JP2003042636A - Refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerator which saves electric power by improving the performance of a machine house condenser. SOLUTION: A machine house 1 is horizontally provided with a compressor 6 at one side thereof and the machine house condenser 8 at the other side. The condenser 8 is constituted of a cross-fin-tube type heat exchanger in which a refrigerant pipe 8b having a meandering form with a number of radiation fins 8a being juxtaposed thereon is provided. A machine house blower 70 is disposed so that the air in the machine house 1 is ventilated in the horizontal direction, and that the portion extending in the horizontal direction of the condenser 8 is rendered to horizontally go along the blower 70. Thus, a suction air duct is defined between the condenser 8 and the blower 70.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerator, and more particularly, it is suitable for a domestic refrigerator having a forced ventilation type condenser in a machine room.

[0002]

2. Description of the Related Art A conventional household refrigerator (prior art 1) will be described with reference to FIG.

This household refrigerator comprises a refrigerator box, a refrigerator door, a refrigerating cycle and the like. The refrigerator box body is composed of an outer box made of steel plate, an inner box made of synthetic resin, and a heat insulating material made of urethane foam filled between them to form a plurality of storage chambers. Further, the refrigerator door is provided to open and close the storage room.

In this refrigeration cycle, a compressor 144 for boosting and circulating a refrigerant, condensers 145 to 147 as a heat exchanger for radiating heat to the outside of the refrigerator, a dew-prevention heat radiating pipe, and a storage chamber installed in the refrigerator. An evaporator 149 as a heat exchanger for cooling, a discharge pipe 153 connecting the compressor 144 and the condenser 145, a capillary 148 connecting the dew prevention pipe and the evaporator, a return pipe 150 connecting the evaporator 149 and the compressor 144, etc. It consists of

The condensers 145 to 147 are installed in the machine room 141 at the lower rear portion of the refrigerator box and are mechanically ventilated by the machine room blower 152.
And a box condensor 146, 147 of a form in which a refrigerant pipe is embedded by contacting with an outer box made of steel plate near the outer surface of the heat insulation wall of the refrigerator box as a natural convection type condenser. It is configured. The machine room condenser 145 has a connection port for the discharge pipe 153 on the anti-compressor side (anti-blowing device side), and the temperature of the refrigerant gas flowing from the connection pipe 153 is generally a high temperature exceeding 180 ° C. . The box condensers 146 and 147 are installed on both sides of the refrigerator box.

The forced ventilation type machine room condenser 145 requires power for forming an air passage and a blower, etc., but can prevent heat from entering the inside of the refrigerator and, at the same time, dispose of the refrigerator in the machine room. It is easy to separate the condenser 145, and has an advantage that power saving of the refrigerator can be achieved due to high performance. On the other hand, box condensers 146 and 147
Has a simple structure and does not require power such as a blower, but it causes performance deterioration due to heat intrusion from the box condensers 146 and 147 into the refrigerator, and the box condenser at the time of discarding the refrigerator. It has the drawback that it becomes difficult to separate 146, 147 from the insulating wall.

The forced ventilation type machine room condenser 145 described above.
For this, a spiral fin type mechanical chamber condenser 145 is used in which a refrigerant pipe in which band-shaped fins are spirally wound is bent in a three-dimensional manner. The spiral fin type machine room condenser 145 is installed in the machine room 141 at the lower back of the refrigerator box, and the machine room blower 152 installed in the machine room 141.
It is forcibly cooled by the cooling air ventilated by.

The machine room blower 152 includes a machine room partition member 152a for partitioning the machine room into left and right compressor room sides and a condenser side, and a machine room blower 152b composed of a propeller type fan and a fan motor. Have The machine room partition member 152a is made of resin in view of price and productivity. The propeller type fan of the machine room blower 152b is
It is completely housed in the machine room partition member 152a including both ends in the axial direction, and the wind is sucked only from the plane perpendicular to the axial direction. On the premise of this, the machine room condensers 145 are simply juxtaposed so as to face each other in the axial direction of the propeller type fan, and the air flows only in the axial direction on the suction side of the propeller type fan.

Incidentally, as for the one related to the prior art 1, Japanese Unexamined Patent Publication No. 7-318222 and Japanese Unexamined Patent Publication No. 11-2.
There is one described in Japanese Patent No. 11316.

On the other hand, in the refrigerating showcase disclosed in Japanese Utility Model Laid-Open No. 58-119178 (Prior Art 2), a refrigerating showcase box body having a large machine room formed on the entire bottom surface and a rear part of the machine room are arranged. Compressor, a cross fin tube type condenser placed in the front part of the machine room, a filter placed in the suction part of the cross fin tube type condenser, and two machine room blowers for forced ventilation of the compressor and the condenser. It has and. In the machine room, an inclined air intake port is formed at the lower corner of the front surface, and an air discharge port is formed at the lower rear surface. The cross fin tube type condenser has 2
It consists of a cross-fin tube type heat exchanger in which multiple fins are arranged side by side so as to intersect the refrigerant pipes in a row, and the refrigerant pipes extend to the left and right, and the bent portions are located on both the left and right sides, and are flat forward and high. It is arranged to be inclined. The machine room blower is installed in a circular hole formed in the fan duct plate, and the circular hole does not have a mouth ring.

[0011]

However, the prior art 1 has an advantage that the spiral fin type condenser 145 can be freely formed in the vertical, horizontal, and depth directions according to the installation space of the machine room 141. However, it is necessary to provide a large gap between each step and each row in order to prevent a rubbing noise associated with the contact of one spiral fin in the vertical and horizontal directions, and to configure a machine room. It was necessary to provide a large gap also with the wall surface. Further, since the discharge pipe 153 is connected on the machine room blower side of the machine room condenser 145 and the machine room blower side of the machine room condenser 145 becomes hot, the machine room partition member 152a made of resin does not deform. The machine room condenser 145 to the machine room partition member 152.
It was necessary to dispose it as far as possible in the axial direction from a. Therefore, the heat transfer area per occupied volume of the spiral fin type condenser 145 is low. This allows
It is difficult to secure a sufficient amount of heat radiation by the spiral fin type condenser 145 installed in the machine room 141 configured in a narrow space to achieve high performance, and it is difficult to save power in the refrigerator. was there.

On the other hand, the prior art 2 relates to a refrigerating showcase in which a machine room is formed large on the entire bottom surface and has a suction port on the front surface and a discharge port on the back surface. It is completely different from the refrigerator that was formed. That is, in the prior art 2, it is shown that the cross-fin type condenser is tilted to increase the suction area to reduce the number of times of cleaning the filter due to clogging of dust. In the case where the machine room is provided, when the filter is installed in the machine room, it is often installed so that it is difficult to take out the filter, and the cleaning is difficult at present. Further, in the conventional technique 2,
Improving the performance of the machine room condenser in a narrow space such as the machine room formed in the lower corner of the back of the refrigerator box to save power, while using an inexpensive configuration or good assembly. There is no description about what to achieve, and how to deal with the capacity change by changing the width of the refrigerator box.

A first object of the present invention is to provide a refrigerator capable of improving the performance of the machine room condenser and saving power.

A second object of the present invention is to improve the performance of the machine room condenser to save electric power, and to prevent the machine room condenser from being clogged on the suction side of the machine room machine. An object of the present invention is to provide a refrigerator in which the operation performance of the refrigerator can be secured by suppressing the deterioration of the performance of the room condenser.

[0015]

The first means of the present invention for attaining the above-mentioned first object is to provide a refrigerator box body having a machine room at the lower corner of the rear surface thereof, a compressor, and a machine room condenser. A refrigeration cycle in which a compressor and an evaporator are connected by a refrigerant pipe, and a machine room blower for forcibly ventilating the compressor and the machine room condenser, the machine room being horizontally long over the entire width of the refrigerator box. Formed, the compressor is installed on one side in the left-right direction, the machine room condenser is installed on the other side in the left-right direction, and the machine room condenser has a large number of refrigerant pipes formed in a meandering shape. It is composed of a cross fin tube type heat exchanger in which radiating fins are arranged in parallel, and has a portion extending in the left-right direction in the machine room, and the machine room blower is configured to ventilate the air in the machine room in the left and right directions. And extend in the left-right direction of the machine room condenser. That portion was overlapped along the lateral direction with respect to the machine room blower, lies in the formation of the space portion comprising a suction air passage between the machine room condenser and a machine chamber blower for this duplicated.

The second means of the present invention for achieving the above-mentioned second object is to provide a refrigerator box body having a machine chamber formed at a lower corner of the back surface, a compressor, a machine room condenser and an evaporator. A refrigeration cycle connected by a pipe, and a machine room blower for forcibly ventilating the compressor and the machine room condenser, the machine room is formed horizontally in the entire width of the refrigerator box, the left-right direction The compressor is installed on one side, and the machine room condenser is installed on the other side in the left-right direction. The machine room condenser has a large number of heat radiating fins arranged in parallel in a meandering refrigerant pipe. It is composed of a cross fin tube type heat exchanger, the machine room blower has a propeller type fan and a mouth ring, and is installed in the center part of the machine room in the left-right direction, and compressed with the space on the machine room condenser side. It is designed to ventilate the space on the machine side. The propeller fan is installed so as to project from the mouth ring toward the machine room condenser side in the axial direction, and the mouth ring of the mouth ring is inclined so that the substantial inner peripheral surface of the mouth ring expands toward the machine room condenser side in the axial direction. There is a face.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A plurality of embodiments of a refrigerator according to the present invention will be described below with reference to the drawings. In addition, in the second and subsequent embodiments, a part of the configuration common to the first embodiment will be omitted, and redundant description will be omitted. The same reference numerals in the drawings of each embodiment indicate the same things.

The overall construction of the refrigerator according to the first embodiment of the present invention will be described with reference to FIGS. 2 to 4. 2 is a vertical sectional view of the refrigerator according to the first embodiment of the present invention, FIG. 3 is a front view of the refrigerator, and FIG. 4 is a refrigeration cycle diagram of the refrigerator.

As shown in FIGS. 2 and 3, the refrigerator box 4
1 is composed of an outer box 41a made of a steel plate, an inner box 41b made of synthetic resin, and a foaming urethane heat insulating material 41c filled between them, and a plurality of storage chambers 42 to 46 are formed vertically. . In the storage chambers 42 to 46, a refrigerating chamber 42, a vegetable chamber 43, a switching chamber 44, an ice making chamber 45, and a freezing chamber 46 are independently formed from the top. Each storage room 42
The doors 47 to 51 are provided on the doors to 46. The refrigerating room 42, the vegetable room 43, the switching room 44, the ice making room 45, and the freezing room 46 have respective functions as ordinary general storage rooms, and detailed description thereof will be omitted.

A machine room 1 is formed at the lower corner of the back of the refrigerator box 41, and a compressor 6,
The evaporation container 63, the machine room blower 70 (see FIG. 1), the machine room condenser 8 (see FIG. 1), and the like are arranged. In this machine room 1, a bottom plate 4 (see FIG. 1) of a refrigerator box 41 has a top wall and a front wall, and a side plate 2 of the refrigerator box 41.
A and 2b (see FIG. 1) form side wall portions, a base 3 forms a bottom wall portion, and a machine room cover 5 forms a rear wall portion. Further, the machine room 1 is formed in a horizontally long shape over the entire width of the refrigerator box 41, and is configured by a space that is closed except for a ventilation port including a suction port and a discharge port. The machine room cover 5 is attached to the refrigerator box body 4 with screws or the like.
1 is detachably attached. The base 3 is fixed to the lower surface of the outer box 41a with screws or the like. Legs 66 are attached to the base 3, and a gap is formed between the base 3 and the floor surface 67.

The refrigerator compartment evaporator 16a is arranged on the back side of the vegetable compartment 43. The refrigerator compartment blower 53 is a blower for cold air ventilation exclusively for the refrigerator compartment evaporator 16 a.
The cool air from the refrigerator compartment evaporator 16a is arranged in the ventilation passage 6a and is supplied to the refrigerator compartment 42 and the vegetable compartment 43. The freezer compartment evaporator 16b is arranged on the back side of the switching room 44, the ice making room 45, and the freezer room 46. The freezer compartment blower 55 is a blower for cold air ventilation exclusively for the freezer compartment evaporator 16b, is arranged in the ventilation passage of the freezer compartment evaporator 16b, and cools air from the freezer compartment evaporator 16b in the switching chamber 44, the ice making chamber 45, Supply to the freezer compartment 46. The refrigerant is supplied to the respective evaporators 16a and 16b by the compressor 6, and each evaporator 16a and 16b forms a part of the refrigeration cycle to perform the cooling operation. The water discharged from the refrigerator compartment evaporator 16a and the freezer compartment evaporator 16b is guided to the evaporation container 63 in the machine room 1 and evaporated using the heat generated in the compressor 6.

As shown in FIG. 4, the refrigeration cycle includes a compressor 6, a machine room condenser 8 using a cross fin tube type heat exchanger, a refrigerant tube embedded type box condenser 59, and a dew condensation prevention heat radiation pipe. 60, the first capillary 15a and the refrigerator compartment evaporator 16a or the second capillary 15b and the freezer compartment evaporator 16b, and the compressor 6 are connected by piping in this order to form a refrigeration cycle. The capillary 15 is composed of a first capillary 15a and a second capillary 15b,
The evaporator 16 is composed of a first evaporator 16a and a second evaporator 16b.

The compressor 6 and the machine room condenser 8 are arranged in the machine room 1 and forcedly ventilated by the machine room blower 70. The box condenser 59 is the heat insulating material 41c of the refrigerator box 41.
This is a natural convection type condenser in which a refrigerant pipe is embedded in contact with one side surface of the outer box 41a. The dew condensation preventing heat radiation pipe 60 is provided along the front opening of the refrigerator box 41 to the outer box 4
It is arranged between 1a and the heat insulating material 41c, and prevents dew condensation on the front surface portion of the outer box 41a.

The refrigerant, as shown by the arrow in FIG.
Compressed by the compressor 6 to reach high temperature and high pressure, and reaches the machine room condenser 8, where heat is dissipated in the machine room condenser 8 to lower the temperature.
The heat is further radiated by the box condenser 59, and the front surface of the outer box 41a is heated by the dew condensation prevention heat radiation pipe 60 to prevent dew condensation, and the pressure is reduced by the first capillary 15a and reaches the refrigerating compartment evaporator 16a. It is decompressed by the second capillary 15b and divided into a flow reaching the freezer compartment evaporator 16b and evaporated in the refrigerating compartment evaporator 16a and the freezer compartment evaporator 16b to take heat from the surroundings, thereby reducing the temperature and low pressure. The state is returned to the compressor 6, and the cooling operation is performed by repeating this process.

The split flow to the refrigerator compartment evaporator 16a and the freezer compartment evaporator 16b is controlled by a valve (not shown). Further, the machine room blower 70 is operated during the operation of this refrigeration cycle, and forcedly ventilates the compressor 6 and the machine room condenser 8 to radiate the heat.

In this refrigeration cycle, as will be described later, the machine room condenser 8 using a cross fin tube type heat exchanger has a greatly increased heat radiation amount, so that the box body condenser 59 of the refrigerator box body 41. Can be significantly reduced. Therefore, heat invasion from the box condenser 59 into the storage chamber can be significantly reduced, power consumption of the refrigerator can be reduced, and the box condenser 59 can be used as the heat insulating material 41c when the refrigerator is disposed of. And the refrigerator can be easily disposed of. In addition, it is preferable to eliminate the box condenser 59 by further increasing the heat radiation amount of the machine room condenser 8. If the box condenser 59 is deleted, only the machine room condenser 8 is provided, and further power saving, easier disposal of the refrigerator, and cost reduction can be achieved.

Next, the detailed structure of the machine room 1 will be described with reference to FIGS. 1 and 5. FIG. 1 is a schematic rear sectional view showing a machine room of a refrigerator according to a first embodiment of the present invention, and FIG. 5 is a rear perspective view showing a part of the machine room.

The machine room 1 is formed in a space which is long in the horizontal direction and high in the vertical direction, that is, a space having a substantially rectangular parallelepiped shape, that is, a space in which the vertical dimension is larger than the depth dimension and the lateral width dimension is larger than the vertical dimension.
Specifically, the upper portion of the front wall portion is inclined, and the central portion of the rear surface slightly projects rearward. The compressor 6 is arranged on one side of the machine room 1 in the left-right direction, and the machine room condenser 8 is arranged on the other side of the machine room 1 in the left-right direction. The machine room blower 70 includes a machine room partition member 7 for partitioning the inside of the machine room 1 into right and left.
1 and a machine room blower 72 that ventilates between the spaces partitioned by the machine room partitioning member 71. The compressor 6 is mounted on the left side of the base 3 as viewed from the back, and the machine room blower 70 and the machine room condenser 8 are mounted on the right side.

In the machine room partition member 71, the frame body portion 7a, the mouth ring 7b, the motor stay 7c, and the partition plate portion 7d are integrally formed of synthetic resin such as polypropylene. Accordingly, the frame portion 7a, the mouth ring 7b, the motor stay 7c, and the partition plate portion 7d can be manufactured inexpensively and compactly,
Good storage and assemblability in the narrow machine room 1.
If this effect is not required, the frame body portion 7a,
The machine room partitioning member 71 may be configured by separately forming the mouth ring 7b, the motor stay 7c, and the partition plate portion 7d.

The frame body portion 7a is formed in a frame shape outside the outer periphery of the mouth ring 7b and around the partition plate portion 7d, and enhances the strength of the machine room partition member 71, and the mounting surface for the machine room 1 is I am configuring. The frame body portion 7a is specifically,
Side plate 10, machine room cover 5, evaporation container 63,
It is formed in a shape having an attachment surface to the bottom plate 4, and is attached to these in an airtight manner.

The mouth ring 7b is formed in a circular ring shape in the central portion of the partition plate portion 7d and forms a central opening. The mouth ring 7b has a substantially inner peripheral surface formed as an inclined surface that expands from the center to the left and right machine chambers. Even if a concave portion or a step portion is formed, the inner peripheral surface of the mouth ring 7b has only to be substantially inclined. The mouth ring 7b is positioned so as to overlap the frame portion 7a in the left and right direction of the machine room (axial direction of the machine room blower 72).

The motor stay 7c is composed of a plurality of beam portions extending in the central direction from the side of the machine room 1 of the mouth ring 7b, and a cylindrical motor mounting portion at the center of the beam portions.

The machine room blower 72 includes a machine room partition member 71.
A propeller fan 7 arranged in the center opening of the propeller fan 7 for ventilating the air in the machine room 1 and a fan motor 12 for driving the propeller fan 7.

The propeller type fan 7 includes a cylindrical cup-shaped boss 13a and a plurality of blades 1 integrally formed on the outer periphery thereof.
3 and 3. The blade 13 is formed such that its axial width dimension is larger than the width dimensions of the mouth ring 7b and the frame body portion 7a.
It slightly protrudes toward the compressor side in the axial direction (about 10% of the blade thickness), and the mouth ring 7b and the frame portion 7a.
It is arranged so as to largely protrude toward the condenser in the axial direction. The amount of protrusion from the mouth ring 7b and the frame body portion 7a toward the condenser in the axial direction is particularly important for increasing the ventilation amount of the blades 13 and ensuring ventilation when the condenser is clogged. It is preferably half or more.

The fan motor 12 has one side housed and mounted in the motor stay 7c, and the other side housed in the boss 13a. As a result, the machine room blower 72 is thinned, and the storability in the machine room 1 is improved. The rotation shaft of the fan motor 12 is fixed to the boss 13a, the rotational force of the fan motor 12 is transmitted to the propeller-type fan 7, and this is rotated.

The machine room blower 70 described above has a solid arrow 1 in FIGS. 1 and 5 in a normal state where the condenser is not clogged.
As shown in FIG. 8, it has a function of ventilating air, and compulsorily ventilates the compressor 6 and the machine room condenser 8 arranged in the machine room 1. The ventilation path from the machine room condenser 8 to the machine room blower 70 is formed by a space surrounded by the bottom plate 4, the base 3, the machine room cover 5, and the like.
The fin gap and the gap of the machine room blower 72 are semi-closed spaces.

The air suction part of the machine room 1 is the base 3
The bottom surface suction port 3a is formed on the lower surface of the machine chamber cover 5, and the back surface suction port 5a is formed on one side of the machine chamber cover 5. The lower surface suction port 3a is formed by a large number of slit-shaped openings formed in the base 3 portion located on the suction side of the machine room blower 70 and below the horizontal portion of the machine room condenser 8.
Further, the box body suction port is formed by an air passage in which the corner of the bottom plate 4 facing the machine room 1 is cut out, and is located in front of the suction side of the machine room condenser 8. Further, the back suction port 5a is
It is formed by a large number of slit-shaped openings formed in the machine chamber cover 5 portion located on the suction side of the vertical portion of the machine chamber condenser 8.

The air discharge portion of the machine room 1 is formed by a rear discharge port formed in the machine room cover 5 and a ventilation path in which a corner of the bottom plate 4 facing the machine room 1 is cut out. It consists of a box body discharge port. The rear discharge port is formed by a large number of slit-shaped openings formed in the machine chamber cover 5 portion located on the discharge side of the machine chamber blower 70.
Further, the box body discharge port is formed substantially symmetrically on the opposite side of the box body suction port.

On the other hand, the machine room condenser 8 includes a refrigerant pipe 8
b, the radiation fin 8a, and the side plates 10 and 10A. The refrigerant pipe 8b is formed in a meandering shape with one refrigerant pipe, and is formed in one row in the ventilation direction. The refrigerant inlet 14 of the refrigerant pipe 8b is provided on the side opposite to the air blower (on the upper right end side in FIG. 5). Further, the radiating fins 8a are formed by corrugated fins, and a large number of the fins 8a are arranged side by side so that the refrigerant pipes 8b in each row penetrate therethrough to form a cross fin tube type heat exchanger. In this embodiment, the fin interval is 1.5 mm, and the range of the fin interval is preferably 1.3 mm to 1.8 mm. Further, the side plates 10 and 10A are located on both sides of the heat radiation fin 8a, and are fixed to the refrigerant pipe 8b so that the refrigerant pipe 8b penetrates and projects to both sides.

The machine room condenser 8 is bent by plastic working in a direction intersecting with the longitudinal direction of the refrigerant pipe 8b (bent in a direction intersecting with the blower device side in the axial direction) to have an overall shape. Is formed in an L shape including a horizontal portion and a vertical portion. In other words, the machine room condenser 8 is bent and formed so as to have a three-dimensional shape extending in the left-right, front-rear, and up-down directions. As described above, the machine room condenser 8 includes a horizontal portion that extends in the axial direction that intersects the water surface of the machine room blower 70 and a vertical portion that faces the machine room blower 70.

Further, the horizontal portion of the machine room condenser 8 is arranged so as to extend toward the compressor side in the axial direction rather than the end of the machine room blower 70 on the condenser side in the axial direction. Specifically, the compressor side end of the horizontal part of the machine room condenser 8 has an overlapping part that overlaps the mouth ring 7b and the frame body part 7a of the machine room blower 70 by an overlapping dimension S. In this overlapping portion, a space is formed between the mouth ring 7b and the frame body portion 7a and the heat radiation fin 8a. This space has a space distance L between the frame body portion 7a and the heat radiation fin 8a. As a result, air can flow in from the heat radiating fins 8a of the machine room condenser 8 in the overlapping portion to improve the heat exchange performance. Machine room blower 7 in this overlapping section
A heat insulating material 9 is attached to the facing surface of 0. This allows
Even if the temperature of the machine room condenser 8 rises to a high temperature due to the high-temperature refrigerant gas that flows in, the machine room blower 70 made of resin can be prevented from being deformed.

The side plates 10 and 10A are for holding the machine room condenser 8 with sufficient strength, and are fixed to both ends of the machine room condenser 8. The side plate 10 on one side is formed in a substantially U-shaped cross section and extends in the front-rear direction, the lower flange 10b is screwed to the base 3, and the upper flange 10a is screwed to the frame body portion 7a with the heat insulating material 11 interposed. Has been done. In this way, the machine room partition member 71
Are supported and fixed on the side plate 10. Then, the height Hs of the side plate 10 is set to the radiation fin 8
It is set higher than the height Hf of a. Thereby, the above-mentioned spatial distance L of the overlapping portion is secured. The height of the machine room partition member 71 is adjusted by interposing an intervening member, for example, a metal intervening member between the upper flange 10a and the heat insulating material 11 or between the heat insulating material 11 and the machine room partitioning member 71. You may do it. Also, the other side plate 10
A extends to the lower surface of the bottom plate 4 and is screwed to the bottom plate 4. In addition, since the corrugated fins are used as the radiation fins 8a, the strength of the machine room condenser 8 is increased, and the attachment and the like can be easily performed.

The machine room condenser 8 is positioned substantially horizontally so that its horizontal part faces the lower surface suction port 3a, and its vertical part is substantially vertical so as to face the side plate 2b forming the side wall of the machine room 1. Is installed in the machine room 1. In other words, the end portion of the refrigerant pipe 8b having the meandering bending portion is located in the machine room 1
The refrigerant pipes 8b formed in a meandering shape are arranged in the front and rear directions (extending in the left and right direction of the machine room 1). Therefore, the bent portion at one end of the refrigerant pipe 8b protrudes in the lateral direction (left direction in FIG. 1) which is the longitudinal direction of the machine chamber 1, and the bent portion at the other end is the longitudinal direction of the machine chamber above. Will be projected. As a result, the portions of the refrigerant pipe 8b that project from the side plates 10 and 10A project to the space side of the machine room 1 that has a relatively large margin, so the storage capacity of the machine room condenser 8 is good, and a large machine is provided. Room condenser 8
Can be stored in a narrow machine room 1, and the machine room condenser 8
The amount of heat radiation can be increased.

The end of the horizontal portion of the machine room condenser 8 and the protruding portion of the refrigerant pipe 8b extend to the dead space located below the machine room blower 72.
From this point as well, the storability of the machine room condenser 8 is improved, and the heat radiation amount of the machine room condenser 8 can be increased. Also,
The side plate 10 of the machine room condenser 8 can also serve as a part of the part that separates the suction side and the discharge side of the machine room blower 70, and the ventilation structure can be simplified.

In the machine room condenser 8, one side of the machine room condenser 8 is fixed to the base 3 via the side plate 10, and the other side of the machine room condenser 8 is fixed to the bottom plate 4 via the side plate 10A. It In this way, the base 3 and the bottom plate 4
By fixing the machine room condenser 8 across the above, it can be easily fixed.

When the machine room blower 72 is operated,
The air 28 sucked into the machine room 1 from the lower surface suction port 3a is mainly heat-exchanged through the horizontal part of the machine room condenser 8 and the air 28 sucked from the back surface suction port 5a and the box body part suction port 28 Is mainly heat-exchanged through the vertical portion of the machine room condenser 8, and the heat-exchanged air 28 is blown from the machine room blower 72 to the compressor 6 side, and the air 29 exchanges heat with the compressor 6. After that, it is discharged to the outside of the machine room 1 from the back surface discharge port and the box body discharge port.

Since the machine room condenser 8 is composed of a cross fin tube type heat exchanger having a radiation fin 8a, the heat transfer area per occupied volume can be remarkably increased as compared with the conventional spiral fin type condenser. Available and small machine room 1
A large amount of heat radiation can be obtained even inside.

Further, since the machine room condenser 8 is formed in an L shape having a horizontal portion and a rising portion, the heat transfer area can be increased while suppressing an increase in ventilation resistance. The amount of heat radiation can be increased. In this case, since the corner portion of the bottom plate 4 of the refrigerator box 41 is cut out to form the box body suction port, a portion for attaching the legs 66 to the base 3 is secured and the strength of the base 3 is secured. However, it is possible to obtain a sufficient amount of suction air into the L-shaped machine room condenser 8 having an increased suction area.

In the present embodiment, a cross-fin tube type heat exchanger in which a large number of heat radiation fins 8a are arranged in parallel in a meandering refrigerant pipe 8b is used as the machine room condenser 8 and forced by the machine room blower 70. The machine room condenser 8 is ventilated so that a surface having a large area extends along the ventilation path.
Since the heat transfer area per unit volume in the narrow machine room 1 can be increased, the heat transfer performance of the machine room condenser 8 can be improved, thereby saving the power consumption of the refrigerator. Can be planned. Especially machine room condenser 8
Since the radiating fins 8a are formed in a corrugated shape and the fin pitch thereof is set within the range of 1.3 mm to 1.8 mm, the machine room condenser 8 installed in the narrow machine room 1 is provided with appropriate ventilation resistance. A wide heat transfer area and high heat transfer performance can be achieved, and the performance of the machine room condenser 8 can be significantly improved.

Further, the machine room air blower 70 is constituted by the propeller fan 7 projecting toward the machine room condenser side in the axial direction from the mouth ring 7b provided on the machine room partition member 71 and the frame body portion 7a. From the condenser 8 to the machine room blower 7
The air passage extending to 0 is closed to form a space where the fin gap of the machine room condenser 8 and the gap of the machine room blower 72 are opened, and a machine room having a large area extends along the air passage. Since the condenser 8 is arranged, when the suction side end surface of the machine room condenser 8 is clogged with dust, the machine room condenser 8 moves the machine room blower 72.
The air in the ventilation passage leading to the air passage is agitated by the machine room blower 72 projecting into the ventilation passage, and the propeller fan 7
The air in and out of the condenser side space is carried out through the condenser chamber 8 and the machine room condenser 8 is cooled by the air in the condenser side space. As a result, even if the suction side of the machine room condenser 8 is clogged, the deterioration of the performance of the machine room condenser 8 can be suppressed, and the operating performance of the refrigerator can be ensured. In particular, since the propeller fan 7 is made to project more than half of the propeller fan 7 from the mouth ring 7b toward the machine room condenser 8 side in the axial dimension, the suction side end surface of the machine room condenser 8 is clogged with dust or the like. In this case, the agitation by the machine room blower 72 and the inflow / outflow of air into the condenser side space can be increased, and the cooling of the machine room condenser 8 can be significantly improved.

Further, a cross-fin tube type heat exchanger in which a large number of heat radiation fins 8a are arranged in parallel in a meandering refrigerant pipe 8b is used as a machine room condenser 8 and is formed in a space whose vertical dimension is larger than its depth dimension. The machine room condenser 8 is installed in the machine room 1 such that the meandering bends of the refrigerant pipe 8b are located in the upper and lower parts and the meandering refrigerant pipes 8b are arranged in the front-rear direction. The front-rear width of the portion where the meandering bending portion of the refrigerant pipe 8b, which does not directly contribute, is reduced, so that the machine room condenser 8 can have a large heat transfer area and a large ventilation area even in the narrow machine room 1. As a result, the meandering bending portion of the refrigerant pipe 8b can be reduced and the structure can be made inexpensive, and the performance of the machine room condenser 8 can be improved, and the power consumption of the refrigerator can be saved. In particular, in the case where the bent portion of the refrigerant pipe 8b of the machine room condenser 8 is formed by a separate bent pipe and brazed and welded, the brazing welding points can be reduced, and a large cost reduction can be achieved. .

Further, a cross fin tube type heat exchanger in which a large number of heat radiation fins 8a are arranged side by side in a meandering refrigerant pipe 8b is used as the machine room condenser 8, and its overall shape is left, right, front and back and up and down. Since it is formed by bending so as to have a three-dimensional shape that extends, the machine room condenser 8 can have a large heat transfer area and a large ventilation area even in the narrow machine room 1. As a result, the performance of the machine room condenser 8 is improved with a simple configuration, and power consumption of the refrigerator can be reduced. In particular, the machine room cover 5 is detachably attached to the refrigerator box 41, and the machine room condenser 8 is opposed to the part facing the base 3 which is the bottom wall of the machine room 1 and the side plate 2b serving as the side wall. Since it is formed in a substantially L-shape consisting of a portion to be opened, a large space is exposed between the machine room air blower 70 and the machine room condenser 8 with the machine room cover 5 removed, and this space is opened. Use machine room blower 72
Can be easily maintained and the machine room condenser 8 and the like can be easily attached and detached. Further, since the machine room condenser 8 is composed of one row of cross fin tube type heat exchangers in the ventilation direction, the ventilation resistance is small as compared with the case of being composed of a plurality of rows of cross fin tube type heat exchangers. The air volume can be increased, the heat exchange performance of the machine room condenser 8 can be improved, and the air volume to the compressor 6 can be increased to reduce the compressor temperature.

Further, the machine room condenser 8 is formed by bending the machine room condenser 8 into a substantially L-shape having a horizontal part facing the base 3 which is the bottom wall part of the machine room 1 and a vertical part facing the side plate 2b which is the side wall part. The end of the horizontal part of the machine room condenser 8 is attached to the base 3 via the side plate 10, and the end of the vertical part is attached to the refrigerator box 4 via the side plate 10A.
Since the lower surface suction port 3a is formed in the base 3 part which is attached to the bottom plate 4 which is 1, and which is opposed to the horizontal part of the machine room condenser 8, it is possible to achieve the effect of power saving of the refrigerator. For a refrigerator in which the width of the refrigerator box 41 is increased to increase the capacity, the horizontal portion of the machine room condenser 8 is extended and enlarged, and the lower surface suction port 3a of the base 3 is formed larger along the horizontal portion. As a result, the capacity of the machine room condenser 8 can be increased, and the side plate 1 can be installed without significantly changing the mounting structure of the machine room condenser 8.
It is possible to share 0 and 10 A and share the manufacturing method, and it is possible to easily and inexpensively deal with it. In particular, since the back suction port 5a and the back discharge port are formed on the left and right of the machine room cover 5, the ventilation resistance can be reduced to increase the air volume, and the performance of the machine room condenser 8 can be improved. For a refrigerator in which the width of the refrigerator box 41 is increased to increase the capacity, it is easy to increase the width by keeping the left and right rear suction ports 5a and the rear discharge ports of the machine chamber cover 5 at the same position on both sides. Can respond.

Further, the machine room condenser 8 is formed in a substantially L-shape including a part facing the base 3 which is the bottom wall of the machine room 1 and a part facing the side plate 4b which is the side wall. The room blower 72 is configured to have a propeller-shaped fan 7 arranged so as to project from the mouth ring 7b toward the machine room condenser 8 side, and is arranged above a portion facing the base 3 which is the bottom bottom of the machine room condenser 8. Therefore, the axial dimension (thickness) of the machine room blower 72 can be easily increased,
It is possible to increase the air volume and improve the condenser performance.

As described above, regarding the equipment storage, since the machine room air blower 70 is housed above the machine room condenser 8, the dimension between the left and right can be reduced to zero. On the discharge side of the machine room blower 70, the blades 13 are fixed by the motor stay 7c that does not rotate.
Since it is covered, it is possible to easily secure a safe distance from the compressor 6, the refrigerant discharge pipe and the return pipe around the compressor, the evaporation container 63, and the like. As for the outer shape of the machine room condenser 8, the machine room blower 70 and the machine room condenser 8 can be accommodated in a large size because they overlap.

Further, in the machine room condenser 8, the heat radiation fins 8a are made to enter below the frame body portion 7a of the machine room partitioning member 71 so that ventilation can be performed from the base 3 as well, and continuous lamination between pipes is performed. Since a large amount of heat transfer surface area is secured for the radiating fins 8a and the refrigerant pipes 8b in the shape, high heat radiating ability can be obtained, and the space can be accommodated in a narrow space in the machine room 1 and a ventilation space is also provided. be able to.

Further, since the side of the machine room condenser 8 opposite to the air blower is bent upward so as to intersect with the axial direction, the heat transfer surface area can be further increased. Further, since the lower surface suction port 3a and the back surface suction port 5a are provided so as to correspond to the suction direction to allow a wide suction, it is possible to increase the air volume. As a result, the heat dissipation capability of the machine room condenser 8 can be improved.

Regarding the machine room blower 70, the blades 13
Is projected to the condenser side in the axial direction from the frame portion 7a, wind can be made to sufficiently flow in from the circumferential direction of the blades 13, and in addition to the axial direction of the condenser 3, it is also possible from the direction perpendicular to the axis. The function of suction is obtained, and the shape of the bending arrangement of the machine room condenser 8 corresponding to this, the lower surface suction port 3a of the base 3, and the rear surface suction port 5a of the rear cover 5 can increase the wind, and the heat dissipation capability is improved. Is obtained. In addition, the suction surface of the mouth ring 7b has a slope 7 that gradually advances toward the discharge side as it approaches the blade.
Since b is provided to form the inflow guide, the airflow can be further increased to improve the heat dissipation capability.

Further, the installation of the machine room blower 70 is as follows.
The side plate 10 of the machine room condenser 8 also serves as an advantage in that the number of parts is not increased and the size of the blower for mounting is not required, and the height of the side plate 10 is increased. By adjusting Hs,
There is an advantage that a space with the heat radiation fin 8a can be easily and accurately secured.

Regarding the high temperature heat, there is a space L between the radiation fins 8a and the frame body portion 7a, and the frame body portion 7a of the blower faces the radiation fins 8a located at the overlapping portion.
Since the heat insulating material 9 is attached to the lower surface of the resin, heat from the heat radiation fins 8a can be blocked, and the temperature rise of the resin frame body portion 7a can be suppressed. Further, with respect to the heat coming from the side plate 10 side, the heat insulating material 11 interposed between the frame body portion 7 a and the upper flange 10 a of the side plate 10 is used.
Thus, the temperature rise of the frame body portion 7a of the blower can be suppressed. Also. The high-temperature refrigerant sent from the compressor 6 enters from the side of the machine room condenser 8 which is opposite to the air blower, and the temperature difference between the air and the refrigerant is large. The temperature can be lowered to such an extent that the frame body portion 7a is not deformed. With these, it is possible to prevent the deformation of the resin frame body portion 7a.

Even when the suction side of the machine room condenser 8 is clogged with cotton dust during use of the refrigerator, the blades 13 of the machine room blower 72 protrude from the mouth ring 7b and the frame body portion 7a toward the heat radiation fin 8a side. Therefore, when the ventilation resistance of the propeller fan 7 increases, the discharge flow changes to the centrifugal direction, and the characteristic that the absolute flow velocity is very large can be utilized. That is, in the internal space surrounded by the machine room blower 70 and the machine room condenser 8, the blades 13
A high-speed swirling centrifugal flow is discharged from the outer peripheral projection of
Forced circulation is performed over the whole from the inner surface side of the machine room condenser 8 to the depth between the radiating fins 8a (to the side of the blower device) to remove heat from the machine room condenser 8 or a part of the machine room condenser 8 or The heat is discharged from a portion of the rotating surface of the propeller-shaped fan 7 where the pressure is weak, for example, near the boss, so that the machine room condenser 8 can radiate heat.

The swirling centrifugal flow has little relation to the air volume, is almost governed by the peripheral speed of rotation of the propeller fan 7, and is about 10 times the speed that normally passes between the radiating fins 8a. , The radiation fin 8a at this large speed
The surface heat transfer coefficient of can be remarkably improved.

Next, the flow of the wind will be described in detail with reference to FIG. In FIG. 1, the solid line showing the streamline shows the case where the refrigerator is normally used, and the dotted line showing the streamline shows the case where the suction side of the machine room condenser is clogged.

The blades 13 of this type of propeller fan 7 are
Since the inflow and outflow directions are determined by changing the cross section along the axial direction, high pressure cannot be obtained. In the machine room air blower 70, when the ventilation load (air flow resistance) increases, the air volume from the machine room condenser side suddenly decreases. However, in this case, the inflow component in the axial direction is small, but the blade rotation is still the same, so the force occupied by the swirling component is relatively large, and the outer peripheral side and the center side of the blade 13 are relatively large. Due to the difference in the peripheral speeds, i.e., the difference in static pressure, the flow becomes a centrifugal flow from the central side toward the outer peripheral side. In the air volume-pressure characteristic curve of the machine room blower 70, this change point is called a surging point or a stall point. This point exists at about 70% of the maximum air volume where there is no load. When the air flow exceeds this point, a centrifugal flow suddenly begins to occur, and the centrifugal fan characteristic is created so that the pressure gradually rises to the deadline. . In the characteristic curve of air flow-pressure, the highest pressure point is at the deadline, and this is a value determined by the peripheral speed of the blade 13 which is not related to the air flow. That is, the absolute velocity of the swirling centrifugal flow is very large even at the deadline.

In the present invention, by utilizing the characteristics of the above-mentioned swirling centrifugal flow and the fact that the absolute velocity is large even if the air volume is reduced, to improve the heat exchange capacity, the condenser 6 can be operated more mechanically than ever before. When the heat is collected in a room and requires more heat dissipation than before, sufficient heat dissipation capacity can be obtained, and the machine room condenser 8
Even if the ventilation load becomes large due to the adhesion of dust to the storage room, a predetermined cooling of the storage chamber can be obtained.

That is, in the normal state, as described above, the wind is widely sucked through the machine room condenser 8 including the lower fin portion of the frame body portion 7a as shown by the solid line 18. When the ventilation load becomes large, the blades 13 are moved from the frame body portion 7a to the radiation fins 8
Since it is projected to the a side, as shown by the broken line 19, in the internal space surrounded by the machine room air blower 70 and the machine room condenser 8, the swirling centrifugal flow causes the swirling centrifugal flow from the projecting portion of the blade 13.
After being discharged along b, the heat can be taken by forcibly circulating the inner surface of the machine room condenser 8 deeply (to the side opposite to the blower). In this case, since the swirling flow of the wind is mainly composed of the dynamic pressure component, it sufficiently reaches the heat radiation fins 8a below the frame portion 7a, and can reach the inner heat radiation fins 8a on the side opposite to the air blower while gradually increasing the static pressure. . Since the pressure on the blower shaft center line is low, the air that has taken the heat and becomes hotter returns inside and returns to the boss 13a having a low peripheral speed.
Of the pressure imbalance on the blade rotation surface due to the asymmetry of the ventilation load that is sent out from the vicinity to the compressor 6 side or that comes from the structure of the peripheral equipment of the machine room blower 70, the blower is from the part where the centrifugal action weakens. It can be sent to the original compressor 6 side to radiate heat.

In order to take in these winds, low-temperature air flows from the compressor 5 side through the vicinity of the boss 13a having a small peripheral speed and the gap between the blade 13 and the mouth ring 7b, and the blade 13 is originally Since the protrusion size of the discharge side to the discharge side is reduced to weaken the generation of the centrifugal action on the discharge side, it is induced from the energy balance to a strong swirling centrifugal flow on the machine room condenser 8 side through a part of the blade rotation surface. To be done. When the above-mentioned wind flow has an extremely large ventilation load, that is, the machine room condenser 8 is comparable to the state where the fin inlet surface is clogged with dust, but when this is not the case, between the fins of the condenser 6 But inflow and outflow are done.

As described above, according to this embodiment,
The machine room blower 70 and the machine room condenser 8 can be easily stored in the machine room 1, and a large amount of heat transfer surface area can be obtained to improve the heat dissipation ability, and the heat deformation due to the high temperature due to the improvement of the heat dissipation ability can be prevented. it can. In addition, the condenser, which has been conventionally dispersed in several places, can be integrated in the machine room to a large extent, and the disposal and recyclability of the refrigerator can be improved.

Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a perspective view of an essential part of a machine room of a refrigerator according to a second embodiment of the present invention. This embodiment is the first as described below.
It is different from the embodiment, and other points are basically the same as the first embodiment.

In the present embodiment, when the machine room air blower 20 and the machine room condenser 21 are arranged vertically, a bridge-like one that straddles the upper side of the radiation fin 21a is separately prepared as the mounting base 22. The machine room blower 20 is attached to the mounting base 22.
The frame body portion 20a is supported and fixed, and the leg portion 2 of the mount 22 is attached.
2a is fixed to the base 3. As a result, in addition to the effects similar to those of the first embodiment, it is particularly easy to optimally select the spatial distance between the condenser fins 21a and the axial overlap dimension S between the blower 20 and the fins 21a. Since the machine room blower 20 and the machine room condenser 21 do not come into direct contact with each other, there is a feature that mutual vibrations can be insulated. A heat insulating material 23 is provided between the mount 22 and the frame body portion 20a to prevent thermal deformation of the frame body portion 20a.
The heat insulating material 23 is sandwiched between the frame body portion 20a and the side plate 23 of the condenser 21 to serve also as a wind seal.

Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 7 is a perspective view of an essential part of a machine room of a refrigerator according to a third embodiment of the present invention. This embodiment is the first as described below.
It is different from the embodiment, and other points are basically the same as the first embodiment.

This embodiment is another embodiment in which the machine room blower 24 and the machine room condenser 25 are arranged vertically, and the mount 26 is attached to the return pipe 25d of the machine room condenser 25. A bridge-shaped member that straddles the upper side is separately prepared, and the frame body 24a is fixed to the mounting base 26.
The leg portion 26a of the above is fixed to the base 3. As a result, in addition to the effect similar to that of the first embodiment, in particular, the effect that the space distance L between the machine room air blower 24 and the radiation fin 25a can be easily selected optimally is obtained, and Since the machine room condenser 25 is not in direct contact with the machine room blower 24, it is possible to prevent deformation of the frame 24a of the machine room blower 24 and to insulate mutual vibration. Mounting base 26
The elastic member 27 is provided between the frame body 24a and the frame body 24a, so that the vibration of the machine room blower 24 can be reduced from being transmitted to the base 3.

Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a perspective view of an essential part of a machine room of a refrigerator according to a fourth embodiment of the present invention. This embodiment is the first as described below.
It is different from the embodiment, and other points are basically the same as the first embodiment.

This embodiment is an embodiment in which the bending work when manufacturing the machine room condenser 29 is eliminated. That is, the heat-radiating fins 29a are stacked along the axial direction according to the axial flow suction of the machine-room blower 28, and the pipes 29b are inserted at right angles to the heat-radiating fins 29a in the same room. The exchanger is composed of a pair in the horizontal direction and the vertical direction.

According to this embodiment, in addition to the same effect as the first embodiment, in particular, the direction of the radiation fins 29a is along the axial direction of the machine room blower 28.
Low-temperature air can be easily taken in from the heat radiation fins 29a below the frame portion 28a, the effect of the overlapping portion can be enhanced, and when the refrigerator is used in close contact with the wall surface, below the base 3. It has the feature that it can capture a lot of body. Further, the refrigerant inlet 30 for the high-temperature gas is the uppermost pipe section on the condenser side which is located on the side opposite to the blower and arranged vertically, and then, meanderingly passes through the horizontal section, so that the refrigerant is blown by the blower 28. There is an advantage that the temperature is sufficiently lowered when approaching to the side, and there is no fear of causing thermal deformation to the resin parts or the like that form the blower 28. Bending technology is not required for manufacturing as well.

[0076]

According to the present invention, it is possible to obtain a refrigerator in which the performance of the machine room condenser can be improved to save power.

Further, according to the present invention, the performance of the machine room condenser can be improved to save electric power, and even if the suction side of the machine room condenser is clogged due to the adhesion of dust or the like, the machine room condenser It is possible to obtain a refrigerator in which the operation performance of the refrigerator can be secured by suppressing the deterioration of the condenser performance.

[Brief description of drawings]

FIG. 1 is a schematic rear sectional view showing a machine room portion of a refrigerator according to a first embodiment of the present invention.

FIG. 2 is a vertical sectional view of the refrigerator.

FIG. 3 is a front view of the refrigerator.

FIG. 4 is a refrigeration cycle diagram of the refrigerator.

FIG. 5 is a perspective view of a main part of a machine room of the refrigerator.

FIG. 6 is a perspective view of a main part of a machine room of a refrigerator according to a second embodiment of the present invention.

FIG. 7 is a perspective view of an essential part of a machine room of a refrigerator according to a third embodiment of the present invention.

FIG. 8 is a perspective view of an essential part of a machine room of a refrigerator according to a fourth embodiment of the present invention.

FIG. 9 is a perspective view of a main part of a machine room of a conventional refrigerator.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Machine room, 2a, 2b ... Side plate, 3 ... Base, 3a ... Lower surface suction port, 4 ... Bottom plate, 5 ... Machine room cover, 5a ... Back surface suction port, 6 ... Compressor, 7 ... Propeller fan, 7a ... Frame part, 7b ... Mouth ring, 7c ... Motor stay, 7d
... Partition plate section, 8 ... Machine room condenser, 8a ... Radiating fins, 8
b ... Refrigerant pipe, 9 ... Insulation material, 10 ... Side plate,
10a ... upper flange, 10b ... lower flange, 11 ... heat insulating material, 12 ... fan motor, 13 ... blades, 13a ... boss,
14 ... Refrigerant inlet, 16 ... Cooler, 41 ... Refrigerator box,
41a ... Outer box, 41b ... Inner box, 41c ... Insulation material, 63 ...
Evaporation container, 70 ... Machine room blower, 71 ... Machine room partition member, 72 ... Machine room blower, Ls ... Spatial distance, Hs ... Side plate height, Hf ... Fin height, S ... Overlap dimension.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hideo Ochiai             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division F-term (reference) 3L045 AA04 AA07 BA01 CA02 DA02                       EA01 PA04 PA05

Claims (11)

[Claims] 1. A refrigerator box in which a machine room is formed at a lower corner of a rear surface, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected by a refrigerant pipe, and the compressor and the machine room condenser. A machine room blower for forced ventilation, wherein the machine room is formed horizontally long over the entire width of the refrigerator box, the compressor is installed on one side in the left-right direction,
The machine room condenser is installed on the other side in the left-right direction, and the machine room condenser is composed of a cross fin tube type heat exchanger in which a large number of heat radiation fins are arranged in parallel in a meandering refrigerant pipe. The machine room blower is configured to ventilate air in the machine room in the left-right direction, and the machine room condenser has a left-right part extending in the left-right direction. A refrigerator characterized in that it is overlapped in the left-right direction with respect to the machine room air blower, and a space portion serving as a suction ventilation path is formed between the overlapping machine room condenser and the machine room air blower. 2. The side plate located on the machine room air blower side of the machine room condenser is used as an air blower mounting base, and the height of the side plate is larger than the height of the heat radiation fins. A refrigerator characterized in that a space is formed between the heat radiation fin portion and the machine room blower to form a suction air passage. 3. The machine room condenser according to claim 1, wherein upper and lower parts of the side plate located on the machine room blower side of the machine room condenser are bent toward the anti-radiation fin side to form a flange portion, and the upper flange portion is attached to the blower device. A refrigerator comprising a base and the lower flange portion fixed to a base forming the machine chamber. 4. The machine room blower according to claim 1, wherein the machine room blower is supported on a bridge-shaped mount that straddles the heat dissipation fin section of the machine room condenser, and the heat dissipation fin section of the machine room condenser and the machine room blower. A refrigerator characterized in that a space portion serving as a suction air passage is formed between the refrigerator and the space. 5. The machine room blower according to claim 1, wherein the machine room blower is supported by a mount that covers a refrigerant pipe portion protruding from a heat radiation fin located on the machine room blower side of the machine room condenser. A refrigerator having a lower side fixed to a base forming the machine room. 6. The refrigerator according to claim 1, wherein a heat insulating material is attached to a surface of the machine room blower corresponding to the radiation fin of the machine room blower. 7. The refrigerator according to claim 1, wherein the refrigerant inlet of the machine room condenser is on the side opposite to the machine room blower. 8. The refrigerator according to claim 2 or 3, wherein a heat insulating material is interposed between the machine room blower and a mounting base for supporting the machine room blower. 9. A refrigerator box in which a machine room is formed at a lower corner of a rear surface, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected by a refrigerant pipe, and the compressor and the machine room condenser. A machine room blower for forced ventilation, wherein the machine room is formed horizontally over the entire width of the refrigerator box, and the compressor is installed on one side in the left-right direction thereof,
The machine room condenser is installed on the other side in the left-right direction, and the machine room condenser is composed of a cross fin tube type heat exchanger in which a large number of heat radiation fins are juxtaposed in a meandering refrigerant pipe. The machine room blower has a propeller-shaped fan and a mouth ring, and is installed in the center of the machine room in the left-right direction,
It is configured to ventilate between the space on the machine room condenser side and the space on the compressor side, and the propeller-shaped fan is installed so as to project toward the machine room condenser side in the axial direction from the mouth ring, and the mouth ring The refrigerator is characterized in that the substantially inner peripheral surface thereof is an inclined surface that expands toward the machine room condenser side in the axial direction. 10. The propeller fan according to claim 9, wherein the propeller fan is installed so as to slightly project from the mouth ring toward the compressor side, and the mouth ring of the propeller fan has a substantially inner peripheral surface axially facing the compressor. Refrigerator with an inclined surface that expands to the side. 11. The machine room condenser according to claim 1, wherein the machine room condenser is formed by combining a condenser extending in the left-right direction of the machine room and a condenser extending in a direction intersecting the left-right direction. And a refrigerator.