KR20020085786A - Refrigerator - Google Patents

Abstract

PURPOSE: A refrigerator is provided to promote the power saving by enhancing the performance of a condenser and to secure the operation performance of the refrigerator by suppressing the drop of the performance of the condenser in a machine room even if the suction side of the condenser in the machine room is clogged. CONSTITUTION: A cross fin type of heat exchanger, where many plate-shaped fins(18b) are juxtaposed on a refrigerant pipe(18a) made in zigzag, is used as a condenser(18) in the machine room, and a blower(17) in the machine room is constituted of a propeller-type blower which is projected toward the side of the condenser in a machine room from a mouth ring(41), and the periphery of a passage leading to the blower in the machine room from the condenser in the machine room is shut off to make a half-sealed space which opens at the section of the blower in the machine room and the section of the blower in the machine room. The face having wire area of the condenser in the machine room faces the half-sealed space.

Description

Refrigerator {REFRIGERATOR}

The present invention relates to a refrigerator, and is particularly suitable for a domestic refrigerator having a condenser of forced ventilation in a machine room.

A medium sized or large sized home refrigerator (first prior art) will be described with reference to FIGS.

This household refrigerator consists of a refrigerator case 1, a refrigerator door, and a freezing cycle. The refrigerator box body 1 is composed of an outer box made of steel, an inner box made of synthetic resin, and a heat insulating material made of foamed urethane filled therebetween, and forms a plurality of storage compartments. Refrigerator doors are also provided to open and close the storage compartment.

This refrigeration cycle is installed in the compressor 16 for boosting and circulating the refrigerant, the condenser 18 and 19 as a heat exchanger in charge of heat dissipation out of the refrigerator, the frost-resistant heat dissipation pipe 20, and the refrigerator as shown in FIG. And an evaporator 12 as a heat exchanger for cooling the refrigerating chamber, and a capillary 21 for connecting them.

These condensers 18 and 19 are installed in the machine room 22 at the lower rear side of the refrigerator box body 1 shown in Fig. 9 and are forced to be ventilated by the machine room blower 17 and natural convection. As a condenser of the type, it is comprised in the form which used together the box condenser 19 of the form which contacted the outer box of steel plate in the vicinity of the outer surface of the heat insulation wall of the refrigerator box 1, and embedded the refrigerant pipe.

The forced-ventilated machine room condenser 18 requires the formation of an air path or a power source such as a blower, but can prevent heat intrusion into the refrigerator and at the same time, it is easy to separate the condenser 18 when disposing the refrigerator. In addition, it has the advantage that the power saving of the refrigerator can be achieved by high performance. On the other hand, although the box condenser 19 has a simple structure and does not require power such as a blower, the box condenser 19 causes performance deterioration due to heat intrusion from the box condenser 19 to the inside of the refrigerator, and at the same time disposes the refrigerator. This has the drawback that it becomes difficult to separate the box condenser 19 from the heat insulation wall.

As the forced-ventilated machine room condenser 18, a spiral fin condenser which meanders and bends a refrigerant pipe 18a wound in a spiral shape with a strip fin shown in Fig. 10 is used. As shown in Fig. 9, the spiral fin condenser is installed in the machine room 22 at the lower rear side of the refrigerator box body 1, and is cooled intake side air (vented by the blower 17 installed in the machine room 22). By force). Moreover, what was related to this 1st prior art has been described in Unexamined-Japanese-Patent No. 7-318222.

On the other hand, in the refrigeration showcase (2nd prior art) described in Unexamined-Japanese-Patent No. 58-119178, the refrigeration showcase box body which enlarged the machine room in the whole bottom part, the compressor arrange | positioned at the rear part in the refrigerating chamber, and the machine room A cross fin tubular condenser disposed in the front part, a filter disposed in the suction part of the cross fin tubular condenser, and two machine room blowers forcibly ventilating the compressor and the condenser are provided. In the machine room, an inclined air inlet is formed at a corner of the front lower portion, and an air outlet is formed at the bottom of the rear surface. The cross fin tube condenser consists of a cross fin tube heat exchanger with a plurality of fins arranged so as to intersect with two rows of refrigerant tubes, and the refrigerant tubes extend from side to side, and the bent portions are located on both sides of the left and right sides to be inclined forward and flat. Is placed. The machine room blower is installed without a mouth ring in a circular hole formed in the fan duct plate.

However, the first prior art fin condenser has the advantage of being able to be formed in a free shape in the horizontal, vertical and inner length directions in accordance with the installation space of the machine room 22, but in the up, down, left and right directions with respect to one spiral fin. In order to prevent the friction sound caused by the contact of the fins, a large gap must be provided between each stage and each row, and a large gap must also be provided between the wall surfaces constituting the machine room. The heat transfer area of was low. For this reason, there is a problem that it is difficult to achieve high performance by securing sufficient heat dissipation with a spiral fin condenser installed in the machine room 22 constituted in a narrow space, and thus it is difficult to save power of the refrigerator.

On the other hand, the second prior art relates to a refrigerating showcase having a large machine room formed on the entire bottom portion, and having a suction port on the front surface and a discharge port on the rear surface thereof, which are completely different from the refrigerator having the machine chamber formed at the corners at the bottom of the rear surface. That is, in the second conventional technology, it is shown that the cross fin-type condenser is inclined to increase the suction area, thereby reducing the number of times the filter is cleaned due to dust clogging. When installed in the machine room, the filter is often installed to be difficult to take out the filter, the cleaning is difficult. In addition, in the second prior art, to improve the performance of the machine room condenser in a narrow place such as a machine room formed at the corners of the lower rear side of the refrigerator box body, to achieve power saving, which is achieved with an inexpensive configuration or good assembly performance. It is not described with respect to the change in capacity due to the change in the width of the refrigerator box body.

The object of the present invention is to improve the performance of the machine room condenser to save power, and to prevent the deterioration of the machine room condenser performance even when dust is attached and the suction side of the machine room condenser is clogged, thereby ensuring the operation performance of the refrigerator. It is to provide refrigerator which can be done.

Another object of the present invention is to provide a refrigerator capable of saving power by improving the performance of a machine room condenser with an inexpensive configuration.

Another object of the present invention is to provide a refrigerator in which the assembly of components in the machine room is good and the performance of the machine room condenser can be improved to save power.

Another object of the present invention is to provide a refrigerator which can easily cope with a capacity change caused by a change in the width of the refrigerator box body, and can improve the performance of the machine room condenser to save power.

1 is a longitudinal sectional view of a refrigerator according to a first embodiment of the present invention;

2 is a front view of the refrigerator of FIG.

3 is a freezing cycle of the refrigerator of FIG.

FIG. 4 is a rear view of the machine compartment of the refrigerator of FIG. 1; FIG.

5 is a rear perspective view of the machine chamber part.

6 is a perspective view of a single state of a machine room condenser disposed in the machine room unit.

7 is a rear view of the machine room cover attached to the machine room part.

Fig. 8 is a rear view showing the machine room of the refrigerator of the second embodiment of the present invention.

Fig. 9 is a rear view showing the machine room of the conventional refrigerator.

Fig. 10 is a perspective view showing a part of a machine room condenser used for a refrigerator.

11 is a freezing cycle diagram of a refrigerator.

Fig. 12 is a rear cross-sectional schematic diagram showing a refrigerator machine room part of another embodiment of the present invention.

FIG. 13 is a perspective view illustrating main parts of the refrigerator machine room of FIG. 12; FIG.

14 is a perspective view illustrating main parts of a refrigerator machine room part in still another embodiment of the present invention;

Fig. 15 is a perspective view showing main parts of a refrigerator machine room part in still another embodiment of the present invention;

Fig. 16 is a perspective view showing main parts of a refrigerator machine room part in still another embodiment of the present invention;

<Explanation of symbols for the main parts of the drawings>

1: refrigerator box body

1a: outer box

1b: inner box

1c: insulation

2: refrigerator

3: vegetable room

4: switching room

5: ice making room

6: freezer

7-11: Moon

12: refrigerator side evaporator

13: Refrigerator Blower

14: freezer side evaporator

15: Freezer side blower

16: compressor

17: machine room blower

18: Machine room condenser

18a: refrigerant pipe

18b: plate pin

18c: horizontal

18d: vertical section

19: box condenser

20: frost resistant heat dissipation pipe

21: capillary

21a: first capillary

21b: second capillary

22: machine room

23: evaporation vessel

24: machine room cover

25: Board

26: legs

27: floor

28: suction side air

29: discharge side air

30: bottom inlet

31: box inlet

32: box discharge port

33 to 35: fixture

40: partition plate

41: mouse ring

42: cover inlet

43: cover discharge port

101: machine room

102a, 102b: side plate

103: base

103a: bottom inlet

104: bottom plate

105: machine room cover

105a: back suction port

106: compressor

107: propeller fan

107a: frame portion

107b: mouse ring

107c: motor stay

107d: partition plate

108: machine room condenser

108a: heat dissipation fin

108b: refrigerant pipe

109: insulation

110: side plate

110a: top flange

110b: bottom flange

111: insulation

112: fan motor

113: wings

113a: boss

114: refrigerant inlet

116: cooler

141: refrigerator box body

141a: outer box

141b: inner box

141c: insulation

163: evaporation vessel

170: machine room blower

171: machine room partition member

172: machine room blower

Ls: Space Distance

Hs: side plate height

Hf: pin height

S: duplicate dimensions.

Representative examples of the present invention for achieving the above object is a refrigerator box body formed with a machine chamber at the bottom corner of the rear surface, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and the compressor and the machine room condenser. Machine chamber blower for forced ventilation, the machine room is formed to extend horizontally across the width of the refrigerator box body, the compressor is installed on one side in the left and right direction and the machine room condenser is installed on the other side in the left and right directions, The machine room condenser comprises a cross fin tube heat exchanger having a plurality of plate fins arranged in a refrigerant pipe formed in a meandering shape, and the machine room blower is provided on a partition plate dividing a ventilation path from the machine room condenser to the compressor. Protruded from the ring to the machine room condenser And a ventilation path from the machine room condenser to the machine room blower is a semi-closed space in which the pin gap of the machine room condenser and the gap between the machine room blower are opened, and the machine room condenser has a large area. Is disposed so as to face the semi-closed space.

EMBODIMENT OF THE INVENTION Hereinafter, each Example of the refrigerator of this invention is described using drawing. In addition, the same code | symbol in the drawing of each Example and a prior art example shows the same thing or an equivalent.

The overall configuration of the refrigerator of the first embodiment of the present invention will be described with reference to FIGS. 1 is a longitudinal sectional view of a refrigerator according to a first embodiment of the present invention, FIG. 2 is a front view of the refrigerator of FIG. 1, and FIG. 3 is a freezing cycle diagram of the refrigerator of FIG.

As shown in Figs. 1 and 2, the refrigerator box body 1 is an outer box 1a made of steel, an inner box 1b made of synthetic resin, and a heat insulating material 1c made of foamed urethane filled therebetween. It is comprised and the refrigeration chamber 2, the vegetable chamber 3, the switching chamber 4, the ice-making chamber 5, and the freezing chamber 6 are formed independently from the top. Each storage chamber 2-6 is provided with the doors 7-11. These refrigerating chambers 2, vegetable chambers 3, switching chambers 4, ice making chambers 5, and freezing chambers 6 each have a function as a general general storage chamber, and detailed description thereof will be omitted.

And a machine room 22 is formed in the corner part of the back lower part of the refrigerator box body 1, The compressor 16, the evaporation container 23, and the machine room blower 17 (refer FIG. 4) in this machine room 22. And a machine room condenser 18 (see Fig. 4) are arranged. The machine room 22 is formed with a refrigerator wall 1, an upper wall part, a front wall part, and both side wall parts, a mounting plate 25, a bottom wall part, and a machine room cover 24 with a rear wall part. In addition, the machine room 22 is formed long horizontally over the entire width of the refrigerator box body 1, and consists of a closed space except for the ventilation opening which consists of a suction port and a discharge port. The machine room cover 24 is detachably attached to the refrigerator box 1 by screws or the like. In addition, the mounting plate 25 is fixed to the lower surface of the outer box 1a by screws or the like. A leg 26 is provided in the placement plate 25, and a gap is formed between the placement plate 25 and the floor surface 27.

The refrigerating chamber side evaporator 12 is arrange | positioned at the back side of the vegetable chamber 3. The refrigerating chamber side blower 13 is a cold air ventilation blower dedicated to the refrigerating chamber side evaporator 12, and is arranged in the evaporator chamber of the refrigerating chamber side evaporator 12 to store the cold air from the refrigerating chamber side evaporator 12 and the refrigerating chamber 2 and the vegetable chamber ( Supply to 3). The freezer compartment side evaporator 14 is arrange | positioned at the back side of the switching chamber 4, the ice-making chamber 5, and the freezing chamber 6. As shown in FIG. The freezer compartment blower 15 is a cold air ventilator dedicated to the freezer compartment side evaporator 14. The freezer compartment blower 15 is disposed in the ventilation path of the freezer compartment side evaporator 14 to switch the cold air from the freezer compartment evaporator 14 to the switching chamber 4 and the ice making chamber ( 5) and supply to the freezing chamber (6). Each evaporator 12, 14 is supplied with a refrigerant by a compressor 16, each forming a part of a refrigeration cycle, and a cooling operation is performed. Water discharged from the refrigerating chamber side evaporator 12 and the freezing chamber side evaporator 14 is led to an evaporation vessel 23 in the machine chamber 22 and evaporated using heat generated by the compressor 16.

As shown in Fig. 3, the refrigeration cycle includes a compressor 16, a machine room condenser 18 using a cross fin tube type heat exchanger, a box condenser 19 having a refrigerant tube embedded type, a heat protection pipe 20 for frost protection, and a first capillary tube. The refrigeration cycle is constituted by contacting the pipes in the order of (21a) and the refrigerating chamber side evaporator 12a or the second capillary tube 21b and the freezing chamber side evaporator 12b and the compressor 16. The capillary tube 21 includes a first capillary tube 21a and a second capillary tube 21b, and the evaporator 12 includes a first evaporator 12a and a second evaporator 12b.

The compressor 16 and the machine room condenser 18 are arranged in the machine room 22 and forcedly ventilated by the machine room blower 17. The box condenser 19 is a natural convection type condenser in which the refrigerant pipe is embedded by contacting one side of the outer box 1a in the heat insulation wall 1c of the refrigerator box 1. The frost preventing heat dissipation pipe 20 is disposed between the outer box 1a and the heat insulator 1c along the front opening of the refrigerator box 1 to prevent frost on the front part of the outer box 1a.

Then, the refrigerant is compressed by the compressor 16, as shown by the arrow in Fig. 3, the high temperature and high pressure to reach the machine room condenser 18, the heat dissipation in the machine room condenser 18, the temperature is lowered and the box condenser 19 ) And heat to the front of the outer box (1a) by the frost-resistant heat dissipation pipe (20) to prevent frost, to reduce the pressure in the first capillary tube (21a) to reach the refrigerator compartment side evaporator (12a) 2, the pressure is reduced in the capillary tube 21b and flows to the freezer compartment evaporator 12b, and is evaporated in each of the refrigerator compartment side evaporator 12a and the freezer compartment side evaporator 12b to take heat from the surroundings, resulting in a low temperature and low pressure. Returning to the compressor 16, the cooling operation is performed by repeating this.

In addition, the classification to the refrigerating chamber side evaporator 12a and the freezing chamber side evaporator 12b is controlled by a valve (not shown). In addition, the machine room blower 17 is operated during the operation of this refrigeration cycle, forcibly ventilates the compressor 16 and the machine room condenser 18, and performs heat dissipation.

In this refrigeration cycle, the box condenser 19 of the refrigerator box body 1 can be significantly reduced by increasing the amount of heat dissipation using the cross fin tube-type machine room condenser 18 as described later. Therefore, the invasion of heat from the box condenser 19 into the storage compartment can be greatly reduced, and the electric power of the refrigerator can be reduced, and the box condenser 19 is separated from the heat insulation wall 1c during the disposal of the refrigerator. It becomes easy to be able to perform disposal of a refrigerator easily. In addition, the box condenser 19 may be reduced by further increasing the heat dissipation amount of the machine room condenser 18.

Next, the detailed structure regarding the machine room 22 is demonstrated, referring FIG. 4 is a rear view showing the machine room part of the refrigerator of FIG. 1, FIG. 5 is a back perspective view of the same machine room part, FIG. 6 is a perspective view of a single state of a machine room condenser disposed in the same machine room part, and FIG. 7 is the same machine room part. Back view of the machine room cover attached to. 4 and 5 show a state where the machine room cover 24 is removed.

The machine room 22 is formed as a space having a shape of a substantially rectangular parallelepiped that is long horizontally and vertically, that is, a vertical dimension larger than the inner length dimension and a larger width dimension than the vertical dimension. Specifically, the upper portion of the front wall portion is inclined, and the rear center portion slightly projects rearward. The compressor 16 is disposed on one side in the left and right directions of the machine room 22, and the machine room condenser 18 is disposed on the other side in the left and right directions of the machine room 22. The machine room blower (17) is composed of a propeller blower and is disposed in the mouth ring (41) of the partition plate (40) for dividing the space in which the compressor (16) is arranged and the space in which the machine room condenser (18) is arranged. It is disposed so as to project more than half in the axial dimension from the mouth ring 41 provided in the partition plate 40 dividing the ventilation path from the machine room condenser 18 to the compressor 16 to the machine room condenser 18 side. This machine room blower 17 has a function of sucking air and discharging air as indicated by arrow 29 as shown by arrows 28 of FIGS. And forced air to the machine room condenser (18). The ventilation path from the machine room condenser 18 to the machine room blower 17 is closed by the refrigerator box body 1, the mounting plate 25, the machine room cover 24, the fixtures 33 to 35, and the like. The pin gap of the condenser 18 and the space between the poles of the machine room blower 17 are set as the semi-sealed space, and the machine room condenser 18 is arrange | positioned so that the surface which has a large area may face this semi-sealed space.

As shown in FIG. 5, the suction part of the air into the machine room 22 is the bottom suction port 30 formed in the mounting plate 25, the box suction port 31 formed in the refrigerator box body 1, and FIG. As described above, the cover suction port 42 is formed on one side of the machine room cover 24. The bottom suction port 30 is formed of a plurality of slit-shaped openings formed at the suction plate 25 of the machine room blower 17 and located at a portion of the mounting plate 25 located below the horizontal portion 18c of the machine room condenser 18. . In addition, the box suction port 31 is formed by the ventilation path which cut out the edge part of the refrigerator box body 1 which faces the machine room 22, and is located in front of the suction side of the machine room condenser 18. As shown in FIG. The cover suction port 42 is formed of a plurality of slit-like mechanisms formed in the machine room cover 24 portion located on the suction side of the vertical portion 18d of the machine room condenser 18.

And the discharge part of the air of the machine room 22 is the cover discharge port 43 formed in the machine room cover 24 as shown in FIG. 7, and the refrigerator box body 1 which faces the machine room 22 as shown in FIG. It consists of the box discharge port 32 formed by the ventilation path which cut out the edge part of the. The cover discharge port 43 is formed of a plurality of slit-shaped openings formed in the part of the machine room cover 24 located on the discharge side of the machine room blower 17. Further, the box discharge port 32 is formed almost symmetrically on the opposite side of the box suction port 31.

The machine room condenser 18 is composed of a refrigerant pipe 18a, a plate fin 18b, and fasteners 33 and 34, as shown in a single state in FIG. The coolant tubes 18a are meandering in one coolant tube and are formed in one row. Further, the plate fin 18b is composed of corrugated fins, and a plurality of plate fins 18b are provided side by side so that the coolant pipes 18a in each row penetrate to form a cross fin heat exchanger. In this embodiment, the pin spacing is 1.5 mm, and the range of the pin spacing is preferably in the range of 1.3 mm to 1.8 mm. Further, the fasteners 33 and 34 are located on both sides of the plate fin 18b and are fixed to the refrigerant pipe 18a so that the refrigerant pipe 18a penetrates and protrudes to both sides. The protruding portion of the refrigerant pipe 18a is formed of a separate bent pipe and welded to form a meandering bent portion.

And the machine room condenser 18 is bent in the direction which cross | intersects in the longitudinal direction of the refrigerant pipe 18a, and the whole shape is formed in the L shape which consists of the horizontal part 18c and the vertical part 18d. That is, the overall shape of the machine room condenser 18 is formed to be bent so as to have a three-dimensional shape extending in the left, right, front, and up and down directions. The fastener 33 on one side has the locking piece 33a which protrudes from a lower end part, and the locking piece 33b which protrudes from a rear end part. Moreover, the other fastener 34 has the locking piece 34a which has a locking hole, and the locking piece 34b which has a screw hole. Since the corrugated fin is used as the plate fin 18b, the strength as the machine room condenser 18 is increased, and attachment and the like can be easily performed.

The machine room condenser 18 is positioned horizontally so that its horizontal portion 18c faces the bottom inlet 30, and its vertical portion 18d is perpendicular to the outer box 1a which forms the side wall of the machine room 22. It is installed in the machine room 22 to be located. In other words, the meandering bent portions of the refrigerant pipe 18 are located above and below the machine room 22, and the refrigerant pipes 18 formed in a meandering shape are arranged in the front-rear direction. Therefore, the bent portion protruding from the fixture 33 of the refrigerant pipe 18a protrudes in the horizontal direction in the longitudinal direction of the machine room 22, and the bent portion protruding from the fixture 34 protrudes upward. As a result, portions protruding from the fasteners 33 and 34 of the refrigerant pipe 18a protrude into a relatively spacious space in the machine chamber 22, whereby the storage of the machine chamber condenser 18 becomes good and a large machine room condenser ( 18 can be stored in the machine room 22, and the heat radiation amount of the machine room condenser 18 can be increased.

Moreover, the edge part of the horizontal part of the machine room condenser 18, and the protruding part of the refrigerant pipe 18a extend to the dead space part located under the machine room blower 17. As shown in FIG. Also in this respect, the storage capacity of the machine room condenser 18 can be improved, and the amount of heat dissipation of the machine room condenser 18 can be increased. Moreover, a part of the part which divides the suction side and the blowout side of the machine room blower 17 can serve as the fixture 33 of the machine room condenser 18, and can simplify a ventilation structure.

In the specific installation structure of the machine room condenser 18, one side of the machine room condenser 18 is fixed to the mounting plate 25 through the fixture 33, and the other side of the machine room condenser 18 is the fixture 34 and the fixture 35. It is fixed to the refrigerator box body (1) through. In this manner, the machine room condenser 18 can be fixed simply by fixing the mounting plate 25 and the refrigerator box body 1.

In more detail, when the installation structure of the machine room condenser 18 is demonstrated, the locking piece 33a which accommodates the machine room condenser 18 from the rear (back side) of the machine room 22, and is located in the front-end | tip part of the fixture 33 is carried out. Is inserted into a locking hole (not shown) of the mounting plate 25, and the locking piece 33b located at one rear end portion is fixed to the rear end of the mounting plate 25 with a screw. Moreover, the fastener 34 fixes the fastener 35 through the locking pieces 34a and 34b, and fixes the locking piece 35a of this fastener 35 to the back surface of the refrigerator box body 1. As shown in FIG. In this way, the machine room condenser 18 is fixed to the refrigerator box body 1.

When the machine room blower 17 is operated, the air 28 sucked from the bottom suction port 30 to the machine room 22 is mainly heat exchanged through the horizontal portion 18c of the machine room condenser 18, and at the same time, the cover suction port ( 42 and the air 28 sucked from the box inlet 31 are mainly heat exchanged through the vertical portion 18b of the machine room condenser 18, and the heat exchanged air 28 is transferred from the machine room blower 17 to the compressor ( 16, the air 29 is discharged to the outside of the machine chamber 22 from the cover discharge port 43 and the box discharge port 32 after heat exchange with the compressor 16.

Since the machine room condenser 18 is constituted by a cross fin tube heat exchanger having a plate fin 18b, the heat transfer area per occupied area can be made significantly larger than that of the conventional spiral fin condenser, so that a large amount of heat dissipation can be achieved even in the narrow machine room 22. You can get it.

Further, since the machine room condenser 18 is formed in an L-shape composed of a horizontal portion and a granular portion, the heat transfer area can be increased while suppressing an increase in the ventilation resistance, and the amount of heat dissipation can be increased. In this case, since the edge of the refrigerator box 1 is cut out to form the box suction port 31, the part 25 is attached to the mounting plate 25 and the strength of the mounting plate 25 is secured. Sufficient suction air volume to the L-shaped machine room condenser 18 with an increased suction area can be obtained while securing the pressure.

In this embodiment, a cross fin heat exchanger in which a plurality of plate fins 18b are provided in a meandering coolant tube 18a is used as the machine room condenser 18 and forcedly ventilated by the machine room blower 17 and has a large area. Since the machine room condenser 18 is arrange | positioned so that the surface which may have a semi-closed space may face, the heat transfer area per occupying area in the narrow machine room 22 can be increased, and the heat transfer performance of the machine room condenser 18 is improved. By doing so, power consumption of the refrigerator can be reduced. In particular, since the plate-shaped fin 18b of the machine room condenser 18 is waveform-formed and its pin pitch is set within the range of 1.3 mm to 1.8 mm, the machine room condenser 18 installed in the narrow machine room 22 is appropriately selected. It is possible to achieve a large heat transfer area and high heat transfer performance by the ventilation resistance, so that the performance of the machine room condenser 18 can be improved significantly.

Further, the machine room blower 17 is constituted by a propeller blower arranged to protrude from the mouth ring 41 provided on the partition plate 40 toward the machine room condenser 18 side, and the machine room blower 17 is connected to the machine room condenser 18. The airtight path is closed and the pin gap of the machine room condenser 18 and the air gap of the machine room blower 17 are opened, and the machine room condenser is formed so that the surface having a large area faces the semitight space. 18) is disposed, the air in the ventilation path from the machine room condenser 18 to the machine room blower 17 is clogged with air in the case where clogged dust is attached to the suction end surface of the machine room condenser 18. While stirring by the machine room blower 17 which protrudes in the inside, the air is taken in and out of the semi-closed space through the machine room blower 17, and the machine room condenser 18 is carried out in the semi-closed space. A is cooled by air. Thereby, even if the suction side of the machine room condenser 18 is clogged, the fall of the performance of the machine room condenser 18 can be suppressed, and the driving performance of a refrigerator can be ensured. Particularly, since the machine room blower 17 protrudes more than half in the axial dimension from the mouth ring 41 to the machine room condenser 18 side, the machine room in the case where dust or the like adheres to the suction end surface of the machine room condenser 18 and is blocked. Stirring by the blower 17 and the inflow of air into the semi-closed space can be increased, and cooling of the machine room condenser 18 can be improved significantly.

In addition, a cross fin heat exchanger in which a plurality of plate fins 18b are provided in a meandering coolant tube 18a is used as the machine room condenser 18, and the machine chamber 22 formed with a space having a larger upper and lower dimension than the inner dimension. Since the machine room condenser 18 is provided so that the meandering bent portions of the refrigerant pipe 18a are located at the upper and lower portions, and the refrigerant pipe 18a formed in the meandering shape is arranged in the front-back direction, the refrigerant which does not directly contribute as a heat transfer part. The front-back width of the part where the meandering bend of the pipe | tube 18a is located becomes narrow, and it can be set as the machine room condenser 18 which has a large heat transfer area and a ventilation area also in the narrow machine room 22. As shown in FIG. As a result, the meandering bent portion of the refrigerant pipe 18a can be reduced, so that the configuration can be inexpensive. In addition, the performance of the machine room condenser 18 can be improved to save power in the refrigerator. In particular, in the case where the bent portion of the refrigerant pipe 18a of the machine room condenser 18 is welded by forming a separate bent pipe, the welded portion can be reduced, so that a significant cost reduction can be achieved.

In addition, a cross fin heat exchanger in which a plurality of plate fins 18b are provided in a meandering refrigerant tube 18a formed in a meandering shape is used as the machine room condenser 18, and a three-dimensional shape in which the overall shape extends in the left, right, front, and up and down directions. Since it is bent and formed so that it may be made, it can be set as the machine room condenser 18 which has a big heat transfer area and a big ventilation area even in the narrow machine room 22. Thereby, the performance of the machine room condenser 18 can be improved by a simple structure, and the electric power saving of a refrigerator can be aimed at. In particular, since the machine room cover is detachably mounted to the refrigerator box body, the machine room condenser 18 is formed in an almost L shape having a portion facing the bottom wall portion of the machine chamber 22 and a portion facing the side wall portion. A large space is exposed between the machine room blower 17 and the machine room condenser 18 while the machine room cover is removed, and the space is used to attach or detach the machine room blower 17 or the machine room condenser 18. It can be done easily. In addition, since the machine room condenser 18 is constituted by a single row of cross fin tube type heat exchanger, the airflow resistance can be increased due to the low ventilation resistance as compared with the case where a plurality of rows of cross fin tube type heat exchangers are formed, thereby increasing the amount of air to the compressor 16. The compressor temperature can be reduced.

Further, the machine room condenser 18 is formed into a substantially L-shaped bent shape including a horizontal portion 18c facing the bottom wall portion of the machine chamber 22 and a vertical portion 18d facing the side wall portion. The end of the horizontal portion 18c of the 18 is attached to the mounting plate 25 through the fixture 33, and the end of the vertical portion 18d is attached to the refrigerator plate 1 through the fixtures 34 and 35. The suction port 30 is formed in the placement plate 25 portion of the machine room condenser 18 facing the horizontal portion 18c of the machine room condenser 18, thereby achieving a power saving of the refrigerator. By extending the horizontal portion 18c of the machine room condenser 18 to increase the width of the refrigerator having a larger width by increasing the width of (1), and forming the suction port 30 of the mounting plate 25 accordingly. , The capability of the machine room condenser 18 can be increased, Without significantly changing the structure of the shared use of the fixture (33-35) or the manufacturing method it can easily cope with the possible cost. In particular, since the suction port 42 and the discharge port 43 are formed on the left and right sides of the machine room cover 24, the airflow resistance can be increased by reducing the ventilation resistance, and the performance of the machine room condenser 18 can be improved. It is easy to increase the width of the refrigerator box body 1 while the suction port 42 and the discharge port 43 on the left and right sides of the machine room cover 24 are the same positions on both sides with respect to the refrigerator which increases the width. Can respond.

Further, the machine room condenser 18 is formed in an almost L shape having a portion facing the bottom wall portion of the machine chamber 22 and a portion facing the side wall portion, and the machine chamber blower 17 is formed from the mouth ring 41 by the machine chamber condenser ( It is configured as a propeller blower arranged to protrude toward the 18) side, and is disposed above the bottom face of the bottom face of the machine room condenser 18, so that the axial dimension (thickness) of the machine room blower 17 can be easily increased. It can improve the condenser performance by increasing the air volume.

Next, a second embodiment of the present invention will be described with reference to FIG. Fig. 8 is a rear view showing the machine room of the refrigerator of the second embodiment of the present invention.

In the present embodiment, the flat fin 18b is a cross fin type heat exchanger in which a plurality of rows of coolant tubes 18 are arranged in parallel to form a flat machine room condenser 18, and the machine room condenser 18 is connected to the machine room blower 17. Is different from the first embodiment in that it is provided perpendicular to the suction side of the filter, and other points are basically the same as in the first embodiment. In the present embodiment, the machine room condenser 18 is simple in shape and can be manufactured at low cost, and it is easy to apply to the refrigerator box body 1 having a narrow width.

Next, the detailed structure regarding the machine room 1 is demonstrated, referring FIG. 12 and FIG. 12 is a rear cross-sectional schematic view showing a machine room part of a refrigerator according to an embodiment of the present invention, and FIG. 13 is a rear perspective view showing a part of the same machine room part.

The machine room 101 is formed as a space having a horizontally long and vertically rectangular parallelepiped space, that is, a space having a larger vertical dimension than the inner length dimension and a larger width dimension than the vertical dimension. Specifically, the upper portion of the front wall portion is inclined while the rear center portion slightly projects rearward. The compressor 106 is disposed on one side in the left and right direction of the machine room 101, and the machine room condenser 108 is disposed on the other side in the left and right direction of the machine room 101. The machine room blower 170 is equipped with the machine room partition member 171 which divides the inside of the machine room 101 from side to side, and the machine room blower 172 which ventilates between the space divided by this machine room partition member 171. The compressor 106 is mounted on the left side of the base 103 on the base 103, and the machine room blower 170 and the machine room condenser 108 are mounted on the right side thereof.

In the machine room partition member 171, the frame portion 107a, the mouth ring 107b, the motor stay 107c, and the partition plate portion 107d are integrally formed of synthetic resin such as polypropylene. Thereby, the frame part 107a, the mouth ring 107b, the motor stay 107c, and the partition plate part 107d can be manufactured inexpensively and compactly, and the storage property and assembly property in the narrow machine room 101 are improved. In addition, when this effect is not required, the frame part 107a, the mouth ring 107b, the motor stay 107c, and the partition plate part 107d may be formed separately, and the machine room partition member 171 may be comprised.

The frame portion 107a is formed on the outer periphery of the mouth ring 107b in a frame shape around the partition plate portion 107d to increase the strength of the machine compartment partition member 171 and constitute an attachment surface to the machine chamber 101. Doing. Specifically, the frame portion 107a is formed in a shape having an attachment surface to the side plate 110, the machine room cover 105, the evaporation container 163, and the bottom plate 104. Attached.

The mouth ring 107b is formed in the center of the partition plate portion 107d in a circular ring shape and forms a central opening. The mouth ring 107b is formed with an inclined surface whose substantially inner circumferential surface extends from the center portion to the left and right machine room sides. As for the inner peripheral surface of this mouth ring 107b, even if a recessed part or an end part is formed, a substantial inner peripheral surface should just be inclined. Further, the mouth ring 107b is positioned so as to overlap the frame portion 107a in the machine room left and right directions (axial direction of the machine chamber blower 172).

The motor stay 107c is comprised from the some part extended in the center direction from the machine room 101 side of the mouth ring 107b, and the cylindrical motor attachment part which is located in the center of this part.

The machine room blower 172 is disposed at the central opening of the machine compartment partition member 171, and includes a propeller fan 107 for ventilating air in the machine room 101 and a fan motor 112 for driving the propeller fan 107. Equipped with.

The propeller fan 107 is composed of a cylindrical cup boss 113a and a plurality of wings 113 integrally formed on the outer circumference thereof. The wing 113 is formed so that its width in the axial direction is larger than that of the mouth ring 107b and the frame portion 107a, and slightly protrudes from the mouth ring 107b and the frame portion 107a toward the compressor side in the axial direction. (Protrudes about 10% of the thickness of the wings) and is provided so as to protrude largely from the mouth ring 107b and the frame portion 107a toward the condenser side in the axial direction. The amount of protrusion from the mouth ring 107b and the frame portion 107a to the condenser side in the axial direction increases the normal ventilation amount of the wing 113 and ensures the ventilation at the time of clogging the condenser. It is preferable to set it as half or more.

One side of the fan motor 112 is accommodated and attached to the motor stay 107c, and the other side thereof is accommodated in the boss 113a. Thereby, the machine room blower 172 becomes thin and the storing property in the machine room 101 becomes favorable. The rotation shaft of the fan motor 112 is fixed to the boss 113a to transmit the rotational force of the fan motor 112 to the propeller fan 107 to rotate.

The above-described machine room blower 170 has a function of ventilating air as shown by solid arrows 118 of FIGS. 12 and 13 in a normal state in which there is no condenser clogging. 106) and forced ventilation in the machine room condenser 108. The ventilation path from the machine room condenser 108 to the machine room blower 170 is composed of a space surrounded by the bottom plate 104, the base 103, the machine room cover 105, and the like, and the machine room condenser 108. It is a semi-closed space in which the pin clearance of the () and the clearance gap of the machine room blower 172 open.

The air suction part of the machine room 101 has a bottom suction port 103a formed in the base 103, a box part suction port formed by cutting a part of the bottom plate 104, and a rear suction port 105a formed on one side of the machine room cover 105. ) The lower suction port 103a is a suction side of the machine room blower 170 and is formed of a plurality of slit-shaped openings formed in the base 103 portion located below the horizontal portion of the machine room condenser 108. In addition, the box suction port is formed by a ventilation path cut out of the corner of the bottom plate 104 facing the machine room 101, and is located in front of the suction side of the machine room condenser 108. The back suction port 105a is formed of a plurality of slit-shaped openings formed in the part of the machine room cover 105 located on the suction side of the vertical part of the machine room condenser 108.

And the discharge of the air of the machine room 101 consists of the back discharge port formed in the machine room cover 105, and the box part discharge port formed by the ventilation path which cut out the edge part of the bottom plate 104 which faces the machine room 101. As shown in FIG. The rear discharge port is formed of a plurality of slit-shaped openings formed in a part of the machine room cover 105 located on the discharge side of the machine room blower 170. Further, the box discharge port is formed almost symmetrically on the opposite side of the box suction port.

On the other hand, the machine room condenser 108 is composed of a refrigerant pipe 108b, a heat radiating fan 108a, and side plates 110 and 110a. The refrigerant pipe 108b is formed meandering with one refrigerant pipe and is formed in one row in the ventilation direction. The coolant inlet 114 of the coolant pipe 108b is provided on the conveying air device side (right upper end side in FIG. 13). In addition, the heat dissipation fan 108a is formed of corrugated fins, and a plurality of heat dissipation fans 108a are installed side by side to pass through the refrigerant pipes 108b of each row to constitute a cross fin tube heat exchanger. In this embodiment, the pin gap is 1.5 mm, and the range of the pin gap is preferably in the range of 1.3 mm to 1.8 mm. Further, the side plates 110 and 110a are located at both sides of the heat dissipation fin 108a and are fixed to the refrigerant pipe 108b so that the refrigerant pipe 108b penetrates and protrudes to both sides.

Then, the machine room condenser 108 is bent in the direction intersecting in the longitudinal direction of the refrigerant pipe 108b by plastic working (bending in the direction intersecting in the axial direction on the side of the air blower) so that the overall shape is perpendicular to the horizontal portion. It is formed in a negative L shape. In other words, the overall shape of the machine room condenser 108 is formed to be bent so as to have a three-dimensional shape extending in left, right, front and rear directions. Thus, the machine room condenser 108 is comprised from the horizontal part extended in the axial direction which cross | intersects the vertical surface of the machine room blower 170, and the vertical part which opposes the machine room blower 170. As shown in FIG.

Moreover, the horizontal part of the machine room condenser 108 is provided so that it may extend from the axial condenser side edge part in the machine room blower 170 to the compressor side in the axial direction. Specifically, the compressor side end of the horizontal part of the machine room condenser 108 has a overlap part which overlaps with the mouth ring 107b and the frame part 107a of the machine room blower 170 by overlap dimension S. As shown in FIG. In this overlapping portion, a space is formed between the mouth ring 107b and the frame portion 107a and the heat dissipation fin 108a. This space has a space distance L between the frame portion 107a and the heat dissipation fin 108a. This enables the inflow of wind from the heat dissipation fin 108a portion of the machine room condenser 108 in the overlapping portion, thereby improving heat exchange performance. The heat insulating material 109 is attached to the opposing surface of the machine room blower 170 in this overlap part. As a result, even if the temperature of the machine room condenser 108 rises to a high temperature due to the high temperature refrigerant gas introduced therein, deformation of the machine room blower 170 made of resin can be prevented.

The side plates 110 and 110a are for maintaining the machine room condenser 108 with sufficient strength and are fixed to both ends of the machine room condenser 108. One side of the side plate 110 is formed in a substantially cross-shaped cross section extending back and forth, the lower flange (110b) is screwed to the base 103 and the upper flange (110a) through the heat insulating material 111 through the frame portion ( It is screwed to 107a). In this way, the machine room partition member 171 is supported on the side plate 110 and fixed. And the height Hs of this side plate 110 was made higher than the height Hf of the heat radiation fin 108a. Thereby, the space distance L of the overlapping part mentioned above is secured. In addition, the height of the machine compartment partition member 171 is provided between the upper flange 110a and the heat insulating material 111, or between the heat insulating material 111 and the machine room partition member 171 with an interposition member, for example, a metal interposition member. May be adjusted. In addition, the other side plate 110a extends to the lower surface of the bottom plate 104 and is screwed to the bottom plate 104. In addition, since the corrugated fin is used as the heat radiation fin 108a, the strength as the machine room condenser 108 is increased so that attachment and the like can be easily performed.

The machine room condenser 108 is positioned almost horizontally with its horizontal part facing the inlet 103a and the machine room 101 is positioned almost vertically with its vertical part facing the side plate 102b forming the side wall of the machine room 101. Is installed in. In other words, the ends with the bent portion of the refrigerant pipe 108b are located above and below the machine room 101, and the refrigerant pipes 108b formed in a meandering shape are arranged in the front-rear direction (right and left of the machine room 101). Direction so as to extend in a direction. Therefore, the bent portion at one end of the refrigerant pipe 108b protrudes in the horizontal direction (the left direction in FIG. 12), which is the longitudinal direction of the machine room 101, and the bent portion at the other end is protruded upwardly in the longitudinal direction of the machine room. As a result, portions protruding from the side plates 110 and 110a of the refrigerant pipe 108b protrude from the machine chamber 101 toward the space with a relatively sufficient space, so that the machine room condenser 108 has good storage capacity and thus a large machine room condenser ( 108 can be accommodated in the narrow machine room 101, and the amount of heat radiation of the machine room condenser 108 can be increased.

Moreover, the edge part of the horizontal part of the machine room condenser 108, and the protruding part of the refrigerant pipe 108b extend to the part of the dead space located under the machine room blower 172. As shown in FIG. Also in this respect, the storage capacity of the machine room condenser 108 is improved and the amount of heat dissipation of the machine room condenser 108 can be increased. Moreover, a part of the part which divides the suction side and the discharge side of the machine room blower 170 can serve as the side plate 110 of the machine room condenser 108, and can make a ventilation structure simple.

The machine room condenser 108 has one side of the machine room condenser 108 fixed to the base 103 through the side plate 110, and the other side of the machine room condenser 108 is connected to the bottom plate 104 through the side plate 110a. It is fixed. Thus, by fixing the machine room condenser 108 over the base 103 and the bottom plate 104, it can be easily fixed.

When the machine room blower 172 is operated, the air 128 sucked into the machine room 101 from the bottom suction port 103a is mainly heat-exchanged through the horizontal part of the machine room condenser 108, and at the same time, the rear suction port 105a and the box are provided. The air 128 sucked into the secondary intake is mainly heat-exchanged through the vertical part of the machine room condenser 108, and this heat-exchanged air 128 is blown out of the machine room blower 172 to the compressor 106, and the air 129. After the heat exchange with the compressor 106, it is discharged to the outside of the machine room 101 from the rear discharge port and the box discharge port.

Since the machine room condenser 108 is constituted by a cross fin tube heat exchanger having a heat dissipation fin 108a, the heat transfer area per occupied area can be made significantly larger than a conventional spiral fin condenser so that a large amount of heat dissipation can be obtained even in a narrow machine room 101. Can be.

In addition, since the machine room condenser 108 is formed in an L shape having a horizontal portion and a granular portion, the heat transfer area can be increased while suppressing an increase in the ventilation resistance, and the amount of heat dissipation can be increased. In this case, since the corner portion of the bottom plate 104 of the refrigerator box body 142 is cut out to form a box suction port, the base 103 is secured with a portion for attaching the leg 106 to the base 103. Sufficient suction air volume to the L-shaped machine room condenser 108 whose suction area is increased while securing strength can be obtained.

In this embodiment, a cross fin tube type heat exchanger in which a plurality of heat dissipation fins 108a are provided in a meandering refrigerant pipe 108b is used as the machine room condenser 108, and forced ventilation is performed by the machine room blower 170. Since the machine room condenser 108 is disposed so that the surface having a large area extends along the ventilation path, the heat transfer area per occupied area in the narrow machine room 101 can be increased, and the heat transfer of the machine room condenser 108 is performed. The performance can be improved and the power consumption of the refrigerator can be saved. In particular, since the heat radiation fin 108a of the machine chamber condenser 108 is corrugated and the pin pitch is set within the range of 1.3 mm to 1.8 mm, the machine chamber condenser 108 installed in the narrow machine chamber 101 is properly ventilated. The resistance allows a large heat transfer area and a high heat transfer performance, so that the machine room condenser 108 can be improved significantly.

In addition, the machine room blower 170 is constituted by a propeller-type fan 107 protruding from the mouth ring 107b and the frame portion 107a in the axial direction to the machine room condenser side in the machine room partition member 171, and the machine room condenser The periphery of the ventilation path from 108 to the machine room blower 170 is closed and the space between the pin gap of the machine room condenser 108 and the gap between the machine room blower 172 is opened, and the surface having a large area is ventilated. Since the machine room condenser 108 is disposed so as to extend along the furnace, when the dust adheres to the suction end surface of the machine room condenser 108 and blockage occurs, the ventilation path from the machine room condenser 108 to the machine room blower 172. While the air inside is stirred by the machine room blower 172 which protrudes into this ventilation path, the air flows in and out of the condenser side space through the propeller fan 107 and the machine room is performed. The condenser 108 is cooled with air in the condenser side space. Thereby, even if the suction side of the machine room condenser 108 is clogged, the fall of the performance of the machine room condenser 108 can be suppressed, and the driving performance of a refrigerator can be ensured. In particular, since the propeller-type fan 107 protrudes more than half in the axial dimension from the mouth ring 107b to the machine room condenser 108 side, when dust or the like adheres to the suction side end surface of the machine room condenser 108 and is blocked. Stirring by the machine room blower 172 and inflow of air into the condenser side space can be increased, and cooling of the machine room condenser 108 can be improved significantly.

In addition, a machine room 101 formed of a space having a larger upper and lower dimension than an inner length dimension using a cross fin tube heat exchanger having a plurality of heat dissipation fins 108b attached to a refrigerant pipe 108b formed in a meandering shape as a machine room condenser 108. The machine room condenser 108 is arranged so that the meandering bent portion of the refrigerant pipe 108b is located at the top and the bottom thereof, and the refrigerant pipe 108b formed in the meandering shape is arranged in the front-rear direction. The front and rear widths of the portion where the meandering bent portion of the refrigerant pipe 108b is not reduced can be used as the machine room condenser 108 having a large heat transfer area and a ventilation area even in the narrow machine room 101. As a result, the meandering bent portion of the coolant pipe 108b is reduced, so that the configuration can be made inexpensive. In addition, the performance of the machine room condenser 108 can be improved to save power in the refrigerator. In particular, in the case where the bent portion of the refrigerant pipe 108b of the machine room condenser 108 is formed by a separate bent pipe and soldered and welded, the soldered welded portion can be reduced, so that a significant cost reduction can be achieved.

In addition, a cross fin tube type heat exchanger in which a plurality of heat dissipation fins 108a are provided in a meandering coolant pipe 108b is used as the machine room condenser 108, and its overall shape is three-dimensionally extending in the left, right, front, and up and down directions. Since it is formed so that it may be bent, it can be set as the machine room condenser 108 which has a big heat transfer area and a big ventilation area even in the narrow machine room 101. As shown in FIG. Thereby, the performance of the machine room condenser 108 can be improved by a simple structure, and the electric power saving of a refrigerator can be aimed at. In particular, the machine room cover 105 is detachably mounted to the refrigerator box body 141, and the machine room condenser 108 is opposed to the base 103, which is the bottom wall of the machine room 101, and the side plate which is a side wall ( Since it is formed in a substantially L-shape which is a part facing 102b), a large space is exposed between the machine room blower 170 and the machine room condenser 108 with the machine room cover 105 removed. By using this method, maintenance and repair of the machine room blower 172, attachment and detachment of the machine room condenser 108, and the like can be easily performed. In addition, since the machine room condenser 108 is constituted by a cross fin tube heat exchanger having one row in the ventilation direction, the airflow resistance can be increased with a smaller ventilation resistance as compared with the case where a plurality of rows of cross fin tube type heat exchangers are used. The heat exchange performance of the compressor can be improved, and the amount of air flow to the compressor 106 can be increased to reduce the compressor temperature.

Further, the machine room condenser 108 is formed into a nearly L-shaped bent shape consisting of a horizontal portion facing the base 103, which is the bottom wall of the machine chamber 101, and a vertical portion facing the side plate 102b, which is the side wall. The end of the horizontal portion of the condenser 108 is attached to the base 103 through the side plate 110, and the end of the vertical portion is attached to the bottom plate 104 of the refrigerator box body 141 through the side plate 110. And the suction port 103a is formed in the base 103 portion facing the horizontal portion of the machine room condenser 108, thereby reducing the power consumption of the refrigerator. By extending the horizontal portion of the machine room condenser 108 to the refrigerator to increase the width to increase the capacity, and by forming the lower inlet 103a of the base 103 accordingly, the machine room condenser 108 Since the capability can be increased, the side plates 110 and 110a can be shared or the manufacturing method can be shared without significantly changing the attachment structure of the machine room condenser 108, thereby making it possible to respond inexpensively and easily. In particular, since the rear suction port 105a and the rear discharge port are formed on the left and right sides of the machine room cover 105, the airflow resistance can be increased by reducing the ventilation resistance, and the performance of the machine room condenser 108 can be improved. For the refrigerator to increase the width by increasing the width of the box body 141, it is easy to cope with increasing the width by keeping the rear suction port 105a and the rear discharge port on the left and right sides of the machine room cover 105 at the same positions on both sides. Can be.

In addition, the machine room condenser 108 is formed in a substantially L shape having a portion facing the base 103 which is the bottom wall of the machine chamber 101 and a portion facing the side plate 104b which is the side wall, and the machine chamber blower 172. Is configured to have a propeller-type fan 107 disposed to protrude from the mouth ring 107b toward the machine room condenser 108 and above the portion facing the base 103 which is the bottom bottom of the machine room condenser 108. Since it arrange | positions, the axial dimension (thickness) of the machine room blower 172 can be easily increased, and an air volume can be increased and a condenser performance can be improved.

As described above, since the machine room blower 170 is stored above the machine room condenser 108, the dimensions between the left and right sides can be zero. Since the discharge side of the machine room blower 170 is covered with a non-rotating motor stay 107c, the blade 113 is secured such that the compressor 106, the discharge pipe and return pipe for the refrigerant around the compressor, the evaporation vessel 163, and the like are secured. The distance can be easily secured. The external shape of the machine room condenser 108 can accommodate a large one as the machine room blower 170 and the machine room condenser 108 overlap.

In addition, the machine room condenser 108 allows the heat dissipation fins 108a to enter below the frame portion 107a of the machine room partition member 171 to allow ventilation from the base 103, thereby allowing continuous heat dissipation between the pipes. Since the heat transfer surface areas of the fins 108a and the refrigerant pipes 108b are secured, high heat dissipation capacity can be obtained, and they can be stored in a narrow space in the machine room 101, and a ventilation space can be provided.

Moreover, since the conveyance air apparatus side of the machine room condenser 108 was bent upward so that it may cross | intersect in the axial direction, further heat transfer surface area can be aimed at. In addition, since the suction port 103a and the rear suction port 105a are provided to be sucked in a wide range, the air volume can be increased. This improves the heat dissipation capability of the machine room condenser 108.

Regarding the machine room blower 170, since the blade 113 protrudes from the frame portion 107a to the condenser side in the axial direction, the wind can be sufficiently introduced from the circumferential direction of the blade 113 and the condenser 103 In addition to the axial direction, the suction function is also obtained from the direction perpendicular to the axial direction. The shape of the bending arrangement of the machine room condenser 108 corresponding to this, and the lower surface suction port 103a of the base 103 and the rear surface of the rear cover 105 are obtained. The wind can be increased by the intake port 105a, so that an improvement in the heat dissipation ability is obtained. In addition, since the inlet guide is formed on the suction surface of the mouth ring 107b as the closer to the wing, the inclined guide 107b gradually moves forward to the discharge side, the wind can be further increased to improve the heat dissipation ability.

In addition, the attachment of the machine room blower 170 does not increase the number of parts by using the side plate 110 of the machine room condenser 108, and also does not require the size of the blower thickness for attachment. In addition to the advantages, it is possible to easily and accurately secure the space with the heat dissipation fin 108a by adjusting the height Hs of the side plate 110.

Regarding the high temperature heat response, there is a space distance L between the heat dissipation fin 108a and the frame portion 107a and the bottom surface of the frame portion 107a of the blower facing the heat dissipation fin 108a located in the overlapping portion. Since the heat insulating material 109 is attached to it, the heat from the heat radiation fin 108a can be interrupted | blocked, and the temperature rise of the resin frame part 107a can be reduced. In addition, with respect to the heat coming from the side plate 110 side, the temperature of the frame part 107a of a blower rises by the interposition heat insulating material 111 between the frame part 107a and the upper flange 110a of the side plate 110. Can be less. In addition, the high temperature refrigerant sent from the compressor 106 enters from the conveying wind device side of the machine room condenser 108, and the temperature difference between the air and the refrigerant is large, and the refrigerant temperature passes through one refrigerant pipe. The temperature can be reduced to such an extent that deformation of 107a does not occur. This can prevent deformation of the frame portion 107a made of resin.

Even when the eyes are clogged by dust or the like on the suction side of the machine room condenser 108 during use of the refrigerator, the heat dissipation fins 108a of the wing 113 of the machine room blower 172 from the mouth ring 107b and the frame portion 107a. Since it protruded to the side, the propeller fan 107 can take advantage of the characteristic that the discharge flow changes in the centrifugal direction when the ventilation resistance increases, and the absolute flow rate is very large. That is, in the inner space surrounded by the machine room blower 170 and the machine room condenser 108, a large-speed turning centrifugal flow is discharged from the outer circumferential protrusion of the blade 113 to radiate heat from the heat dissipation fins on the inner surface side of the machine room condenser 108. Forced to circulate all the way deep inside (up to the side of the blower) between 108a) and withdrawing heat from the machine room condenser 108, the pressure in the part of the machine room condenser 108 or in the rotational surface of the propeller type fan 107 It can be discharged from this weak portion, for example, near the boss, to perform heat dissipation of the machine room condenser 108.

The orbital centrifugal flow has little relationship with the air volume, and is almost governed by the rotational circumferential speed of the propeller fan 107, and is about 10 times as large as that normally passes between the heat dissipation fins 108a. The surface heat transfer rate of the heat dissipation fin 108a can be particularly improved.

Next, this wind flow will be described in detail with reference to FIG. In FIG. 12, the solid line indicating the streamline shows a case where the refrigerator is in a normal use state, and the dotted line indicating the streamline shows a case where the suction side of the machine room condenser causes clogging.

The blade 113 of this kind of propeller fan 107 determines the direction of inflow and outflow by changing the cross section along the axial direction, and a high pressure cannot be obtained. In the machine room blower 170, when the ventilation load (resistance of the ventilation) becomes large, the amount of air flow from the machine room condenser side decreases rapidly. However, in this case, the blade rotation is still the same as the inflow component in the axial direction becomes smaller, so that the force occupied by the turning component becomes relatively large, so that the difference in the peripheral speed between the outer peripheral side and the center side of the blade 113 is different. That is, the flow is centrifugal flow from the center side to the outer circumference side due to the static pressure difference. In the characteristic curve of air volume-pressure of the machine room blower 170, this change point is called a surge point or a stall point. This point is present at about 70% of the maximum no-load air flow, and when the ventilation load is higher than this, the pressure starts to be rapidly centrifugal and becomes the centrifugal fan characteristic, and the pressure is gradually increased until it is completely completed. The maximum pressure point in the characteristic curve of the air volume-pressure is at full completion, which is determined by the main speed of the blade 113 regardless of the air volume. In other words, even when complete, the absolute speed of the turning centrifugal flow is very large.

In the present invention, by utilizing the characteristics of the above-mentioned turning centrifugal flow and the fact that the absolute speed is large even when the air volume decreases, the condenser 106 is concentrated in the machine room more than conventionally and requires much heat radiation than conventionally. In this case, sufficient heat dissipation capacity is obtained so that a predetermined cooling of the storage compartment is obtained even if the ventilation load is increased due to dust adhesion to the machine room condenser 108 or the like.

That is, normally, as described so far, the air is sucked through the machine room condenser 108 widely, including the lower fin portion of the frame portion 107a, like the solid line 118. When the ventilation load increases, the wing 113 protrudes from the frame portion 107a toward the heat dissipation fin 108a, so that the inside surrounded by the machine room blower 170 and the machine room condenser 108 as indicated by the broken line 119 is shown. In the space, the turning centrifugal flow is discharged along the slope 107b from the protruding portion of the blade 113, after which the inner surface of the machine room condenser 108 is forced to circulate deeply (to the side of the blowing device) to remove heat. It may have been. In this case, since the vortex flow of the wind mainly uses the dynamic pressure component, it also reaches the heat dissipation fin 108a below the frame portion 107a sufficiently to reach the deep heat dissipation fin 108a on the side of the carrier wind device while increasing the static pressure. Can be. Since the pressure on the blower shaft line is low, the air whose temperature has been taken away by the heat is returned to the inside and is returned to the compressor from the vicinity of the boss 113a where the circumferential speed is small, or in the structure of the peripheral equipment of the machine room blower 170. Among the pressure unbalances on the blade rotation surface due to the asymmetry of the ventilation load, the centrifugal action is discharged from the portion where the centrifugal action is weakened to the original compressor 106 of the blower to perform heat dissipation.

Blowing of these winds, in addition to the low-temperature air flows from the compressor 105 side near the boss 113a with a small main speed and between the wings 113 and the gap between the mouth ring 107b, the wing 113 Since the protruding dimension on the original discharge side is reduced to reduce the generation of centrifugal action on the discharge side, it is attracted by a strong turning centrifugal flow on the machine room condenser 108 side through a portion on the blade rotating surface with energy balance. do. The above wind flow is comparable to the state in which the ventilation load is extremely high, that is, the pin inlet surface of the machine room condenser 108 is clogged with dust. If not, the inflow and outflow occurs between the fins of the condenser 106. .

As described above, according to the present embodiment, the machine room blower 170 and the machine room condenser 108 to the machine room 101 have excellent storage properties, and a large amount of heat transfer surface area can be obtained to improve the heat dissipation ability. It is also possible to prevent thermal deformation due to the high temperature due to the improvement. In addition, the condenser, which has been dispersed in several places in the past, can be concentrated in the machine room to some extent, so that the disposal and recyclability of the refrigerator can be improved.

Next, another embodiment of the present invention will be described with reference to FIG. 14 is a perspective view of main parts of a machine room of a refrigerator of an embodiment of the present invention;

In this embodiment, when arranging the machine room blower 120 and the machine room condenser 121 up and down, the bridge | cross type thing which spreads upward of the heat radiation fin 121a as the mounting base 122 is prepared separately, The frame part 120a of the machine room blower 120 is supported and fixed to this mounting base 122, and the leg part 122a of the mounting base 122 is fixed to the base 103. As shown in FIG. As a result, in addition to obtaining the same effects as in the above-described embodiment, in particular, the space distance between the fin 121a portion of the condenser and the axial overlapping dimension S between the blower 120 and the fin 121a portion can be easily selected optimally. Since the machine room blower 120 and the machine room condenser 121 do not directly contact each other, the vibration of the mutual vibration can be insulated. A heat insulating material 123 is installed between the mounting table 122 and the frame part 120a to prevent thermal deformation of the frame part 120a, and the heat insulating material 123 is connected to the frame part 120a and the condenser. It is sandwiched between the side plates 123 of 121 and serves as a wind seal.

Next, another embodiment of the present invention will be described with reference to FIG. Fig. 15 is a perspective view of main parts of a machine room of a refrigerator of an embodiment of the present invention. This embodiment differs from the first embodiment as described below, and other points are basically the same as the first embodiment.

This embodiment is another embodiment in the case where the machine room blower 124 and the machine room condenser 125 are arranged up and down, and the bridge type attachment which spreads over the return pipe 125b of the machine room condenser 125 is shown. The stand 126 is prepared separately and the frame 124a is fixed to the mounting table 126, and the leg 126a of the mounting table 126 is fixed to the base 103. As a result, in addition to obtaining the same effect as the above-described embodiment, in particular, the effect that the optimum space distance L between the machine room blower 124 and the heat dissipation fin 125a can be selected easily is obtained, and thus the machine room blower 124 and Since the machine room condenser 125 does not directly contact, it is possible to prevent deformation of the frame 124a of the machine room blower 124 and to insulate the vibration of each other. An elastic material 127 is provided between the mounting table 126 and the frame 124a so that the vibration of the machine room blower 124 can be transmitted to the base 103.

Next, another embodiment of the present invention will be described with reference to FIG. Fig. 16 is a perspective view of main parts of a machine room of a refrigerator in accordance with the embodiment of the present invention;

This embodiment removes the bending work when the machine room condenser 129 is manufactured. That is, the storage in the machine room 101 is the same place, and the heating fin 129a is laminated along the axial direction in accordance with the axial flow suction of the machine room blower 128, and the pipe 129b is inserted at an axial right angle. The heat exchanger consists of a pair in the horizontal direction and the vertical direction.

According to the present embodiment, in addition to obtaining the same effect as the above-described embodiment, in particular, the direction of the heat dissipation fins 129a is made to follow the axial direction of the machine room blower 128, and thus the heat dissipation fins below the frame portion 128a. Low-temperature air can be blown easily from 129a, and the effect of the overlapping portion can be enhanced, and when the refrigerator is used in close contact with the wall, it can be blown in from the lower portion of the base 103. In addition, the coolant inlet 130 of the hot gas is positioned on the conveying blower side to be the uppermost pipe part on the condenser side arranged in the up and down direction, and afterwards, the refrigerant flows to the horizontal direction part to meander the coolant to the blower 128 side. When there is a close proximity, there is an advantage that there is no fear of thermal deformation such as a resin part constituting the blower 128 sufficiently low temperature. There is no need for bending techniques in terms of fabrication.

According to the present invention, it is possible to improve the performance of the machine room condenser to save power, and at the same time, even when dust is attached and the suction side of the machine room condenser is blocked, the deterioration of the machine room condenser performance can be suppressed to ensure the operation performance of the refrigerator. A refrigerator can be obtained.

Moreover, according to this invention, the refrigerator which can improve the performance of a machine room condenser in an inexpensive structure, and can save power is obtained.

Further, according to the present invention, a refrigerator having good assembly property of components in the machine room, which can improve the performance of the machine room condenser, and which can save power can be obtained.

In addition, according to the present invention, a refrigerator can be easily responded to a capacity change caused by a change in the width of the refrigerator box body, and the power of the machine room condenser can be improved to save power.

Claims (22)

A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room is formed to extend horizontally over the entire width of the refrigerator box body, the compressor is installed on one side in the left and right direction and the machine room condenser is installed on the other side in the left and right directions, The machine room condenser is composed of a cross fin tube heat exchanger in which a plurality of plate fins are installed in a refrigerant pipe formed in a meandering shape. The machine room blower is composed of a propeller type blower installed to protrude toward the machine room condenser from a mouth ring installed on a partition plate dividing a ventilation path from the machine room condenser to the compressor, The ventilation path from the machine room condenser to the machine room blower is closed to form a semi-closed space in which the pin gap of the machine room condenser and the gap between the machine room blower are opened. And the machine room condenser is disposed such that a surface having a large area faces the semi-closed space. The refrigerator according to claim 1, wherein the machine room blower protrudes more than half in the axial dimension from the mouth ring provided on the partition plate to the machine room condenser side. The refrigerator according to claim 1 or 2, wherein the plate-shaped fin of the machine room condenser is formed in a wave shape, and its pin pitch is set within a range of 1.3 mm to 1.8 mm. A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room is formed of a space having an upper and lower dimension larger than an inner length dimension, wherein the compressor is installed at one side in the left and right direction and the machine room condenser is installed at the other side in the left and right direction, and the machine room is located between the machine room condenser and the compressor. Blower is installed, The machine room condenser includes a cross fin tube heat exchanger having a plurality of plate-shaped fins arranged in a meandering refrigerant pipe, wherein the meandering bent portions of the refrigerant pipe are located in the upper and lower portions of the machine room and are meandering. A refrigerator, wherein the coolant pipes are arranged in the front and rear directions. The refrigerator according to claim 4, wherein the meandering bent portion of the refrigerant pipe is formed by welding a separate bent pipe. A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room forms a rear wall part with a machine room cover, and is formed to extend horizontally over the entire width of the refrigerator box body. The compressor is installed on one side of the refrigerator and the machine room condenser is installed on the other side of the refrigerator. And a machine room blower is disposed on the mouth ring installed on the partition plate divided into left and right sides of the compressor side and the mechanical condenser side. The machine room condenser is composed of a cross fin tube heat exchanger in which a plurality of plate fins are provided in a meandering refrigerant tube, and bent to form a three-dimensional shape extending in the left, right, front, and up and down directions. Featured refrigerator. 7. The L-shaped device according to claim 6, wherein the machine room cover which is detachable to the refrigerator box body forms a rear wall part of the machine room, and the machine room condenser is formed in an L shape having a part facing the bottom wall part of the machine room and a part facing the side wall part. The refrigerator characterized by the above-mentioned. 8. The refrigerator according to claim 6 or 7, wherein the machine room condenser is constituted by a row of cross fin tube heat exchangers in which a plurality of plate fins are provided in a meandering refrigerant tube. A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The refrigerator compartment forms an upper wall portion, a front wall portion and both side wall portions with the refrigerator box body, forms a bottom wall portion with a mounting plate, and forms a rear wall portion with a machine room cover, and horizontally over the entire width of the refrigerator box body. It is formed long, the compressor is installed on one side in the left and right direction, the machine room condenser is installed on the other side in the left and right direction, and the machine room blower is installed in the mouth ring installed on the partition plate divided into the compressor side and the machine room condenser side. , The machine room condenser is composed of a cross fin tube type heat exchanger having a plurality of plate fins arranged in a meandering refrigerant tube, and has an almost L shape having a horizontal part facing the bottom wall part of the machine room and a vertical part facing the side wall part. The bent shape, attaching the end of the horizontal portion to the mounting plate through a fastener, and attaching the end of the vertical portion to the refrigerator box body through a fastener, And the placement plate forms a suction port at a portion of the machine room that faces the horizontal portion of the condenser. 10. The apparatus as claimed in claim 9, wherein an intake port is formed in a part of the machine room cover located between the machine room condenser and the side wall part of the refrigerator box body, and a discharge port is formed in a part located on the compressor side of the partition plate. Refrigerator. A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room is formed to extend horizontally over the entire width of the refrigerator box body, the compressor is installed on one side in the left and right direction and the machine room condenser is installed on the other side in the left and right directions, The machine room condenser is composed of a cross fin tube type heat exchanger having a plurality of plate fins arranged in a meandering refrigerant tube, and is formed in an almost L shape having a portion facing the bottom wall portion and a portion facing the side wall portion of the machine chamber. And The machine room blower is composed of a propeller blower arranged to protrude toward the machine room condenser side by a mouth ring installed on a partition plate dividing the ventilation path from the machine room condenser to the compressor, and at the same time facing the bottom wall surface of the machine room condenser. A refrigerator, which is arranged above the refrigerator. A refrigerator box body having a machine room formed at a corner of the lower rear surface, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room is formed to extend horizontally over the entire width of the refrigerator box body, the compressor is installed on one side in the left and right direction and the machine room condenser is installed on the other side in the left and right directions, The machine room condenser is composed of a cross fin tube heat exchanger having a plurality of heat dissipation fins in a refrigerant pipe formed in a meandering shape, and has a portion extending in the machine room in a lateral direction. The machine room blowing device is configured to ventilate the air in the machine room in left and right directions, A part extending in the left and right direction of the machine room condenser is overlapped along the left and right directions with respect to the machine room blower, and a space part that becomes a suction ventilation path is formed between the overlapped machine room condenser and the machine room blower. Refrigerator. The side plate located on the machine room blower side of the machine room condenser as the blower unit is attached, and the height of the side plate is greater than the heat sink fin height so that the heat sink fin unit and the machine room blower are separated. A refrigerator comprising a space therein to form a suction passage. The upper and lower portions of the side plates positioned on the machine room blower side of the machine room condenser are bent toward the semi-heat-dissipating fin side to form a flange portion, and the upper flange portion is attached to the blower device. Refrigerator, characterized in that the fixing portion to the base for forming a. 13. The air chamber according to claim 12, wherein the machine room blower is supported on a bridge-type mounting plate extending over the heat sink fin of the machine room condenser, and a space portion, which is a suction ventilation path, is formed between the heat sink fin part of the machine room condenser and the machine room blower. Refrigerator characterized by one. 13. The machine room blower according to claim 12, wherein the machine room blower is supported on a mounting table covering a refrigerant pipe portion protruding from the heat dissipation fin located on the machine room blower side of the machine room condenser, and the lower side of the mounting table is placed on a base constituting the machine room. A refrigerator characterized in that fixed. The refrigerator according to claim 12, wherein a heat insulating material is attached to a surface corresponding to the heat radiation fin of the machine room blower overlapping the machine room condenser. The refrigerator according to claim 12, wherein the refrigerant inlet of the machine room condenser is at the side of the semi-machine room blower. The refrigerator according to claim 13 or 14, wherein an insulating material is interposed between the machine room blowing device and a mounting table for supporting the same. A refrigerator box body having a machine room formed at a corner of a lower rear side thereof, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected to a refrigerant pipe, and a machine room blower forcibly venting the compressor and the machine room condenser, The machine room is formed to extend horizontally over the entire width of the refrigerator box body, the compressor is installed on one side in the left and right direction and the machine room condenser is installed on the other side in the left and right directions, The machine room condenser is composed of a cross fin tube heat exchanger having a plurality of heat dissipation fins in a refrigerant pipe formed in a meandering shape. The machine room blowing device has a propeller-type fan and a mouth ring, which is installed in the center portion in the left and right directions of the machine room so as to ventilate between the space on the machine room condenser side and the space on the compressor side, The propeller fan is installed to protrude from the mouth ring to the machine room condenser side in the axial direction, The mouth ring is a refrigerator, characterized in that the substantially inner peripheral surface of the inclined surface extending from the axial direction toward the machine room condenser. 21. The propeller type fan is installed so as to protrude slightly from the mouth ring to the compressor side in the axial direction, and the mouth ring has a substantially inner circumferential surface of the inclined surface that is also widened from the axial direction to the compressor side. Refrigerator. 22. The refrigerator according to claim 12 or 21, wherein the machine room condenser is formed by combining a condenser extending in the left and right directions of the machine room and a condenser extending in the direction crossing the left and right directions.