the second radiator 32b and the third radiator 32c into the refrigerator is reduced, it is possible to save energy in the refrigerator 100.

FIG. 14 is an explanatory diagram showing changes in the thermal resistance of air and the thermal resistance of the refrigerant in the first radiator 32a (see FIG. 7 as appropriate).
The horizontal axis in FIG. 14 indicates the position from the inlet to the outlet of the first radiator 32a. That is, the horizontal axis in FIG. 14 is from the inlet to the outlet of the first radiator 32a so that the right side of the paper in FIG. 14 is the downstream side of the flow of the refrigerant. On the other hand, the vertical axis in FIG. 14 indicates the thermal resistance of the refrigerant. Moreover, the solid line in FIG. 14 shows the change in the thermal resistance of the refrigerant in the first embodiment. On the other hand, the broken line indicates a comparative example in which the connecting pipe ka and the heat exchanger tube 322a (see FIG. 6) are not grooved pipes but smooth pipes. Moreover, the dashed-dotted line in FIG. 14 shows the thermal resistance of the air sent into the first radiator 32a.

As shown in FIG. 14, in both the first embodiment (solid line) and the comparative example (broken line), the phase change from gas refrigerant to gas-liquid two-phase refrigerant occurs in the process of flowing through the first radiator 32a. The thermal resistance of the refrigerant is significantly reduced.
However, in the first embodiment, as described above, the upstream connecting pipe ka of the first radiator 32a is a grooved tube, and the heat transfer tube 322a of the first radiator 32a is a grooved tube. As a result, the thermal resistance of the gas refrigerant flowing into the refrigerant inlet of the first radiator 32a is significantly lower than that of the comparative example.

Further, in the first embodiment, the gas refrigerant can be changed to the gas-liquid two-phase refrigerant at a position closer to the refrigerant inlet of the first radiator 32a than in the comparative example. As a result, gas-liquid two-phase refrigerant with low thermal resistance flows through most of the first radiator 32a (other than the vicinity of the refrigerant inlet), so that the heat transfer promotion function of the fins 321a (see FIG. 9) is enhanced. fully utilized.

In addition, in the second radiator 32b (see FIG. 4) and the third radiator 32c (see FIG. 4), the gas-liquid two-phase refrigerant flows, so the heat transfer coefficient of the refrigerant is high. Since the heat exchange is based on natural convection, the heat transfer coefficient of air is low. Therefore, in heat exchange between the second radiator 32b and the third radiator 32c, the thermal resistance of air becomes dominant. Therefore, in the first embodiment, by using smooth tubes, which are cheaper than grooved tubes, as the heat transfer tubes of the second radiator 32b and the third radiator 32c, the refrigerator 100 can save energy while reducing cost. I'm trying to make it easier to understand.

In this way, according to the first embodiment, in addition to the connection pipe ka, the heat exchanger tubes 322a of the first radiator 32a are grooved tubes, while the heat exchanger tubes of the second radiator 32b and the third radiator 32c are By using a smooth tube, it is possible to improve the cost performance of the refrigerator 100 and to save energy.

<<Modification of the first embodiment>>
In a modification of the first embodiment (see FIG. 15), in addition to the connection pipe ka and the heat transfer tube 322a of the first radiator 32a, the first evaporator 36a (see FIG. 4) and the second evaporator 36b (see FIG. 4) ) is also configured as a grooved tube. Regarding the modification of the first embodiment, the overall configuration of the refrigerator 100 (see FIGS. 1 to 5) and the configuration of each device provided in the machine room R6 (see FIGS. 6 to 11) are as described in the first embodiment. Since this is the same as the embodiment, the explanation thereof will be omitted.

FIG. 15 is a cross-sectional view of the heat transfer tube 322a of the first radiator 32a and the heat transfer tube 362a of the first evaporator 36a included in the refrigerator.
As shown in FIG. 15, the average tube inner diameter Dd of the heat transfer tubes 322a of the first radiator 32a is smaller than the average tube inner diameter Ds of the heat transfer tubes 362a of the first evaporator 36a (see FIG. 4). Here, the "average pipe inner diameter" is the average value in the circumferential direction of the inner diameter of a grooved pipe whose inner circumferential surface exhibits an uneven shape.

Note that the same can be said of the connection pipe ka (see FIG. 7) connected to the discharge side of the compressor 31 (see FIG. 7) as well as the heat exchanger tube 322a of the first radiator 32a. Furthermore, the same can be said of the heat exchanger tubes (not shown) of the second evaporator 36b (see FIG. 4) as well as the heat exchanger tubes 362a of the first evaporator 36a. In other words, the average tube inner diameter Ds of the heat transfer tubes (grooved tubes) of the first evaporator 36a (evaporator) and the second evaporator 36b (evaporator) is The average pipe inner diameter Dd of the heat exchanger tubes 322a (grooved tubes) of the heat transfer tubes 322a (grooved tubes) is smaller.

In this way, by reducing the average pipe inner diameter Dd of the connecting pipe ka and the first radiator 32a, the flow rate of the refrigerant is increased, and the heat transfer coefficient of the refrigerant is increased. Note that the refrigerant flowing through the connection pipe ka and the first radiator 32a has a relatively high density, so even if the flow rate of the refrigerant is increased, pressure loss is unlikely to increase. On the other hand, in the first evaporator 36a and the second evaporator 36b, the density of the refrigerant is relatively low. Therefore, by increasing the average pipe inner diameter Ds (reducing the flow velocity of the refrigerant), the pressure loss of the refrigerant is suppressed and the power of the compressor 31 is reduced.

FIG. 16 is a Mollier diagram of a refrigerator according to a modification of the first embodiment and a comparative example.
The horizontal axis in FIG. 16 is the specific enthalpy of the refrigerant, and the vertical axis is the pressure of the refrigerant. The saturated liquid line rw shown in FIG. 16 is a boundary line between the liquid phase state of the refrigerant and the gas-liquid two-phase state. Further, the saturated vapor line rg is a boundary line between the gas-liquid two-phase state and the gas-phase state of the refrigerant. In the region surrounded by the saturated liquid line rw and the saturated vapor line rg, the refrigerant is in a gas-liquid two-phase state. Further, the critical point rc is a boundary point between the saturated liquid line rw and the saturated vapor line rg.
In addition, the square solid line in FIG. 16 is a Mollier diagram in a modified example of the first embodiment (see FIG. 15), and the broken line is a Mollier diagram in which no grooved pipe is provided in the refrigerant circuit Q (see FIG. 4). This is a comparative example when a smooth tube is used.

As shown by the solid line in FIG. 16, the well-known processes of refrigerant compression (state G1d→state G1a), condensation (state G1a→state G1b), expansion (state G1b→state G1c), and evaporation (state G1c→state G1d) In the refrigeration cycle, refrigerant circulates in a refrigerant circuit Q (see FIG. 4). Note that the same applies to the comparative example indicated by the rectangular broken line.

As described above, when the connecting pipe ka and the first radiator 32a are grooved pipes to increase the heat transfer coefficient of the refrigerant, the heat radiation ability of the refrigerant increases. As a result, the refrigerant temperature (condensation temperature) on the high-pressure side decreases, and accordingly, the refrigerant pressure on the high-pressure side also decreases. This increases the volumetric efficiency of the compressor 31, so the amount of refrigerant circulated in the refrigerant circuit Q can be increased.

In addition, in the modification of the first embodiment, the first evaporator 36a and the second evaporator 36b use grooved tubes as heat transfer tubes, so that the first evaporator 36a and the second evaporator 36b have sufficient cooling capacity to correspond to the increase in the amount of refrigerant circulation. have. This suppresses a pressure drop in the refrigerant on the suction side of the compressor 31 (see FIG. 4), and in turn suppresses an increase in the compression ratio in the compressor 31. As a result, the energy required to drive the compressor 31 is reduced, so that the refrigerator 100 can save energy.

≪Second embodiment≫
In the second embodiment, the first radiator 32a (see FIG. 7) provided in the machine room R6 is omitted from the configuration of the first embodiment, and the connection pipe kAa (see FIG. 17) on the discharge side of the compressor 31 is replaced. This embodiment differs from the first embodiment in that it is a grooved tube. Note that the overall configuration of the refrigerator 100 (see FIGS. 1 to 5) is the same as that of the first embodiment. Therefore, the parts that are different from the first embodiment will be explained, and the explanation of the overlapping parts will be omitted.

FIG. 17 is an explanatory diagram regarding the arrangement of each device in the machine room R6 of the refrigerator according to the second embodiment.
In the example shown in FIG. 17, the discharge pipe kv of the compressor 31 and the upstream end of the connecting pipe kAa are connected at a welding point wa. Further, the upstream end of the connecting pipe kb connected to the second radiator 32b (see FIG. 4) is connected to the downstream end of the connecting pipe kAa at the welding point wc. This connecting pipe kAa is provided over the range SA1 on the suction side and the blowout side of the machine room blower Fm, and is configured as a grooved pipe. The refrigerant discharged from the compressor 31 then passes through the three-way valve 35 ( (see Figure 4).

Further, the connecting pipe kAa, which is a grooved pipe, is bent in a predetermined manner on the suction side and the blowout side of the machine room blower Fm, and its length (that is, heat transfer area) is sufficiently ensured. On the other hand, the connecting pipe kb and the like on the downstream side of the welding point wc are smooth pipes.

<Action/Effect>
FIG. 18 is an explanatory diagram showing temperature changes of the refrigerant in the connecting pipe kAa, the second radiator 32b, and the third radiator 32c included in the refrigerator according to the second embodiment.
In addition, on the horizontal axis of FIG. 18, the symbols of the connection pipe kAa, the second radiator 32b, and the third radiator 32c are sequentially written so that the right side of the page is on the downstream side of the flow of the refrigerant. On the other hand, the vertical axis in FIG. 18 indicates the temperature of the refrigerant flowing through the pipes and the like. Moreover, the solid line in FIG. 18 shows the case of the second embodiment in which the connecting pipe kAa is a grooved pipe. On the other hand, the broken line indicates a comparative example in which the connecting pipe kAa is a smooth pipe.

As shown in FIG. 18, the temperature of the gas refrigerant in the connection pipe kAa decreases at a steeper gradient in the second embodiment (solid line) than in the comparative example (broken line). As a result, almost all of the refrigerant flowing into the second radiator 32b (see FIG. 4) through the connecting pipe kAa is in a gas-liquid two-phase state, so that heat radiation from the second radiator 32b into the refrigerator is suppressed. . Therefore, the cooling load on the refrigerator can be reduced and energy savings can be achieved. Moreover, since it is not necessary to provide the first radiator 32a (see FIG. 7) in the machine room R6, the refrigerator can be made more compact and cost-effective.

≪Third embodiment≫
The third embodiment differs from the second embodiment (see FIG. 17) in that a spiral fin tube 41 is provided on the outlet side of the machine room blower Fm in the connection piping kBa (see FIG. 19). . Note that other aspects (such as the overall configuration of the refrigerator 100: see FIGS. 1 to 5) are the same as those in the second embodiment. Therefore, portions that are different from the second embodiment will be described, and descriptions of overlapping portions will be omitted.

FIG. 19 is an explanatory diagram regarding the arrangement of each device in the machine room R6 of the refrigerator according to the third embodiment.
The connecting pipe kBa shown in FIG. 19 is provided over the range SB1 on the suction side and the blowout side of the machine room blower Fm, and is configured as a grooved pipe. This connecting pipe kBa is provided with a spiral fin tube 41 in a part thereof. To explain in more detail, a spiral fin tube 41 is provided in at least a part of the connecting pipe kBa that exists on the blowing side of the machine room blower Fm. This spiral fin tube 41 is also configured as a grooved tube with a plurality of grooves provided on its inner wall.

The spiral fin tube 41 has the function of promoting heat dissipation of the refrigerant, and also has the advantage of being easy to install in the connecting pipe kBa that is bent in a predetermined shape. In particular, on the blowing side of the machine room blower Fm, the speed of the air increases on the radially outer side of the motor Fma, so as mentioned above, it is desirable to bend the connecting pipe kBa to a predetermined position (see also Fig. 11). . Here, by using a spiral fin tube 41 as a part of the connection piping kBa on the outlet side of the machine room blower Fm, the heat dissipation performance of the refrigerant is improved. Easy to install.

<Action/Effect>
According to the third embodiment, the connecting pipe kBa is formed of a grooved pipe, and furthermore, a spiral fin tube 41 is provided in at least a part of the connecting pipe kBa that exists on the outlet side of the machine room blower Fm. This promotes heat radiation from the refrigerant flowing through the connection pipe kBa to the air, so that the temperature of the refrigerant flowing into the second radiator 32b (see FIG. 4) can be lowered. As a result, heat conduction from the second radiator 32b to the inside of the refrigerator is reduced, making it possible to save energy in the refrigerator.

≪Fourth embodiment≫
The fourth embodiment differs from the first embodiment in that a part of the connection pipe kCa (see FIG. 20) is disposed in the recess 51a of the evaporating dish 51, but the other points are different from the first embodiment. The same is true. Therefore, the parts that are different from the first embodiment will be explained, and the explanation of the overlapping parts will be omitted.

FIG. 20 is an explanatory diagram regarding the arrangement of each device in the machine room R6 of the refrigerator according to the fourth embodiment.
As shown in FIG. 20, an evaporating dish 51 is installed at a predetermined location in the machine room R6. The evaporation dish 51 is a dish that receives water due to defrosting or condensation in the refrigerant circuit Q (see FIG. 4), and has a concave portion 51a that is concave downward in cross-sectional view. Water is stored in this recess 51a.

In the example shown in FIG. 20, the connecting pipe kCa is bent and arranged in a predetermined manner in the range SC1 on the suction side and the blowout side of the machine room blower Fm, and is configured as a grooved pipe. Further, a part of the connecting pipe kCa is arranged in the recess 51a of the evaporating dish 51. Note that the connection pipe kCa is appropriately arranged so that the connection pipe kCa arranged in the recess 51a comes into contact with water when water is accumulated up to a predetermined water level in the recess 51a. As a result, heat is radiated from the refrigerant flowing through the connection pipe kCa to the water collected in the evaporation dish 51.

Note that there may be cases where no water is collected in the evaporation dish 51 or the water level of the water collected in the evaporation dish 51 is very low, but even in such cases, the connecting pipe kCa is formed as a grooved pipe. As a result, heat is properly radiated from the refrigerant to the air.

<Effect>
According to the fourth embodiment, since a part of the connecting pipe kCa is disposed in the recess 51a of the evaporating dish 51, there is a gap between the refrigerant flowing through the connecting pipe kCa and the water accumulated in the evaporating dish 51. Heat exchange takes place. This, together with the fact that the connecting pipe kCa is a grooved pipe, promotes heat dissipation of the refrigerant flowing through the connecting pipe kCa.

≪Modification example≫
Although the refrigerator 100 and the like according to the present invention have been described above using the respective embodiments, the present invention is not limited to these descriptions, and various changes can be made.
For example, in the first embodiment (see FIG. 7), a configuration in which both the connecting pipe ka and the heat exchanger tube 322a of the first radiator 32a are grooved tubes has been described, but the present invention is not limited to this. For example, one of the connection pipe ka and the heat exchanger tube 322a of the first radiator 32a may be a grooved tube, and the other may be a smooth tube.

Further, in the first embodiment (see FIG. 7), a case has been described in which the entire connecting pipe ka is a grooved pipe, but the present invention is not limited to this. For example, at least a part of the connection pipe included in the refrigerant path from the discharge side of the compressor 31 (see FIG. 4) to the inlet of the second radiator 32b (outer condenser) may be provided with a grooved pipe provided with a groove on its inner wall. It may also be a tube. It is preferable that the upstream end of "at least a portion" of this connection pipe is connected to the discharge side of the compressor 31 (that is, the discharge pipe kv: see FIG. 7). As a result, the gas refrigerant immediately after being discharged from the compressor 31 flows through the grooved tube, so that the gas refrigerant having high thermal resistance can appropriately radiate heat through the grooved tube. Note that the discharge pipe kv of the compressor 31 may also be configured as a grooved pipe. Further, for example, the connecting pipe kb (see FIG. 7) that guides the refrigerant to the second radiator 32a may be a grooved pipe.

Further, the upstream side of the refrigerant path from the discharge side of the compressor 31 (see FIG. 4) to the capillary tubes 34a, 34b (throttle mechanism) is composed of a grooved tube, and the downstream side is composed of a smooth tube. The side connecting pipe may include a grooved pipe.

In addition, in the refrigerant circuit Q (see FIG. 4), this refrigerant It is preferable that the sum of the lengths of the grooved tubes included in the path is larger. Furthermore, in the refrigerant circuit Q, the sum of the lengths of the grooved tubes included in another refrigerant path from the inlet of the second radiator 32b (outer condenser) to the capillary tubes 34a, 34b (throttle mechanism) is It is preferable that the sum of the lengths of the smooth tubes included in another refrigerant path is larger. Even with this configuration, the effect of heat radiation by the grooved tube can be obtained in the refrigerant path from the discharge side of the compressor 31 to the inlet of the second radiator 32b. Further, in another refrigerant path from the inlet of the second radiator 32b (outer condenser) to the capillary tubes 34a and 34b, cost reduction is achieved by mainly using smooth tubes.

In addition, in the first embodiment, the portion of the connecting pipe ka (see FIG. 11) provided radially outward from the motor Fma of the machine room blower Fm is 180° or more in the circumferential direction with respect to the rotation axis of the motor Fma. Although the configuration including the area has been described, the configuration is not limited thereto. For example, in the space between the compressor 31 and the machine room blower Fm (air blower), at least a part of the connecting pipe ka (the part where the grooved pipe is provided) is located on the radially outer side than the blower motor Fma. The configuration may include a portion located in the . Even in this configuration, since high-speed air hits the grooved tube portion included in the connecting pipe ka, heat radiation from the refrigerant flowing through the grooved tube to the air is promoted.

Further, in the first embodiment (see FIG. 7), a case has been described in which the heat transfer tube 322a of the first radiator 32a (machine room condenser) is a grooved tube, but the present invention is not limited to this. That is, at least a portion of the heat transfer tube 322a of the first radiator 32a (machine room condenser) may be a grooved tube having a groove on its inner wall.

Further, in a modification of the first embodiment (see FIG. 15), in addition to the connection pipe ka and the heat exchanger tube 322a of the first radiator 32a, the heat exchanger tube 362a of the first evaporator 36a and the second evaporator 36b Although the structure in which the heat exchanger tube (not shown) is a grooved tube has been described, the present invention is not limited to this. For example, one of the heat exchanger tubes of the first evaporator 36a and the second evaporator 36b may be a grooved tube, and the other heat exchanger tube may be a smooth tube. Moreover, at least some of the heat transfer tubes of the first evaporator 36a and the second evaporator 36b (that is, the evaporators) may be configured to be grooved tubes having grooves on their inner walls. In such a configuration, for example, the connecting pipe ka and the heat exchanger tube of the first radiator 32a may be grooved pipes, or only the connecting pipe ka may be a grooved pipe.

Further, in the third embodiment (see FIG. 19), a case has been described in which the spiral fin tube 41 is provided in the connection pipe kBa on the outlet side of the machine room blower Fm, but the present invention is not limited to this. For example, the spiral fin tube 41 may be provided on the connection pipe kBa on the suction side of the machine room blower Fm, or the spiral fin tube 41 may be provided on both the suction side and the blowout side. That is, the spiral fin tube 41 may be provided in at least a portion of the connecting pipe kBa. Even in this configuration, the spiral fin tube 41 promotes heat radiation from the refrigerant to the air.

Further, in the fourth embodiment (see FIG. 20), the connection pipe kCa is a grooved pipe, and a part of the pipe is disposed in the recess 51a of the evaporating dish 51. However, the present invention is not limited to this. That is, in a configuration in which at least a portion of the connecting pipe kCa is a grooved pipe, at least the above-mentioned portion may include a portion disposed in the recess 51a where water is stored in the evaporating dish 51.

Further, the refrigerator 100 described in each embodiment is an example, and the present invention can be applied to other types of refrigerators. For example, each embodiment can be applied to a refrigerator in which an expansion valve (throttle mechanism) is used instead of the capillary tubes 34a and 34b (throttling mechanism: see FIG. 4).
Moreover, each embodiment can be combined as appropriate. For example, in a configuration in which the first embodiment and the third embodiment are combined and the first radiator 32a is provided in the machine room R6 (first embodiment: see FIG. 7), the connection piping on the outlet side of the machine room blower Fm A part of ka may be a spiral fin tube 41 (third embodiment: see FIG. 19).

Further, each embodiment is described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described. Furthermore, it is possible to add, delete, or replace some of the configurations of the embodiments with other configurations.
Further, the mechanisms and configurations described above are those considered necessary for explanation, and not all mechanisms and configurations are necessarily shown in the product.

31 Compressor 32a First radiator (condenser, machine room condenser)
321a Fin 322a Heat exchanger tube 32b Second radiator (condenser, outer condenser)
32c Third radiator (condenser, outer condenser)
34a, 34b Capillary tube (throttling mechanism)
36a First evaporator (evaporator)
362a Heat exchanger tube 36b Second evaporator (evaporator)
41 Spiral fin tube 51 Evaporating dish 51a Recess 100 Refrigerator Fm Machine room blower (blower)
Fma Motor Fmb Wing Fmc Frame ka, kAa, kBa, kCa Connection piping M Housing ma Groove (connection piping groove)
m2 groove (groove of heat exchanger tube in machine room condenser)
m6 groove (evaporator heat transfer tube groove)
R6 Machine room Q Refrigerant circuit

Claims (9)

A refrigerant circuit in which refrigerant circulates through a compressor, a condenser, a throttle mechanism, and an evaporator in sequence, and
comprising a housing having a machine room in which at least the compressor and the blower are installed;
The condenser includes an outer condenser installed outside the machine room in the housing,
At least a part of the connecting pipe included in the refrigerant path from the discharge side of the compressor to the inlet of the outer condenser is a grooved pipe with a groove provided in its inner wall,
The axial blower is fitted into a constriction portion formed by inwardly recessing the wall surface of the machine room,
The internal space of the throttle part is included in the machine room,
The blower is installed in the internal space of the constriction part,
The refrigerator characterized in that the at least part of the connecting pipe includes a portion disposed on the leeward side of the blower and radially outward than the motor of the blower. The condenser includes a cross-fin tube type machine room condenser installed in the machine room,
The machine room condenser and the outer condenser are sequentially connected toward the downstream side of the flow of refrigerant from the compressor,
The connection pipe is a pipe that connects the discharge pipe of the compressor and the heat transfer pipe of the machine room condenser,
The refrigerator according to claim 1, wherein the connecting pipe is a grooved tube, and further, the heat transfer tube is also a grooved tube. The refrigerator according to claim 1, wherein an upstream end of at least a portion of the connecting pipe is connected to a discharge side of the compressor. In the refrigerant circuit, the sum of the lengths of the grooved tubes included in the refrigerant path is longer than the sum of the lengths of the smooth tubes included in the refrigerant path from the discharge side of the compressor to the inlet of the outer condenser. is larger,
In the refrigerant circuit, the sum of the lengths of the smooth pipes included in the other refrigerant route is longer than the sum of the lengths of the grooved pipes included in the other refrigerant route from the inlet of the outer condenser to the throttling mechanism. 2. The refrigerator according to claim 1, wherein: is larger. The refrigerator according to claim 1, wherein the following formula (1) is satisfied regarding the rotational speed N of the compressor.
Here, N included in formula (1) is the rotation speed [rotation speed/s] of the compressor, π is pi, and D is the average inner diameter [mm] of the grooved pipe, Vst is the stroke volume [cm ³ ] of the compressor, η _v is the average volumetric efficiency [-] of the compressor, and ν _d is the average kinematic viscosity [m ^{2 ]} of the gas refrigerant on the high pressure side of the compressor. /s], ρ _d is the density of the gas refrigerant on the high pressure side of the compressor [kg/m ³ ], and ρ _s is the density of the gas refrigerant on the low pressure side of the compressor [kg/m ³ ]. be.

A claim characterized in that, in the connecting pipe, the portion of the blower that is arranged radially outward from the motor includes an area of 180° or more in the circumferential direction with respect to the rotation axis of the motor. The refrigerator according to item 1. At least some of the heat transfer tubes of the evaporator are grooved tubes having grooves on their inner walls,
The refrigerator according to claim 2, wherein an average inner diameter of the grooved tubes of the machine room condenser is smaller than an average inner diameter of the grooved tubes of the evaporator. a spiral fin tube provided in at least a portion of the connecting pipe;
The refrigerator according to claim 1, wherein the spiral fin tube is provided in a space on the outlet side of the blower. comprising an evaporation dish that receives water accompanying defrosting or condensation in the refrigerant circuit;
The refrigerator according to claim 1, wherein the at least a portion of the connecting pipe includes a portion disposed in a recess where water is stored in the evaporating dish.

Images