JP2012032112A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger that allows a uniform amount of refrigerant to flow into a refrigerant passage of a refrigerant pipe from a distribution header, while reducing manufacturing costs.SOLUTION: An evaporator 24 includes: a tubular distribution header 241 including a distribution flow channel 2412 to allow the refrigerant flowing therein through an inlet 2411 at one end, to pass toward the closed other end; and a plurality of refrigerant pipes 243 formed in a flat shape by arranging a plurality of refrigerant passages 2431 along the horizontal direction, and inserted and mounted along the pipe axial direction of the distribution header 241 while inlets 2431a of the refrigerant passages 2431 face the distribution flow channel 2412. The evaporator 24 distributes the refrigerant to the refrigerant passages 2431 of the refrigerant pipes 243 from the distribution header 241 to exchange heat between the refrigerant passing through the refrigerant passages 2431 and fluid passing around it. The amount of insertion to the distribution header 241 of the refrigerant pipe 243 at one end side is larger than that of the refrigerant pipe 243 at the other end side.

Description

  The present invention relates to a heat exchanger, and more particularly to an evaporator constituting a refrigeration cycle or a heat pump cycle used for cooling a product in a vending machine or the like.

  Conventionally, for example, in vending machines that sell products such as canned beverages and beverages in plastic bottles, the components of the refrigeration cycle and heat pump cycle are installed in the interior of the product cabinet of the main body cabinet, which is the main body of the vending machine. An evaporator (heat exchanger) is provided.

  As this kind of heat exchanger, what is provided with a distribution header, a plurality of refrigerant pipes, and a merge header is known. The distribution header is formed such that an opening serving as a refrigerant inlet is formed at one end and the other end is closed, and is arranged along the horizontal direction. Inside the distribution header is formed a distribution channel through which the refrigerant passes along the horizontal direction from one end to the other end.

  Each of the refrigerant tubes has a flat shape, and refrigerant passages serving as refrigerant flow paths are arranged in parallel along the horizontal direction. Each of the refrigerant pipes extends in a meandering manner, and is inserted and attached along the pipe axis direction of the distribution header in such a manner that the inlet of each refrigerant passage faces the distribution flow path.

  The merge header is arranged in a manner parallel to the distribution header. This merging header is formed by forming an opening which is a refrigerant outlet at one end and closing the other end. Inside this merging header, a merging channel for allowing the refrigerant to pass along the horizontal direction is formed. And the refrigerant | coolant pipe | tube is attached to the confluence | merging header in the aspect in which the exit of the refrigerant path of each refrigerant | coolant pipe | tube faces the own confluence | merging flow path.

  In such a heat exchanger, the refrigerant is distributed to the refrigerant passage of each refrigerant pipe from the distribution header, and heat exchange is performed between the refrigerant passing through the refrigerant passage and the fluid passing around the refrigerant passage. The refrigerant that has passed through the refrigerant passage reaches the merging channel of the merging header, passes through the merging channel, and flows out from the outlet.

  The insertion amount of the refrigerant pipe with respect to the distribution header is gradually decreased in accordance with the arrangement order from the one end so that the refrigerant flows uniformly in the refrigerant passages of the respective refrigerant pipes, and a liquid drain hole is formed in the pipe wall of the refrigerant pipe. A heat exchanger formed is proposed (see, for example, Patent Document 1).

JP-A-10-132422

  By the way, in the heat exchanger proposed by patent document 1 as mentioned above, since the liquid drain hole is formed in the pipe wall of a refrigerant pipe, it is liquid according to the insertion amount of the refrigerant pipe with respect to a distribution header. It is necessary to adjust the position of the hole. For this reason, since the position of the liquid discharge hole is different for each refrigerant pipe, a common refrigerant pipe cannot be used, resulting in an increase in manufacturing cost.

  In view of the above circumstances, an object of the present invention is to provide a heat exchanger that can make the refrigerant flowing from the distribution header into the refrigerant passage of the refrigerant pipe uniform while reducing the manufacturing cost. .

  In order to achieve the above object, a heat exchanger according to claim 1 of the present invention passes a refrigerant flowing in through a flow inlet formed at one end portion along a horizontal direction toward the other closed end portion. Each of the refrigerant passages has a flat shape in which a plurality of refrigerant passages are juxtaposed in the horizontal direction, and an inlet of each refrigerant passage faces the distribution passages. And a plurality of refrigerant tubes inserted and attached along the pipe axis direction of the distribution header, and distributes the refrigerant from the distribution header to the refrigerant passages of the refrigerant tubes and passes through the refrigerant passages. In the heat exchanger that performs heat exchange between the refrigerant that passes and the fluid that passes around the refrigerant, the amount of insertion of the refrigerant pipe on the other end side is greater than the amount of insertion of the refrigerant pipe on the one end side with respect to the distribution header. Characterized by being enlarged.

  The heat exchanger according to claim 2 of the present invention is the heat exchanger according to claim 1 described above, wherein the amount of insertion as the end face of the refrigerant pipe inserted into the distribution header moves from the one end to the other end. Is formed in such a manner that gradually increases.

  In the heat exchanger according to claim 3 of the present invention, the distribution flow path for allowing the refrigerant flowing in through the inlet formed at one end portion to pass along the horizontal direction toward the closed other end portion is provided inside. The distribution header is formed in a flat shape in which a plurality of refrigerant passages are arranged side by side in the horizontal direction, and an inlet of each refrigerant passage faces the distribution flow path. A plurality of refrigerant tubes inserted and attached along the tube axis direction of the refrigerant, distributing the refrigerant from the distribution header to the refrigerant passages of the refrigerant tubes and passing through the refrigerant passages, and In the heat exchanger for exchanging heat with the fluid passing through the surroundings, at least the one end side refrigerant provided between the one end side refrigerant pipe and the other end side refrigerant pipe adjacent thereto. Projection height of the pipe from the inner wall surface in the distribution channel Characterized by comprising a wall member having a greater protruding height.

  According to the present invention, since the insertion amount of the refrigerant pipe on the other end side is larger than the insertion amount of the refrigerant pipe on the one end side with respect to the distribution header, the end face of the refrigerant pipe on the other end side in the distribution header The gap with the inner wall surface can be made smaller than the gap between the end surface of the refrigerant pipe on the one end side and the inner wall surface, thereby increasing the fluid resistance at the inlet of the refrigerant passage in the refrigerant pipe on the other end side. become. As a result, the refrigerant inflow into the refrigerant passage in the refrigerant pipe on the one end portion side can be promoted, and the refrigerant flowing into the refrigerant passage can be made uniform. In addition, since the insertion amount of the refrigerant pipe on the other end side with respect to the distribution header only needs to be larger than the insertion amount of the refrigerant pipe on the one end side, it is possible to apply a refrigerant pipe having the same extension length. Therefore, a common refrigerant pipe can be used, and as a result, the manufacturing cost can be reduced. Therefore, there is an effect that the refrigerant flowing from the distribution header into the refrigerant passage of the refrigerant pipe can be made uniform while reducing the manufacturing cost.

  Further, according to the present invention, the wall member provided between the refrigerant pipe on one end side and the refrigerant pipe on the other end side adjacent thereto is at least an inner portion of the distribution channel of the refrigerant pipe on the one end side. Since it has a protruding height larger than the protruding height from the wall surface, the gap between the end of the wall member and the inner wall surface of the distribution channel can be reduced, so that the inlet of the refrigerant passage in the refrigerant pipe on the other end side can be reduced. The fluid resistance will increase. The increase in fluid resistance due to the provision of the wall member in this way, that is, gas-liquid separation of the refrigerant (gas-liquid two-phase refrigerant) flowing into and passing through the distribution flow path is caused by viscous resistance, and the liquid refrigerant is generated by the wall member By retaining the refrigerant, it is possible to promote the inflow of the refrigerant to the refrigerant passage in the refrigerant pipe on the one end side, and it is possible to make the refrigerant flowing into the refrigerant passage uniform. In addition, since it is only necessary to provide the wall member inside the distribution header, it is possible to apply refrigerant pipes having the same extension length, and thus it is possible to use a common refrigerant pipe. Reduction can be achieved. Therefore, there is an effect that the refrigerant flowing from the distribution header into the refrigerant passage of the refrigerant pipe can be made uniform while reducing the manufacturing cost.

FIG. 1 is a cross-sectional view showing a case where the internal structure of a vending machine to which the heat exchanger according to Embodiment 1 of the present invention is applied as an evaporator is viewed from the front. 2 is a cross-sectional side view showing the internal structure of the vending machine shown in FIG. FIG. 3 is a front view schematically showing the evaporator shown in FIG. 2 (the heat exchanger according to the first embodiment of the present invention). FIG. 4 is a plan view schematically showing the evaporator shown in FIG. 2 (the heat exchanger according to the first embodiment of the present invention). 5 is a cross-sectional view of the refrigerant pipe taken along line AA in FIG. FIG. 6 shows the inside of the distribution header, which is a main part of the evaporator shown in FIGS. 3 to 5, and is an explanatory view showing the case where the internal structure of the distribution header is viewed from above. FIG. 7 shows the inside of the distribution header, which is the main part of the evaporator shown in FIGS. 3 to 5, and is an explanatory view showing the case where the internal structure of the distribution header is viewed from the inlet side. FIG. 8 shows the inside of the distribution header, which is the main part of the evaporator according to the second embodiment of the present invention, and is an explanatory view showing the case where the internal structure of the distribution header is viewed from above. FIG. 9 is an explanatory diagram showing an enlarged end surface of the refrigerant pipe shown in FIG. FIG. 10 is an explanatory diagram schematically illustrating how the refrigerant flows through the refrigerant flow path and the refrigerant passage illustrated in FIGS. 8 and 9. FIG. 11 shows the inside of the distribution header, which is the main part of the evaporator according to Embodiment 3 of the present invention, and is an explanatory view showing the case where the internal structure of the distribution header is viewed from above. FIG. 12 shows the inside of the distribution header, which is the main part of the evaporator according to Embodiment 3 of the present invention, and is an explanatory view showing the case where the internal structure of the distribution header is viewed from the inlet side. FIG. 13 shows the inside of a distribution header which is a main part of an evaporator which is a modified example of Embodiment 3 of the present invention, and is an explanatory diagram showing a case where the internal structure of the distribution header is viewed from the inlet side. is there.

  Hereinafter, preferred embodiments of a heat exchanger according to the present invention will be described in detail with reference to the accompanying drawings.

<Embodiment 1>
FIG. 1 is a cross-sectional view showing a case where the internal structure of a vending machine to which the heat exchanger according to Embodiment 1 of the present invention is applied as an evaporator is viewed from the front. The vending machine illustrated here includes a main body cabinet 1.

  The main body cabinet 1 has a rectangular shape with an open front surface. The main body cabinet 1 is provided with three independent commodity containers 3 partitioned by, for example, two heat insulating partition plates 2 in a side-by-side manner. This product storage 3 is for storing products such as canned beverages and beverages containing plastic bottles while maintaining them at a desired temperature, and has a heat insulating structure.

  2 is a cross-sectional side view showing the internal structure of the vending machine shown in FIG. As shown in FIG. 2, an outer door 4 and an inner door 5 are provided on the front surface of the main body cabinet 1. The outer door 4 is for opening and closing the front opening of the main body cabinet 1, and the inner door 5 is for opening and closing the front surface of the commodity storage 3. The inner door 5 is divided into upper and lower parts, and the upper door 5a opens and closes when a product is replenished.

  The product storage 3 is provided with a product storage rack 6, a carry-out mechanism 7 and a carry-out shooter 8. The commodity storage rack 6 is for storing commodities in a manner arranged in the vertical direction. The carry-out mechanism 7 is provided at the lower part of the product storage rack 6 and is used to carry out the products at the bottom of the product group stored in the product storage rack 6 one by one. The carry-out shooter 8 is for guiding the product carried out from the carry-out mechanism 7 to the product take-out port 4 a provided in the outer door 4.

  An evaporator 24 and a heater H are disposed below the carry-out shooter 8. The evaporator 24 is disposed on the front side of the rear duct D, and is sequentially connected through a compressor 21, a condenser 22, an expansion mechanism 23 and a refrigerant pipe 25 disposed in the machine room 9 to form a refrigeration cycle 20. is doing. The compressor 21 sucks the refrigerant through the suction port, compresses the sucked refrigerant to be in a high-temperature and high-pressure state (high-temperature and high-pressure refrigerant), and discharges it from the discharge port. The condenser 22 condenses the refrigerant that passes therethrough. More specifically, the refrigerant compressed by the compressor 21 and discharged from the discharge port and sent out through the refrigerant pipe 25 is condensed by exchanging heat with ambient air. The expansion mechanism 23 is for adiabatic expansion by reducing the pressure of the refrigerant passing therethrough.

  By circulating the refrigerant in the refrigeration cycle 20, the refrigerant compressed by the compressor 21 is condensed by the condenser 22, and then adiabatically expanded by the expansion mechanism 23 and passes through the evaporator 24. When the refrigerant passes through the evaporator 24, heat exchange is performed with the internal air of the commodity storage 3 in which the evaporator 24 is disposed, and the refrigerant evaporates to cool the internal air. The evaporated refrigerant is sucked into the compressor 21.

  The cooled internal air moves inside the product storage 3 by driving the internal blower fan F1, so that the product stored in the product storage rack 6 of the product storage 3 has a desired temperature (for example, 5 ° C.). It will be cooled down.

  The heater H is arrange | positioned in the front area of the internal ventilation fan F1. The heater H heats the surrounding air when energized. The air heated by the heater H moves inside the product storage case 3 by driving the internal blower fan F1, so that the product stored in the product storage rack 6 of the product storage case 3 has a desired temperature (for example, 55 ° C.).

  3 and 4 schematically show the evaporator 24 (the heat exchanger according to the first embodiment of the present invention) shown in FIG. 2, respectively. FIG. 3 is a front view, and FIG. It is a top view. The evaporator 24 exemplified here is a so-called multiflow heat exchanger, and includes a distribution header 241, a merge header 242, and a plurality (two in the illustrated example) of refrigerant pipes 243. is there.

  The distribution header 241 is disposed along the horizontal direction. A refrigerant inlet 2411 is formed at one end of the distribution header 241, and the other end is a closed tube. The inlet 2411 is connected to a refrigerant pipe 25 connected to the outlet of the expansion mechanism 23. In the distribution header 241, a distribution flow path 2412 (FIG. 6) allows the refrigerant flowing in from the inlet 2411 from one end portion to the other end portion to pass along the horizontal direction, that is, along its own tube axis direction. Reference) is formed.

  The merge header 242 is arranged along the horizontal direction in a mode parallel to the distribution header 241 in a lower area of the distribution header 241. A refrigerant outlet (not shown) is formed at one end of the merge header 242 and the other end is a closed tube. The outlet is connected to a refrigerant pipe 25 connected to the suction port of the compressor 21. Inside this merging header 242, a merging channel (not shown) is formed that passes along the horizontal direction from one end to the other end, that is, along the direction of its own tube axis.

  As shown in FIG. 5, each of the refrigerant tubes 243 is a flat tube in which a plurality of refrigerant passages 2431 are arranged in parallel along the horizontal direction, and is referred to as a flat multi-hole tube. That is, the plurality of refrigerant passages 2431 are juxtaposed along the pipe axis direction of the distribution header 241 (merging header 242). The refrigerant pipes 243 are formed to meander from side to side in such a manner that the refrigerant pipes 243 are arranged along the pipe axis direction of the distribution header 241. Hereinafter, the refrigerant pipe 243 on the inlet 2411 side (one end side) of the distribution header 241 is also referred to as an upstream refrigerant pipe 243a, and the refrigerant pipe 243 on the other end side is also referred to as a downstream refrigerant pipe 243b.

  In the refrigerant pipe 243 (upstream refrigerant pipe 243a and downstream refrigerant pipe 243b), the upper end opening of each refrigerant passage 2431 serves as a refrigerant inlet 2431a, and the lower end opening serves as a refrigerant outlet (not shown). It has become. These refrigerant pipes 243 (upstream refrigerant pipe 243a and downstream refrigerant pipe 243b) are inserted from the side of the distribution header 241 such that the inlet 2431a of the refrigerant passage 2431 faces the distribution flow path 2412 of the distribution header 241. It is attached and inserted from the side of the merge header 242 so that the outlet of its own refrigerant passage 2431 faces the merge flow path of the merge header 242.

  In addition, corrugated fins 244 are joined to the refrigerant pipe 243 (upstream refrigerant pipe 243a and downstream refrigerant pipe 243b). The corrugated fins 244 are formed to be bent in a wave shape, and the bent portion outside 2441 is disposed between the horizontally extending portions of the refrigerant pipe 243 by brazing or the like. Such a corrugated fin 244 is formed with a strip-shaped louver that is cut and raised from the surface, though not shown in the drawing. The corrugated fins 244 are for promoting heat exchange between the refrigerant passing through the refrigerant passage 2431 of the refrigerant pipe 243 and the air (fluid) around the evaporator 24.

  6 and 7 show the inside of the distribution header 241 which is a main part of the evaporator 24 shown in FIGS. 3 to 5. FIG. 6 shows the internal structure of the distribution header 241 as viewed from above. FIG. 7 is an explanatory diagram showing a case where the internal structure of the distribution header 241 is viewed from the inlet 2411 side. As shown in FIGS. 6 and 7, in the evaporator 24 according to the first embodiment, the insertion amount of the downstream refrigerant pipe 243b is set larger than the insertion amount of the upstream refrigerant pipe 243a into the distribution header 241. is there. That is, the protruding height of the downstream refrigerant pipe 243b from the inner wall surface 2412a of the distribution flow path 2412 is larger than the protruding height of the upstream refrigerant pipe 243a from the inner wall surface 2412a. The protruding height of the refrigerant pipe 243b is larger than the central axis of the distribution flow path 2412 (the pipe axis of the distribution header 241), and the insertion amount of the downstream refrigerant pipe 243b is larger than the upstream refrigerant pipe 243a. For example, it is about 1.5 to 2.5 times as large as the insertion amount.

  In the evaporator 24 (heat exchanger) having the above-described configuration, the refrigerant (gas-liquid two-phase refrigerant) adiabatically expanded by the expansion mechanism 23 flows into the distribution flow path 2412 through the inlet 2411, and the other end passes through the other end. The refrigerant enters the refrigerant passage 2431 of the refrigerant pipe 243 (upstream refrigerant pipe 243a and downstream refrigerant pipe 243b) from the inlet 2431a while passing through the distribution channel 2412 toward the end. That is, the refrigerant is distributed from the distribution header 241 to the refrigerant passage 2431 of each refrigerant pipe 243. The refrigerant that has entered the refrigerant passage 2431 evaporates by exchanging heat with the internal air of the product container 3 in which the evaporator 24 is disposed while passing along the extending direction of each refrigerant pipe 243. The internal air is cooled. The cooled internal air circulates inside the product storage 3 by driving the internal blower fan F1, cools the product stored in the product storage rack 6 and adjusts it to a desired temperature.

  On the other hand, the refrigerant that has evaporated through the refrigerant passage 2431 reaches the merge flow path of the merge header 242 from the outlet, flows out to the refrigerant pipe 243 through the outlet, and is sucked into the compressor 21 and compressed.

  By the way, in the evaporator 24, the insertion amount of the downstream refrigerant tube 243b in the distribution header 241 is larger than the insertion amount of the upstream refrigerant tube 243a into the distribution header 241 so that the downstream refrigerant tube 243b is inserted. The gap S1 between the inner wall surface 2412b on the opposite side and the downstream side refrigerant pipe 243b can be made smaller than the gap S2 between the inner wall surface 2412b and the upstream side refrigerant pipe 243a. The fluid resistance at the inlet 2431a of the refrigerant passage 2431 increases. As a result, the refrigerant inflow into the refrigerant passage 2431 in the upstream refrigerant pipe 243a can be promoted, and the refrigerant flowing into the refrigerant passage 2431 can be made uniform. Moreover, since it is only necessary to make the insertion amount of the downstream refrigerant tube 243b into the distribution header 241 larger than the insertion amount of the upstream refrigerant tube 243a, it is possible to apply the refrigerant tube 243 having the same extension length. A common refrigerant pipe 243 can be used, and as a result, the manufacturing cost can be reduced.

  Therefore, according to the evaporator 24 according to the first embodiment, it is possible to make the refrigerant flowing from the distribution header 241 into the refrigerant passage 2431 of the refrigerant pipe 243 uniform while reducing the manufacturing cost.

<Embodiment 2>
FIG. 8 shows the inside of the distribution header 241 which is the main part of the evaporator 24 according to the second embodiment of the present invention, and is an explanatory diagram showing the case where the internal structure of the distribution header 241 is viewed from above. In addition, the same code | symbol is attached | subjected to what has the same structure as the evaporator 24 which is Embodiment 1 mentioned above, and the description is abbreviate | omitted. The evaporator 24 according to the second embodiment is a so-called multiflow type heat exchanger, and includes a distribution header 241, a merge header 242, and a plurality (two in the illustrated example) of refrigerant pipes 243. Configured.

  Each of the refrigerant tubes 243 is a flat tube in which a plurality of refrigerant passages 2431 are arranged in parallel along the horizontal direction, and is referred to as a flat multi-hole tube. That is, the plurality of refrigerant passages 2431 are juxtaposed along the pipe axis direction of the distribution header 241 (merging header 242). The refrigerant pipes 243 are formed to meander from side to side in such a manner that the refrigerant pipes 243 are arranged along the pipe axis direction of the distribution header 241. Hereinafter, the refrigerant pipe 243 on the inlet 2411 side (one end side) of the distribution header 241 is also referred to as an upstream refrigerant pipe 243c, and the refrigerant pipe 243 on the other end side is also referred to as a downstream refrigerant pipe 243d.

  In the refrigerant pipe 243 (upstream refrigerant pipe 243c and downstream refrigerant pipe 243d), the upper end opening of each refrigerant passage 2431 serves as a refrigerant inlet 2431a, and the lower end opening serves as a refrigerant outlet. These refrigerant pipes 243 (upstream refrigerant pipe 243c and downstream refrigerant pipe 243d) are inserted from the side of the distribution header 241 such that the inlet 2431a of the refrigerant passage 2431 faces the distribution flow path 2412 of the distribution header 241. It is attached and inserted from the side of the merge header 242 so that the outlet of its own refrigerant passage 2431 faces the merge flow path of the merge header 242.

  In such an evaporator 24, the insertion amount of the downstream refrigerant tube 243d is larger than the insertion amount of the upstream refrigerant tube 243c into the distribution header 241. That is, of the refrigerant pipe 243 (upstream refrigerant pipe 243c and downstream refrigerant pipe 243d), the end face 245 inserted into the distribution header 241, that is, the end face 245 including the inlet 2431 a of each refrigerant passage 2431, extends from one end of the distribution header 241. The insertion amount is formed so as to gradually increase toward the other end. More specifically, the end face 245 of the upstream refrigerant pipe 243c and the end face 245 of the downstream refrigerant pipe 243d are along the virtual straight line m in FIG. It is formed by cutting away toward the side.

  In the evaporator 24 (heat exchanger) having the above-described configuration, the refrigerant (gas-liquid two-phase refrigerant) adiabatically expanded by the expansion mechanism 23 flows into the distribution flow path 2412 through the inlet 2411, and the other end passes through the other end. The refrigerant enters the refrigerant passage 2431 of the refrigerant pipe 243 (upstream refrigerant pipe 243c and downstream refrigerant pipe 243d) from the inlet 2431a while passing through the distribution channel 2412 toward the end. That is, the refrigerant is distributed from the distribution header 241 to the refrigerant passage 2431 of each refrigerant pipe 243. The refrigerant that has entered the refrigerant passage 2431 evaporates by exchanging heat with the internal air of the product container 3 in which the evaporator 24 is disposed while passing along the extending direction of each refrigerant pipe 243. The internal air is cooled. The cooled internal air circulates inside the product storage 3 by driving the internal blower fan F1, cools the product stored in the product storage rack 6 and adjusts it to a desired temperature.

  On the other hand, the refrigerant that has evaporated through the refrigerant passage 2431 reaches the merge flow path of the merge header 242 from the outlet, flows out to the refrigerant pipe 243 through the outlet, and is sucked into the compressor 21 and compressed.

  By the way, in the evaporator 24, the end surface 245 inserted into the distribution header 241 among the refrigerant tubes 243 (the upstream refrigerant tube 243c and the downstream refrigerant tube 243d), that is, the end surface 245 including the inlet 2431a of each refrigerant passage 2431 is provided. Since the insertion amount is gradually increased from one end portion of the distribution header 241 toward the other end portion, the edge portion 2431b of each refrigerant passage 2431 is connected to the pipe of the distribution header 241 as shown in FIG. A step is formed along the axial direction. As a result, as shown in FIG. 10, the refrigerant (gas-liquid two-phase refrigerant) that flows in from the inlet 2411 and passes through the distribution flow path 2412 can be sequentially blocked by the edge portion 2431 b of each refrigerant passage 2431. The refrigerant inflow into the refrigerant passage 2431 in the pipe 243c can be promoted, and the refrigerant flowing into the refrigerant passage 2431 can be made uniform. Moreover, the end surface 245 inserted into the distribution header 241 among the refrigerant tubes 243 (the upstream refrigerant tube 243c and the downstream refrigerant tube 243d), that is, the end surface 245 including the inlet 2431a of each refrigerant passage 2431 extends from one end of the distribution header 241. Since the insertion amount is only formed so as to gradually increase toward the other end, it is possible to apply the refrigerant pipe 243 having the same extension length, thereby using the common refrigerant pipe 243. As a result, the manufacturing cost can be reduced.

  Therefore, according to the evaporator 24 according to the second embodiment, the refrigerant flowing from the distribution header 241 to the refrigerant passage 2431 of the refrigerant pipe 243 can be made uniform while reducing the manufacturing cost.

<Embodiment 3>
11 and 12 show the inside of the distribution header 241 which is a main part of the evaporator 24 according to Embodiment 3 of the present invention. FIG. 11 shows the internal structure of the distribution header 241 as viewed from above. FIG. 12 is an explanatory diagram showing a case where the internal structure of the distribution header 241 is viewed from the inflow port 2411 side. In addition, the same code | symbol is attached | subjected to what has the same structure as the evaporator 24 which is Embodiment 1 mentioned above, and the description is abbreviate | omitted. The evaporator 24 according to the third embodiment is a so-called multiflow type heat exchanger, and includes a distribution header 241, a merge header 242, and a plurality (two in the illustrated example) of refrigerant pipes 243. Configured.

  Each of the refrigerant tubes 243 is a flat tube in which a plurality of refrigerant passages 2431 are arranged in parallel along the horizontal direction, and is referred to as a flat multi-hole tube. That is, the plurality of refrigerant passages 2431 are juxtaposed along the pipe axis direction of the distribution header 241 (merging header 242). The refrigerant pipes 243 are formed to meander from side to side in such a manner that the refrigerant pipes 243 are arranged along the pipe axis direction of the distribution header 241. Hereinafter, the refrigerant pipe 243 on the inlet 2411 side (one end side) of the distribution header 241 is also referred to as an upstream refrigerant pipe 243e, and the refrigerant pipe 243 on the other end side is also referred to as a downstream refrigerant pipe 243f.

  In the refrigerant pipe 243 (upstream refrigerant pipe 243e and downstream refrigerant pipe 243f), the upper end opening of each refrigerant passage 2431 serves as a refrigerant inlet 2431a, and the lower end opening serves as a refrigerant outlet. These refrigerant pipes 243 (upstream refrigerant pipe 243e and downstream refrigerant pipe 243f) are inserted from the side of the distribution header 241 such that the inlet 2431a of the refrigerant passage 2431 faces the distribution flow path 2412 of the distribution header 241. It is attached and inserted from the side of the merge header 242 so that the outlet of its own refrigerant passage 2431 faces the merge flow path of the merge header 242.

  In such an evaporator 24, the amount of insertion of the upstream refrigerant pipe 243e into the distribution header 241 and the amount of insertion of the downstream refrigerant pipe 243f are made equal. A wall member 246 is provided between the upstream refrigerant pipe 243e and the downstream refrigerant pipe 243f inserted into the distribution header 241, that is, between the upstream refrigerant pipe 243e and the downstream refrigerant pipe 243f in the distribution flow path 2412. It is. The protruding height of the wall member 246 is larger than the protruding height of the upstream refrigerant pipe 243e and the downstream refrigerant pipe 243f from the inner wall surface 2412a in the distribution flow path 2412, and the central axis of the distribution flow path 2412 (distribution) The pipe axis of the header 241).

  In the evaporator 24 (heat exchanger) having the above-described configuration, the refrigerant (gas-liquid two-phase refrigerant) adiabatically expanded by the expansion mechanism 23 flows into the distribution flow path 2412 through the inlet 2411, and the other end passes through the other end. The refrigerant enters the refrigerant passage 2431 of the refrigerant pipe 243 (upstream refrigerant pipe 243e and downstream refrigerant pipe 243f) from the inlet 2431a while passing through the distribution channel 2412 toward the end. That is, the refrigerant is distributed from the distribution header 241 to the refrigerant passage 2431 of each refrigerant pipe 243. The refrigerant that has entered the refrigerant passage 2431 evaporates by exchanging heat with the internal air of the product container 3 in which the evaporator 24 is disposed while passing along the extending direction of each refrigerant pipe 243. The internal air is cooled. The cooled internal air circulates inside the product storage 3 by driving the internal blower fan F1, cools the product stored in the product storage rack 6 and adjusts it to a desired temperature.

  On the other hand, the refrigerant that has evaporated through the refrigerant passage 2431 reaches the merge flow path of the merge header 242 from the outlet, flows out to the refrigerant pipe 243 through the outlet, and is sucked into the compressor 21 and compressed.

  By the way, in the evaporator 24, the protruding height of the wall member 246 provided between the upstream refrigerant pipe 243e and the downstream refrigerant pipe 243f in the distribution flow path 2412 is equal to the upstream refrigerant pipe 243e and the downstream refrigerant. Since the height of the pipe 243f protruding from the inner wall surface 2412a in the distribution flow path 2412 is larger than the gap between the inner wall surface 2412b and the wall member 246 on the opposite side of the distribution header 241 from the side where the wall member 246 is provided. S3 can be reduced, thereby increasing the fluid resistance of the inlet 2431a of the refrigerant passage 2431 in the downstream refrigerant pipe 243f. The increase in fluid resistance due to the wall member 246 thus provided, that is, gas-liquid separation of the refrigerant (gas-liquid two-phase refrigerant) that flows into and passes through the distribution channel 2412 from the inlet 2411 due to viscous resistance, By retaining the liquid refrigerant by the wall member 246, it is possible to promote the refrigerant inflow to the refrigerant passage 2431 in the upstream refrigerant pipe 243e, and to make the refrigerant flowing into the refrigerant passage 2431 uniform. Moreover, since it is only necessary to provide the wall member 246 inside the distribution header 241, it is possible to apply the refrigerant pipes 243 having the same extension length, thereby using the common refrigerant pipe 243, and as a result. Thus, the manufacturing cost can be reduced.

  Therefore, according to the evaporator 24 according to the third embodiment, the refrigerant flowing from the distribution header 241 into the refrigerant passage 2431 of the refrigerant pipe 243 can be made uniform while reducing the manufacturing cost.

  As mentioned above, although Embodiment 1-3 of this invention was demonstrated, this invention is not limited to this, A various change can be performed.

  In Embodiment 3 described above, the amount of insertion of the upstream refrigerant pipe 243e into the distribution header 241 and the amount of insertion of the downstream refrigerant pipe 243f are equal, but the present invention is not limited to this, and the upstream refrigerant The insertion amount of the downstream refrigerant pipe may be larger than the insertion amount of the pipe with respect to the distribution header.

  In Embodiment 3 described above, the refrigerant pipe 243 is inserted from the side of the distribution header 241, but in the present invention, as shown in FIG. The refrigerant pipe 243 may be inserted at the location.

  As described above, the heat exchanger according to the present invention is useful for an evaporator constituting a refrigeration cycle or the like used for cooling a product in a vending machine or the like.

1 Main body cabinet
3 Commodity storage box 24 Evaporator 241 Distribution header 2411 Inflow port 2412 Distribution flow path 2412a Inner wall surface 2412b Inner wall surface 242 Merge header 243 Refrigerant tube 243a Upstream refrigerant tube 243b Downstream refrigerant tube 243c Upstream refrigerant tube 243d Downstream refrigerant tube 243e Upstream refrigerant pipe 243f Downstream refrigerant pipe 2431 Refrigerant passage 2431a Inlet 244 Corrugated fin 245 End face 246 Wall member

Claims (3)

A tubular distribution header having a distribution channel formed therein for allowing the refrigerant flowing in through the inlet formed at the one end to pass along the horizontal direction toward the closed other end;
Each has a flat shape in which a plurality of refrigerant passages are arranged in parallel along the horizontal direction, and the inlets of the respective refrigerant passages are inserted along the pipe axis direction of the distribution header in such a manner as to face the distribution flow path. A plurality of attached refrigerant pipes, and distributes the refrigerant from the distribution header to the respective refrigerant passages of the refrigerant pipes to exchange heat between the refrigerant passing through the refrigerant passages and the fluid passing through the surroundings of the refrigerant pipes. In the heat exchanger to perform
The heat exchanger according to claim 1, wherein an insertion amount of the refrigerant pipe on the other end side is made larger than an insertion amount of the refrigerant pipe on the one end side with respect to the distribution header.   2. The heat according to claim 1, wherein an end face of the refrigerant pipe inserted into the distribution header is formed such that an insertion amount gradually increases from the one end portion toward the other end portion. Exchanger. A tubular distribution header having a distribution channel formed therein for allowing the refrigerant flowing in through the inlet formed at the one end to pass along the horizontal direction toward the closed other end;
Each has a flat shape in which a plurality of refrigerant passages are arranged in parallel along the horizontal direction, and the inlets of the respective refrigerant passages are inserted along the pipe axis direction of the distribution header in such a manner as to face the distribution flow path. A plurality of attached refrigerant pipes, and distributes the refrigerant from the distribution header to the respective refrigerant passages of the refrigerant pipes to exchange heat between the refrigerant passing through the refrigerant passages and the fluid passing through the surroundings of the refrigerant pipes. In the heat exchanger to perform
A protrusion that is provided between the refrigerant pipe on the one end side and the refrigerant pipe on the other end side adjacent thereto, and that is at least larger than the protrusion height of the refrigerant pipe on the one end side from the inner wall surface in the distribution channel. A heat exchanger comprising a wall member having a height.

Images