JP5408951B2 - Refrigerant evaporator and air conditioner using the same - Google Patents

Description

  The present invention relates to a refrigerant evaporator provided in a refrigeration cycle, and more particularly to an aluminum alloy refrigerant evaporator suitable for application to a vehicle air conditioner and an air conditioner using the same.

  As a refrigerant evaporator used in a refrigeration cycle of a vehicle air conditioner, it has a refrigerant flow path for flowing a refrigerant in the vertical direction, and is arranged in parallel in a direction orthogonal to the flow direction of air flowing outside the refrigerant flow path. In addition, a large number of refrigerant tubes arranged in a plurality of rows before and after along the air flow direction, and a plurality of rows connected to the upper and lower ends of the many refrigerant tubes in a direction orthogonal to the air flow direction The refrigerant is divided into a first tank part and a second tank part by a partition wall in a row direction corresponding to the refrigerant tubes, and includes a pair of upper and lower tanks for distributing or collecting the refrigerant, and refrigerant flowing from the refrigerant inlet Is configured to cool the air by sequentially circulating the refrigerant in the refrigerant tubes of a plurality of blocks partitioned by partition plates provided at a plurality of locations in the tank to exchange heat with the air. Alloy refrigerant evaporator is known.

  In the refrigerant evaporator having the above configuration, in one of the plurality of blocks, the refrigerant flows into the first tank portion of the upper tank from the direction along the partition wall, and passes through the side refrigerant passage from the first tank portion to the second tank. Patent Document 1 describes a U-turn block unit that is distributed to a plurality of refrigerant tubes and further distributed from a first tank unit and a second tank unit to a plurality of refrigerant tubes. Further, in Patent Document 2, a plurality of refrigerant tubes are arranged on the partition wall in order to distribute the refrigerant collected in the second tank part of the upper tank through the plurality of refrigerant tubes to the first tank part with the partition wall therebetween. The thing which perforate | pierced this communication hole is described.

Japanese Patent No. 3637314 Japanese Patent No. 3391339

  However, in the refrigerant evaporator described in Patent Document 1, the liquid refrigerant easily flows into the refrigerant tube on the near side in the refrigerant inflow direction due to inertia in the upper U-turn block portion of the upper tank, and from the first tank portion. In some cases, the liquid refrigerant that has flowed into the second tank portion cannot sufficiently reach its innermost side. For this reason, the distribution of the liquid refrigerant to the plurality of refrigerant tubes connected to the second tank portion becomes non-uniform, and there is a portion where heat exchange with the air flowing outside the refrigerant tubes is not effectively performed. There is a problem that the performance deteriorates.

  On the other hand, in the refrigerant evaporator described in Patent Document 2, a refrigerant wall having a plurality of communication holes formed in a partition wall that partitions the first tank portion and the second tank portion is described. The refrigerant collected in the second tank part of the upper tank is circulated as it is to the first tank part with the partition wall therebetween, and in the U-turn block part of the upper tank, the first tank part of the upper tank This suggests that the liquid refrigerant flowing in from the direction along the partition wall is evenly distributed over the entire area in the length direction with respect to both the first tank portion and the second tank portion constituting the U-turn block portion. Not what you want.

  In addition, when a plurality of communication holes are drilled in the partition wall that separates the tanks, the stress due to the refrigerant pressure applied to the tank acts on the wall surface between the plurality of communication holes, which affects the pressure resistance of the tank. Will be affected. Therefore, in order to ensure the pressure resistance of the tank, there is a configuration in which restrictions such as ensuring a uniform refrigerant distribution function and securing an opening area are imposed, while preventing an increase in refrigerant pressure loss and increasing the plate thickness. It is necessary to set a communication hole in the partition wall.

  This invention is made in view of such a situation, Comprising: Distribution of the liquid refrigerant | coolant to the several refrigerant | coolant tube connected to the 1st tank part and 2nd tank part of a U-turn block part is equalize | homogenized. An object of the present invention is to provide a refrigerant evaporator capable of improving the heat exchange performance and ensuring sufficient pressure resistance of the tank section, and an air conditioner using the refrigerant evaporator.

In order to solve the above problems, the refrigerant evaporator of the present invention and the air conditioner using the same employ the following means.
That is, the refrigerant evaporator according to the present invention has a refrigerant flow path for flowing the refrigerant in the vertical direction, and is arranged in parallel in a direction orthogonal to the flow direction of the external fluid flowing outside the refrigerant flow path. A large number of refrigerant tubes arranged in a plurality of rows back and forth along the flow direction of the external fluid, and connected to the upper and lower ends of the multiple refrigerant tubes and arranged in a direction orthogonal to the flow direction of the external fluid, Corresponding to the plurality of rows of refrigerant tubes, the interior is partitioned into a first tank portion and a second tank portion by a partition wall in the row direction, and includes a pair of upper and lower tanks for distributing or collecting refrigerant, Are provided with a refrigerant inlet and a refrigerant outlet, and the refrigerant flowing in from the refrigerant inlet sequentially passes through the refrigerant tubes of a plurality of blocks partitioned by partition plates provided at a plurality of locations in the tank. In the refrigerant evaporator made of aluminum alloy that flows out from the refrigerant outlet after being circulated, one of the plurality of blocks is configured such that the refrigerant is either the first tank part or the second tank part of the upper tank. U flows from the direction along the partition wall, flows from there to the other tank portion, and is distributed from each of the first tank portion and the second tank portion to the plurality of refrigerant tubes. A clad in which the partition wall for partitioning the upper and lower tanks between the first tank portion and the second tank portion is made of A3003-H14 as a core block. A plurality of refrigerant distribution holes are provided in the partition wall along the length direction of the partition wall communicating between the first tank portion and the second tank portion; , When the distance of a plurality of holes b, and hole column pore length a, the partition wall thickness was t, a / b ≦ -0.0697 × t 2 + 0.3274 × t + 0.4594, but , T = 1 to 2 mm.

According to the present invention, in the U-turn block portion, the liquid refrigerant in the gas-liquid two-phase refrigerant that flows into the first tank portion or the second tank portion from the direction along the partition wall is transferred to the partition wall. A plurality of refrigerant distribution holes provided along the length direction are sequentially distributed to the other tank portion, and the refrigerant inflow direction is supplied to both the first tank portion and the second tank portion of the U-turn block portion. Since it can be made to flow in substantially uniformly over the whole area, it becomes possible to distribute liquid refrigerant substantially uniformly to a plurality of refrigerant tubes connected to the 1st tank part and the 2nd tank part. Therefore, the distribution of the liquid refrigerant that mainly contributes to cooling of the external fluid can be made more uniform, and the heat exchange performance of the refrigerant evaporator can be improved. In addition, when the distance between the plurality of holes in the refrigerant distribution hole is b, the hole length in the hole row direction is a, and the thickness of the partition wall with A3003-H14 as the core is t, a / b ≦ −0 .0697 × t ² + 0.3274 × t + 0.4594, where t = 1 to 2 mm. Therefore, the distance between the plurality of refrigerant distribution holes provided in the partition wall is at least 2.55 MPa or more. The dimensions can satisfy the withstand pressure. Therefore, it is possible to easily secure the pressure resistance of the tank portion against the internal pressure by optimizing the dimensions of the refrigerant distribution holes in the partition wall having a restricted configuration.

Furthermore, the refrigerant evaporator of the present invention is the above-described refrigerant evaporator, wherein a / b of the refrigerant distribution hole is a / b ≦ −0.0744 × t ² + 0.3577 × t + 0.3786, where t = It is characterized by being 1 to 2 mm.
According to the present invention, the a / b of the refrigerant distribution hole is a / b ≦ −0.0744 × t ² + 0.3577 × t + 0.3786, where t = 1 to 2 mm. The distance between the refrigerant distribution holes can be set to a dimension that can satisfy a breaking pressure of at least 3.3 MPa. Therefore, by optimizing the dimensions of the refrigerant distribution holes, the pressure resistance of the tank portion against the internal pressure can be easily increased further.

Furthermore, the refrigerant evaporator of the present invention is the above-described refrigerant evaporator, wherein a / b of the refrigerant distribution hole is a / b ≦ −0.0763 × t ² + 0.3810 × t + 0.2847, where t = It is characterized by being 1 to 2 mm.

According to the present invention, a / b of the refrigerant distribution hole is a / b ≦ −0.0763 × t ² + 0.3810 × t + 0.2847, where t = 1 to 2 mm. Even if the variation in the distance between the refrigerant distribution holes is taken into consideration, the dimension can satisfy the breaking pressure of 4.5 MPa or more. Therefore, the pressure-resistant strength of the tank portion against the internal pressure can be easily ensured easily by optimizing the dimensions of the refrigerant distribution hole group.

  The refrigerant evaporator according to the present invention is characterized in that, in any one of the refrigerant evaporators described above, the refrigerant distribution holes are elongated holes in a direction perpendicular to the direction of the hole rows of the refrigerant distribution holes. To do.

  According to the present invention, since the refrigerant distribution hole is a long hole extending in a direction orthogonal to the direction of the hole row of the refrigerant distribution hole, the a / b of the plurality of refrigerant distribution holes can be reduced to reduce the tank portion. The opening area of the refrigerant distribution hole can be made large enough to allow the refrigerant to pass through without increasing the pressure loss while ensuring the pressure resistance. Therefore, it is possible to increase the pressure resistance of the tank portion while suppressing an increase in the pressure loss of the refrigerant due to the refrigerant distribution hole and eliminating the influence on the heat exchange performance.

Furthermore, the refrigerant evaporator according to the present invention is characterized in that, in the refrigerant evaporator, the long hole is an elliptical hole or an oval hole.

  According to the present invention, since the long hole is an elliptical hole or an oval hole, the refrigerant can be passed through the opening area of the plurality of refrigerant distribution holes without increasing the pressure loss. The distance between the distribution holes can be set to a dimension that sufficiently satisfies the pressure resistance or the breaking pressure. Accordingly, it is possible to easily increase the pressure resistance of the tank portion against the internal pressure by optimizing the hole shape of the refrigerant distribution hole while suppressing the increase in the pressure loss of the refrigerant due to the refrigerant distribution hole and eliminating the influence on the heat exchange performance.

  Furthermore, the air conditioner according to the present invention is characterized in that the refrigerant evaporator provided in the refrigeration cycle is any one of the refrigerant evaporators described above.

  According to the present invention, since the refrigerant evaporator provided in the refrigeration cycle is one of the refrigerant evaporators described above, the performance of the air conditioner can be improved by improving the performance of the refrigerant evaporator. At the same time, the reliability of the air conditioner can be improved by increasing the pressure resistance of the refrigerant evaporator.

  According to the refrigerant evaporator of the present invention, the liquid refrigerant in the gas-liquid two-phase refrigerant flowing from the direction along the partition wall is supplied to the first tank portion and the second tank portion of the U-turn block portion formed in the upper tank. Since the liquid can be distributed and distributed almost uniformly over the entire region in the refrigerant inflow direction, the liquid refrigerant is more evenly distributed to the plurality of refrigerant tubes connected to the first tank portion and the second tank portion. And the heat exchange performance of the evaporator can be improved. In addition, since the distance between the plurality of refrigerant distribution holes provided in the partition wall having A3003-H14 as a core material can be set to a dimension that can satisfy a pressure pressure of at least 2.55 MPa, the restriction By optimizing the dimensions of the refrigerant distribution holes in the partition wall having the above structure, it is possible to easily secure the pressure resistance of the tank portion against the internal pressure.

  Furthermore, according to the air conditioner of the present invention, the performance of the air conditioner can be improved by improving the performance of the refrigerant evaporator, and at the same time, the reliability of the air conditioner can be improved by increasing the pressure resistance of the refrigerant evaporator. Can do.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 5, 7, and 8. FIG. 1 is a perspective view of the refrigerant evaporator 1 according to the first embodiment of the present invention, FIG. 2 is an exploded perspective view thereof, and FIG. 3 is a front view (A) thereof. A right side view (B) is shown. FIG. 4 shows a side view of the partition wall provided in the tank.

  The refrigerant evaporator 1 includes a large number of refrigerant tubes 2 having a plurality of refrigerant flow paths 2A along the length direction. The refrigerant tube 2 is manufactured by, for example, an aluminum alloy flat tube manufactured by extrusion molding or pultrusion molding, or by forming a plate material into an elliptical cylinder and inserting and installing an inner fin therein. Can be configured.

  A large number of refrigerant tubes 2 are stacked in parallel in a direction orthogonal to the flow direction of the external fluid (air) A that flows outside the refrigerant tubes 2. The refrigerant tubes 2 are arranged in a plurality of rows (two rows) in the front-rear direction with respect to the air A flow direction. In this way, between a large number of refrigerant tubes 2 stacked in parallel in a direction perpendicular to the flow direction of the air A, a transmission formed by corrugating a thin plate made of, for example, an aluminum alloy into a corrugated shape. A heat fin 3 is interposed and brazed to the outer surface of the refrigerant tube 2 by a known method.

  An upper tank 4 and a lower tank 5 each having a substantially oval cross section are brazed and joined to upper ends and lower ends of a large number of refrigerant tubes 2. The upper tank 4 and the lower tank 5 are divided into upper and lower members 4A and 5A and lower members 4B and 5B, and the interiors of the upper tank 4 and the lower tank 5 correspond to the plurality of rows of refrigerant tubes 2. The partition walls 4C and 5C partitioning the first tank portion 6, the second tank portion 7, the first tank portion 8 and the second tank portion 9 in the direction, and both ends of the upper tank 4 and the lower tank 5 are respectively closed. The cap members 4D and 5D and 4E and 5E are configured. These upper members 4A, 5A, lower members 4B, 5B, partition walls 4C, 5C, cap members 4D, 5D and 4E, 5E are constituted by press-formed products made of aluminum alloy, and are brazed together by a known method. Has been.

  In the lower members 4B and 5B constituting the upper tank 4 and the lower tank 5, tube insertion holes 4F and 5F for inserting and brazing and joining the ends of a large number of refrigerant tubes 2 correspond to the arrangement of the refrigerant tubes 2. Many are provided. The cap member 5E of the lower tank 5 is provided with a refrigerant inlet 5G communicated with the first tank portion 8, and the refrigerant inlet header 10 is brazed and joined so as to communicate with the refrigerant inlet 5G of the cap member 5E. ing. Further, the cap member 4E of the upper tank 4 is provided with a refrigerant outlet 4G communicating with the second tank portion 7, and the refrigerant outlet header 11 is brazed so as to communicate with the refrigerant outlet 4G of the cap member 4E. It is joined. A refrigerant inlet pipe 12 and a refrigerant outlet pipe 13 are connected to the refrigerant inlet header 10 and the refrigerant outlet header 11, respectively.

  Inside the upper tank 4 and the lower tank 5, the second tank portion 7 of the upper tank and the first tank portion 8 of the lower tank 5 are respectively along a direction (tank length direction) perpendicular to the flow direction of the air A. In addition, partition plates 4H and 5H for partitioning into two left and right regions are provided. In the present embodiment, the partition plates 4H and 5H are positions where the ratio of the number of the refrigerant tubes 2 in the left area shown in the drawing and the number of the refrigerant tubes 2 in the right area is substantially 1: 2 Is provided. Further, on the second tank portion 9 side of the lower tank 5, throttle holes 5 </ b> K and 5 </ b> L that gradually decrease toward the end portion on the cap member 5 </ b> E side at two appropriate positions in the tank length direction in the right region of the drawing. The two diaphragm plates 5I and 5J are provided at a predetermined interval.

  Furthermore, the partition walls 4C and 5C of the upper tank 4 and the lower tank 5 are provided with the first tank portion 6 and the second tank portion 7 and the lower tank of the upper tank 4 in the left region of the figure partitioned by the partition plates 4H and 5H. A plurality of refrigerant distribution holes 4M and 5M communicating the first tank portion 8 and the second tank portion 5 are provided along the length direction of the partition walls 4C and 5C. The refrigerant distribution holes 4M, 5M are liquid refrigerants in the gas-liquid two-phase refrigerant that flows into the left region from the right region in the figure along the length direction of the partition wall 4C in the first tank portion 6 of the upper tank 4. The second tank portion 7 has a function of flowing in while being distributed substantially evenly in the length direction of the left side region of the figure.

  Further, the partition plate 5H is provided in the first tank portion 8 of the lower tank 5 to which the refrigerant inlet header 10 is connected, and the partition plate 4H is provided in the second tank portion 7 of the upper tank 4 to which the refrigerant outlet header 11 is connected. Thus, the refrigerant flow path in the refrigerant evaporator 1 is divided into three blocks, a first block 14, a second block (U-turn block) 15, and a third block 16 described below. The first block 14 allows the refrigerant flowing from the refrigerant inlet header 10 to the first tank portion 8 of the lower tank 5 through the plurality of refrigerant tubes 2 connected to the right region of the partition plate 5H. It is a block that circulates to one tank unit 6.

  The second block (U-turn block) 15 causes the refrigerant flowing into the first tank portion 6 of the upper tank 4 to flow along the partition wall 4C to the left region in the figure, and from there, a plurality of refrigerant distribution holes 4M is distributed almost evenly along the length direction of the second tank part 7 to the left side region of the partition plate 4H of the second tank part 7, and the inside of the plurality of refrigerant tubes 2 from both the first tank part 6 and the second tank part 7. This is a block that flows down and flows to the first tank portion 8 and the second tank portion 9 of the lower tank 5, and is also referred to as a U-turn block. The refrigerant that has flowed down to the first tank portion 8 and the second tank portion 9 of the lower tank 5 is collected in the second tank portion 9 through the refrigerant distribution hole 5M.

  Further, the third block 16 causes the refrigerant collected in the second tank portion 9 to flow to the right region along the partition wall 5C, and from there to the second tank portion 7 of the upper tank 4 through the plurality of refrigerant tubes 2. It is a block to distribute. The refrigerant circulated in the second tank portion 7 of the upper tank 4 in the third block 16 flows out to the refrigerant outlet pipe 13 through the outlet header 11.

  As shown in FIG. 4, the plurality of refrigerant distribution holes 4M, 5M provided in the partition walls 4C, 5C can secure a sufficient opening area so that the pressure loss of the circulating refrigerant does not increase, and the internal pressure In order to relieve the stress concentration caused by the above and to ensure sufficient pressure resistance, it is constituted by elongated holes 4m, 5m such as elliptical holes or oval holes elongated in the direction orthogonal to the hole row direction. Further, the long holes 4m and 5m have a distance of a plurality of long holes (hole pitch) as b, a hole length in the hole row direction as a, and a thickness of the partition walls 4C and 5C as t. In order to improve the pressure resistance of the tank 4 and the lower tank 5, the following structure is provided.

  FIG. 7 shows a / b (horizontal axis) and tank partition part breaking pressure P [MPa] (vertical axis) when the thicknesses t of the partition walls 4C and 5C are 1 mm, 1.3 mm, and 2 mm, respectively. FIG. 8 shows the graph of FIG. 7 in which the thickness t of the partition walls 4C and 5C is the horizontal axis, and a / b is the vertical axis. In consideration of the partition wall thickness t, the a / b range in which the necessary tank partition breaking pressure P (P = 2.55, P = 3.3, P = 4.5) can be secured is represented. A graph converted to a polynomial is shown.

From this analysis result, in order to satisfy a pressure resistance of at least 2.55 MPa (P = 2.55), the a / b is a polynomial of P = 2.55, that is, a / b ≦ −0.0697 × t. ² + 0.3274 × t + 0.4594, where t = 1 to 2 mm indicates that a pressure resistance of 2.55 MPa or more is satisfied and a necessary pressure resistance can be ensured. The partition walls 4C and 5C are double-sided clad materials having a core material of A3003-H14 and a skin material of A4343. If the plate thickness t is too thin, the strength is insufficient, and if it is thick, the thickness direction dimension of the tank is increased. Or since the passage area in a tank reduces, it is normally set to 1-2 mm.

Further, since the long holes 4m and 5m satisfy a breaking pressure of at least 3.3 MPa, the a / b is a / b ≦ −0.0744 × t ² + 0.3577 × t + 0.3786, where t = It is desirable to be 1 to 2 mm, and furthermore, it is possible to satisfy a fracture pressure of 4.5 MPa or more even when taking into account variations in the distance between the holes of the plurality of long holes 4 m and 5 m. Thus, a / b ≦ −0.0763 × t ² + 0.3810 × t + 0.2847, where t = 1 to 2 mm is more desirable.

According to this embodiment described above, the following operational effects are obtained.
The gas-liquid two-phase refrigerant that has flowed into the first tank 8 part of the lower tank 5 from the refrigerant inlet pipe 12 through the refrigerant inlet header passes through the plurality of refrigerant tubes 2 of the first block 14 in the first tank part of the upper tank 4. During the flow toward 6, heat is exchanged with the air A through the heat transfer fins 3, and a part thereof is evaporated. The refrigerant collected in the first tank portion 6 of the upper tank 4 flows into the left region through the first tank portion 6 and enters the second block (U-turn block) 15. The gas-liquid two-phase refrigerant that has flowed into the second block (U-turn block) 15 passes through the first tank portion 6 and is secondly supplied by the refrigerant distribution holes 4M including the long holes 4m provided in the partition wall 4C. Evenly distributed to the tank unit 7.

  The refrigerant equally distributed to the first tank portion 6 and the second tank portion 7 of the upper tank 4 in the second block (U-turn block) 15 is in the refrigerant tubes 2 of the second block (U-turn block) 15. The air is exchanged with the air A via the heat transfer fins 3 while flowing down toward the first tank portion 8 and the second tank portion 9 of the lower tank 5 and further evaporated. The refrigerant that has flowed down to the first tank portion 8 and the second tank portion 9 of the lower tank 5 is collected in the second tank portion 9 by the refrigerant distribution holes 5M (long holes 5m) provided in the partition wall 5C, and 2 circulates in the right side area in the tank unit 9 and enters the third block 16. This refrigerant rises in the plurality of refrigerant tubes 2 of the third block 16 toward the second tank portion 7 of the upper tank 4, and during this time, heat exchange with the air A is performed, and all the gas is evaporated and gasified. 7 is assembled. The air A cooled by heat exchange with the refrigerant is supplied into the passenger compartment and used for cooling. On the other hand, the evaporated gas refrigerant is sucked into the compressor from the outlet header 11 via the refrigerant outlet pipe 13. Circulates in the refrigeration cycle.

  As described above, in the second block (U-turn block) 15 in which the refrigerant makes a U-turn in the upper tank 4, the gas-liquid two-phase flow that flows into the first tank portion 6 of the upper tank 4 along the partition wall 4C. As shown in FIG. 5, the refrigerant is sequentially increased from the front side by a plurality of refrigerant distribution holes 4M including long holes 4m elongated in the vertical direction provided along the length direction of the partition wall 4C. Since it is distributed to the two tank parts 7, the liquid refrigerant can be made to flow into the second tank part 7 almost uniformly over the entire region in the length direction. As a result, the liquid refrigerant can be distributed substantially uniformly to the plurality of refrigerant tubes 2 connected to the first tank portion 6 and the second tank portion 7 of the second block.

  Therefore, according to the refrigerant evaporator 1 described above, in particular, the distribution of the liquid refrigerant between the first tank part 6 and the second tank part 7 of the U-turn block 15 is improved, contributing to the cooling of the air A that is the external fluid. Since the distribution of the liquid refrigerant to be performed to the plurality of refrigerant tubes 2 can be made more uniform, the heat transfer area can be effectively functioned and the heat exchange performance of the refrigerant evaporator 1 can be improved.

  On the other hand, it is necessary to increase the pressure resistance of the upper tank 4 and the lower tank 5 with respect to the refrigerant used. In particular, in the upper tank 4 and the lower tank 5 in which the refrigerant distribution holes 4M and 5M are provided in the partition walls 4C and 5C, the stress due to the internal pressure is concentrated on the hole row portions of the refrigerant distribution holes 4M and 5M. For this reason, in the refrigerant distribution holes 4M and 5M, a hole array is provided so that an opening area is sufficiently ensured so that pressure loss of the circulating refrigerant is not increased, and stress concentration due to internal pressure is eased to sufficiently secure pressure resistance. It is constituted by elongated holes 4m, 5m such as elliptical holes or oval holes elongated in a direction perpendicular to the direction.

  Thus, the opening area of the refrigerant distribution holes 4M, 5M (long holes 4m, 5m) is made large enough to allow the refrigerant to pass through without increasing pressure loss, and a plurality of refrigerant distribution holes 4M, 5M (long holes 4m, 4m, The distance between the holes of 5 m) can be set to a dimension that can sufficiently satisfy the pressure resistance or breaking pressure. Therefore, the pressure-resistant strength of the upper tank 4 and the lower tank 5 with respect to the internal pressure can be easily reduced by optimizing the hole shape of the refrigerant distribution holes 4M and 5M while suppressing an increase in the pressure loss of the refrigerant in the partition walls 4C and 5C having a limited configuration. It becomes possible to raise.

Further, regarding the plurality of refrigerant distribution holes 4M and 5M (long holes 4m and 5m), when the distance between the plurality of holes is b, the hole length in the hole row direction is a, and the partition wall thickness is t, a /B≦−0.0697×t ² + 0.3274 × t + 0.4594, where t = 1 to 2 mm, and therefore, a plurality of refrigerant distribution holes 4M and 5M provided in the partition walls 4C and 5C ( The distance between the long holes 4m and 5m) can be set to a dimension that can satisfy a pressure resistance of at least 2.55 MPa.

FIG. 7 shows the above a / b (horizontal axis) and tank partition part breaking pressure P [MPa] (vertical axis) when the thicknesses t of the partition walls 4C and 5C are 1 mm, 1.3 mm, and 2 mm, respectively. FIG. 8 shows the graph shown in FIG. 7 in which the thickness t of the partition walls 4C and 5C is the horizontal axis, a / b is the vertical axis, and the partition wall thickness t is considered. Above, the graph converted into a polynomial representing the range of a / b that can secure the necessary tank partitioning portion breaking pressure P is shown. From this result, in order to satisfy a pressure resistance of at least 2.55 MPa, a / b is a / b ≦ −0.0697 × t ² + 0.3274 × t + 0.4594, where t = 1 to 2 mm. In this case, it is clear that the pressure resistance can be satisfied and the necessary pressure strength can be secured.

Similarly, by setting a / b to a / b ≦ −0.0744 × t ² + 0.3577 × t + 0.3786, where t = 1 to 2 mm, a breaking pressure of at least 3.3 MPa or more is obtained. In addition, a / b ≦ −0.0763 × t ² + 0.3810 × t + 0.2847, where t = 1 to 2 mm, so that a plurality of long holes 4 m and 5 m are formed. It is clear that even when the variation in the distance is taken into consideration, it is possible to satisfy the breaking pressure of 4.5 MPa or more, and to sufficiently secure the necessary pressure strength.

  Therefore, according to this embodiment, since the tank size increases, the plate thickness cannot be increased, the number of holes cannot be reduced to ensure a uniform distribution function of the refrigerant, and the pressure loss of the passing refrigerant is suppressed. Therefore, in the partition walls 4C and 5C in which restrictions such as the need to increase the opening area are imposed, the internal pressure can be easily obtained by optimizing the dimensions of the refrigerant distribution holes 4M and 5M (long holes 4m and 5m). The pressure resistance of the tank part against the

  In the above embodiment, as shown in FIG. 3, a large number of ribs 4N, 5N may be integrally formed on the surfaces of the upper members 4A, 5A of the headers 4, 5. Further, each component of the refrigerant evaporator 1 shown in FIG. 2 is not individually brazed and joined, and as is well known, after all the components are temporarily assembled, they are carried into the furnace. It can be manufactured by heating and brazing together in a furnace.

  Further, the above-described aluminum alloy refrigerant evaporator 1 is suitable as a refrigerant evaporator constituting a refrigeration cycle of a vehicle air conditioner that is particularly required to be reduced in weight and size, and by applying the refrigerant evaporator 1 The performance of the air conditioner can be improved, and at the same time, the reliability as the air conditioner can be improved by increasing the pressure resistance of the refrigerant evaporator 1.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
The present embodiment is different from the first embodiment in the way of providing the refrigerant distribution holes 4M and 5M (long holes 4m and 5m) provided in the partition walls 4C and 5C. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, in the second block (U-turn block) 15, a plurality of refrigerant distribution holes 4M, 5M (long holes 4m, 5m) provided in the partition walls 4C, 5C are as shown in FIG. When the total length (the dimension from the left end of the upper tank 4 to the partition plate 4H) of the upper tank 4 constituting the second block (U-turn block) 15 is L2, the front side in the refrigerant inflow direction A plurality of areas are provided in the range of the length L1 of the rear area excluding the partial area.

  The back side region length L1 is a length from the innermost end of the first tank unit 6 and the second tank unit 7 to the position of the refrigerant distribution hole 4M on the front side, and the length of the back side region. L1 is practically in a range of 0.7 <L1 / L2 <0.9 with respect to the total length L2, and L1 / L2 is most preferably around 0.8. By setting it as such a structure, compared with the case of 1st Embodiment, a refrigerant | coolant distribution state can be improved further and the heat exchange performance of the refrigerant | coolant evaporator 1 can further be improved. If L1 / L2 is less than 0.7, the liquid refrigerant distribution to the region from the partition plate 4H in the second tank portion 7 is slightly insufficient, whereas if L1 / L2 exceeds 0.9, On the contrary, the liquid refrigerant distribution with respect to the innermost region is slightly insufficient, and from this, it can be said that L1 / L2 is most preferably about 0.8.

  In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, in the above-described embodiment, the plurality of refrigerant distribution holes 4M and 5M (long holes 4m and 5m) provided along the length direction of the partition walls 4C and 5C are all the same size. The distribution holes 4M and 5M (long holes 4m and 5m) may be configured to gradually increase in size from the near side to the far side in the refrigerant inflow direction. As a result, the liquid refrigerant that is easily distributed to the refrigerant distribution hole 4M (long hole 4m) on the front side due to inertia is sequentially shifted to the refrigerant distribution hole 4M (long hole 4m) on the back side. Improving the distribution of the liquid refrigerant flowing into the second tank part 7 in the refrigerant inflow direction, and distributing the liquid refrigerant almost evenly over the entire area of the first tank part 6 and the second tank part 7 in the refrigerant inflow direction. Thus, the distribution of the liquid refrigerant to the plurality of refrigerant tubes 2 can be made uniform, and the heat exchange performance of the refrigerant evaporator 1 can be further improved.

  Moreover, in the said embodiment, although what made the refrigerant | coolant flow from the 1st tank part 6 side to the 2nd tank part side was illustrated in the U-turn block 15, conversely, the 1st tank part from the 2nd tank part side Of course, it is good also as a structure which flows to 6 side. Moreover, although the said embodiment demonstrated the example which divided the refrigerant | coolant distribution path in the refrigerant evaporator 1 into 3 blocks, about the number of blocks, it is not limited to 3 blocks. Further, the inlet and outlet of the refrigerant with respect to the refrigerant evaporator 1 may be provided either on the top or bottom or on the left or right.

It is a perspective view of the refrigerant evaporator concerning a 1st embodiment of the present invention. It is a disassembled perspective view of the refrigerant evaporator shown in FIG. It is the front view (A) of the refrigerant evaporator shown in FIG. 1, and its right view (B). It is a side view of the partition wall provided in the upper tank and lower tank of a refrigerant evaporator shown in FIG. It is a top view which shows the refrigerant | coolant distribution state of the U-turn block part in the refrigerant evaporator shown in FIG. It is a top view which shows the refrigerant | coolant distribution state of the U-turn block part in the refrigerant evaporator concerning 2nd Embodiment of this invention. The relationship between the ratio a / b of the hole length a in the row direction of the plurality of refrigerant distribution holes provided in the partition wall of the refrigerant evaporator according to the present invention and the distance b of the plurality of holes, and the tank partition portion breaking pressure P It is an analysis graph which shows. FIG. 8 is a graph in which the graph shown in FIG. 7 is expressed by converting the partition wall thickness t into a horizontal axis and a / b into a vertical axis.

DESCRIPTION OF SYMBOLS 1 Refrigerant evaporator 2 Refrigerant tube 2A Refrigerant flow path 4 Upper tank 5 Lower tank 4C, 5C Partition wall 4G Refrigerant outlet 4H, 5H Partition plate 4M, 5M Refrigerant distribution hole 4m, 5m Long hole 5G Refrigerant inlet 6,8 First tank Parts 7, 9 second tank part 14 first block 15 second block (U-turn block)
16 3rd block a Hole length b of the refrigerant distribution hole (long hole) in the hole row direction Distance between the plurality of refrigerant distribution holes (long hole)

Claims (6)

It has a refrigerant flow path for flowing the refrigerant in the vertical direction, and is arranged in parallel in a direction orthogonal to the flow direction of the external fluid flowing outside the refrigerant flow path, and a plurality of front and rear along the flow direction of the external fluid A number of refrigerant tubes arranged in rows;
The first tank unit is connected to the upper and lower ends of the plurality of refrigerant tubes and arranged in a direction orthogonal to the flow direction of the external fluid, and the interior corresponds to the plurality of rows of refrigerant tubes with a partition wall in the row direction. And a second tank part, and a pair of upper and lower tanks for distributing or collecting the refrigerant,
The tank is provided with a refrigerant inlet and a refrigerant outlet, and the refrigerant flowing in from the refrigerant inlet sequentially passes through the refrigerant tubes of a plurality of blocks partitioned by partition plates provided at a plurality of locations in the tank. In the refrigerant evaporator made of aluminum alloy that flows out from the refrigerant outlet after distribution,
In one of the plurality of blocks, the refrigerant flows into one of the first tank portion and the second tank portion of the upper tank from the direction along the partition wall, and from there, the other tank portion And a U-turn block portion distributed from each of the first tank portion and the second tank portion to the plurality of refrigerant tubes and circulated.
In the U-turn block portion, the partition wall partitioning the first tank portion and the second tank portion of the upper and lower tanks is a clad material using A3003-H14 as a core material, and the partition The wall is provided with a plurality of refrigerant distribution holes along the length direction of the partition wall communicating between the first tank portion and the second tank portion,
The refrigerant distribution hole has a / b ≦ −0.0697 × t ² + 0.3274 ×, where b is the distance between the plurality of holes, a is the hole length in the hole row direction, and t is the partition wall thickness. t + 0.4594, wherein t = 1 to 2 mm. The a / b of the refrigerant distribution hole is a / b ≦ −0.0744 × t ² + 0.3577 × t + 0.3786, where t = 1 to 2 mm. The refrigerant evaporator as described. The a / b of the refrigerant distribution hole is a / b ≦ −0.0763 × t ² + 0.3810 × t + 0.2847, where t = 1 to 2 mm. The refrigerant evaporator as described.   The refrigerant evaporator according to any one of claims 1 to 3, wherein the refrigerant distribution hole is a long hole extending in a direction orthogonal to a hole row direction of the refrigerant distribution hole. The refrigerant evaporator according to claim 4, wherein the elongated hole is an elliptical hole or an oblong hole. An air conditioner, wherein the refrigerant evaporator provided in the refrigeration cycle is the refrigerant evaporator according to any one of claims 1 to 5 .

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