JP2006064201A - Header tank of heat exchanger and connecting structure of header tank of heat exchanger and refrigerant circulating pipe - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a header tank of a heat exchanger capable of reducing a cost while securing sufficient pressure resistance to a refrigerant of high pressure without causing the difference from tube width and the increase of pressure loss. <P>SOLUTION: This header tank 140 is composed of a tank part 121 having a circulating passage 124, and a plate part 122 having a tube insertion hole 122a for inserting an end part 111 of a tube 110. A partitioning part 126 is formed on a part not opposite to the tube insertion hole 122a, of the tank part 121 in a state of being kept into contact with the plate part 122 to partition the circulating passage 124 of the tank part 121 into two or more, and a communication part 125 communicated with two or more circulating passages 124 of the tank part 121 is formed on a part opposite to the tube insertion hole 122a, of the tank part 121. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a header tank of a heat exchanger that performs heat exchange between a refrigerant such as carbon dioxide and external air, and a connection structure between the header tank and a refrigerant circulation pipe.

  Conventionally, a heat exchanger as shown in FIG. 12 is known. The heat exchanger 1 shown in FIG. 12 includes a pair of headers in which a core portion 3 in which a plurality of tubes 2 are stacked and a flow passage (not shown) through which fluid flows along the stacking direction of the tubes 2 is formed. It consists of a tank 4.

  In the core portion 3, a plurality of tubes 2 and a plurality of fins 5 formed in a corrugated shape are alternately stacked, and among these fins 5, those located at the uppermost portion and the lowermost portion are reinforced by a reinforcing member 6. End caps 7 are brazed to both ends of each header tank 4. In addition, a separator (not shown) for closing the flow passage is inserted in an intermediate portion of one header tank 4, and an inlet joint 8 and an outlet joint 9 are provided above and below the separator, respectively. Among these, when the inlet joint 8 receives a high-temperature refrigerant from, for example, the discharge side of a compressor (not shown), the inlet joint 8 flows from the left side to the right side in FIG. After flowing into the tank 4, the tube 2 group below the separator flows from the right side to the left side in FIG. 12 and flows out from the outlet joint 9 to an expansion valve (not shown). During this time, when passing through the plurality of tubes 2, heat is exchanged with the external air, and the high-temperature refrigerant is cooled. In FIG. 12, one header tank 4 provided with an inlet joint 8 and an outlet joint 9 is shown, but in addition to this, one header tank is provided with an inlet joint, and the other header tank is provided with an outlet joint. There is also a heat exchanger provided, in which case the refrigerant flows through the tube group from one header tank toward the other header tank.

  13A to 13C are partial cross-sectional views showing a configuration example of the header tank 4. The header tank 4 in FIG. 13A is obtained by integrating a tank portion 41 and a plate portion 42 by brazing, and one internal flow path for one tube 2 inserted into the header tank 4. 43 is formed. FIGS. 13B and 13C show structures in the case of different cross-sectional shapes.

Further, in Patent Document 1, in order to ensure the pressure resistance strength of the header tank, the cross-sectional shape of the tank portion is a substantially circular multi-hole structure, and the cross-sectional area of the internal flow path that receives the internal pressure is reduced to reduce the high pressure resistance. The one corresponding to the specification is disclosed.
Japanese Patent Laid-Open No. 11-226685

  By the way, in order to apply a heat exchanger having a structure as shown in FIG. 12 (FIG. 13) to a refrigeration cycle using high-temperature and high-pressure carbon dioxide (CO2) as a refrigerant, the stress applied to the members constituting the header tank is reduced. In addition, it is necessary to reduce the cross section of the flow path. However, simply reducing the cross section of the flow path may cause a difference from the tube width or increase the pressure loss due to a reduction in the cross-sectional area. In addition, when a plurality of flow paths are formed using an extruded material as shown in Patent Document 1, it is necessary to form a tube insertion hole and a communication path between the internal flow paths by cutting or the like. It has become.

  The object of the present invention is to ensure sufficient pressure resistance against the refrigerant of carbon dioxide gas, without causing a difference from the tube width and an increase in pressure loss, and in comparison with the case where an extruded material is used. An object of the present invention is to provide a header tank of a heat exchanger that can be reduced.

  Another object of the present invention is to provide a connection structure between the header tank of the heat exchanger and the refrigerant distribution pipe that can reduce the deviation of the refrigerant flow rate at the refrigerant inlet side and the outlet side as the entire header tank. .

  In order to achieve the above object, the invention of claim 1 is connected to a heat exchanger core formed by alternately laminating a plurality of tubes through which a medium circulates and cooling fins, and circulates a refrigerant through each of the tubes. A header tank of a heat exchanger, comprising a tank portion in which a flow passage through which a refrigerant flows is formed, and a plate portion having a tube insertion hole into which an end portion of the tube is inserted, the tank portion In the portion of the tank portion that does not face the tube insertion hole, a partition portion that contacts the plate portion and divides the flow passage of the tank portion into two or more is provided, and in the portion of the tank portion that faces the tube insertion hole, The present invention is characterized in that a communication portion communicating with two or more flow passages of the tank portion is provided.

  According to a second aspect of the present invention, in the first aspect, the relationship between the tank portion width (a), the plate thickness (t), and the tube width (b) is a-2t <b <a, The end of the tube is positioned by bringing the end of the tube into contact with the end section of the tube.

  The invention of claim 3 is characterized in that, in the part of claim 1 or 2, the end section of the tank part does not contact the main surface of the plate part in the part where the tank part faces the tube insertion hole. To do.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, at least in a fitting portion between the tank portion and the plate portion, an end cross section of the tank portion is a main surface of the plate portion. It contacts, It is characterized by the above-mentioned.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, there is no brazing material layer on at least the surface of the tank portion on the flow path side, and there are brazing material layers on both surfaces of the plate portion. It is characterized by doing.

  A sixth aspect of the present invention is characterized in that, in any one of the first to fifth aspects, the tank portion and the plate portion are each formed by pressing.

  A seventh aspect of the invention is characterized in that, in any one of the first to sixth aspects, the communicating portion provided in the tank portion is formed by press working.

  The invention of an eighth aspect is characterized in that, in any one of the first to seventh aspects, the plate portion has side walls at both ends inclined toward the outside.

  In order to achieve the other object, the invention of claim 9 is a connection structure between the header tank of the heat exchanger and the refrigerant circulation pipe according to claim 1, wherein the refrigerant circulation pipe is a straight pipe. And a bent pipe joined so as to communicate with the inside of the straight pipe, and on the refrigerant inlet side, the first straight pipe is connected to one of the two or more flow paths of the tank portion, A first bent pipe branched from the first straight pipe is connected to at least one other flow passage, and a flow different from the flow passage connected to the first straight pipe on the refrigerant inlet side on the refrigerant outlet side. A second straight pipe is connected to the path, and a second bent pipe branched from the second straight pipe is connected to at least one other flow passage.

  A tenth aspect of the invention is characterized in that, in the ninth aspect, the refrigerant circulation pipe has a structure in which an opening hole formed in a side wall portion of the straight pipe and an opening end of the bent pipe are joined.

  The invention of claim 11 is the structure according to claim 9, wherein the refrigerant flow pipe is joined between an opening hole formed in a side wall portion of the straight pipe and an open end of the bent pipe via a connecting member. It is characterized by being.

  The invention of a twelfth aspect is the invention according to the ninth aspect, wherein the refrigerant circulation pipe has a lower end portion on the refrigerant inflow side between an opening hole formed in a side wall portion of the straight pipe and an open end of the bent pipe. It is the structure joined via the connection member formed so that it might protrude inside the said linear piping.

  According to invention of Claim 1, since it was set as the structure which provides two or more flow paths with respect to one tube, the cross section of each flow path can be made small, and it starts by this about the member which comprises a header tank. Stress can be reduced. Further, even when the cross section of each flow passage is made small and the cross section of the flow path is substantially circular, it is possible to prevent the difference from the tube width. In addition, even if the cross-sectional area is reduced in one flow passage, a sufficient cross-sectional area can be secured for the entire flow passage, so that an increase in pressure loss can be prevented.

  According to the invention of claim 2, since the tube can be positioned by bringing both end portions of the end of the tube into contact with the end section of the tank, it is necessary to use an external jig for inserting the tube. In addition, since the tube is attached after the tank portion and the plate portion are fitted, there is no restriction on the process. Further, since there is no need to double the tube insertion hole and it is not necessary to define the depth of the hole, there is no need for an increase in the hole drilling process or high machining accuracy. Furthermore, it is not necessary to form an inclined portion or the like in the tank portion, and there is no factor that complicates the tank shape, so that the number of tank processing steps can be reduced.

  According to invention of Claim 3, the insertion allowance of a tube can be arbitrarily set by adjusting the length of the edge part of a tank part.

  According to the invention of claim 4, when the tank portion and the plate portion are combined, the positioning can be performed reliably, and when the fitting portion is caulked and fixed by applying pressure from the outside, It is possible to prevent the road from being deformed.

  According to the invention of claim 5, when the tank part and the plate part are combined and brazed, the brazing material melted at the end section of the tank part does not clog the hole that becomes the refrigerant flow path of the tube. can do.

  According to the invention of claim 6, since the header tank can be manufactured with a cheap plate material instead of an expensive material such as an extruded material, the material cost can be reduced. Moreover, since the tank part and the plate part can be molded by press working, it becomes easy to process the entire heat exchanger, and it is not necessary to form an inclined part in the tank part, and the tank shape is complicated. Since there is no factor, the processing cost can be reduced without increasing the number of tank processing steps.

  According to the seventh aspect of the present invention, since the communication portion is formed, it is not necessary to cut the header tank, and the number of processing steps and the processing cost can be reduced.

  According to the invention of claim 8, even when the width of the tank part and the clearance between the side wall parts of the plate part are reduced in order to improve the pressure resistance, the tank part and the plate part can be easily fitted together. Is possible.

  According to the ninth aspect of the present invention, since the difference in pressure loss between the refrigerant inlet side and the outlet side can be made substantially uniform, the deviation of the refrigerant flow rate can be reduced as a whole of the header tank. Sufficient strength can be ensured even when using.

  According to the invention of claim 10, since it is a simple structure that only joins two pipes, a plurality of different pipes are joined to one pipe, or a plurality of flow paths are formed by processing the inside of the block. Compared to the case, the processing is easy, and the cost can be reduced.

  According to the eleventh aspect of the invention, since the straight pipe and the bent pipe are joined via the connecting member, the strength of the connecting portion can be improved.

  According to the twelfth aspect of the present invention, since the refrigerant can flow more into the bent pipe side where the refrigerant inflow amount is small by the connecting member, the refrigerant inlet can be obtained by appropriately setting the protruding length of the lower end portion. The difference in the pressure loss between the side and the outlet side can be made substantially uniform, and the deviation of the refrigerant flow rate can be reduced as a whole header tank.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments that are the best mode for carrying out the present invention will be described below with reference to the drawings.

  FIG. 3 is a front view illustrating the overall configuration of the heat exchanger according to the first embodiment. The heat exchanger 100 includes a core portion 101 and header tanks 140 disposed at both ends thereof.

  The core portion 101 is formed by alternately laminating a plurality of flat tubes (hereinafter referred to as “tubes”) 110 through which a refrigerant flows and a plurality of fins 120 formed in a corrugated shape. A side plate 130 as a substantially U-shaped strength member is disposed, and is integrally brazed and joined.

  The tubes 110 are laminated in the thickness direction in parallel with each other in a state where a gap for air to flow between adjacent ones is secured, and fins 120 are disposed in the respective gaps between the tubes 110.

  The header tank 140 is disposed at both ends of the core portion 101, that is, at both end portions 111 in the longitudinal direction of the plurality of tubes 110, and has two flow passages 124 (a) extending along the stacking direction of the tubes 110 inside. , B) are formed. End portions 111 of the tubes 110 are brazed to the header tank 140, and the flow passages 124 of the header tank 140 and the internal passages of all the tubes 110 communicate with each other.

  End caps 180 for closing both ends of the flow passage 124 are brazed and joined to the longitudinal ends of both header tanks 140. A separator 141 that partitions the flow passage 124 in the longitudinal direction is brazed in the header tank 140 on the left side in the drawing. An inlet joint 191 for guiding the refrigerant into the header tank is provided above the separator 141 of the left header tank 140, and an outlet joint 192 for taking out the heat-exchanged refrigerant out of the header tank at the lower side. Are joined by brazing.

  Next, the configuration of the header tank 140 according to the first embodiment will be described.

  FIG. 1 is a schematic cross-sectional view of the header tank 140 according to the first embodiment, which corresponds to the AA cross-sectional view of FIG. FIG. 2 is a schematic cross-sectional view corresponding to the BB cross-sectional view of FIG.

  The header tank 140 according to the first embodiment has a substantially U-shaped tank section 121 in which two flow passages 124 through which a refrigerant flows is formed, and a tube insertion hole 122 a for connecting each tube 110. And a U-shaped plate portion 122.

  As shown in FIG. 1, the tank part 121 is a partition part that contacts the main surface 122b of the plate part 122 and partitions the flow passage 124 into 124a and 124b at a part that does not face the tube insertion hole 122a of the plate part 122. 126 is provided. In this embodiment, the plate part 122 has a brazing material layer formed on both surfaces, and the partition part 126 and the main surface 122b of the plate part 122 are joined by brazing in the furnace. As a result, the flow passages 124a and 124b are partitioned by the partition portion 126 at a portion of the plate portion 122 that does not face the tube insertion hole 122a. In the present embodiment, an example in which one partition 126 is provided at the center of the tank 121 and the flow passage is divided into two is shown. However, by providing a plurality of partition portions 126 at a predetermined interval, the flow passage can be further increased. It can also be partitioned into multiple pieces.

  In addition, as shown in FIG. 2, the tank portion 121 is provided with a communication portion 125 that communicates between the flow passages 124 a and 124 b at a portion of the plate portion 122 that faces the tube insertion hole 122 a. Accordingly, a part of the refrigerant flowing through the flow passages 124 a and 124 b is dispersed in the width direction of the tube 110 at each insertion position of the tube 110 and flows into the tube 110.

  When the plate part 122 is combined with the tank part 121, several fitting parts 123 that are bent so as to wrap the upper surface of the tank part 121 are provided in the longitudinal direction (see FIG. 3). The fitting portion 123 is provided at a predetermined position in the longitudinal direction of the header tank 140 so as to be located between the adjacent tube insertion holes 122a. Then, the plate portion 122 and the tank portion 121 are overlapped as shown in the figure, and the fitting portion 123 is bent inward so as to wrap the upper surface of the tank portion 121 and fixed by caulking, and in that state, brazed in the furnace The tank part 121 and the plate part 122 can be integrated.

  As shown in FIG. 1, the plate portion 122 in this embodiment has the side wall portions 122 c at both ends inclined at an angle c toward the outside. Thereby, in order to improve pressure resistance, even when the clearance between the width a of the tank part 121 and the side wall part 122c of the plate part 122 is reduced, the tank part 121 and the plate part 122 can be easily fitted together. Is possible. Further, the side wall portion 122 c of the plate portion 122 is provided with a linear portion having a length d that comes into contact with the end portion 121 b of the tank portion 121 when combined with the tank portion 121. This length d is not less than the plate thickness t of the plate portion 122. Thereby, a required strength can be ensured in the brazed portion.

  The tank part 121 and the plate part 122 can be molded by pressing a plate material. Among these, the tank part 121 can process the flow paths 124a and 124b, the communication part 125, and the partition part 126 simultaneously by press work.

  Moreover, the tank part 121 and the plate part 122 can use the clad material in which the brazing material layer was formed in the surface. In the tank part 121 in the present embodiment, the tank part 121 in which the brazing material layer is not formed on the end cross section 121a and the surface on the flow path 124 side is used. According to this, it is possible to prevent clogging of the hole serving as the refrigerant flow path of the tube 110 by the brazing material melted at the time of brazing. In order to obtain the above effect, it is desirable that the brazing material layer has a structure in which at least the surface on the flow passage 124 side is not formed. Further, the brazing material layer is not formed in the end cross section 121a. Thus, a more desirable effect can be obtained.

  The tube 110 is a molding material having an extruded multi-hole tube structure in which a plurality of refrigerant flow paths (not shown) are formed inside, and is positioned when the end 111 comes into contact with the end section 121 a of the tank 121.

In the present embodiment, the relationship between the width a of the tank portion 121, the plate thickness t, and the width b of the tube 110 is a-2t <b <a.
The dimensions of each part are set so that Thus, when the tube 110 is inserted into the tube insertion hole 122 a of the plate portion 122, both end portions of the end portion 111 of the tube 110 can be reliably brought into contact with the end cross section 121 a of the tank portion 121.

  According to the header tank 140 of the first embodiment, since the two flow passages 124a and 124b are provided for one tube 110, the cross section of each flow passage can be reduced, and thus the header tank can be reduced. The stress applied to the constituent members can be reduced. Further, even when the cross section of each flow passage is made small and the cross section of the flow path is substantially circular, it is possible to prevent the difference from the tube width. In addition, even if the cross-sectional area is reduced in one flow passage, a sufficient cross-sectional area can be secured for the entire flow passage, so that an increase in pressure loss can be prevented.

  In addition, since the tube 110 is positioned by bringing both end portions of the end portion 111 of the tube 110 into contact with the end section 121a of the tank portion 121, it is not necessary to use an external jig for inserting the tube 110. Moreover, since the tube 110 can be attached after fitting the tank part 121 and the plate part 122, there is no restriction on the process. Moreover, since it is not necessary to make the tube insertion hole 122a double, and it is not necessary to define the depth of the hole, an increase in the drilling process and high processing accuracy are not required.

  Furthermore, since the header tank can be made of an inexpensive material rather than an expensive material such as an extruded material, the material cost can be reduced. Moreover, since the tank part 121 and the plate part 122 can be shape | molded by press work, the process of the whole heat exchanger can be made easy. At the same time, since the communication portion 125 for communicating between the flow passages can be formed by press working, it is not necessary to cut the header tank, and the number of processing steps and the processing cost can be reduced. In addition, since it is not necessary to form an inclined portion or the like in the tank portion 121 and there is no factor that complicates the tank shape, the processing cost can be reduced without increasing the number of tank processing steps.

  Therefore, according to the header tank of the present embodiment, while ensuring sufficient pressure resistance against the refrigerant of high-pressure carbon dioxide gas, there is no difference with the tube width and no increase in pressure loss, and the extruded material is used. Cost can be reduced compared to the case of using. Furthermore, the tube can be positioned without increasing the process restrictions and the number of processing steps.

  FIG. 4 is a schematic cross-sectional view of the header tank according to the second embodiment, and corresponds to a cross-sectional view taken along the line BB in FIG. FIG. 5 is a schematic cross-sectional view corresponding to the AA cross-sectional view of FIG. Hereinafter, the same parts as those in the first embodiment will be described with the same reference numerals.

  As shown in FIG. 4, in the header tank 140 </ b> A, the tank portion 121 is in a portion facing the tube insertion hole 122 a of the plate portion 122, and the end cross section 121 a of the tank portion 121 is in contact with the main surface 122 b of the plate portion 122. In order to avoid this, the length of the end 121b is shorter than the length of other portions. Therefore, the insertion allowance of the tube 110 can be arbitrarily set by adjusting the length of the end portion 121b of the tank portion 121.

  As shown in FIG. 5, the tank portion 121 is configured such that the end cross section 121 a abuts the main surface 122 b of the plate portion 122 in a portion that does not face the tube insertion hole 122 a of the plate portion 122. According to this, when the tank part 121 and the plate part 122 are combined, positioning can be performed reliably, and when the fitting part 123 is caulked and fixed by applying pressure from the outside, It is possible to prevent the deformation of 124a and 124b. It should be noted that the region where the end cross section 121 a of the tank portion 121 abuts against the main surface 122 b of the plate portion 122 may be at least around the fitting portion 123 of the plate portion 122.

  Also in the header tank 140A of the second embodiment, while ensuring sufficient pressure resistance against the refrigerant of high-pressure carbon dioxide gas, there is no difference from the tube width and no increase in pressure loss, and an extruded material is used. Compared to the case, the header tank can be reduced in cost. Similarly, the material cost and the processing cost can be reduced by forming the tank part 121 and the plate part 122 by pressing the plate material.

  In particular, according to the present embodiment, the insertion allowance of the tube 110 can be arbitrarily set by adjusting the length of the end portion 121b of the plate portion 122.

  Next, as a third embodiment, a connection structure between a header tank and a refrigerant circulation pipe that supplies a refrigerant to the header tank will be described.

  As in the above-described Patent Document 1 (Japanese Patent Laid-Open No. 11-226665), when supplying a refrigerant to a header tank having a multi-hole structure with a substantially circular cross-section of the tank portion, a plurality of refrigerants are allowed to flow. For example, the structures shown in FIGS. 6A to 6C are conceivable as structures to be distributed to the roads.

  FIG. 6A shows a structural example in which a flange 11 connected to an external pipe is combined with a block 11 having flow paths 13 and 14 formed therein. 6B, the supply pipe 22 is connected to the header tank 21, and a part of the header partition 23 facing the supply pipe 22 is cut away so that the two flow passages 24a and 24b are communicated. An example of the structure is shown. FIG. 6C shows an example of a structure in which the block 31 in which the trifurcated flow paths 32 to 34 are formed is combined with the header tank 140A of the second embodiment.

  By the way, in the case where the flow path is branched inside the block as shown in FIG. 6A, it is necessary to open at least three holes to be the flow paths. Two separate pipes must be joined. In addition, as shown in FIG. 6B, in the structure in which a part of the header partition 23 is cut and communicated, it is difficult to process the header tank, and the strength may be impaired. Moreover, since the refrigerant flowing in from the outside flows into the respective flow passages after striking the partition 23, it is considered that the pressure loss increases. Furthermore, when the flow path is divided into three as shown in FIG. 6C, if this is formed as a block, the processing becomes complicated, leading to an increase in cost. Further, when the pipe is combined into a three-branch pipe, the joining of the branch portions becomes complicated, and there is a concern that the strength is insufficient when a high-pressure carbon dioxide refrigerant or the like is used.

  A present Example shows the connection structure of the header tank and refrigerant | coolant circulation piping which solved the said subject. The refrigerant circulation pipes 150 and 160 shown in the present embodiment correspond to, for example, the inlet joint 191 and the outlet joint 192 shown in FIG.

  FIG. 7 is a schematic cross-sectional view showing the structure of the refrigerant distribution pipe according to the third embodiment, where (a) shows the refrigerant inlet side and (b) shows the refrigerant outlet side. In the present embodiment, an example in which the refrigerant distribution pipe and the header tank 140A of the second embodiment are combined will be described, and the same parts are all described with the same reference numerals.

  As shown in FIG. 7A, the refrigerant circulation pipe 150 includes a straight pipe 151 and a bent pipe 152 joined so as to communicate with the inside of the straight pipe 151. In the refrigerant circulation pipe 150 on the refrigerant inlet side, a straight pipe 151 is connected to the flow path 124b, and a bent pipe 152 branched from the straight pipe 151 is connected to the other flow path 124a. Further, as shown in FIG. 7B, the refrigerant circulation pipe 160 includes a straight pipe 161 and a bent pipe 162 joined so as to communicate with the inside of the straight pipe 161. In the refrigerant distribution pipe 160 on the refrigerant outlet side, the straight pipe 161 is connected to the flow path 124a different from the flow path 124b to which the straight pipe 151 is connected on the refrigerant inlet side in FIG. 7A, and the other flow path 124b. A bent pipe 162 branched from the straight pipe 161 is connected to the pipe.

  In the above configuration, when the refrigerant is supplied to the refrigerant circulation pipe 150 on the refrigerant inlet side, the refrigerant branches in two directions inside the refrigerant circulation pipe 150 and flows into the flow passages 124a and 124b, respectively. At this time, since a larger amount of refrigerant flows into the straight pipe 151 having a small pressure loss, more refrigerant flows through the flow passage 124b than the flow passage 124a. On the other hand, in the refrigerant outlet pipe 160 on the refrigerant outlet side, the straight pipe 161 is connected to the flow passage 124a, and the bent pipe 162 is connected to the flow passage 124b. Will be discharged. According to this, since the pressure loss in the two flow passages is substantially equal, the header tank 140A as a whole can reduce the deviation of the refrigerant flow rate at the refrigerant inlet side and the outlet side. In FIG. 7, the refrigerant inlet side and outlet side connections may be reversed. That is, FIG. 7B may be a refrigerant inlet side connection structure, and FIG. 7A may be a refrigerant outlet side connection structure.

  Next, the connection part of straight piping and bending piping is demonstrated. Here, the refrigerant distribution pipe 150 on the refrigerant inlet side will be described as an example, but the refrigerant distribution pipe 160 on the refrigerant outlet side is similarly connected. However, the refrigerant inlet side and the outlet side do not necessarily have the same structure.

  FIG. 8 is an exploded cross-sectional view illustrating a configuration example of the straight pipe 151 and the bent pipe 152. An opening hole 151 b connected to the internal flow path is formed in the side wall portion 151 a of the straight pipe 151. The opening hole 151b is joined and integrated with the opening end 152a of the bent pipe 152 by brazing. According to the present embodiment, since it is a simple structure that only joins two pipes, a plurality of separate pipes are joined to one pipe, or a plurality of flow paths are formed by processing the inside of a block Compared to the above, processing is easy, and the cost can be reduced. In addition, in the header tank 140A in the present embodiment, since the communication portion 125 that communicates between the flow passages 124a and 124b is provided, it is not necessary to perform a cutting process or the like for diverting the refrigerant. In addition to not damaging the strength, the difference in pressure loss between the refrigerant inlet side and the outlet side can be made almost uniform, so that the bias of the refrigerant flow rate can be reduced as a whole header tank. Even when used, sufficient strength can be ensured.

  FIG. 9 is an exploded sectional view showing another configuration example of the straight pipe 151 and the bent pipe 152. In the present embodiment, the straight pipe 151 and the bent pipe 152 are joined via the connection member 170. Here, the outer diameter of the connection member 170 substantially matches the inner diameter of the opening hole 151 b formed in the straight pipe 151, and the inner diameter of the opening end 152 a of the bent pipe 152 substantially matches the outer diameter of the connection member 170. The notch 152b is formed. When the connecting member 170 is made of a clad material having a brazing material layer on the surface, the straight pipe 151, the bent pipe 152, and the connecting member 170 are combined and brazed in the furnace so that the respective parts are integrated together. be able to.

  According to the configuration of the present embodiment, since the straight pipe 151 and the bent pipe 152 are joined via the connecting member 170, the strength of the connecting portion can be improved.

  FIG. 10 is an exploded cross-sectional view showing still another configuration example of the straight pipe 151 and the bent pipe 152. FIG. 11 is a schematic perspective view of the connection member 180. The present embodiment is applied to the refrigerant flow pipe 150 on the refrigerant inlet side, and a lower end portion on the refrigerant inflow side between the opening hole 151b formed in the straight pipe 151 and the open end 152a of the bent pipe 152. 180a is joined via a connecting member 180 formed so as to protrude into the straight pipe 151. In the present embodiment, the straight pipe 151 and the flow passage 124b of the header tank 140A are joined via the connection member 181, and the bent pipe 152 and the flow passage 124a are joined via the connection member 182. ing. Also in this embodiment, the connection members 180 to 182 can be made of a clad material having a brazing material layer on the surface.

  In the present embodiment, most of the refrigerant supplied to the refrigerant circulation pipe 150 on the refrigerant inlet side is received by the lower end portion 180a of the connecting member 180 and flows into the bent pipe 152 side. As described above, in this embodiment, since the pressure loss is larger than that of the straight pipe 151 and the refrigerant can flow more into the bent pipe 152 side where the refrigerant inflow amount is small, the protruding length of the lower end portion 180a is appropriately set. By setting to, the difference in the pressure loss between the refrigerant inlet side and the outlet side can be made substantially uniform, and the deviation of the refrigerant flow rate can be reduced as a whole of the header tank. Further, since the refrigerant circulation pipe 150 and the header tank 140A are joined via the connecting members 181 and 182, the strength of the connecting portion can be improved.

FIG. 3 is a schematic cross-sectional view of a portion of the header tank according to the first embodiment that does not face the tube insertion hole. FIG. 3 is a schematic cross-sectional view of a portion facing the tube insertion hole in the header tank according to the first embodiment. 1 is a front view showing an overall configuration of a heat exchanger according to Embodiment 1. FIG. FIG. 6 is a schematic cross-sectional view of a portion facing a tube insertion hole in the header tank according to the second embodiment. FIG. 10 is a schematic cross-sectional view of a portion of the header tank according to the second embodiment that does not face the tube insertion hole. (A)-(c) is explanatory drawing which shows the structure of the prior art example of a refrigerant | coolant supply part. (A), (b) is a schematic sectional drawing which shows the structure of the refrigerant | coolant distribution | circulation piping concerning Example 3. FIG. FIG. 6 is an exploded cross-sectional view illustrating a configuration example of a straight pipe and a bent pipe in the third embodiment. FIG. 10 is an exploded cross-sectional view illustrating another configuration example of the straight pipe and the bent pipe in the third embodiment. FIG. 12 is an exploded cross-sectional view showing still another configuration example of the straight pipe and the bent pipe in the third embodiment. The schematic perspective view of a connection member. The perspective view which shows the external appearance of the conventional general heat exchanger. (A)-(c) is a fragmentary sectional view which shows the structural example of the header tank in a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 ... Heat exchanger 101 ... Core part 110 ... Tube 111 ... (tube) end part 120 ... Fin 121 ... Tank part 121a ... (tank part) end cross section 121b ... (tank part) end part 122 ... Plate part 122a ... Tube Insertion hole 122b ... (plate part) main surface 122c ... (plate part) side wall part 123 ... fitting part 124a, 124b ... flow path 126 ... partition part 130 ... side plate 140, 140A ... header tank 150, 160 ... refrigerant distribution piping 151, 161 ... straight piping 152, 162 ... bent piping 170, 180, 181, 182 ... connecting member 180a ... lower end

Claims (12)

Heat exchange in which a plurality of tubes (110) through which refrigerant flows and cooling fins (120) are alternately stacked are connected to a heat exchanger core (101), and the refrigerant flows through the tubes (110). A container header tank (140),
A plate part (122) having a tank part (121) in which a flow passage (124) through which a refrigerant flows is formed and a tube insertion hole (122a) into which an end part (111) of the tube (110) is inserted. And consists of
A partition portion that is in contact with the plate portion (122) and separates the flow passage (124) of the tank portion (121) into two or more at a portion of the tank portion (121) that does not face the tube insertion hole (122a). (126) and a communication portion (125) communicating with two or more flow passages (124) of the tank portion (121) at a portion facing the tube insertion hole (122a) of the tank portion (121). A header tank of a heat exchanger, characterized in that it is provided. The relationship between the width (a) of the tank part (121), the plate thickness (t), and the width (b) of the tube is as follows.
a-2t <b <a
And positioning the end (111) of the tube (110) by bringing the end (111) of the tube (110) into contact with the end cross section (121a) of the tank (121). The header tank of the heat exchanger according to claim 1, wherein the header tank is a heat exchanger.   In the portion where the tank portion (121) faces the tube insertion hole (122a), the end section (121a) of the tank portion (121) does not contact the main surface (122b) of the plate portion (122). The header tank of the heat exchanger according to claim 1 or 2, wherein   At least in the fitting part (122b) between the tank part (121) and the plate part (122), the end section (121a) of the tank part (121) is the main surface (122d) of the plate part (122). The header tank of the heat exchanger according to any one of claims 1 to 3, wherein the header tank is in contact with the heat exchanger.   The brazing material layer does not exist on at least the surface of the tank portion (121) on the flow path (124) side, and the brazing material layer exists on both surfaces of the plate portion (122). The header tank of the heat exchanger as described in any one of thru | or 4.   The header tank of the heat exchanger according to any one of claims 1 to 5, wherein the tank part (121) and the plate part (122) are each formed by press working.   The heat exchanger header according to any one of claims 1 to 6, wherein the communication part (125) provided in the tank part (121) is formed by press working. tank.   The header tank of the heat exchanger according to any one of claims 1 to 7, wherein the plate portion (122) has side wall portions (122c) at both ends inclined toward the outside. A connection structure between the header tank of the heat exchanger according to claim 1 and the refrigerant circulation pipe,
The refrigerant distribution pipe (150, 160) is composed of a straight pipe (151, 161) and a bent pipe (152, 162) joined so as to communicate with the inside of the straight pipe.
On the refrigerant inlet side, a first straight pipe (151) is connected to one of the two or more flow passages (124) of the tank portion (121), and the first straight line is connected to at least one other flow passage. The first bent pipe (152) branched from the pipe (151) is connected,
On the refrigerant outlet side, the second straight pipe (161) is connected to a flow path different from the flow path to which the first straight pipe (151) is connected on the refrigerant inlet side, and the second straight pipe (161) is connected to at least one other flow path. A connection structure between the header tank of the heat exchanger and the refrigerant circulation pipe, wherein the second bent pipe (162) branched from the two straight pipes (161) is connected.   The refrigerant circulation pipe (150, 160) has a structure in which an opening hole formed in a side wall portion of the straight pipe (151, 161) and an opening end of the bent pipe (152, 162) are joined. A connection structure between the header tank of the heat exchanger according to claim 9 and the refrigerant circulation pipe.   The refrigerant circulation pipes (150, 160) are connected between the opening holes formed in the side walls of the straight pipes (151, 161) and the open ends of the bent pipes (152, 162). 10. The connection structure between the header tank of the heat exchanger and the refrigerant circulation pipe according to claim 9, wherein The refrigerant flow pipe (150) has a lower end part (180a) on the refrigerant inflow side between an opening hole formed in a side wall part of the straight pipe (151) and an open end of the bent pipe (152). The header tank and the refrigerant distribution pipe of the heat exchanger according to claim 9, wherein the straight line (151) is joined through a connecting member (180) formed so as to protrude inside the straight pipe (151). Connection structure with.

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