JP2007327664A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve performance by smoothing the flow of a refrigerant in a heat exchanger while securing pressure tightness and reducing the generation of foreign noise in circulating the refrigerant, when the weight of the heat exchanger is reduced by thinning constructional elements of a header tank. <P>SOLUTION: The header tank 5 of the shape extending in the parallel arrangement direction of tubes 2 is composed of an inner plate member 10 and an outer plate member 11. Tube insertion holes 10a are formed at the inner plate member 10, and the tubes 2 are inserted into the tube insertion holes 10a. Projecting portions 11a projecting to an inner part of the header tank 5 are formed on parts of the outer plate member 11 opposite to ends of the tubes 2. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat exchanger used in, for example, an air conditioner.

Conventionally, a plurality of flat tubes arranged side by side in a direction intersecting the flow direction of the external air, and a pair of header tanks provided in a state connected to both ends of the tubes and extending in the direction in which the tubes are arranged in parallel. A heat exchanger provided is known (for example, see Patent Document 1). The end portion of the tube is inserted into a tube insertion hole formed in the peripheral wall portion of the header tank and opens in the header tank. In this heat exchanger, the refrigerant that has flowed into the one header tank from the outside flows into the tubes from one end of each tube while flowing in the direction in which the tubes are juxtaposed. The refrigerant that has flowed through the tube is blown from the other end of the tube into the other header tank and gathers while flowing in the direction in which the tubes are juxtaposed.
Japanese Patent Laid-Open No. 2001-50686

  However, in the heat exchanger of Patent Document 1, since the flow direction of the refrigerant in the header tank is the juxtaposed direction of the tubes, when the refrigerant flows into the tubes from the header tank and the refrigerant that has flowed through the tubes is the header tank. After blowing out, the direction of the flow of the refrigerant changes. Thus, in the location where the flow direction of the refrigerant changes, the flow is less likely to be smooth, and the pressure loss of the refrigerant tends to increase. Further, the refrigerant that has flowed through the tube is blown out from the end of the tube into the header tank. This refrigerant flow is bent downstream by the refrigerant flow formed in the header tank, but most of the refrigerant hits the surface of the header tank facing the end of the tube in multiple directions. This also causes an increase in pressure loss.

  It is also conceivable to reduce the thickness of the header tank components in order to reduce the weight of the heat exchanger. However, when the thickness of the header tank components is reduced, the strength is insufficient, the pressure resistance of the header tank is reduced, and the peripheral wall portion of the header tank easily vibrates due to the pressure fluctuation of the refrigerant, generating abnormal noise. There is also a fear.

  The present invention has been made in view of such points, and the object of the present invention is to devise the shape of the tank when reducing the thickness of the constituent members of the tank and reducing the weight of the heat exchanger. Ensuring the pressure resistance of the tank and suppressing the generation of abnormal noise during the circulation of the refrigerant, and also smoothing the flow of the refrigerant flowing from the tank to the tube and the flow of the refrigerant flowing from the tube to the tank. It is to improve performance.

  In order to achieve the above object, in the present invention, a projecting portion projecting inward is provided at a portion of the tank facing the end portion of the tube.

  Specifically, in the invention of claim 1, in the heat exchanger comprising a tube arranged in parallel in a predetermined direction and a tank connected to an end of the tube and extending in the direction of juxtaposition of the tube, the tank In the part which opposes the edge part of the tube, it is set as the structure by which the protrusion part which protrudes toward the inner side of this tank is provided.

  According to this configuration, since the projecting portion is provided in the tank, it is possible to sufficiently ensure the strength of the tank even when the constituent members of the tank are thinned. Moreover, the refrigerant | coolant which flowed through the tube at the time of refrigerant | coolant distribution | circulation blows off toward the protrusion part in a tank from the edge part of a tube. At this time, since a large flow of the refrigerant is formed in the tank, the refrigerant blown out from the tube is bent to the downstream side in the refrigerant flow direction in the tank by this flow, and the downstream side in the refrigerant flow direction of the protruding portion. Reach the composing surface. The refrigerant that has reached the surface constituting the downstream side of the projecting portion flows toward the base end side of the projecting portion along the surface, and the direction of the flow is directed to the downstream side. Thereby, it is suppressed that the flow of the refrigerant blown out from the tube spreads in multiple directions, and the flow direction is smoothly converted.

  Further, when the refrigerant in the tank flows into the tube, when the refrigerant flowing through the tank hits the protrusion, the refrigerant flows toward the tip side of the protrusion along the surface constituting the protrusion. It is converted smoothly so as to go to the end of the.

  In the invention of claim 2, in the invention of claim 1, the projecting portion extends in the circumferential direction of the tank.

  According to this structure, the range which provides a protrusion part becomes wide.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the tip end surface of the protruding portion is curved toward the inside of the tank.

  According to this configuration, the direction of the refrigerant flow can be changed more smoothly.

  According to a fourth aspect of the present invention, in any one of the first to third aspects of the present invention, the size of the protruding portion in the protruding direction is set to be equal to or greater than the thickness of the material constituting the tank.

  According to this configuration, the height of the protruding portion from the tank inner surface can be sufficiently obtained.

  According to the first aspect of the present invention, since the projecting portion is formed in the tank, the heat exchanger is provided by reducing the thickness of the constituent members of the tank while ensuring the pressure resistance and suppressing the generation of abnormal noise during the circulation of the refrigerant. Weight can be reduced. Then, by arranging the protruding portion so as to face the end portion of the tube, the flow of the refrigerant flowing into the tube from the tank and the flow from the tube into the tank using the large flow of the refrigerant formed in the tank. The direction of the flowing refrigerant can be changed smoothly by the protrusion. Thereby, the pressure loss of the refrigerant | coolant in a heat exchanger can be suppressed, and the performance of a heat exchanger can be improved.

  According to invention of Claim 2, since the protrusion part was made into the shape extended in the circumferential direction of a tank, it can be provided over the wide range of a tank. As a result, the strength of the tank can be further improved, the direction of the refrigerant flow can be smoothly changed over a wide range of the tank, and the performance of the heat exchanger can be further improved.

  According to invention of Claim 3, since the front end surface of the protrusion part was comprised by the curved surface, the direction of the flow of a refrigerant | coolant can be changed more smoothly and the performance of a heat exchanger can be improved further.

  According to invention of Claim 4, the effect by providing the protrusion part in the tank can fully be acquired.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  FIG. 1 shows a heat exchanger 1 according to an embodiment of the present invention. This embodiment demonstrates the case where the heat exchanger 1 is a heat exchanger for cooling of the vehicle air conditioner mounted in a motor vehicle. The heat exchanger 1 constitutes a refrigerant evaporator of a refrigeration circuit, and although not shown, a heat exchanger for heating and the like are placed inside a resin casing disposed inside an instrument panel of a passenger compartment. Is housed in.

  The heat exchanger 1 is provided on a core 4 formed by juxtaposing a large number of tubes 2 and fins 3 extending in the vertical direction in a direction intersecting the flow direction of external air, and on the upper end and lower end of the tube 2, respectively. The upper and lower header tanks 5 and 6 and the end plate 7 provided at the outer end of the core 4 are provided. The tubes 2 are flat tubes having a long cross-sectional shape in the direction of external air flow (indicated by an arrow Y in FIG. 2), and are arranged in two rows in the direction of external air flow. It is connected to the side header tank 6. As these tubes 2, for example, a tube formed by roll forming an aluminum alloy plate material or a tube formed by extruding an aluminum alloy can be used. In the case of a plate material, a brazing material may be provided in layers on the surface of the plate material.

  The fin 3 is a corrugated fin having a wave shape when viewed in the flow direction of the external air, and is made of a thin plate material made of an aluminum alloy. The end plate 7 is also formed by molding a plate made of an aluminum alloy. The tube 2, the fin 3 and the end plate 7 are brazed and integrated.

  The upper header tank 5 extends in the left-right direction of the heat exchanger 1, which is the direction in which the tubes 2 are juxtaposed, and the inner plate member 10 constituting the core 4 side of the header tank 5 and the opposite side of the core 4 The outer plate member 11 is provided. As shown in FIGS. 3 and 4, the inner plate member 10 is formed by forming an aluminum alloy plate material into a channel shape opened upward. A tube insertion hole 10 a is formed in the inner plate member 10 so as to correspond to the interval between the tubes 2. As shown in FIG. 5, the end of the tube 2 is brazed to the peripheral edge of the tube insertion hole 10a in a state of being inserted into the tube insertion hole 10a so as to protrude inward of the header tank 5. . As described above, the inner plate member 10 is brazed to a large number of tubes 2 to ensure strength.

  As shown in FIG. 5, a bulging portion 10b formed to bulge outward from the header tank 5 between the tube insertion holes 10a, 10a adjacent to each other in the tube 2 juxtaposition direction of the inner plate member 10. Is provided. Further, as shown in FIGS. 3 and 4, between the tube insertion holes 10 a and 10 a adjacent to each other in the flow direction of the outside air of the inner plate member 10, a protrusion that protrudes outward from the header tank 5 and extends in the longitudinal direction. Part 10c is formed. The lower edge portion of the first partition member 12 that partitions the inner space of the header tank 5 into an upstream space R1 and a downstream space R2 in the flow direction of the external air is fitted inside the header tank 5 of the protruding portion 10c. Yes. This 1st partition member 12 shape | molds the board | plate material made from an aluminum alloy.

  The outer plate member 11 is formed by forming an aluminum alloy plate so as to form a channel shape opened downward, and is fitted inside the inner plate member 10. As shown in FIG. 5, the outer plate member 11 is provided with a plurality of reinforcing protrusions 11 a that protrude inward of the header tank 5, thereby improving the strength of the outer plate member 11. Yes.

  The protrusion 11 a is positioned at a portion of the outer plate member 11 that faces the end of the tube 2, and extends linearly across both ends of the outer plate member 11 in the outer air flow direction, which is the circumferential direction of the header tank 5. It is formed to extend. The dimension W of the projecting portion 11 in the juxtaposed direction of the tube 2 is set so as to be shorter toward the distal end side in the projecting direction, and the distal end surface of the projecting portion 11a is configured by an arc surface that curves toward the inner side of the header tank 5 Has been. The dimension W of the base end portion of the protruding portion 11 is set longer than the thickness dimension of the tube 2.

  Further, the dimension H in the protruding direction of the protruding portion 11 a is set to be equal to or greater than the thickness of the outer plate member 11 and not more than twice the thickness of the outer plate member 11. The dimension H in the projecting direction of the projecting portion 11a is suppressed to twice or less the thickness of the outer plate member 11. If the projecting height of the projecting portion 11a is too high, the flow resistance of the refrigerant is increased, and the outer plate This is because the moldability of the member 11 is deteriorated. Moreover, the intensity | strength of the outer side plate member 11 comes to be fully acquired by making the dimension H of the protrusion direction of the protrusion part 11a into more than the thickness of the outer side plate member 11. FIG.

  A space between adjacent projecting portions 11a and 11a of the outer plate member 11 is constituted by a flat portion 11b formed substantially flat. As shown in FIGS. 3 and 4, a protrusion 11 c that protrudes outward from the header tank 5 and extends in the longitudinal direction is formed at a substantially central portion of the outer plate member 11 in the flow direction of the external air. The upper edge of the first partition member 12 is fitted inside the header tank 5 of the ridge 11c. Further, as shown in FIG. 1, a second partition member 13 that partitions the inner space in the left-right direction is disposed in the inner space of the upper header tank 5. By the second partition member 13, each of the upstream space R1 and the downstream space R2 of the upper header tank 5 is partitioned into a left portion and a right portion. Note that a communication hole 12a is formed on the first partition member 12 on the left side of the second partition member 13 so that the left side portions of the upstream space R1 and the downstream space R2 communicate with each other.

  A brazing material is provided in layers on the surfaces of the inner plate member 10 and the outer plate member 11, the members 10 and 11 are brazed together, and the first and second partition members 12 and 13 are both plates. The members 10 and 11 are brazed.

  Cap members 15, 15 for closing the end openings formed by the two plate members 10, 11 are provided at the left and right ends of the upper header tank 5. These cap members 15 and 15 are brazed to both plate members 10 and 11. The right cap member 15 is provided with a block member 17 for connecting a refrigerant pipe (not shown). As shown in FIG. 2, the block member 17 has a refrigerant inflow hole 17a communicating with the downstream space R2 of the upper header tank 5, and a refrigerant outflow hole 17b communicating with the upstream space R1. Although not shown, a cooler pipe through which the refrigerant that has passed through the expansion valve flows is connected to the refrigerant inflow hole 17a, and a cooler pipe that communicates with the suction port of the compressor is connected to the refrigerant outflow hole 17b. Yes.

  The lower header tank 6 is configured in the same manner as the upper header tank 5, and as shown in FIG. 1, an inner plate member 20, an outer plate member 21, a first partition member (not shown), and a cap member 25. It has. As shown in FIG. 6, the inner plate member 20 has a tube insertion hole 20a, a bulging portion 20b, and a protrusion (not shown), and the outer plate member 21 has a protruding portion 21a and a flat portion 21b. And a protrusion (not shown). The lower header tank 6 is not provided with a second partition member.

  While providing the 1st partition member 12 and the 2nd partition member 13 as mentioned above, and forming the communicating hole 12a in the 1st partition member 12, as shown in FIG. 1, the tube of the flow direction downstream of external air is shown. 2, the tube 1 located on the right side of the second partition member 13 constitutes the downstream first path P <b> 1, and the tube 2 located on the left side constitutes the downstream second path P <b> 2. Further, among the tubes 2 on the upstream side in the flow direction of the external air, the tube 2 positioned on the left side of the second partition member 13 forms an upstream first path (not shown), and the tube 2 positioned on the right side. An upstream second path (not shown) is configured.

  In the heat exchanger 1 configured as described above, the refrigerant flowing into the right side portion of the downstream space R2 of the upper header tank 5 from the refrigerant inflow hole 17a has the tubes 2 arranged in the left-right direction. As shown by an arrow X, a large flow toward the left side is formed, and as shown by an arrow Z in the figure, it flows into the tube 2 constituting the downstream first path P1. At this time, since the protruding portion 11a is formed at a portion of the outer plate member 11 facing the end of the tube 2, the refrigerant flowing in the downstream space R2 hits the protruding portion 11a from the upstream side in the refrigerant flow direction. . Then, the flow direction of the refrigerant is changed so that the refrigerant flows downward along the surface constituting the protruding portion 11a, which is the tip side of the protruding portion 11a. Thereby, the flow of the refrigerant flowing to the left in the header tank 5 is smoothly converted so as to go to the end of the tube 2.

  The refrigerant that has flowed downward through the tube 2 of the downstream first path P1 is blown out from the lower end portion of the tube 2 toward the protruding portion 21a of the lower header tank 6. At this time, in the header tank 6, as indicated by an arrow X in FIG. 8, a large flow of refrigerant is formed toward the second path P2, that is, the left side. As shown by an arrow Z, the flow reaches the surface constituting the downstream side in the refrigerant flow direction of the protruding portion 21a while being bent to the left side of the lower header tank 6 by this flow. The refrigerant that has reached the surface constituting the downstream side of the projecting portion 21a flows toward the left side of the projecting portion 21a along the surface, so that the flow direction is directed to the left side. Thereby, it is suppressed that the flow of the refrigerant blown out from the tube 2 spreads in multiple directions, and the flow direction is smoothly converted to the downstream side.

  The refrigerant blown out from the tube 2 of the downstream first path P1 to the lower header tank 6 flows into the tube 2 constituting the downstream second path P2 while flowing to the left, and flows upward through the tube 2 to the upper side. Blow out to the left side of the downstream space R2 of the header tank 5. The refrigerant flows into the left side portion of the upstream space R1 through the communication hole 12a of the first partition plate 12. The refrigerant flowing into the left portion flows into the tube 2 constituting the upstream first path and flows downward, and then blows out into the upstream space of the lower header tank 6. The refrigerant blown into the upstream space of the lower header tank 6 flows to the right side, flows into the tube 2 constituting the upstream second path, flows upward through the tube 2, and then upstream of the upper header tank 5. After flowing into the right portion of the space R1, it is discharged from the refrigerant discharge hole 17b. When the refrigerant flows into and out of the tube 2 as described above, the flow of the refrigerant is smoothly converted as described above by providing the protruding portions 11a and 21a.

  As described above, according to the heat exchanger 1 according to this embodiment, since the protruding portions 11a and 21a are formed in the header tanks 5 and 6, the pressure resistance of both the header tanks 5 and 6 is ensured, and the refrigerant It is possible to reduce the weight of the heat exchanger 1 by reducing the thickness of the constituent members of the header tanks 5 and 6 while suppressing the generation of abnormal noise during distribution. And since the said protrusion part 11a, 21a was arrange | positioned so that the edge part of the tube 2 might be opposed, the big flow of the refrigerant | coolant formed in the header tanks 5 and 6 was utilized, and the tube 2 from the header tanks 5 and 6 was used. The direction of the refrigerant flowing into the tank and the direction of the refrigerant flowing from the tube 2 into the header tanks 5 and 6 can be smoothly changed by the protruding portions 11a and 21a. Thereby, the pressure loss of the refrigerant | coolant in the heat exchanger 1 can be suppressed, and the performance of the heat exchanger 1 can be improved.

  In addition, since the protruding portions 11 a and 21 a have a shape extending in the circumferential direction of the header tanks 5 and 6, the protruding portions 11 a and 21 a can be formed in a wide range of the header tanks 5 and 6. As a result, the strength of the header tanks 5 and 6 can be further improved, and the direction of the refrigerant flow can be smoothly changed over a wide range of the header tanks 5 and 6, thereby further improving the performance of the heat exchanger 1. This can be further improved.

  Moreover, since the front end surfaces of the protrusions 11a and 21a are configured by curved surfaces, the direction of the refrigerant flow can be changed more smoothly, and the performance of the heat exchanger 1 can be further improved.

  Further, since the dimension H in the protruding direction of the protruding portions 11a and 21a is equal to or greater than the plate thickness of the outer plate members 11 and 21, the effect obtained by providing the protruding portions 11a and 21a can be sufficiently obtained.

  In this embodiment, the protrusions 11 a and 21 a are provided over the entire length of the header tanks 5 and 6. However, the protrusions 11 a and 21 a are provided only in a part of the header tanks 5 and 6 in the longitudinal direction. You may do it. Further, the protruding portions 11 a and 21 a may be smaller than the number of the tubes 2, for example, every other tube 2 may be provided.

  Moreover, although this embodiment demonstrated the case where the heat exchanger 1 was an evaporator, this invention can also be applied to a refrigerant condenser, a heater core, a radiator, etc.

  As described above, the heat exchanger according to the present invention is suitable, for example, as a cooling heat exchanger for a vehicle air conditioner.

It is the figure which looked at the heat exchanger which concerns on embodiment of this invention from the flow direction downstream of external air. It is a right view of a heat exchanger. It is the sectional view on the AA line in FIG. It is the BB sectional view taken on the line in FIG. It is a fragmentary sectional view near an upper header tank and a tube upper end part. It is a fragmentary sectional view near a lower header tank and a tube lower end part. FIG. 6 is a view corresponding to FIG. 5 for explaining the flow of the refrigerant. FIG. 7 is a view corresponding to FIG. 6 for explaining the flow of the refrigerant.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Tube 3 Fin 4 Core 5 Upper header tank 6 Lower header tank 10 Inner plate member 10a Tube insertion hole 11 Outer plate member 11a Protrusion

Claims (4)

In a heat exchanger comprising tubes arranged in parallel in a predetermined direction, and a tank to which ends of the tubes are connected and extend in the direction in which the tubes are arranged,
The heat exchanger according to claim 1, wherein a projecting portion projecting inward of the tank is provided at a portion of the tank facing the end of the tube. The heat exchanger according to claim 1,
The heat exchanger characterized in that the protrusion extends in the circumferential direction of the tank. The heat exchanger according to claim 1 or 2,
The heat exchanger characterized by the front end surface of the protrusion being curved toward the inside of the tank. The heat exchanger according to any one of claims 1 to 3,
A heat exchanger characterized in that the dimension of the protruding portion in the protruding direction is set to be equal to or greater than the thickness of the material constituting the tank.

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