JP2008111664A - refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To save electric power by enhancing performance of a machine room condenser, in a refrigerator, and to restrain the performance of the machine room condenser from getting low to secure operation performance of the refrigerator even when dust or the like is deposited to plug a suction side of the machine room condenser. <P>SOLUTION: This refrigerator is installed with a compressor 6 in a lateral-directional one side of a machine room 1 and the machine room condenser 8 in the other side, the machine room condenser 8 is constituted of a heat exchanger with a large number of heat radiation fins 8a juxtaposed in a refrigerant pipe 8b formed into a meandering shape, a propeller-shaped fan 7 is installed to be projected toward a machine room condenser side in an axial direction of a mouth ring 7b, and a substantial inner circumferential face of the mouth ring 7 is formed into a sloped face expansion-opened to the machine room condenser side along the axial direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

  A conventional household refrigerator (prior art 1) will be described with reference to FIG.

  This household refrigerator is composed of a refrigerator box, a refrigerator door, a refrigeration cycle, and the like. And this refrigerator box is comprised from the outer box made from a steel plate, the inner box made from a synthetic resin, and the heat insulating material made from the urethane foam filled among these, and forms the some storage chamber. The refrigerator door is provided so as to open and close the storage room.

  In this refrigeration cycle, a compressor 144 that boosts and circulates refrigerant, condensers 145 to 147 as heat exchangers that release heat to the outside of the cabinet, a dew-preventing heat radiating pipe, and a storage chamber that is installed inside the cabinet to cool the storage chamber An evaporator 149 as a heat exchanger, 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, and the like. ing.

  The condensers 145 to 147 are a machine room condenser 145 installed in the machine room 141 at the lower back of the refrigerator box body and forcedly ventilated by the machine room blower 152, and a refrigerator box as a natural convection type condenser. It is comprised in the form which used together the box condensers 146 and 147 of the form which contacted the outer case made from steel plates near the outer surface in the heat insulation wall of a body, and embedded the refrigerant | coolant pipe | tube. The machine room condenser 145 has a connection port for the discharge pipe 153 on the anti-compressor side (anti-blower side), and the temperature of the refrigerant gas flowing in from the connection pipe 153 is generally a high temperature exceeding 180 ° C. . Moreover, the box condensers 146 and 147 are installed on both side surfaces of the refrigerator box.

  The forced ventilation type machine room condenser 145 requires the formation of an air passage and the power of a blower or the like, but can prevent heat from entering the inside of the cabinet and at the time of disposal of the refrigerator, the machine room condenser 145. Can be easily separated, and there is an advantage that power saving of the refrigerator can be achieved by high performance. On the other hand, the box condensers 146 and 147 have a simple structure and do not require power from a blower or the like, but incur performance degradation due to heat penetration from the box condensers 146 and 147 into the cabinet, It has a drawback that it is difficult to separate the box condensers 146 and 147 from the heat insulating wall when the refrigerator is disposed of.

  As the forced ventilation type machine room condenser 145 described above, a spiral fin type machine room condenser 145 is used in which a refrigerant pipe spirally wound with a belt-like fin is meandered in a three-dimensional shape. The spiral fin-type machine room condenser 145 is installed in the machine room 141 at the lower back of the refrigerator box, and is forcibly cooled by the cooling air ventilated by the machine room air blower 152 installed in the machine room 141. .

  The machine room blower 152 includes a machine room partition member 152a that divides the machine room into left and right compressor room sides and a condenser side, and a machine room blower 152b including a propeller fan and a fan motor. Yes. The machine room partition member 152a is made of resin from the viewpoint of price and productivity. The propeller fan of the machine room blower 152b is completely stored in the machine room partition member 152a including both ends in the axial direction, and sucks the wind only from the plane perpendicular to the axial direction. On the premise of this, the machine room condenser 145 is simply juxtaposed so as to face the axial direction of the propeller fan, and the air flows only in the axial direction on the suction side of the propeller fan.

  In addition, as a thing relevant to this prior art 1, there exists what was described in Unexamined-Japanese-Patent No. 7-318222 (patent document 1) and Unexamined-Japanese-Patent No. 11-212316 (patent document 2).

On the other hand, in the refrigerated showcase (prior art 2) described in Japanese Utility Model Publication No. 58-119178 (Patent Document 3), a refrigerated showcase box having a large machine room on the entire bottom surface, and a rear part of the machine room , The compressor placed in the front of the machine room, the filter placed in the suction part of the cross-fin tube condenser, and two machines forcibly ventilating the compressor and the condenser Room fan. In the machine room, an inclined air suction port is formed at the corner of the lower front surface, and an air discharge port is formed at the lower back surface. The cross fin tube type condenser is composed of a cross fin tube type heat exchanger in which a large number of fins are arranged in parallel so as to intersect two rows of refrigerant pipes, and the refrigerant pipe extends left and right, and its bent portion is left and right. It is located on both sides and is inclined to be high and flat in the front. 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.
JP-A-7-318222 JP 11-2111316 A Japanese Utility Model Publication No. 58-119178

  However, the prior art 1 has an advantage that the spiral fin condenser 145 can be formed in any shape in the vertical, horizontal and depth directions according to the installation space of the machine room 141. On the other hand, it is necessary to provide a large gap between each stage and each row in order to prevent rubbing sound accompanying fin contact in the vertical and horizontal directions, and a large gap between the walls constituting the machine room. It was necessary to install. Further, since the discharge pipe 153 is connected on the machine room air blower side of the machine room condenser 145 and the machine room air blower side of the machine room condenser 145 becomes high temperature, the machine room partition member 152a made of resin is not deformed. Thus, it is necessary to dispose the machine room condenser 145 as far as possible in the axial direction from the machine room partition member 152a. For this reason, the heat transfer area per occupied volume of the spiral fin condenser 145 is low. As a result, it is difficult to secure a sufficient amount of heat dissipation and achieve high performance with the spiral fin-type condenser 145 installed in the machine room 141 constituted by a narrow space, and power saving of the refrigerator can be achieved. There was a difficult problem.

  On the other hand, Prior Art 2 relates to a refrigerated 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. Is completely different. In other words, in the prior art 2, it is shown that the cross fin type condenser is inclined to increase the suction area to reduce the number of times the filter is cleaned due to dust clogging. 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 remove the filter, and it is difficult to clean the filter. Further, in the prior art 2, power consumption is improved by improving the performance of the machine room condenser in a narrow place such as a machine room formed in the lower corner of the back of the refrigerator box, and this is an inexpensive configuration. Further, there is no description about achieving it while improving the assemblability, and dealing with capacity change by changing the width of the refrigerator box.

  The object of the present invention is to improve the performance of the machine room condenser to save power, and to reduce the performance of the machine room condenser even if dust or the like adheres to the suction side of the machine room condenser. It is providing the refrigerator which can suppress the noise and can ensure the driving performance of the refrigerator.

  Means of the present invention for achieving the above object includes a refrigerator box having a machine room formed at a back corner, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected by a refrigerant pipe, and the compressor And a machine room air blower that forcibly ventilates the machine room condenser, the machine room is formed horizontally across the entire width of the refrigerator box, and 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 constituted by a heat exchanger in which a large number of heat radiation fins are arranged in parallel on a refrigerant pipe formed in a meandering manner, The apparatus has a propeller-type fan and a mouth ring, is installed in the center in the left-right direction of the machine room, and is configured to ventilate between the space on the machine room condenser side and the space on the compressor side, The propeller fan is more axial than the mouth ring In installed to protrude in the machine room the condenser side, the mouth ring is to have an inclined surface expanding in a machine room condenser side thereof substantially inner circumferential surface in the axial direction.

  According to the present invention, it is possible to improve the performance of the machine room condenser to save power and to reduce the performance of the machine room condenser even if dust or the like adheres to the suction side of the machine room condenser. Thus, a refrigerator capable of ensuring the driving performance of the refrigerator can be obtained.

  Hereinafter, several examples of the refrigerator of the present invention will be described with reference to the drawings. In the second and subsequent embodiments, a part of the configuration common to the first embodiment is omitted, and a duplicate description is omitted. The same reference numerals in the drawings of the respective embodiments indicate the same items.

  The overall configuration of the refrigerator according to the first embodiment of the present invention will be described with reference to FIGS. 2 is a longitudinal 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 41 is composed of a steel plate outer box 41a, a synthetic resin inner box 41b, and a foamed urethane heat insulating material 41c filled therebetween. A plurality of storage chambers 42 to 46 are formed. In the storage chambers 42 to 46, a refrigeration chamber 42, a vegetable chamber 43, a switching chamber 44, an ice making chamber 45, and a freezing chamber 46 are formed independently from above. Each storage chamber 42-46 is provided with doors 47-51. These refrigeration room 42, vegetable room 43, switching room 44, ice making room 45, and freezing room 46 have functions as respective ordinary general storage rooms, and detailed description thereof will be omitted.

  And the machine room 1 is formed in the corner | angular part of the back surface lower part of the refrigerator box 41, In this machine room 1, the compressor 6, the evaporation container 63, the machine room air blower 70 (refer FIG. 1), machine room condenser 8 (see FIG. 1) and the like are arranged. The machine room 1 has a top wall portion and a front wall portion formed of a bottom plate 4 (see FIG. 1) of a refrigerator box 41, and both side wall portions of side plates 2a and 2b (see FIG. 1) of the refrigerator box body 41. The bottom wall portion is formed by the base 3, and the back wall portion is formed by the machine room cover 5. 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 closed space except for a ventilation port including a suction port and a discharge port. The machine room cover 5 is detachably attached to the refrigerator box 41 with screws or the like. 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 16 a is arranged on the back side of the vegetable compartment 43. The refrigerating room blower 53 is a cooling air blower dedicated to the refrigerating room evaporator 16 a and is disposed in the ventilation path of the refrigerating room evaporator 16 a, and cool air from the refrigerating room evaporator 16 a is supplied to the refrigerating room 42 and the vegetable room 43. Supply. The freezer compartment evaporator 16 b is disposed on the back side of the switching chamber 44, the ice making chamber 45, and the freezer compartment 46. The freezer compartment blower 55 is a blower for cold air ventilation dedicated to the freezer compartment evaporator 16b, and is disposed in the ventilation path of the freezer compartment evaporator 16b, and the cold air from the freezer compartment evaporator 16b is switched to the switching chamber 44, the ice making room 45, Supply to freezer compartment 46. Each of the evaporators 16a and 16b is supplied with a refrigerant by the compressor 6, and forms a part of the refrigeration cycle to perform a 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 heat exchanger, a box condenser 59 embedded with a refrigerant pipe, a dew prevention heat radiation pipe 60, The first capillary 15a and the refrigerator compartment evaporator 16a or the second capillary 15b, the freezer compartment evaporator 16b, and the compressor 6 are connected by a pipe in this order to constitute a refrigeration cycle. The capillary 15 includes a first capillary 15a and a second capillary 15b, and the evaporator 16 includes a first evaporator 16a and a second evaporator 16b.

  The compressor 6 and the machine room condenser 8 are disposed in the machine room 1 and forcedly ventilated by the machine room blower 70. The box condenser 59 is a natural convection type condenser in which a refrigerant pipe is embedded in contact with one side surface of the outer box 41 a in the heat insulating material 41 c of the refrigerator box 41. The anti-dew heat radiating pipe 60 is disposed between the outer box 41a and the heat insulating material 41c along the front opening of the refrigerator box 41, and prevents dew on the front part of the outer box 41a.

  Thus, as shown by the arrows in FIG. 4, the refrigerant is compressed by the compressor 6 to become high temperature and high pressure and reaches the machine room condenser 8, and is radiated by the machine room condenser 8 to decrease the temperature. The heat is further radiated by the body condenser 59, and the front surface of the outer box 41a is heated by the dew prevention heat radiating pipe 60 to prevent dew, and the first capillary 15a is depressurized to reach the refrigerator compartment evaporator 16a. The pressure is reduced by the two capillaries 15b and divided into the flow reaching the freezer compartment evaporator 16b, and is evaporated by the respective refrigerator compartment evaporator 16a and the freezer compartment evaporator 16b to take heat away from the surroundings, in a low temperature and low pressure state. Then, the cooling operation is performed by returning to the compressor 6 and repeating this.

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

  In this refrigeration cycle, as will be described later, since the heat radiation amount is greatly increased as the machine room condenser 8 using the cross fin tube heat exchanger, the box condenser 59 of the refrigerator box 41 is greatly increased. Can be reduced. Therefore, the heat intrusion from the box condenser 59 into the storage chamber can be greatly reduced, the power consumption of the refrigerator can be reduced, and the box condenser 59 at the time of disposal of the refrigerator is provided with the heat insulating material 41c. It becomes easy to separate from the refrigerator, and the disposal of the refrigerator can be easily performed. In addition, it is preferable to delete 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, easy disposal of the refrigerator, and cost reduction can be achieved.

  Next, a detailed configuration related to 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 part 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 part.

  The machine room 1 is formed in a substantially rectangular parallelepiped space that is horizontally long and vertically long, that is, a space having a vertical dimension larger than the depth dimension and a horizontal dimension larger than the vertical dimension. Specifically, the upper portion of the front wall portion is inclined and the central portion of the back surface slightly protrudes rearward. The compressor 6 is disposed on one side of the machine room 1 in the left-right direction, and the machine room condenser 8 is disposed 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 71 that partitions the inside of the machine room 1 into left and right sides, and a machine room blower 72 that ventilates a space partitioned by the machine room partition member 71. On the base 3, the compressor 6 is mounted on the left side 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 a synthetic resin such as polypropylene. Thereby, the frame part 7a, the mouth ring 7b, the motor stay 7c, and the partition plate part 7d can be manufactured inexpensively and compactly, and the storage property and the assembly property in the narrow machine room 1 are good. In addition, when this effect is not required, the frame part 7a, the mouth ring 7b, the motor stay 7c, and the partition plate part 7d may be formed separately to constitute the machine room partition member 71.

  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. The frame body portion 7a increases the strength of the machine room partition member 71 and constitutes a mounting surface to the machine room 1. Yes. Specifically, the frame body portion 7a is formed in a shape having attachment surfaces to the side plate 10, the machine room cover 5, the evaporation container 63, and the bottom plate 4, and is airtightly attached thereto. .

  The mouth ring 7b is formed in a circular ring shape at the central portion of the partition plate portion 7d, and forms a central opening. The mouth ring 7b is formed in an inclined surface whose substantial inner peripheral surface expands from the center to the left and right machine room side. Even if the inner peripheral surface of the mouth ring 7b is formed with a concave portion or a stepped portion, the substantial inner peripheral surface may be inclined. Further, the mouth ring 7b is positioned so as to overlap with the frame body portion 7a in the left-right direction of the machine room (the axial direction of the machine room blower 72).

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

  The machine room blower 72 is disposed in the central opening of the machine room partition member 71 and includes a propeller fan 7 that ventilates the air in the machine room 1 and a fan motor 12 that drives the propeller fan 7.

  The propeller fan 7 is composed of a cylindrical cup-shaped boss 13a and a plurality of blades 13 integrally formed on the outer periphery thereof. The blade 13 is formed so that its axial width is larger than the width of the mouth ring 7b and the frame portion 7a, and slightly protrudes toward the compressor in the axial direction from the mouth ring 7b and the frame portion 7a (blade thickness). And approximately larger than the mouth ring 7b and the frame body portion 7a in the axial direction. The protruding amount toward the condenser side in the axial direction from the mouth ring 7b and the frame body portion 7a is, in particular, the blade width of the blade 13 in order to increase the normal ventilation amount of the blade 13 and to ensure the ventilation when the condenser is clogged. It is preferable to make it more than half.

  One side of the fan motor 12 is housed and mounted in the motor stay 7c, and the other side is housed in the boss 13a. Thereby, the machine room blower 72 is thinned, and the storage property in the machine room 1 is good. 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 fan 7, and this is rotated.

  The machine room blower 70 described above has a function of passing air as shown by a solid line arrow 18 in FIGS. 1 and 5 in a normal state where the condenser is not clogged, and is disposed in the machine room 1. Forced ventilation to the machine 6 and the machine room condenser 8. The ventilation path from the machine room condenser 8 to the machine room air blower 70 is constituted by a space surrounded by the bottom plate 4, the base 3, the machine room cover 5, and the like. And it is set as the semi-sealed space which the clearance gap between the machine room air blowers 72 opens.

  The air suction part of the machine room 1 is formed on one side of the machine room cover 5 and a lower face suction port 3 a formed in the base 3, a box part suction port formed by cutting a part of the bottom plate 4. And the rear suction port 5a. The lower surface suction port 3 a is formed by a large number of slit-like openings formed in the base 3 portion located on the suction side of the machine room air blower 70 and below the horizontal part of the machine room condenser 8. Further, the box body suction port is formed by a ventilation path in which a corner portion 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 rear suction port 5a is formed by a large number of slit-like openings formed in the machine room cover 5 portion located on the suction side of the vertical part of the machine room condenser 8.

  And the discharge part of the air of the machine room 1 is the box part formed by the back surface discharge port formed in the machine room cover 5, and the ventilation path which notched the corner | angular part of the bottom face board 4 facing the machine room 1. It consists of a discharge port. The rear discharge port is formed by a large number of slit-like openings formed in the machine room cover 5 portion located on the discharge side of the machine room air blower 70. Moreover, the box part discharge port is formed substantially symmetrically on the opposite side of the box part suction port.

  On the other hand, the machine room condenser 8 includes a refrigerant pipe 8b, heat radiation fins 8a, and side plates 10 and 10A. The refrigerant pipe 8b is formed in a meandering manner 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 anti-blower side (upper right end side in FIG. 5). Moreover, the radiation fin 8a is comprised with a corrugated fin, and many are provided in parallel so that the refrigerant | coolant pipe 8b of each row | line | column may penetrate, and the cross fin tube type heat exchanger is comprised. 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. Furthermore, 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 protrudes on both sides.

  The machine room condenser 8 is bent in a direction intersecting in the longitudinal direction of the refrigerant pipe 8b by plastic working (bent in a direction intersecting the anti-blower side in the axial direction), and the entire shape is horizontal. And a vertical portion. In other words, the overall shape of the machine room condenser 8 is bent so as to have a three-dimensional shape extending in the left and right, front and rear, and up and down directions. As described above, the machine room condenser 8 includes the horizontal portion extending in the axial direction intersecting the water surface of the machine room blower 70 and the vertical portion facing the machine room blower 70.

  Moreover, the horizontal part of the machine room condenser 8 is arrange | positioned so that it may extend in the axial direction from the condenser side edge part in the machine room air blower 70 to the compressor side. 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 part 7a of the machine room air blower 70 by the overlapping dimension S. In this overlapping portion, a space is formed between the mouth ring 7b and the frame body portion 7a and the radiation fin 8a. This space has a spatial distance L between the frame body portion 7a and the heat radiating fins 8a. Thereby, inflow of a wind is enabled from the radiation fin 8a part of the machine room condenser 8 in an overlap part, and the heat exchange performance is improved. The heat insulating material 9 is affixed to the opposing surface of the machine room air blower 70 in this overlapping portion. Thereby, even if the temperature of the machine room condenser 8 rises to a high temperature due to the flowing high-temperature refrigerant gas, it is possible to prevent the machine room blower 70 made of resin from being deformed.

  The side plates 10, 10 </ b> A 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 via the heat insulating material 11. Has been. In this way, the machine room partition member 71 is supported and fixed on the side plate 10. And the height Hs of this side plate 10 is made higher than the height Hf of the radiation fin 8a. Thereby, the spatial distance L of the overlap part mentioned above is ensured. In addition, the height of the machine chamber partition member 71 is adjusted so that an intermediate member, for example, a metal intermediate member, is interposed between the upper flange 10a and the heat insulator 11 or between the heat insulator 11 and the machine chamber partition member 71. You may make it do. The other side plate 10 </ b> A extends to the lower surface of the bottom plate 4 and is screwed to the bottom plate 4. Since corrugated fins are used as the heat radiating fins 8a, the strength of the machine room condenser 8 is increased, and attachment and the like can be easily performed.

  The machine room condenser 8 is positioned almost horizontally so that its horizontal part faces the lower surface suction port 3a, and its vertical part is located almost vertically so that it faces the side plate 2b forming the side wall of the machine room 1. Installed in the machine room 1. In other words, the end portions of the refrigerant pipe 8b with the meandering bent portion are positioned at the upper and lower portions of the machine chamber 1, and the refrigerant pipes 8b formed in a meandering manner are aligned in the front-rear direction (the left-right direction of the machine chamber 1). Installed to extend). Therefore, the bent portion at one end of the refrigerant pipe 8b protrudes in the horizontal direction (left direction in FIG. 1) which is the longitudinal direction of the machine room 1, and the bent portion at the other end is the upper direction which is the longitudinal direction of the machine chamber. Will protrude. Thereby, since the part which protrudes from the side plates 10 and 10A of the refrigerant | coolant pipe 8b protrudes in the space side in the machine room 1 which has comparatively sufficient margins, the storage property of the machine room condenser 8 becomes favorable, and a large machine The room condenser 8 can be stored in the narrow machine room 1, and the heat radiation amount of the machine room condenser 8 can be increased.

  Further, the end of the horizontal portion of the machine room condenser 8 and the protruding portion of the refrigerant pipe 8 b extend to a dead space located below the machine room blower 72. Also from this point, the storage capacity of the machine room condenser 8 is improved, and the heat radiation amount of the machine room condenser 8 can be increased. Moreover, a part of the part which partitions the suction side and discharge side of the machine room air blower 70 can be shared by the side plate 10 of the machine room condenser 8, 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. Thus, by fixing the machine room condenser 8 across the base 3 and the bottom plate 4, it can be easily fixed.

  Thus, 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 portion of the machine room condenser 8, and the rear surface suction port 5a. The air 28 sucked from the box body suction port mainly exchanges heat through the vertical part of the machine room condenser 8, and the heat-exchanged air 28 is blown out from the machine room blower 72 to the compressor 6 side. After the air 29 exchanges heat with the compressor 6, the air 29 is discharged to the outside of the machine room 1 from the rear discharge port and the box body discharge port.

  Since the machine room condenser 8 is composed of a cross fin tube heat exchanger having heat radiating fins 8a, the heat transfer area per occupied volume can be remarkably increased as compared with the conventional helical fin condenser, and it is narrow. A large amount of heat radiation can be obtained even in the machine room 1.

  Furthermore, since the machine room condenser 8 is formed in an L shape composed of a horizontal portion and a rising portion, the heat transfer area can be increased while suppressing an increase in ventilation resistance, and the amount of heat radiation can be reduced. Can be increased. In this case, the corner portion of the bottom plate 4 of the refrigerator box 41 is cut out to form the box body suction port, so that a portion for attaching the leg 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 air sucked into the L-shaped machine room condenser 8 having an increased suction area.

  In this embodiment, a cross fin tube heat exchanger in which a large number of radiating fins 8a are arranged in parallel to the meandering refrigerant pipe 8b is used as the machine room condenser 8, and forced ventilation is performed by the machine room blower 70. Since the machine room condenser 8 is arranged so that the surface having a large area extends along the ventilation path, the heat transfer area per occupied volume in the narrow machine room 1 can be increased, and the transfer of the machine room condenser 8 can be increased. Thermal performance can be improved, and thereby power saving of the refrigerator can be achieved. In particular, since the heat radiation fins 8a of the machine room condenser 8 are formed in a waveform and the fin pitch is set in the range of 1.3 mm to 1.8 mm, the machine room condenser installed in the narrow machine room 1 8 can have a wide heat transfer area and high heat transfer performance with an appropriate ventilation resistance, and can greatly improve the performance of the machine room condenser 8.

  The machine room blower 70 is constituted by the mouth ring 7b provided in the machine room partition member 71 and the propeller fan 7 projecting toward the machine room condenser in the axial direction from the frame part 7a, and the machine room condenser 8 The space around the ventilation path extending from the machine room to the machine room blower 70 is closed to form a space in which the gaps between the fins of the machine room condenser 8 and the machine room blower 72 are opened, and a surface having a large area extends along the ventilation path. Since the machine room condenser 8 is arranged so as to extend, when there is a case where cotton dust adheres to the suction side end face of the machine room condenser 8 and is clogged, the machine room condenser 8 supplies the machine room blower. The air in the ventilation path leading to 72 is agitated by the machine room blower 72 projecting into the ventilation path, and the air is taken into and out of the condenser side space through the propeller fan 7, and the machine room condenser 8 is Air in the condenser side space It is cooled. Thereby, even if the suction side of the machine room condenser 8 is clogged, the performance degradation of the machine room condenser 8 can be suppressed, and the operation performance of the refrigerator can be ensured. In particular, since the propeller fan 7 protrudes more than half in the axial dimension from the mouth ring 7b to the machine room condenser 8 side, dust or the like adheres to the suction side end face of the machine room condenser 8 and is clogged. In this case, the stirring by the machine room blower 72 and the flow of air into and out of the condenser side space can be increased, and the cooling of the machine room condenser 8 can be significantly improved.

  A machine room 1 formed in a space whose vertical dimension is larger than the depth dimension is used as a machine room condenser 8 using a cross fin tube heat exchanger in which a large number of heat radiating fins 8a are arranged in parallel to a meandering refrigerant pipe 8b. Since the machine room condenser 8 is installed so that the meandering bent portions of the refrigerant pipe 8b are located at the upper and lower portions and the refrigerant pipes 8b formed in a meandering manner are arranged in the front-rear direction, it does not contribute directly as a heat transfer portion. The front-rear width of the portion where the meandering bent portion of the refrigerant pipe 8b is reduced, and the machine room condenser 8 having a large heat transfer area and ventilation area even in the narrow machine room 1 can be obtained. Thereby, the meandering bending part of the refrigerant pipe 8b can be reduced and the construction can be made inexpensive, and the performance of the machine room condenser 8 can be improved, and the power saving of the refrigerator can be achieved. 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 cost of brazing can be reduced by reducing the number of brazed welds. .

  Further, a cross fin tube heat exchanger in which a large number of radiating fins 8a are arranged in parallel on a meandering refrigerant pipe 8b is used as a machine room condenser 8, and the overall shape thereof extends three-dimensionally in the left-right, front-back, and up-down directions. Therefore, the machine room condenser 8 having a large heat transfer area and a large ventilation area can be obtained even in the narrow machine room 1. Thereby, with the simple configuration, the performance of the machine room condenser 8 can be improved, and the power saving of the refrigerator can be achieved. In particular, the machine room cover 5 is detachably attached to the refrigerator box 41, and the machine room condenser 8 is opposed to a portion facing the base 3 which is the bottom wall portion of the machine room 1 and the side plate 2b which is the side wall portion. Therefore, when the machine room cover 5 is removed, a large space is exposed between the machine room air blower 70 and the machine room condenser 8, and this space is formed. Utilizing this, maintenance of the machine room blower 72, attachment and removal of the machine room condenser 8 and the like can be easily performed. In addition, since the machine room condenser 8 is configured by a single row of cross fin tube heat exchangers in the direction of ventilation, the ventilation resistance is smaller than that in the case of a plurality of rows of cross fin tube heat exchangers. The air volume can be increased, the heat exchange performance of the machine room condenser 8 can be improved, and the air temperature to the compressor 6 can be increased to reduce the compressor temperature.

  Further, the machine room condenser 8 is bent into a substantially L shape comprising 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 portion of the room condenser 8 is attached to the base 3 via the side plate 10, and the end of the vertical portion is attached to the bottom plate 4 which is the refrigerator box 41 via the side plate 10A. Since the lower surface suction port 3a is formed in the base 3 portion facing the horizontal portion of the condenser 8, the width of the refrigerator box 41 is increased while achieving the effect of saving power in the refrigerator. The capacity of the machine room condenser 8 can be increased by extending the horizontal part of the machine room condenser 8 and increasing the size of the lower surface suction port 3a of the base 3 with respect to the refrigerator having an increased capacity. Can increase , Without significantly changing the mounting structure of the machine chamber condenser 8, can side plate shared and sharing of fabrication methods 10,10A are capable of inexpensively and easily cope. In particular, since the rear suction port 5a and the rear discharge port are formed on the left and right sides of the machine room cover 5, the ventilation resistance can be reduced and the air volume can be increased, and the performance of the machine room condenser 8 can be improved. For a refrigerator whose capacity is increased by increasing the width of the refrigerator box 41, it is easy to increase the width by keeping the left and right back suction ports 5a and back discharge ports of the machine room cover 5 at the same positions on both sides. Can respond.

  Further, the machine room condenser 8 is formed in a substantially L shape including a portion facing the base 3 that is the bottom wall portion of the machine chamber 1 and a portion facing the side plate 4 b that is the side wall portion, and the machine room blower 72. Is disposed above the portion facing the base 3 at the bottom of the bottom of the machine room condenser 8. Therefore, the axial dimension (thickness) of the machine room blower 72 can be easily increased, and the air volume can be increased to improve the condenser performance.

  As described above, since the machine room air blower 70 is housed above the machine room condenser 8 with respect to equipment storage, the size between the left and right sides can be made zero. Since the vane 13 is covered with a motor stay 7c that does not rotate on the discharge side of the machine room air blower 70, a safe distance from the compressor 6, the refrigerant discharge pipe and return pipe around the compressor, the evaporation container 63, and the like is easy. Can be secured. The outer shape of the machine room condenser 8 can also accommodate a larger one by overlapping the machine room air blower 70 and the machine room condenser 8.

  Further, the machine room condenser 8 allows the heat radiating fins 8a to enter the lower part of the frame body part 7a of the machine room partitioning member 71 so as to allow ventilation from the base 3, and the laminated heat radiating fins 8a continuous between the pipes. In addition, since a large heat transfer surface area of the refrigerant pipe 8b is ensured, a high heat dissipation capability can be obtained, and it can be stored in a narrow space in the machine room 1, and a ventilation space can also be provided.

  Moreover, since the anti-blower side of the machine room condenser 8 is bent upward so as to intersect the axial direction, the heat transfer surface area can be further increased. Further, since the lower surface suction port 3a and the rear surface suction port 5a corresponding to the suction direction are provided so as to be sucked in a wide range, the air volume can be increased. Thereby, the improvement of the heat dissipation capability of the machine room condenser 8 is obtained.

  With respect to the machine room air blower 70, the blades 13 are protruded axially from the frame body portion 7a toward the condenser, so that the wind can be sufficiently allowed to flow from the circumferential direction of the blades 13 and the condenser 3 In addition to the axial direction, a function of sucking from the direction perpendicular to the axis is obtained, and the configuration of the bending arrangement of the machine room condenser 8 corresponding to this, the lower surface suction port 3a of the base 3, the rear surface suction port 5a of the rear cover 5, and Can increase wind and improve heat dissipation. In addition, since the inflow guide is formed by providing the suction surface of the mouth ring 7b with the inclined surface 7b that gradually advances toward the discharge side as it approaches the blade, the wind can be increased to improve the heat dissipation capability.

  Moreover, the attachment of the machine room air blower 70 does not increase the number of parts by using the side plate 10 of the machine room condenser 8 and does not require the size of the air blower thickness for attachment. In addition, there is an advantage that the space with the radiation fins 8a can be easily and accurately secured by adjusting the height Hs of the side plate 10.

  Regarding the high temperature heat response, if there is a spatial distance L between the radiating fins 8a and the frame body part 7a, the heat insulating material 9 is placed on the lower surface of the frame body part 7a of the blower so as to face the radiating fins 8a located in the overlapping part. Therefore, the heat from the heat radiating fins 8a can be blocked, and the temperature rise of the resin frame portion 7a can be reduced. Moreover, with respect to the heat coming from the side plate 10 side, the temperature rise of the frame body portion 7a of the blower can be reduced by the interstitial heat insulating material 11 between the frame body portion 7a and the upper flange 10a of the side plate 10. Also. The high-temperature refrigerant sent from the compressor 6 enters from the side of the machine room condenser 8 opposite to the air blowing device, and in addition to the large temperature difference between the air and the refrigerant, the refrigerant temperature passes through one refrigerant pipe. The temperature can be lowered to such an extent that the frame body portion 7a is not deformed. By these, deformation of the resin frame body portion 7a can be prevented.

  Even when the suction side of the machine room condenser 8 is clogged with dust or the like during use of the refrigerator, the blades 13 of the machine room blower 72 are projected from the mouth ring 7b and the frame body part 7a toward the heat radiating fins 8a. Therefore, the propeller fan 7 can take advantage of the characteristic that the discharge flow changes in the centrifugal direction when the ventilation resistance increases, and the absolute flow velocity is very large. That is, in the internal space surrounded by the machine room air blower 70 and the machine room condenser 8, a swirling centrifugal flow having a high speed is discharged from the outer peripheral protrusion of the blade 13, and the heat radiating fins from the inner surface side of the machine room condenser 8. It is forced to circulate all the way between 8a (to the side opposite to the air blower), takes heat from the machine room condenser 8, and a part of the machine room condenser 8 or the pressure of the rotating surface of the propeller fan 7 The machine room condenser 8 can be dissipated by being discharged from a weak portion, for example, near the boss.

  The swirling centrifugal flow has little relationship with the air volume, is almost governed by the rotational peripheral speed of the propeller fan 7, and is about 10 times the normal speed passing between the radiating fins 8a. The surface heat transfer coefficient of the radiating fin 8a can be remarkably improved at a speed.

  Next, the flow of the wind will be described in detail with reference to FIG. In FIG. 1, the solid line indicating the streamline indicates the case where the refrigerator is in a normal use state, and the dotted line indicating the streamline indicates the case where the suction side of the machine room condenser is clogged.

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

  In the present invention, the condenser 6 is more concentrated in the machine room than in the past by utilizing the characteristics of the above-described 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. Thus, sufficient heat dissipation capability is obtained when more heat dissipation is required than before, and predetermined cooling of the storage chamber can be obtained even if the ventilation load becomes large due to dust adhering to the machine room condenser 8 or the like. It is a thing.

  That is, during normal operation, as described above, wind is sucked through the machine room condenser 8 widely including the lower fin portion of the frame body portion 7a as indicated by the solid line 18. When the ventilation load becomes large, the blades 13 are projected from the frame body portion 7a toward the heat radiating fins 8a, so that the internal space surrounded by the machine room blower 70 and the machine room condenser 8 as shown by the broken line 19 , The swirling centrifugal flow is discharged from the protruding portion of the blade 13 along the inclined surface 7b, and then the inner surface of the machine room condenser 8 can be forcibly circulated deeply (to the anti-air blower side) to take heat away. . In this case, since the swirling flow of the wind is mainly composed of the dynamic pressure component, it sufficiently reaches the heat dissipating fins 8a below the frame body part 7a, and can reach the inner heat dissipating fins 8a on the anti-blower side while gradually increasing the static pressure. . Since the pressure on the blower shaft line is lower, the air that has been deprived of heat and raised in temperature returns inside and is sent to the compressor 6 side from the vicinity of the boss 13a where the peripheral speed is low, or the machine Out of the pressure imbalance on the blade rotation surface due to the asymmetry of the ventilation load coming from the structure of the surrounding equipment of the room blower 70, it is sent to the original compressor 6 side of the blower from the part where the centrifugal action is weakened to dissipate heat. Can do.

  In the intake of these winds, low-temperature air flows from the compressor 5 side in the vicinity of the boss 13a where the peripheral speed is small and through the gap between the blade 13 and the mouth ring 7b. Since the generation of the centrifugal action on the discharge side is weakened by reducing the projecting dimension to the discharge side, it is attracted by a strong swirling centrifugal flow on the machine room condenser 8 side through a part on the blade rotation surface from the energy balance. The above wind flow is extremely large when the ventilation load is large, that is, the machine room condenser 8 is dusty and the fin entrance surface is comparable to the clogged state, but if not so much, even between the fins of the condenser 6 Inflow and outflow are performed.

  As described above, according to the present embodiment, the storage capacity of the machine room air blower 70 and the machine room condenser 8 in the machine room 1 is excellent, a large heat transfer surface area can be obtained, and the heat dissipation capability can be improved. Thermal deformation associated with higher temperatures due to improved heat dissipation capability can be prevented. In addition, the condensers that have been dispersed in several places can be concentrated in the machine room, and the disposal and recycling 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 the machine room of the refrigerator according to the second embodiment of the present invention. This embodiment is different from the first embodiment as described below, and is basically the same as the first embodiment in other points.

  In the present embodiment, when the machine room air blower 20 and the machine room condenser 21 are arranged up and down, a mounting bridge 22 that is bridged over the radiating fins 21a is prepared separately. The frame body portion 20a of the machine room blower 20 is supported and fixed to the base room 3, and the leg portion 22a of the mounting base 22 is fixed to the base 3. As a result, the same effects as those of the first embodiment can be obtained, and in particular, the spatial distance between the fins 21a of the condenser and the axial overlap dimension S between the blower 20 and the fins 21a can be easily selected optimally. Since the machine room blower 20 and the machine room condenser 21 are not in direct contact with each other, there is a feature that the mutual vibration can be insulated. A heat insulating material 23 is provided between the mounting base 22 and the frame body portion 20a to prevent thermal deformation of the frame body portion 20a, and the heat insulating material 23 is interposed between the frame body portion 20a and the side plate 23 of the condenser 21. It is also used as a wind seal with a pinch.

  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 the machine room of the refrigerator according to the third embodiment of the present invention. This embodiment is different from the first embodiment as described below, and is basically the same as the first embodiment in other points.

  This embodiment is another embodiment in which the machine room blower 24 and the machine room condenser 25 are arranged up and down, and the mounting base 26 is straddled over the return pipe 25d of the machine room condenser 25. A bridge is prepared separately, the frame 24 a is fixed to the mounting base 26, and the legs 26 a of the mounting base 26 are fixed to the base 3. Thereby, in addition to the same effect as the first embodiment, in particular, the effect of easily selecting the spatial distance L between the machine room air blower 24 and the radiation fins 25a can be obtained optimally. Since the machine room condenser 25 is not in direct contact with the machine room air blower 24, the frame body 24a of the machine room air blower 24 can be prevented from being deformed, and the mutual vibration can be insulated. An elastic member 27 is provided between the mounting base 26 and the frame body 24a, and vibrations of the machine room air 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 the machine room of the refrigerator according to the fourth embodiment of the present invention. This embodiment is different from the first embodiment as described below, and is basically the same as the first embodiment in other points.

  In this embodiment, the bending operation when the machine room condenser 29 is manufactured is eliminated. That is, heat is stored in the machine room 1 in the same place, with the radiating fins 29a laminated in the axial direction along with the axial flow suction of the machine room air blower 28, and the pipe 29b inserted perpendicularly to the axis. The exchanger is configured as a pair in the horizontal and vertical directions.

  According to the present embodiment, in addition to the same effects as those of the first embodiment, in particular, since the direction of the radiating fins 29a is aligned with the axial direction of the machine room air blower 28, the frame body portion 28a Low temperature air can be easily taken in from the lower radiating fins 29a, the effect of the overlapping portion can be enhanced, and when the refrigerator is used in close contact with the wall surface, a large amount can be taken from below the base 3. There are features. Further, the refrigerant inlet 30 for the high-temperature gas is positioned on the side opposite to the air blower and is the uppermost pipe portion on the condenser side arranged in the vertical direction. When approaching the side, there is an advantage that the temperature is sufficiently lowered and there is no fear of causing thermal deformation to the resin parts constituting the blower 28. For production, it does not require bending technology.

1 is a schematic rear cross-sectional view showing a machine room part of a refrigerator according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the refrigerator. It is a front view of the refrigerator. It is a refrigeration cycle figure of the refrigerator. It is a principal part perspective view of the machine room of the refrigerator. It is a principal part perspective view of the machine room of the refrigerator of 2nd Example of this invention. It is a principal part perspective view of the machine room of the refrigerator of 3rd Example of this invention. It is a principal part perspective view of the machine room of the refrigerator of 4th Example of this invention. It is a principal part perspective view of the machine room of the 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 body part, 7b ... Mouth ring, 7c ... Motor stay, 7d ... Partition plate part, 8 ... Machine room condenser, 8a ... Radiation fin, 8b ... Refrigerant pipe, 9 ... Heat insulating material, 10 ... Side plate, 10a ... Upper flange, 10b ... lower flange, 11 ... heat insulating material, 12 ... fan motor, 13 ... blade, 13a ... boss, 14 ... refrigerant inlet, 16 ... cooler, 41 ... refrigerator box, 41a ... outer box, 41b ... inside Box, 41c ... Insulating 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: Overlapping dimensions.

Claims (4)

Refrigerator box having a machine room formed at the corner at the back, a refrigeration cycle in which a compressor, a machine room condenser and an evaporator are connected by a refrigerant pipe, and a machine room air forcibly ventilating the compressor and the machine room condenser With the device,
The machine room is formed horizontally across the entire width of the refrigerator box, the compressor is installed on one side in the left-right direction, and the machine room condenser is installed on the other side in the left-right direction,
The machine room condenser is composed of a heat exchanger in which a large number of heat radiation fins are arranged in parallel on a refrigerant pipe formed in a meandering shape,
The machine room air blower has a propeller fan and a mouth ring, and is installed at the center in the left-right direction of the machine room so as to ventilate between the space on the machine room condenser side and the space on the compressor side. To configure
The propeller-type fan is installed so as to protrude from the mouth ring toward the machine room condenser in the axial direction,
The refrigerator is characterized in that a substantial inner peripheral surface of the mouth ring is an inclined surface that expands in the axial direction toward the machine room condenser.   2. The propeller fan according to claim 1, wherein the propeller fan is installed so as to protrude slightly toward the compressor in the axial direction from the mouth ring, and the mouth ring has its substantial inner peripheral surface expanded in the axial direction toward the compressor. A refrigerator characterized by having an inclined surface.   The refrigerator according to claim 2, wherein the machine room condenser is formed by combining a condenser extending in a left-right direction of the machine room and a condenser extending in a direction crossing the left-right direction.   4. The refrigerator according to claim 1, wherein the machine room condenser is configured by a cross fin tube heat exchanger in which a large number of heat radiation fins are arranged in parallel on a meandering refrigerant pipe. 5.

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