freezer and the refrigerator compartment 4, a door 3a of the freezer compartment and a hinged refrigerator door 4a with hinge respectively to the front sides of the freezer compartment 3 and the refrigerator compartment 4, a heat exchange chamber 5 including an evaporator 6 and a blower fan 7 and placed on the rear side of the freezer compartment 3. In addition, the division 2 is formed with a freezer return duct 21 and a refrigerator return duct 22, to respectively return the cooled air in the freezer compartment 3 and the refrigerator compartment 4 to the heat exchange chamber 5 . A cooled air duct 8 is formed on the rear side of the refrigerator compartment 4 to communicate with the freezer compartment 3 and has a plurality of chilled air discharge orifices 8a. A fourth machine M is formed on the lower rear side of the main body 1 to accommodate a compressor 9 and a condenser (not shown). The air in the freezer compartment 3 and the refrigerator compartment 4 is sucked into the heat exchange chamber 5 by the blower fan 7 of the heat exchange chamber 5 through the freezer return duct 21 and the duct 22 of return of the refrigerator formed in division 2 to undergo heat exchange in the evaporator 6, and is discharged into the freezer compartment 3 and the refrigerator compartment 4 through the chilled air discharge orifices 8a of the air duct 8 cooled, and this cycle repeats itself. At that time, the surfaces of the evaporator 6 are charged due to the temperature difference between the ambient air and the air circulating in the freezer compartment 3 and the refrigerator compartment 4 re-introduced into the evaporator via the duct 21 of return of freezer compartment and refrigerator return duct 22. In order to defrost, the evaporator 6 includes a defrosting heater 10 on the underside thereof, and the defrosting water generated when the frost is thawed is collected in a defrosting water vessel (not shown) provided on the underside of the main room 1 by means of a defrost water discharge tube 11. The fourth M of machine, as shown in
Figure 2, is provided with the compressor 9 to change a low temperature and high pressure gaseous refrigerant in a high temperature and high pressure gaseous refrigerant, a condenser 12 to generate the high temperature and high pressure gaseous refrigerant in a refrigerant ambient temperature and high pressure liquid when performing the heat exchange between the high temperature and high pressure gaseous refrigerant generated by the compressor 9 and the ambient air, and a cooling fan 13 for blowing ambient air introduced in the room M from machine to condenser 12. In general, capacitor 12, as shown in Figure 3, has a tube-like wire structure such that the straight portions of the tube are parallel to each other, the "U" shaped tube portions "are connected to the straight parts of the tube in a zigzag fashion to form a tube 121 of refrigerant in the form of a serpentine and to have multiple layers, and fins 122 Wire cutters with a small circular cross-section are placed in the serpentine-shaped coolant tube 121 and welded thereto by spot welding. In the conventional condenser 12, in order to increase the contact surface between the ambient air blown by the cooling fan 13 and the refrigerant tube 121, as shown in Figure 2, the refrigerant tube 121 has a stepped arrangement formed from the front side facing the cooling fan 13 to the rear side thereof. In other words, the straight portions of the tube and the "U" tube portions of the coolant tube 121 are misaligned therewith in the other layers. In this way, due to the narrow distance between the straight parts of the refrigerant tube 121 in the same layer, since the pneumatic resistance to the air is increased when the ambient air blown by the cooling fan 13 passes through the condenser 12, there is a difference of ambient air flow velocity between the front side and the rear side of the condenser 12, the ambient air passing through the condenser 12, and in this way the cooling efficiency of the condenser 12 is deteriorated and the energy consumption is increased of the same. In this way, the economic value and reliability of the refrigerator deteriorate.
Brief Description of the Invention Therefore, the present invention has been made in view of the above and / or other problems, and it is an object of the present invention to provide a condenser for a refrigerator in which a cooling fan is installed in one side thereof and the difference between the flow velocities on the front side and the rear side of the condenser when the condenser refrigerant is thermally exchanged with the ambient air by the blowing operation of the cooling fan is minimized.
It is another object of the present invention to provide a condenser for a cooler to minimize the difference between the flow rates and increase the heat transfer surface. According to the present invention, the above objects and others can be achieved by a provision of a condenser that includes: an arrangement in lines in which a refrigerant pipe is arranged such that the parts of the refrigerant pipe are arranged in lines in the forward and backward direction; and a stepped arrangement in which the parts of the refrigerant pipe are arranged on the rear side of the array in lines in the forward and backward direction to misalign with each other; and wherein the ratio of the arrangement in lines to the stepped arrangement varies from 50% to 60%, the distance (SI) between the parts of the refrigerant pipe in a row direction varies from 10 mm to 15 mm, a distance ( S2) between the parts of the refrigerant pipe varies from 5 mm to 10 mm. Preferably, the ratio of the line arrangement to the stepped arrangement is 50%, the distance (SI) between the parts of the refrigerant tube in the direction of the rows is 11 mm, and the distance (S2) between the parts of the tube of refrigerant is 6 mm. The coolant tube has radiating fins and bends in a zigzag fashion to have multiple layers. The radiating fins have a screw shape and are formed integrally with the outer circumference of the refrigerant pipe. The refrigerant pipe is constructed such that the extruded parts of the refrigerant pipe are straightened by plastic deformation using rolls, the radiating fins are formed on the outer circumference of the coolant pipe by cutting the outer circumference of the coolant pipe, and the pipe of Coolant formed with the radiating fins is bent into the serpentine form in multiple layers. The radiating fins are formed symmetrically on the outer circumference of the refrigerant pipe and have a plurality of nozzles that penetrate the radiating fins in the vertical direction. The mouths have a rectangular shape. The radiator fins are made of aluminum plates having penetration holes formed in a central portion thereof and fixed around the outer circumference of the refrigerant tube at regular intervals.
BRIEF DESCRIPTION OF THE DRAWINGS OBJECTS AND ADVANTAGES OF THE PRESENT INVENTION WILL BECOME OBVIOUS AND MORE APPELLANT FROM THE FOLLOWING DESCRIPTION OF AN EMBODIMENT, TAKEN IN CONNECTION WITH THE ANNEXED FIGURES, IN WHICH: FIGURE 1 is a view in FIG. schematic vertical section illustrating the structure of a conventional refrigerator; Figure 2 is a partially enlarged rear side view illustrating a machine room of the conventional refrigerator; Figure 3 is a perspective view illustrating the structure of a conventional condenser; Figure 4 is a partially enlarged rear side view illustrating the structure of a machine room of a refrigerator employing a condenser according to a preferred embodiment of the present invention; Figure 5 is a front view illustrating a refrigerant tube according to a first embodiment of the present invention; Figure 6 is an enlarged view of the portion
"A" in Figure 5; Figure 7 is a graph obtained from a first experiment performed in the present invention; Figure 8 is a graph illustrating the amount of heat in Figure 7;
Figure 9 is a graph illustrating the pressure loss of Figure 7 / Figure 10 is a graph illustrating the heat transfer performance of a capacitor used in the first experiment of the present invention; Figure 11 is a graph 2 obtained from a second experiment performed in the present invention; Figure 12 is a graph illustrating the heat transfer performance of a capacitor performed in the second experiment of the present invention; Figure 13 is a graph 3 obtained from a third experiment performed in the present invention; Figure 14 is a perspective view illustrating a refrigerant tube of a condenser according to a second preferred embodiment of the present invention; and Figure 15 is a perspective view illustrating a refrigerant tube of a condenser according to a third preferred embodiment of the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a condenser for a refrigerator according to the preferred embodiment of the present invention will be described in detail with reference to the accompanying Figures. Figure 4 is a back side view illustrating the structure of a machine room of a refrigerator employing a condenser according to a preferred embodiment of the present invention. In general, the machine room of a refrigerator is provided with a compressor 9 for changing a gaseous low temperature and low pressure refrigerant in a high temperature and high pressure gaseous refrigerant, a condenser 12 for condensing the high temperature gaseous refrigerant and high pressure in a liquid refrigerant of room temperature and high pressure when performing the heat exchange between the high temperature and high pressure gaseous refrigerant generated by the compressor 9 with ambient air, and a cooling fan 13 for blowing the ambient air introduced in the machine room M to the condenser 12. In this refrigerator, according to the preferred embodiment of the present invention, the capacitor 12 is structured such that the difference between the flow rates on the front side of the capacitor 12 is minimized. It goes towards the cooling fan 13 and the rear side of the condenser 12. For this purpose, the condenser 12 includes an array 123 in lines provided on the front side of the condenser 12 and a stepped arrangement 124 provided on the rear side of the condenser 12. The array 123 in lines is structured such that the straight portions of a refrigerant tube 121 are parallel to each other. yes, the "U" tube parts of the refrigerant tube 121 are connected to the straight parts of the tube in a zigzag fashion to have multiple layers, and the straight parts of the tube and the "U" shaped tube parts "They line up in other parts of the tube in vertical and horizontal directions. The stepped arrangement 124 is structured such that, like the conventional condenser, the straight portions of the tube and the "U" tube portions of the coolant tube 121 are misaligned therewith in other layers in the horizontal direction. Meanwhile, the stepped arrangement of the conventional condenser 12 serves to increase the contact area between the ambient air blown by the cooling fan 13 and the refrigerant tube 121. When the array 123 in lines is provided on the front side of the condenser 121 as in the present invention, the velocity of the ambient air flow can be increased due to the decrease in air pneumatic resistance. However, the increase in the contact area between the refrigerant tube 121 and the ambient air can not be expected.
However, the capacitor 12 according to the preferred embodiment of the present invention is characterized in that the difference between the air flow velocities on the front side and the rear side of the condenser 12 is minimized and the area is increased Heat transfer of the condenser. To solve the decrease of the contact area between in condenser 12. and the ambient air, the refrigerant tube 121 of the present invention, as shown in Figure 5, is structured in the form of a coolant tube 125 of a screw type heat exchanger. The screw-type heat exchanger, as shown in Figure 6, includes screw-shaped radiating fins 125a formed on the outer circumference of the refrigerant tube 121, and the refrigerant tube 125 formed with the radiator fins 125 is bent at the form of serpentine in multiple layers. The reference number 120 is assigned to the supports to support the sides of the refrigerant tube 125. As described above, the condenser 12 of a refrigerator according to the preferred embodiment of the present invention includes the front side of the capacitor 12 having the array 123 in lines, the rear side thereof having the stepped array 124 such that it is it minimizes the difference between the air flow velocities on the front side and the rear side of the condenser 12 due to the decrease in air pneumatic resistance. In addition, the refrigerant tube 125 that includes the array 123 in lines and the stepped array 124 is manufactured as a refrigerant tube in which the radiating fins 125a are formed in the form of a screw on the outer circumference of the refrigerant tube 125 such that the heat transfer area of the capacitor 12 is increased and the cooling performance of the capacitor 12 is also increased. In doing so, when the capacitor 12 according to the preferred embodiment of the present invention is compared with the conventional wire capacitor in In terms of surface area, the condenser 12 according to the preferred embodiment of the present invention exhibits a cooling performance equal to or greater than the cooling performance of the conventional condenser even when the condenser 12 has a surface area corresponding to 70% of the surface area of the conventional condenser. A heat exchanger used in the condenser should be designed taking sufficient consideration of the heat transfer performance and the distance between the parts of the tube, while the heat transfer performance and the performance of the condenser depend on the distance between the parts of the tube. In general, when the distance between the parts of the tube is increased, the pneumatic resistance of the air is decreased due to the parts of the tube so that the loss of air pressure due to the parts of the tube is reduced. On the other hand, when the distance between the parts of the tube is decreased, the pneumatic resistance of the air is increased due to the parts of the tube so that the loss of air pressure is increased. In this way, heat transfer efficiency and capacitor performance deteriorate. Therefore, since the heat transfer performance and the performance of the heat exchanger used in the condenser are determined according to the distance between the parts of the tube, the optimum distance between the parts of the tube and the optimal arrangement of the Parts of the tube must be determined optimally when the condenser is designed. In order to determine the optimal conditions for the condenser as described above, the applicant of the present invention has performed heat transfer experiments according to variations of the distance between the parts of the tube as follows, and as a result, determined the conditions optimal.
< Experiment 1 > . In this experiment, the heat transfer performance of the capacitor was measured according to the SI distance between the tube portions in the horizontal direction and the distance S2 between the parts of the tube in the vertical direction, and the experimental conditions were substantially identical to the conditions when the condenser applies to a refrigerator. Described in detail, the condense temperature was 37 degrees Celsius (9.5 kg / cm2), the condenser inlet temperature was 65 degrees Celsius, the coolant flow rate was 3.8 kg / h), and flow velocity of air was 1.0 CMM. Both the heat exchangers and the samples to be measured have 10 rows, 8 layers, the SI distances of 8, 11, 14, and 16 mm, and the distance S2 of 6, 9, and 12 mm, respectively. The measurements were made 12 times. The heat exchanger is not restricted to 10 rows and 8 layers and may be the number of layers that can be freely modified. The parts of the condenser tubes are arranged in the stepped arrangement. According to Figure 1 of Figure 7, a No. 1 sample of the heat exchangers is measured under the conditions Sl = 8 mm and S2 = 6 mm, and the amount of heat exhibited (Q (W)) of 92.3 , loss of air pressure (?? (pa)) of 14.8, resulting in a heat transfer performance (Q / (AP) 1/3) of 37.6. On the other hand, a sample No. 4 of the heat exchangers was measured under the conditions of S = ll mm and S2 = 6 mm, and the amount of heat exhibited (Q (W)) of 99.4, loss of air pressure (?? (pa)) of 9.2, resulting in a heat transfer performance (Q / (AP) 1/3) of 47.4. In this way, the difference between sample No. 1 and sample No. 4 in view of heat transfer performance is 9.8. In other words, although sample No. 4 has SI, that is, the distance between the parts of the tube, greater than that of sample No. 1, sample No. 4 exhibits better heat transfer performance than the performance of heat transfer of sample No. 1. According to the results of the experiment, the heat transfer performance increases as the amount of heat increases, in particular samples Nos. 4, 5, 7, 8 exhibit the highest heat transfer performance (see Figure 10). In other words, sample No. 4, under the conditions of Sl = ll mm and S2 = 6 mm, the amount of heat exhibited (Q (W)) of 99.4, loss of air pressure (?? (pa)) of 9.2, resulting in the highest heat transfer performance (Q / (AP) 1/3) of 47.4, and sample No. 5 under the conditions of Sl = ll mm and S2 = 9 mm, exhibited the following performance highest heat transfer performance of 46.9, and sample No. 8 and sample No. 7, in turn. In this way, it is understood that the capacitor exhibits excellent heat transfer performance "under the conditions of Sl = 10 to 15 mm and S2 = 5 mm to 10 mm, in particular, the highest heat transfer performance under the conditions of Sl = ll mm and S2 = 6 mm.
< Experiment 2 > In this experiment, the heat quantity of the heat exchanger according to the ratio of the stepped arrangement and the line arrangement of the parts of the tubes was done five times by changing the arrangement of the parts of the sample tubes that exhibit the highest heat performance under the conditions of Sl = ll mm and S2 = 6 mm, and a heat exchanger having 10 rows and 8 layers was used. According to Figure 2 in Figure 10, when the ratio of the number of parts of the pipe in the arrangement in lines to that of the stepped arrangement is 0:10, that is, when the heat exchanger has only stepped arrangement of the parts of the tube, the heat exchanger exhibited a quantity of heat (Q (W)) of 99.4, loss of air pressure (AP (pa)) of .9.2, resulting in a heat transfer performance (?) / ( ??) 1 3) of 47.4. When the ratio of the number of parts of the pipe in the arrangement in lines to that of the stepped arrangement was 3: 7, that is, when the heat exchanger has 30% line arrangement and 70% staggered arrangement of tube parts, the heat exchanger exhibited heat amount ((Q (W)) of 103.2, pressure loss of air (AP (pa)) of 9.1, resulting in a heat transfer performance (Q / (AP) 1/3) of 49.5 Thus, it can be understood that the heat transfer performance is improved by approximately 2.1 compared to the case of the heat exchanger which has only stepped arrangement of the parts of the tube.When the line arrangement of the parts of the tube was increased to 50%, the heat transfer performance of the heat exchanger was improved by approximately 1.9 However, when the line arrangement of the tube parts was increased more than 70% as in samples Nos. 4 and 5 in Chart 2, the heat exchanger exhibited improved heat transfer performance by 1.2 and 4.4 compared to cas or of the heat exchanger that has 50% of arrangement in lines of the parts of the tube. Therefore, the heat exchanger having 50% line arrangement of the tube parts exhibited the highest heat transfer performance, the heat exchanger having 70% line arrangement of the tube parts exhibited a secondary superior heat transfer performance, and the heat exchanger that has 30% line arrangement of the tube parts exhibited a superior third heat transfer performance. In other words, it is understood that the heat exchanger provided with 50% to 60% line arrangement of the tube parts on the front side of the condenser exhibits an optimal heat transfer performance (see Figure 12).
< Experiment 3 > In this experiment, the refrigeration performance and the energy consumption of a refrigerator were measured according to the ratio of the stepped arrangement and the line arrangement, and it is understood that the relationship has an influence on the cooling speed and the cooling capacity of a refrigerator and the refrigerator's energy consumption due to it. According to Figure 3 in Figure 13, a No. 3 sample under the conditions of 50% line arrangement of the tube parts exhibited the highest cooling speed in the freezer compartment (compartment F) and the compartment Refrigerator (R compartment), the highest cooling performance due to cooling capacity, and the lowest power consumption. In this way, when the capacitor is designed such that the ratio of the arrangement in lines of the parts of the tube to the stepped arrangement of the parts of the tube is from 50% to 60%, SI (the distance between the parts of the tube in the direction of the rows) is from 10 mm to 15 mm, and S2 (the distance of the parts of the tube in the vertical direction) is from 5 mm to 10 mm, the condenser exhibits the highest heat transfer performance, and so Preferred, the capacitor exhibits the optimum efficiency of heat transfer and performance when the ratio of the array in lines is 50%, Sl = ll mm and S2 = 6 mm. The structure of the radiator fins of the condenser according to the preferred embodiment of the present invention, as described above, has the shape of a screw and can be changed in the structure shown in Figures 13 and 14. The radiating fins 125b are formed integrally with the outer circumference of the refrigerant tube 125 to be symmetrically arranged together and to have a plurality of nozzles that penetrate the radiating fins 125b of the vertical direction. The radiator fins 125d as shown in Figure 15, are made of aluminum plates to be affixed to the outer circumference of the coolant tube 125 at regular intervals, such as the fin-general tube heat exchanger. The radiator fins 125b are applied to the condenser heat exchanger when considering the heat transfer efficiency, the intervals and the arrangements of the parts of the tube, and more particularly, the radiator fins 125b satisfy the conditions such that the ratio of the arrangement in lines of the parts of the tube to the stepped arrangement of the parts of the tube is adjusted to 50% to 60%, SI (the distance of the parts of the tube in the direction of the rows) adjusts to 10 mm to 15mm, and S2 (the distance of the parts of the tube in the vertical direction) adjusts to 5 mm to 10 mm. As described above, according to the condenser for a cooler according to the present invention, since the difference between the air flow velocities on the front side and the rear side of the condenser when the exchange of liquid is carried out is minimized. heat of the condenser with the ambient air by the blower operation of the cooling fan installed on one side of the condenser, which improves the condensation efficiency of the condenser and reduces the consumption of the same so that the reliability and economic utility of the condenser is improved .
The difference between the air flow velocities in the condenser is minimized and the radiator tube with radiating fins such as radiating fins is provided in the form of a screw such that the heat transfer area is increased to ensure sufficient transfer area of heat, so that the heat transfer efficiency and the cooling performance of the condenser are improved due to sufficient heat transfer area. Although the preferred embodiment of the present invention has been described for illustrative purposes, those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the invention as described in the appended claims.