JP2007064506A - Cooler - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve cooling efficiency of a radiator by securing the air amount of a flow flowing through a ventilation passage irrespective of an output of a first fan. <P>SOLUTION: The Stirling cooler is provided with a cooler body 1A, a high temperature side condenser 7 for cooling of a high temperature part 2 of a Stirling refrigerating machine 4 provided in the cooler body 1, the ventilation passage 1B passing through air for cooling of the high temperature side condenser 7, and a fan 12C and a fan 8 generating an air flow in the ventilation passage 1B. The fan 8 is provided so as to generate an air flow along a flow of an air flow in a downstream side of an air flow flowing along the ventilation passage 1B generated by the fan 12C, and a passage 1C being a bypass path stretching from an upstream side of the fan 12c to a middle of the fan 12C and the fan 8 is provided on the ventilation passage 1B. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a refrigerator, and more particularly to a refrigerator having a blower fan.

A refrigerator having a blower fan is conventionally known.
For example, Japanese Patent Laying-Open No. 2005-16740 (Patent Document 1) discloses a refrigerator having a blower fan for sending cold air to the top of the refrigerator main body. Here, the air cooled by driving the blower fan is blown to the high-temperature heat radiating section. The high temperature heat radiation part is cooled by this low temperature air. The air that has cooled the high-temperature heat radiating portion is exhausted out of the refrigerator through the discharge port.
JP 2005-16740 A

  In order to effectively cool the above-described high-temperature heat radiation unit, it is desirable to use a large-capacity air passage and a high-power fan. On the other hand, from the viewpoint of reducing the size of the refrigerator, it is desirable to reduce the capacity of the duct through which the air flow from the blower fan flows to some extent. In addition, reduction of power consumption of the blower fan is also required. Therefore, it is necessary to increase the amount of air reaching the high-temperature heat radiating portion under the limited duct capacity and blower fan output.

  This invention is made | formed in view of the above problems, and the objective of this invention is to provide the refrigerator with the high cooling efficiency of a heat radiator.

  The cooler according to the present invention includes a cooler main body, a radiator provided in the cooler main body, a ventilation path through which cooling air of the radiator flows, and first and second fans that generate an airflow in the ventilation path. The second fan is provided on the downstream side of the airflow flowing along the air passage generated by the first fan so as to generate the airflow along the flow of the airflow, and the first fan from the upstream side of the first fan. And a bypass path reaching between the second fan and the second fan.

  According to the above configuration, since the outside air passes directly through the bypass path and is directly guided to the second fan, even if the air volume of the first fan is insufficient, the function of the second fan is not hindered. Therefore, the air volume of the airflow flowing through the ventilation path can be ensured regardless of the output of the first fan. As a result, the cooling efficiency of the radiator is improved.

  Preferably, the refrigerator further includes a drain pan for storing defrosted water from the refrigerator main body. The first fan is provided in the vicinity of the drain pan, and the second fan is provided in the vicinity of the radiator.

  Thereby, the airflow which passed the vicinity of the drain pan which stores defrost water can be guide | induced to the vicinity of a radiator. Since the airflow passing through the vicinity of the drain pan is humid air having a relatively high humidity, the heat transport potential is high, and as a result, the heat dissipation efficiency of the radiator is increased.

  Preferably, the cooler further includes a partition section that divides the ventilation path into a flow path of an air flow generated by the first fan and a bypass path. A portion where the second fan is provided in the air passage is formed to extend vertically. The partition is connected to the horizontal plate provided in accordance with the height of the drain pan, the inclined plate connected to the downstream end of the horizontal plate, and the downstream end of the inclined plate, and the airflow from the first fan And a vertical rectifying plate that faces the vertical direction.

  According to the said structure, the airflow which passed over the drain pan can be efficiently flowed along an air flow path by providing a horizontal plate. In addition, since the inclined plate and the vertical rectifying plate are provided, the airflow that has passed over the horizontal plate can easily be directed in the vertical direction, so that the airflow can be efficiently flowed along the ventilation path.

  In the refrigerator, the vertical rectifying plate is preferably provided so as to reach a vertically extending portion in the air passage. Thereby, the air volume in a ventilation path can be increased more effectively.

  Preferably, the refrigerator further includes a Stirling engine having a high temperature part and a low temperature part. In this case, the radiator is a condenser for discharging the heat of the high temperature part. This provides a Stirling cooler with high cooling efficiency for the high-temperature side condenser.

  According to the present invention, in the cooler, it is possible to ensure the air volume of the airflow flowing in the ventilation path regardless of the output of the first fan. As a result, the cooling efficiency of the radiator is improved.

  Below, the embodiment of the refrigerator based on this invention is described. Note that the same or corresponding portions are denoted by the same reference numerals, and the description thereof may not be repeated.

  In the present specification, the “refrigerator” is a concept including all of “refrigerator”, “freezer” and “refrigerator”.

  FIG. 1 is a piping system diagram of a Stirling cooler as an example of a cooler according to one embodiment of the present invention.

  As shown in FIG. 1, the Stirling refrigerator 1 includes a Stirling refrigerator 4 (Stirling engine) having a high temperature part 2 and a low temperature part 3, a high temperature side evaporator 5 attached to the high temperature part 2, and a high temperature side condenser. 7 and the first high temperature side circulation circuit including the pipes 2A and 2B, the second high temperature side circulation circuit including the high temperature side evaporator 5, the circulation pump 6, the dew condensation prevention pipe 9 and the pipes 2C to 2E, and the low temperature section 3 And a low-temperature side circulation circuit including the low-temperature side condenser 10, the low-temperature side evaporator 11, and the pipes 3A and 3B. The first high temperature side circulation circuit cools the high temperature part 2 of the Stirling refrigerator 4, and the second high temperature side circulation circuit supplies heat to the dew condensation prevention pipe 9. The low temperature side circulation circuit exchanges heat between the air in the refrigerator and the low temperature part 3 of the Stirling refrigerator 4 via the low temperature side evaporator 11.

Water (H ₂ O) or the like is sealed as a refrigerant in the first and second high temperature side circulation circuits. The refrigerant vaporized in the high temperature side evaporator 5 reaches the high temperature side condenser 7 via the pipe 2A (high temperature side conduit) (broken arrow in FIG. 1). The refrigerant is liquefied by heat exchange with the outside air in the high temperature side condenser 7. In order to promote this heat exchange, a fan 8 that generates an air flow in the vicinity of the high-temperature side condenser 7 is provided. The liquefied refrigerant returns to the high temperature side evaporator 5 through the pipe 2B (high temperature side return pipe). In the first high temperature side circulation circuit, the heat generated in the high temperature part 2 can be transferred to the high temperature side condenser 7 by utilizing the natural circulation caused by the vaporization and liquefaction of the refrigerant. The side condenser 7 is disposed above the high temperature side evaporator 5. Further, in order to adjust the boiling point of the refrigerant, the pressure in the circulation circuit system is adjusted (reduced pressure from atmospheric pressure).

  On the other hand, a pipe 2 </ b> C is connected to the lower part of the high temperature side evaporator 5. Liquid phase refrigerant flows from the high temperature side evaporator 5 into the pipe 2C. The refrigerant flowing into the pipe 2 </ b> C reaches the circulation pump 6 positioned below the Stirling refrigerator 4. The refrigerant discharged from the circulation pump 6 is sent to the dew prevention pipe 9 via the pipe 2D. The refrigerant that has flowed through the dew condensation prevention pipe 9 returns to the high temperature side evaporator 5 through the pipe 2E. Thus, forced circulation by the circulation pump 6 is performed in the second high temperature side circulation circuit.

  Here, the refrigerant flowing in the dew condensation prevention pipe 9 is kept at a relatively high temperature by the heat given from the high temperature part 2 of the Stirling refrigerator 4. Therefore, the dew condensation prevention pipe 9 can be arranged in the front opening of the refrigerator to suppress the dew condensation at the door portion or the like.

  Further, carbon dioxide, hydrocarbons, and the like are sealed as a refrigerant in the low temperature side circulation circuit. The refrigerant liquefied in the low temperature side condenser 10 reaches the low temperature side evaporator 11 through the pipe 3A (low temperature side conduit). Heat exchange is performed as the refrigerant evaporates in the low-temperature side evaporator 11. In order to promote this heat exchange, a fan 12 that generates an air current in the vicinity of the low-temperature evaporator 11 is provided. After heat exchange, the vaporized refrigerant returns to the low temperature side condenser 10 via the pipe 3B (low temperature side return pipe). In the low temperature side circulation circuit, the low temperature side evaporation is performed so that the cold generated in the low temperature part 3 can be transmitted to the low temperature side evaporator 11 by utilizing natural circulation caused by the vaporization and liquefaction of the refrigerant. The vessel 11 is disposed below the low temperature side condenser 10. Further, the pressure in the circulation circuit system is adjusted in order to adjust the boiling point of the refrigerant.

  When the Stirling refrigerator 4 is operated, heat generated in the high temperature part 2 of the refrigerator 4 is exchanged with the outside air via the high temperature side condenser 7. On the other hand, the cold generated in the low temperature part 3 of the Stirling refrigerator 4 is heat exchanged with the air in the refrigerator through the low temperature side evaporator 11. The warmed airflow from the inside of the refrigerator is sent again to the vicinity of the low-temperature side evaporator 11 and repeatedly cooled.

  With the implementation of the cooling cycle described above, frost forms on the low temperature side evaporator 11. About this defrosting method with respect to frost formation, since a generally well-known technique can be used, detailed description is not repeated.

  By performing defrosting of the low temperature side evaporator 11, defrosted water is generated. The defrost water is guided to the drain pan 12B (evaporating dish) installed at the lower part of the bottom surface of the refrigerator main body through the drain pipe 12A. A fan 12C is provided on the top of the drain pan 12B, and an air flow is formed near the surface of the defrost water accumulated in the drain pan 12B by the fan 12C, and relatively dry air is supplied onto the defrost water. Evaporation of defrost water is promoted.

  Next, an example of the structure of the Stirling refrigerator 4 and its operation will be described with reference to FIG.

  As shown in FIG. 2, the Stirling refrigerator 4 of the present embodiment is a free piston type Stirling engine, and includes a casing 30, a cylinder 13 assembled to the casing 30, and a reciprocating motion in the cylinder 13. Piston 14 and displacer 15, regenerator 16, working space 17 including a compression space 17 </ b> A and an expansion space 17 </ b> B, a high temperature portion 2, a low temperature portion 3, a linear motor 23 as a piston driving means, and a piston spring 24, a displacer spring 25, a displacer rod 26, and a back pressure space 27.

  In the example of FIG. 2, the outer shell (outer wall) of the Stirling refrigerator 4 is not constituted by a single container, but is positioned on the back pressure space 27 side and the casing 30 (vessel portion) and on the working space 17 side. The high-temperature part 2, the tube 18A, and the low-temperature part 3 are mainly configured. The casing 30 defines a back pressure space 27. Various parts including the cylinder 13, the linear motor 23, the piston spring 24, and the displacer spring 25 are assembled to the casing 30. The outer shell is filled with a working medium such as helium gas, hydrogen gas, or nitrogen gas.

  The cylinder 13 has a substantially cylindrical shape, and receives therein a piston 14 and a displacer 15 as a free piston so as to be capable of reciprocating. In the cylinder 13, the piston 14 and the displacer 15 are coaxially spaced apart, and the piston 14 and the displacer 15 divide the working space 17 in the cylinder 13 into a compression space 17 </ b> A and an expansion space 17 </ b> B. More specifically, the working space 17 is a space located closer to the displacer 15 than the end face of the piston 14 on the displacer 15 side, and a compression space 17A is formed between the piston 14 and the displacer 15, and the displacer 15 and the low temperature portion 3, an expansion space 17 </ b> B is formed. The compression space 17A is mainly surrounded by the high temperature part 2, and the expansion space 17B is mainly surrounded by the low temperature part 3.

  Between the compression space 17 </ b> A and the expansion space 17 </ b> B, a regenerator 16 in which a film is wound on the outer peripheral surface of the cylinder 13 with a predetermined gap is disposed. Thus, the compression space 17A and the expansion space 17B communicate with each other. Thereby, a closed circuit is formed in the Stirling refrigerator 4. The working medium sealed in the closed circuit flows in accordance with the operations of the piston 14 and the displacer 15, thereby realizing a reverse Stirling cycle described later.

  A linear motor 23 is disposed in the back pressure space 27 located outside the cylinder 13. The linear motor 23 includes an inner yoke 20, a movable magnet portion 21, an outer yoke 22 and a coil, and the piston 14 is driven in the axial direction of the cylinder 13 by the linear motor 23.

  One end of the piston 14 is connected to a piston spring 24 constituted by a leaf spring or the like. The piston spring 24 functions as an elastic force applying means for applying an elastic force to the piston 14. By applying an elastic force by the piston spring 24, the piston 14 can be reciprocated in the cylinder 13 more stably and periodically. One end of the displacer 15 is connected to a displacer spring 25 via a displacer rod 26. The displacer rod 26 is disposed through the piston 14, and the displacer spring 25 is constituted by a leaf spring or the like. The peripheral edge of the displacer spring 25 and the peripheral edge of the piston spring 24 are supported by a support member that extends from the linear motor 23 toward the back pressure space 27 of the piston 14 (hereinafter sometimes referred to as the rear).

A back pressure space 27 surrounded by a casing 30 is disposed on the opposite side of the piston 14 from the displacer 15. The back pressure space 27 includes an outer peripheral area located around the piston 14 in the casing 30 and a rear area located closer to the piston spring 24 (rear side) than the piston 14 in the casing 30. There is also a working medium in the back pressure space 27.

  The high temperature part 2 is attached to the casing 30 via the base member 30A. The high temperature part 2 and the low temperature part 3 are connected via the tube 18A. On the inner peripheral surfaces of the high temperature part 2 and the low temperature part 3, an internal heat exchanger 18 and an internal heat exchanger 19 are provided, respectively. The internal heat exchangers 18 and 19 perform heat exchange between the compression space 17A and the expansion space 17B and the high temperature part 2 and the low temperature part 3, respectively.

  A balance mass 29 is attached to the rear side of the casing 30 via a leaf spring 28. The balance mass 29 is a mass member that absorbs vibration of the casing 30 that is generated when the piston 14 and the displacer 15 vibrate. Specifically, when the vibration is generated in the casing 30 due to the vibration of the piston 14 or the displacer 15, the balance mass 29 is vibrated so as to follow the vibration of the casing 30, whereby the Stirling refrigerator 4. Vibration is reduced.

Next, the operation of the Stirling refrigerator 4 will be described.
First, the linear motor 23 is actuated to drive the piston 14. The piston 14 driven by the linear motor 23 approaches the displacer 15 and compresses the working medium (working gas) in the compression space 17A.

  When the piston 14 approaches the displacer 15, the temperature of the working medium in the compression space 17 </ b> A rises, but heat generated in the compression space 17 </ b> A by the high temperature portion 2 is released to the outside. Therefore, the temperature of the working medium in the compression space 17A is maintained almost isothermal. That is, this process corresponds to an isothermal compression process in a reverse Stirling cycle.

  After the piston 14 approaches the displacer 15, the displacer 15 moves to the low temperature part 3 side. On the other hand, the working medium compressed in the compression space 17A by the piston 14 flows into the regenerator 16, and further flows into the expansion space 17B. At that time, the heat of the working medium is stored in the regenerator 16. That is, this process corresponds to an isovolumetric cooling process in a reverse Stirling cycle.

  The high-pressure working medium that has flowed into the expansion space 17B expands when the displacer 15 moves to the piston 14 side (rear side). As the displacer 15 moves rearward in this way, the center portion of the displacer spring 25 is also deformed so as to protrude rearward.

  When the working medium expands in the expansion space 17B as described above, the temperature of the working medium in the expansion space 17B decreases, but external heat is transferred into the expansion space 17B by the low temperature portion 3, The inside of the expansion space 17B is kept almost isothermal. That is, this process corresponds to an isothermal expansion process of a reverse Stirling cycle.

  Thereafter, the displacer 15 starts to move away from the piston 14 (front side). Thereby, the working medium in the expansion space 17B passes through the regenerator 16 and returns to the compression space 17A side again. At this time, since the heat stored in the regenerator 16 is applied to the working medium, the working medium is heated. That is, this process corresponds to a constant volume heating process of a reverse Stirling cycle.

  By repeating this series of processes (isothermal compression process-isovolume cooling process-isothermal expansion process-isovolume heating process), an inverse Stirling cycle is configured. As a result, the low temperature part 3 is gradually lowered in temperature and has an extremely low temperature (for example, about −50 ° C.). On the other hand, the high temperature part 2 becomes gradually high temperature (for example, about 60 ° C.). As described above, the cold heat in the low temperature section 3 is supplied into the refrigerator through the low temperature side circulation circuit, and the heat in the high temperature section 2 is released to the outside of the refrigerator through the first and second high temperature side circulation circuits. Is done.

  3-5 is a figure which shows the structure of the ventilation path in the Stirling cooler shown by FIG. 3 shows a state in which the air passage is seen from the front of the refrigerator (from the direction of arrow III in FIG. 4), and FIG. 5 shows the air passage from the side of the refrigerator (in FIG. 4). The state seen from the direction of the arrow V is shown.

  Referring to FIGS. 3 to 5, the airflow generated by fans 8 and 12 </ b> C is guided into air passage 1 </ b> B through lower filter 31. The ventilation path 1B is formed on the back surface of the refrigerator main body from the lower part of the cover 34 provided on the bottom surface of the refrigerator main body.

  The fan 12C and the fan 8 are arranged in series along the flow direction of the airflow flowing through the air passage 1B. That is, the fan 8 is provided so as to generate an air flow along the flow of the air flow on the downstream side of the air flow generated by the fan 12C. Thereby, the synergy effect of the fans 8 and 12C is obtained, and the power consumption is reduced.

  3 to 5, the drain pan 12B is divided into a main drain pan 12B1 and a sub drain pan 12B2. First, the defrost water from the cooling body 1A flows into the main drain pan 12B1. The defrost water overflowing from the main drain pan 12B1 is guided to the sub drain pan 12B2 via the overflow pipe 120B. The fan 12C is disposed between the main drain pan 12B1 and the sub drain pan 12B2 and in the vicinity of the main drain pan 12B1. The fan 12C generates an air flow 100D toward the water surface of the defrost water stored in the main drain pan 12B1. The airflow 100D is directed to the back side of the cooler body through the flow path 1D.

  As described above, by installing the fan 12C in the vicinity of the main drain pan 12B1 to which the defrost water is preferentially guided, evaporation of the defrost water can be promoted at a higher rate. Moreover, evaporation of defrost water can be accelerated | stimulated using a collision jet by directing the airflow by the fan 12C to the water surface of the defrost water stored by main drain pan 12B1.

In the example shown in FIGS. 3 to 5, the Stirling refrigerator 4 is provided above the drain pan 12 </ b> B. Thereby, the airflow which passed the drain pan 12B vicinity which stores defrost water can be guide | induced to the high temperature side condenser 7 vicinity using a natural phenomenon. Since humid air with high humidity has a higher heat transport potential than dry air, the heat dissipation efficiency in the vicinity of the high-temperature side condenser 7 is enhanced.

  By the way, in order to cool the high temperature side condenser 7 effectively, it is desirable to use a large-capacity air passage 1B and high-power fans 12C and 8. On the other hand, from the viewpoint of reducing the size of the Stirling refrigerator 1, it is desirable to reduce the capacity of the air passage 1B to some extent. Further, reduction of power consumption of the blower fans 12C and 8 is also required. Therefore, it is necessary to increase the amount of air reaching the high-temperature side condenser 7 under the limited air passage capacity and the blower fan output.

  Here, the output of the fan 12 </ b> C necessary for generating the airflow for promoting the evaporation of the defrost water tends to be smaller than the output of the fan 8 necessary for promoting the cooling of the high-temperature side condenser 7. is there. On the other hand, as a result of restricting the air volume of the fan 12C, the air volume of the airflow supplied to the fan 8 may be insufficient, and the function of the fan 8 may be hindered. Therefore, it is necessary to adjust the air volume balance of the fans 8 and 12C. As a result, the output of the fan 12C may have to be set larger than the output necessary for simply promoting the evaporation of the defrosted water.

  On the other hand, in the Stirling cooler 1 according to the present embodiment, a flow path 1C is provided that directly communicates between the fan 12C and the fan 8 without passing through the fan 12C from the lower filter 31. The flow paths 1 </ b> C and 1 </ b> D are partitioned by the partition portion 33. The partition portion 33 includes a horizontal plate 33A provided in accordance with the height of the main drain pan 12B1, an inclined guide plate 33B connected to the downstream end of the horizontal plate 33A, and a vertical connected to the downstream end of the inclined guide plate 33B. Current plate 33C. Thereby, the airflow 100C flowing between the fan 12C and the fan 8 can be generated from the lower filter 31 without passing through the fan 12C.

  FIG. 6 is a diagram schematically showing the structure of the air passage of the Stirling cooler 1. On the other hand, FIG. 7 is a diagram schematically showing the structure of the air passage of the refrigerator according to the reference example. As shown in FIG. 7 (reference example), when the output of the fan 12C located on the upstream side of the air passage 1B is smaller than the output of the fan 8, the air volume of the airflow supplied to the fan 8 is insufficient. Function may be hindered. In contrast, as shown in FIG. 6 (the present embodiment), the air volume of the air flow 100C flowing through the flow path 1C, which is a “bypass path”, is not affected by the output of the fan 12C. Therefore, a sufficient air volume can be guided to the fan 8 regardless of the output of the fan 12C. As a result, compared with the structure according to the reference example, it is possible to improve the heat dissipation characteristics of the high-temperature side condenser 7 that is a “heat radiator”.

  Referring to FIG. 3 again, the protruding length L1 of the inclined guide plate 33B, the gap L2 between the cover 34 and the inclined guide plate 33B, the gap L3 between the cover 34 and the main drain pan 12B1, and the horizontal plane of the inclined guide plate 33B The angle θ is appropriately changed according to the specifications of the fans 8 and 12C so that the airflow of the airflow flowing in the duct that houses the high temperature side condenser 7 is maximized. For example, as shown in FIGS. 8 and 9, the gap L2 (for example, 40 mm) between the cover 34 and the inclined guide plate 33B and the gap L3 (for example, 65 mm) between the cover 34 and the main drain pan 12B1 are fixed, and the inclined guide plate 33B. By changing the inclination angle θ and the protruding length L1 of the inclined guide plate, and measuring the duct air volume under each condition, the optimum inclination angle θ and the protruding length L1 can be obtained. In FIGS. 8 and 9, “projecting only” means that the vertical rectifying plate 33C is omitted, and “projecting + rectifying plate” means the vertical rectifying plate 33C at the downstream end of the inclined guide plate 33B. Means that the vertical rectifier plate 33C provided at the downstream end of the inclined guide plate 33B is extended so as to reach the inside of the duct. Means. From the results shown in FIGS. 8 and 9, it can be seen that θ = 30 ° and L1 = 30 mm are desirable values.

  The above contents are summarized as follows. That is, the Stirling cooler 1 according to the present embodiment includes a cooler main body 1A, a high-temperature side condenser 7 as a “radiator” provided in the cooler main body 1A, and cooling air for the high-temperature side condenser 7. , A fan 12C as a “first fan” and a fan 8 as a “second fan” for generating an air flow in the ventilation path 1B. The fan 8 is a ventilation path generated by the fan 12C. A flow path 1 </ b> C as a “bypass path” provided between the fan 12 </ b> C and the fan 8 from the upstream side of the fan 12 </ b> C is provided on the downstream side of the airflow flowing along 1 </ b> B so as to generate an airflow along the airflow. Is provided in the ventilation path 1B.

  According to the above configuration, since the airflow is directly guided to the fan 8 through the flow path 1C, even if the airflow of the fan 12C is insufficient, the function of the fan 8 is not hindered. Therefore, the air volume of the airflow flowing through the ventilation path 1B can be ensured regardless of the output of the fan 12C. As a result, the cooling efficiency of the high temperature side condenser 7 is improved.

  The refrigerator 1 is provided with a drain pan 12B for storing defrosted water from the refrigerator main body 1A. The fan 12C is provided in the vicinity of the drain pan 12B. On the other hand, the fan 8 is provided in the vicinity of the high-temperature side condenser 7.

  Thereby, the airflow which passed the vicinity of the drain pan 12B which stores defrost water can be guide | induced to the vicinity of the high temperature side condenser 7. FIG. Since the airflow that has passed through the vicinity of the drain pan 12B is humid air having relatively high humidity, the heat transport potential is high, and as a result, the heat dissipation efficiency of the high-temperature side condenser 7 is enhanced.

  The refrigerator includes a partition 33. The partition portion 33 divides the air passage 1B into a flow passage 1C and a flow passage 1D serving as a flow passage for the air flow generated by the fan 12C. A portion where the fan 8 is provided in the air passage 1B is formed to extend vertically. The partition 33 includes a horizontal plate 33A provided in accordance with the height of the main drain pan 12B1, an inclined guide plate 33B as an “inclined plate” connected to the downstream end of the horizontal plate 33A, and an inclined guide plate 34. And a vertical rectifying plate 33C that directs the airflow from the fan 12C in the vertical direction.

  By providing the horizontal plate 33A, the airflow that has passed over the drain pan 12B can be efficiently flowed along the flow path 1D. Further, by providing the inclined guide plate 33B and the vertical rectifying plate 33C, the airflow that has passed over the horizontal plate 33 is easily directed in the vertical direction.

  The vertical rectifying plate 33C is provided so as to reach a vertically extending portion in the air passage 1B. Thereby, the air volume in the ventilation path 1B can be increased more effectively.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a piping distribution diagram of an example of a refrigerator concerning one embodiment of the present invention. It is sectional drawing which showed the Stirling refrigerator in the Stirling refrigerator shown by FIG. It is a figure (the 1) which shows the structure of the ventilation path in the Stirling refrigerator shown by FIG. FIG. 3 is a diagram (No. 2) illustrating a structure of an air passage in the Stirling cooler illustrated in FIG. 1. FIG. 3 is a diagram (No. 3) illustrating the structure of an air passage in the Stirling cooler illustrated in FIG. 1. It is a figure which shows typically the structure of the ventilation path of the refrigerator which concerns on one embodiment of this invention. It is a figure which shows typically the structure of the ventilation path of the refrigerator which concerns on a reference example. It is FIG. (1) which shows the relationship between the protrusion length of an inclination guide plate, and a duct air volume. It is a figure (the 2) which shows the relationship between the protrusion length of an inclination guide plate, and a duct air volume.

Explanation of symbols

  1 Stirling cooler, 1A cooler body, 1B air passage, 1C, 1D flow path, 2 high temperature part, 2A-2E pipe (high temperature side circulation circuit), 3 low temperature part, 3A, 3B pipe (low temperature side circulation circuit), 4 Stirling refrigerator, 5 high temperature side evaporator, 6 circulation pump, 7 high temperature side condenser, 8 fan, 9 dew condensation prevention pipe, 10 low temperature side condenser, 11 low temperature side evaporator, 12 fan, 12A drain pipe, 12B drain pan 12B1 Main drain pan, 12B2 Sub drain pan, 12C fan, 31 Lower filter, 32 Upper filter, 33 Partition, 33A Horizontal plate, 33B Inclined guide plate, 33C Vertical rectifying plate, 34 Cover, 100C, 100D Airflow.

Claims (5)

The refrigerator body,
A radiator provided in the cooling body,
An air passage through which cooling air of the radiator flows,
A first and a second fan for generating an air flow in the air passage;
The second fan is provided to generate an air flow along the flow of the air flow on the downstream side of the air flow flowing along the ventilation path generated by the first fan,
A refrigerator in which a bypass path reaching between the first and second fans from the upstream side of the first fan is provided in the ventilation path. Further comprising a drain pan for storing defrosted water from the cooling body,
The first fan is provided in the vicinity of the drain pan,
The refrigerator according to claim 1, wherein the second fan is provided in the vicinity of the radiator. A partition section that divides the ventilation path into a flow path of an air flow generated by the first fan and the bypass path;
A portion of the ventilation path where the second fan is provided is formed to extend vertically,
The partition is
A horizontal plate provided in accordance with the height of the drain pan;
An inclined plate connected to the downstream end of the horizontal plate;
The refrigerator according to claim 2, further comprising: a vertical rectifying plate that is connected to a downstream end portion of the inclined plate and directs an airflow from the first fan in a vertical direction.   The refrigerator according to claim 3, wherein the vertical rectifying plate is provided so as to reach a vertically extending portion of the air passage. Further comprising a Stirling engine having a high temperature part and a low temperature part,
The refrigerator according to any one of claims 1 to 4, wherein the radiator is a condenser for discharging the heat of the high temperature part.

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