JP6504367B2 - Heat exchanger - Google Patents

Description

  The present disclosure relates to a heat exchanger, and more particularly to a laminated plate fin heat exchanger configured by stacking plate-like plate fins through which a refrigerant flows.

  As heat exchangers used to exchange thermal energy between fluids having different thermal energy, it is used in many devices, especially heat exchangers with laminated plate fins, for example for home use and vehicles Are widely used in air conditioners for computers, computers, and various electric devices.

  The heat exchanger of the laminated plate fin exchanges heat between the fluid (refrigerant) flowing in the flow path formed in the plate-like plate fin and the fluid (air) flowing between the laminated plate fins Form.

  In the field of heat exchangers of laminated plate fins as described above, various configurations have been proposed for the purpose of weight reduction, miniaturization and efficiency of heat exchange (for example, see Patent Document 1 and Patent Document 2). ).

Patent No. 3965901 gazette Utility model registration number 3192719 gazette

  As described above, in the field of heat exchangers for laminated plate fins, it has been proposed that the plate fins be formed of a material having a small thickness and a high thermal conductivity for the purpose of weight reduction, miniaturization, and efficiency improvement. . In addition, in order to enhance the heat exchange capacity of the heat exchanger, it is considered to flow the fluid (refrigerant) at a higher pressure than the conventional heat exchanger through the flow path formed in the plate fins. There is.

  In the field of heat exchangers, forming plate fins from thin material with high thermal conductivity is advantageous in achieving weight reduction, miniaturization and efficiency, but has problems in reliability. It was something I had. In particular, in the case of providing a configuration in which a high pressure refrigerant flows to the flow path formed in the plate fin, the flow path of the refrigerant in the plate fin is deformed, and the flow rate and the flow rate of the refrigerant vary. There was a possibility that the performance as a heat exchanger would be lowered. Furthermore, in some cases, there is a problem that the refrigerant leaks from the refrigerant channel in the thin plate fin.

  An object of the present disclosure is to provide a highly reliable heat exchanger even in a configuration in which a high-pressure refrigerant flows while achieving weight reduction, downsizing, and efficient heat exchange.

As a heat exchanger of one aspect of the present disclosure,
A plate fin laminate in which plate fins having a flow path through which the first fluid flows are stacked;
And a supply / discharge pipe through which the first fluid flows in the flow path of each plate fin in the plate fin laminate.
A heat exchanger for flowing a second fluid between the stacks of the plate fin stacks to exchange heat between the first fluid and the second fluid,
The plate fins are
A flow passage region having a plurality of linear first fluid flow passages such that the first fluid flows in parallel;
A header area having a header flow path communicating each first fluid flow path of the flow path area with the supply and discharge pipe;
The outer wall of the header channel is configured to contact the outer wall of the header channel of the plate fin adjacent in the stacking direction in the plate fin laminate.

  According to the present disclosure, it is possible to provide a highly reliable heat exchanger even in a configuration in which high-pressure refrigerant flows while achieving weight reduction, downsizing, and efficiency improvement.

The perspective view showing the appearance of the lamination type plate fin heat exchanger of an embodiment concerning the present disclosure Plan view showing plate fins in the laminated plate fin heat exchanger of the present embodiment An exploded view showing a part of the configuration of plate fins in the laminated plate fin heat exchanger of the present embodiment in an enlarged manner The figure which shows the various cross-sectional shapes of the refrigerant | coolant flow path in the laminated type plate fin heat exchanger of this embodiment A plan view showing a part of plate fins in a plate fin laminate in the laminated plate fin heat exchanger of the present embodiment The perspective view which shows the cross section which cut the plate fin laminated body shown in FIG. 5 by the VI-VI line In the present embodiment, a cross-sectional view showing a part of a header area or a refrigerant flow path obtained by processing plate materials having different thicknesses. The figure which shows that different plate fins were laminated | stacked and the plate fin laminated body was comprised in this embodiment. The perspective view which shows the cross section which cut | disconnected the plate fin laminated body shown in FIG. 8 by the IX-IX line. In the present embodiment, a perspective view showing a state in which positioning pins are attached to a plate fin laminate In the present embodiment, a cross-sectional view showing an enlarged plate fin laminate on which positioning pins are mounted. A plan view of a plate fin showing a modification of the embodiment according to the present disclosure A plan view of a plate fin showing a modification of the embodiment according to the present disclosure A plan view of a plate fin showing a modification of the embodiment according to the present disclosure The perspective view which shows the upper end plate provided in the upper end of the plate fin laminated body in this embodiment The perspective view which shows the lower end plate provided in the lower end of the plate fin laminated body in this embodiment An enlarged perspective view showing the header region and the upper end plate of the plate fin laminate in the present embodiment An enlarged perspective view showing a bonding state of the plate fin laminate and the lower end plate in the present embodiment An enlarged perspective view showing a bonded state of a plate fin laminate and a lower end plate showing a modification of the embodiment according to the present disclosure The top view which shows the upper surface of the lower end plate shown in FIG. An enlarged perspective view showing a bonded state of a plate fin laminate and a lower end plate showing a modification of the embodiment according to the present disclosure The top view (a) and side view (b) which show the upper surface of the lower end plate shown in FIG. An enlarged perspective view showing a bonded state of a plate fin laminate and a lower end plate showing a modification of the embodiment according to the present disclosure The top view (a) and side view (b) which show the upper surface of the lower end plate shown in FIG. An enlarged perspective view showing a bonded state of a plate fin laminate and a lower end plate showing a modification of the embodiment according to the present disclosure A perspective view of a plate fin laminate showing a modification of the embodiment according to the present disclosure

The heat exchanger according to the first aspect of the present disclosure is
A plate fin laminate in which plate fins having a flow path through which the first fluid flows are stacked;
And a supply / discharge pipe through which the first fluid flows in the flow path of each plate fin in the plate fin laminate.
A heat exchanger for flowing a second fluid between the stacks of the plate fin stacks to exchange heat between the first fluid and the second fluid,
The plate fins are
A flow passage region having a plurality of linear first fluid flow passages such that the first fluid flows in parallel;
A header area having a header flow path communicating each first fluid flow path of the flow path area with the supply and discharge pipe;
The outer wall of the header channel is configured to contact the outer wall of the header channel of the plate fin adjacent in the stacking direction in the plate fin laminate.

  In the heat exchanger according to the second aspect of the present disclosure, the header flow path according to the first aspect includes a plurality of flow paths for flowing the refrigerant of the supply and discharge pipe to the first fluid flow paths of the flow path region. It may have a branch channel.

  In the heat exchanger according to the third aspect of the present disclosure, in the second aspect, the multi-branched flow path is an outer wall of a multi-branched flow path in plate fins adjacent in the stacking direction in the plate fin laminate. It may be configured to abut.

  In the heat exchanger according to the fourth aspect of the present disclosure, in the header area according to any one of the first to third aspects, the tube wall of the header flow passage is formed thicker than other portions. May be

  In the heat exchanger according to the fifth aspect of the present disclosure, in the flow path region according to any one of the first to fourth aspects, the pipe wall of the flow path is formed thicker than other portions. May be

  A heat exchanger according to a sixth aspect of the present disclosure is the plate fin according to any one of the first to fourth aspects, wherein the header areas are provided on both sides, and the header areas on both sides are provided. The header channel may be configured to have a symmetrical shape.

  The heat exchanger according to a seventh aspect of the present disclosure is the plate fin according to the sixth aspect, wherein the header region is provided on both sides, wherein each of the header flow paths includes the supply and discharge pipe and the multi-branch The bypass flow passage including the bypass flow passage communicating with the flow passage, and the bypass flow passage and the multi-branch flow passage disposed on both sides of the plate fin have a point symmetrical shape with the center of the plate fin as a center of symmetry. It may be configured as follows.

  A heat exchanger according to an eighth aspect of the present disclosure is the plate fin wherein the header area according to any one of the first to seventh aspects is provided on both sides, and the flow path in the header area And a plurality of projecting header area supports different from the above, and the header area supports disposed on both sides of the plate fin have a point symmetrical shape with the center of the plate fin as the center of symmetry. It may be configured.

  A heat exchanger according to a ninth aspect of the present disclosure is the plate fin according to any one of the first to fifth aspects, wherein the header region is provided at one end side, and the supply and discharge pipe is provided. It is good also as composition provided in the position corresponding to the header field.

  A heat exchanger according to a tenth aspect of the present disclosure includes a plurality of projecting header area supports different from the flow path in the header area of the plate fin according to any one of the first to ninth aspects. Are formed, and the header region supporting portion abuts against the header regions of the adjacent plate fins in the stacking direction in the plate fin laminate to form a predetermined space between the plate fins adjacent in the stacking direction. It may be configured.

  In the heat exchanger according to the eleventh aspect of the present disclosure, at least two of the header area support portions provided in the header area of the tenth aspect have through holes, and the through holes are positioning holes and May be configured to

  The heat exchanger according to the twelfth aspect of the present disclosure may have a configuration in which the positioning pin is fixed to the positioning hole of the eleventh aspect.

  The heat exchanger according to a thirteenth aspect of the present disclosure is the heat exchanger according to any one of the first to twelfth aspects, wherein the flow path area of the plate fin is different from the flow path in the flow path area. A portion may be formed, and the flow path region support portion may be configured to abut on the flow path region of the adjacent plate fin in the stacking direction in the plate fin laminate to form a predetermined space between the stackings.

  The heat exchanger according to a fourteenth aspect of the present disclosure is the heat exchanger according to any one of the first to thirteenth aspects, wherein the plate fin laminate is formed by laminating the plate fins having different flow channel shapes. It may be configured.

  The heat exchanger according to a fifteenth aspect of the present disclosure is the plate fin laminate according to any one of the first to thirteenth aspects, wherein the plate fin laminate has two types of flow path shapes. It may be configured to be alternately stacked.

  In the heat exchanger according to a sixteenth aspect of the present disclosure, the plate fin laminates according to the fifteenth aspect are alternately stacked in a cross section orthogonal to the flow direction of the first fluid in the flow passage region. The channels in the plate fins may be arranged in a staggered arrangement.

  The heat exchanger according to a seventeenth aspect of the present disclosure is the heat exchanger according to the fourteenth or fifteenth aspect, wherein a projecting flow path support portion different from the flow path is formed in the flow path region of the plate fin The channel support portion may be configured to abut on the pipe wall of the first fluid channel in the channel region of the plate fin adjacent in the stacking direction in the plate fin laminate.

  The heat exchanger according to an eighteenth aspect of the present disclosure is the heat exchanger according to the eighteenth aspect, wherein the flow path support portion provided to project from the plate fin according to the seventeenth aspect is a second fluid that flows between layers of the plate fin laminate. It may be arranged in a staggered arrangement with respect to the flow direction.

  In the heat exchanger according to the nineteenth aspect of the present disclosure, the number of the flow path support portions provided protruding in the plate fin according to the seventeenth aspect is such that the downwind side is a wind in the flow direction of the second fluid B. More than the upper side may be provided.

  The heat exchanger according to a twentieth aspect of the present disclosure is the plate fin having the two types of flow path shapes according to the fifteenth aspect, wherein the flow path region of one of the plate fins has a protrusion different from the flow path A flow path area convex portion is formed, and a flow path area concave portion is formed at a position corresponding to the flow path area convex portion in the flow path area of the other plate fin, and adjacent in the stacking direction in the plate fin laminate The flow path region convex portion of the plate fin and the flow path region concave portion may be engaged, and a predetermined space may be held between the laminations of the adjacent plate fins.

  The heat exchanger according to a twenty-first aspect of the present disclosure is the heat exchanger according to any one of the first to twentieth aspects, wherein at least the flow path of the flow path region in the plate fin is the flow path in the flow path The cross section orthogonal to the direction in which the first fluid flows may have a rectangular shape.

  The heat exchanger according to a twenty-second aspect of the present disclosure is the heat exchanger according to any one of the first to twentieth aspects, wherein at least the flow path of the flow path region in the plate fin is the flow path in the flow path The cross section orthogonal to the direction in which the first fluid flows may have a circular shape.

  The heat exchanger according to a twenty-third aspect of the present disclosure is the heat exchanger according to any one of the first through twenty-second aspects, wherein at least the flow path of the flow path region in the plate fin is the plate fin laminate It may be protruded and formed only in one side of the lamination direction in the above.

  The heat exchanger according to a twenty-fourth aspect of the present disclosure is the heat exchanger according to any one of the first to twenty-second aspects, wherein the flow path of at least the flow path region in the plate fin is the plate fin laminate It may be formed to project on both sides in the stacking direction in

  Hereinafter, as an embodiment according to the heat exchanger of the present disclosure, a laminated plate fin heat exchanger will be described with reference to the attached drawings. In addition, the heat exchanger of this indication is not limited to the structure of the lamination type plate fin heat exchanger described in the following embodiment, The heat exchanger equivalent to the technical idea demonstrated in the following embodiment Including the configuration of The embodiments described below show an example of the present invention, and configurations, functions, operations and the like shown in the embodiments are exemplifications and do not limit the present disclosure. Among the components in the following embodiments, components that are not described in the independent claim indicating the highest concept are described as optional components.

  FIG. 1 is a perspective view showing an appearance of a laminated plate fin heat exchanger (hereinafter simply referred to as a heat exchanger) 1 according to the present embodiment. As shown in FIG. 1, the heat exchanger 1 of the present embodiment is configured by laminating a feed pipe (inlet header) 4 into which a refrigerant as a first fluid is fed and a plurality of plate fins 2 a in the form of a rectangular plate. And a discharge pipe (outlet header) 5 for discharging the refrigerant flowing through the flow path formed in the plate fins 2a. In the present embodiment, the inlet pipe 4 and the outlet pipe 5 are collectively referred to as an inlet and outlet pipe.

  Further, at both ends (upper and lower ends) of the plate fin laminate 2 formed by laminating a plurality of plate fins 2a in the stacking direction, end plates 3a and 3b having substantially the same shape as the rectangular plate fins 2a It is provided. The end plates 3a and 3b are formed of a rigid plate material, and are formed, for example, by grinding a metal material such as aluminum, an aluminum alloy, or stainless steel. The end plates 3a and 3b are disposed so as to sandwich the stacked plate fins 2a from above and below, and are configured to reliably hold a predetermined interval between the stacked plate fins 2a.

  In the present embodiment, the stacking direction of the plate fin laminate 2 is the vertical direction, and the upper end plate 3 a disposed at the upper end of the plate fin laminate 2 is provided with the supply / discharge pipes 4, 5. In the upper end plate 3a, the inlet pipe 4 and the discharge pipe 5 are provided in the vicinity of both end portions in the longitudinal direction of the plate fin laminate 2, respectively. Accordingly, the refrigerant, which is the first fluid supplied from the inlet pipe 4, flows horizontally through the plurality of flow paths formed inside the plate fins 2 a and is discharged from the discharge pipe 5.

  In the heat exchanger 1 of the present embodiment configured as described above, the refrigerant, which is the first fluid, flows in parallel in the longitudinal direction in the plurality of flow paths inside the plate fins 2 a of the plate fin laminate 2. It is. On the other hand, air, which is the second fluid, is configured to pass through the gap formed between the stacks of the plate fins 2 a in the plate fin stack 2. In the heat exchanger 1 configured as described above, heat exchange between the first fluid and the second fluid is performed in the plate fin laminate 2.

  The plate fin laminate 2 in the heat exchanger 1 of the present embodiment is configured by laminating plate fins 2a (6, 7) having two types of flow path configurations. The first plate fins 6 and the second plate fins 7 of the two types of plate fins 2 a are alternately arranged in the plate fin laminate 2.

  First, the 1st plate fin 6 used for the heat exchanger 1 of this embodiment is demonstrated. FIG. 2 is a plan view showing the first plate fins 6. As shown in FIG. 2, the first plate fin 6 has a header area H formed on both sides in the longitudinal direction and a flow path area P formed between the header areas H on both sides.

  In the header area H formed on both sides of the first plate fin 6, a header opening 8 through which the refrigerant from the inlet pipe 4 or the refrigerant to the outlet pipe 5 flows is formed. Further, in the header region H, the header channels 10 through which the refrigerant from the header opening 8 or the refrigerant to the header opening 8 flows are respectively formed, and the respective headers formed on both sides of the first plate fins 6 The flow path 10 has a symmetrical shape. In the present embodiment, the header channels 10 disposed on both sides of the first plate fin 6 are point symmetrical with the center of the plan view of the first plate fin 6 as the center of symmetry as described later. It has a shape.

  A plurality of refrigerant flow paths (first fluid flow paths) for flowing the refrigerant from the inlet pipe 4 to the discharge pipe 5 in the flow path area P formed between the header areas H on both sides in the first plate fin 6 11 are formed. The plurality of refrigerant channels 11 are formed in parallel in the longitudinal direction, and communicate with the header channels 10 of the header region H on both sides.

  As shown in FIG. 2, a header opening 8 which is a circular through hole is formed substantially at the center of each of the header regions H on both sides, and a header flow passage 10 in which a refrigerant flows is formed around the header opening 8. It is done. The header flow passage 10 is formed from an outer peripheral flow passage 10 a formed to bulge upward and downward around the outer periphery of the header opening 8 and a short from the flow passage region P side (central side of the first plate fin 6) in the outer peripheral flow passage 10 a. It includes a single bypass flow passage 10 b extending in the hand direction, and a multi-branch flow passage 10 c connecting the bypass flow passage 10 b to each refrigerant flow passage 11 in the flow passage region P. The header channels 10 provided on both sides of the first plate fins 6 have a symmetrical shape. For example, the bypass flow passage 10b of the header flow passage 10 on the left side shown in FIG. 2 extends from the flow passage region P side of the outer peripheral flow passage 10a to one in the short direction (upward in FIG. 2) The bypass flow passage 10b of the header flow passage 10 extends from the flow passage region P side of the outer peripheral flow passage 10a to the other side (downward direction in FIG. 2) in the short side direction. That is, the header flow paths 10 provided on both sides of the first plate fin 6 have a point-symmetrical shape with the center of the first plate fin 6 in a plan view as the center of symmetry.

  In the header flow passage 10, the bypass flow passage 10b extending in the short direction of the first plate fins 6 is branched and connected to the plurality of refrigerant flow passages 11 in parallel in the flow passage region P. It is connected to the road 10c. The position where the bypass flow passage 10 b is connected to the multi-branch flow passage 10 c is on the flow passage extension of the refrigerant flow passage 11 at the end in the short direction of the first plate fin 6. Therefore, as shown in FIG. 2, the header flow passage 10 is formed in a U shape by the bypass flow passage 10b extending from the outer peripheral flow passage 10a and the multi-branch flow passage 10c, and the bypass flow passage 10b and the multi-branch flow It is formed to be folded back by the path 10c. That is, the bypass flow passage 10b and the multi-branch flow passage 10c on both sides of the first plate fin 6 have a point symmetrical shape with the center of the first plate fin 6 in a plan view as the center of symmetry. In the header flow passage 10 configured in this manner, the refrigerant flowing through the bypass flow passage 10 b is sequentially arranged in parallel from the refrigerant flow passage 11 at the end in the short direction of the first plate fins 6. The refrigerant is fed to the

  As shown in FIG. 2, a plurality of protrusions 12 (first dowels 12 a and second dowels 12 b) are formed at predetermined intervals in the flow passage region P so as to be adjacent to the refrigerant flow passage 11. ing. These protrusions 12 (12a, 12b) have two types of shapes (in particular, the protrusion lengths are different). The first dowel 12 a is a flow path region support portion, and is provided so as to protrude from an edge (lower edge in FIG. 2) of the flow path region P. The first dowels 12 a are configured to be in contact with the edge of the flow passage area P in the plate fins 2 a adjacent in the stacking direction in the plate fin laminate 2. Thus, the distance between the laminations of the adjacent plate fins 2a is surely defined as a predetermined length by the first dowels 12a coming into contact with the edge portion of the flow passage region P of the adjacent plate fins 2a.

  The second dowels 12 b are flow path support portions, and are arranged at predetermined intervals between the flow paths of the refrigerant flow paths 11 arranged in parallel in the flow path region P. In the present embodiment, the second dowels 12 b are arranged along the flow direction of the second fluid (air) together with the first dowels 12 a. The second dowels 12 b are disposed to face the coolant channels 11 in the adjacent plate fins 2 a in the stacking direction in the plate fin laminate 2, and the pipe wall of the coolant channels 11 in the adjacent plate fins 2 a (outer wall Abuts). As described above, since the second dowel 12b abuts on the outer wall of the refrigerant channel 11 of the adjacent plate fin 2a, the gap between the adjacent plate fin 2a and the refrigerant channel 11 is reliably defined to a predetermined length. Be done.

  The first dowels 12 a and the second dowels 12 b may be arranged in a staggered arrangement with respect to the flow direction of the second fluid (air: B) flowing between the laminations of the plate fin laminate 2, The dowels 12b may be arranged in a staggered arrangement in the flow direction of the second fluid. By this configuration, the second fluid flowing between the laminations of the plate fin laminate 2 becomes a turbulent flow, a flow path is secured, and the heat transfer rate is improved.

  Further, in the first plate fins 6, two positioning holes 13 which are positioning through holes are formed in each header region H. The positioning hole 13 is a positioning hole when laminating a plurality of plate fins 2a (6, 7), and a positioning pin is attached to the positioning hole 13 to hold the stacking position with other plate fins 2a with high accuracy. Ru. In addition, as a positioning pin, it may be fixed in the state inserted in the positioning hole, and it is good also as a structure which improves the rigidity as a heat exchanger. On the other hand, the positioning pins may be finally withdrawn from the heat exchanger in order to reduce the weight of the heat exchanger and the like.

  Further, a positioning outer peripheral portion 13 a which bulges up and down is formed on the outer peripheral portion of the positioning hole 13. The positioning outer peripheral portion 13a forms a space different from the flow path through which the refrigerant flows. The positioning outer peripheral portion 13a abuts between the plate fins 2a (6, 7) adjacent in the stacking direction as described later, and holds a predetermined space between the plate fins 2a adjacent in the stacking direction. And a header area support portion.

  The header channels 10 (10 a, 10 b, 10 c) formed in the header region H and the positioning outer peripheral portion 13 a formed around the positioning holes 13 have predetermined heights on the upper surface and the lower surface of the first plate fins 6. It is formed to have and project. The projecting surfaces (upper end surface and lower end surface) of the header channel 10 (10a, 10b, 10c) and the positioning outer peripheral portion 13a are formed to be flat surfaces. Therefore, the vertical cross-sectional shape orthogonal to the flow direction in the header flow channel 10 (10a, 10b, 10c) has a flat rectangular shape in which the projecting portions (upper end portion and lower end portion) are flat.

  In the present embodiment, the heights of the header channel 10 and the positioning outer peripheral portion 13a are half the length (1/2 pitch) of the gap (distance) between the plate fins 2a adjacent in the stacking direction in the plate fin laminate 2 Is formed. For this reason, in the header region H of the plate fins 2a adjacent in the stacking direction, the pipe wall (outer wall) of the header flow passage 10 and the positioning outer peripheral portion 13a are opposite to the pipe wall (outer wall) of the header flow passage 10 and the positioning outer periphery It abuts on the part 13a respectively. Since the outer wall of the header channel 10 to be in contact is a flat surface, it is a surface that can be securely fixed by, for example, brazing. Therefore, the header region H of each plate fin 2 a in the plate fin laminate 2 is in a state of being stacked with certain predetermined intervals set in advance.

  FIG. 3 is an exploded view showing a part of the configuration of the first plate fin 6 in the plate fin laminate 2 in an enlarged manner. The first plate fins 6 are formed of a metal plate such as aluminum, an aluminum alloy, or stainless steel. In the plate fin laminate 2, the second plate fins 7 alternately stacked with the first plate fins 6 are also formed of the same material as the first plate fins 6.

  As shown in FIG. 3, the first plate fins 6 are formed by pressing a plate material having the same configuration as the first plate member 6a obtained by pressing a plate material having at least one brazing material layer formed on a core material. It is formed by bonding together the plate-like member 6b. In the first plate member 6a and the second plate member 6b, the positioning outer peripheral portion 13a formed around the header flow passage 10 and the positioning hole 13 in the header region H, and the refrigerant flow passage 11 in the flow passage region P, protrusion The (first dowel 12a and the second dowel 12b) 12 is pressed into a shape in which each is formed.

  As described above, the outer peripheral flow passage 10a formed in the header region H, the header flow passage 10 formed of the bypass flow passage 10b and the multi-branch flow passage 10c, and the positioning outer peripheral portion 13a formed around the positioning hole 13 Are formed protruding on the upper and lower surfaces of the first plate fins 6, and each have the same height of half (1/2 pitch) of the distance between the adjacent plate fins 2a in the stacking direction There is. Further, the outer peripheral flow passage 10a, the bypass flow passage 10b, and the multi-branch flow passage 10c in the header flow passage 10 are formed wider than the refrigerant flow passage 11 provided in parallel in the flow passage region P The longitudinal cross-sectional shape orthogonal to the has a rectangular shape. On the other hand, in the refrigerant flow path 11 formed in the flow path region P, the hydraulic diameter is desirably 1 mm or less.

  In the present embodiment, the cross-sectional shape (the cross-sectional shape orthogonal to the direction in which the refrigerant flows) of the coolant channel 11 is described as a circular shape, but the present disclosure is not limited to the circular shape. In the present disclosure, the circular shape also includes a compound curve shape formed by a circle, an ellipse, and a closed curve. As the coolant channel 11 in the present disclosure, for example, as shown in FIG. 4, the cross-sectional shape orthogonal to the flowing direction of the coolant includes a rectangular shape and the like in addition to a circular shape, and protrudes only on one side in the stacking direction. It includes a configuration having a shape or protruding on both sides in the stacking direction. In addition, in FIG. 4 showing various cross-sectional shapes of the refrigerant flow path, although it is shown in a separated state to show that the refrigerant flow path 11 is formed of two plate-like members, actually it is shown as two The plate-like member abuts and a refrigerant channel 11 having a predetermined cross-sectional shape is formed.

  FIG. 5 is a plan view showing the vicinity of the header region H of the first plate fin 6 in the plate fin laminate 2. FIG. 6 is a perspective view showing a cross section of the plate fin laminate 2 shown in FIG. 5 taken along line VI-VI. As shown in the plate fin laminate 2 of FIG. 6, the plate fin laminate 2 is configured by alternately laminating first plate fins 6 and second plate fins 7. Although FIG. 6 shows a state in which four plate fins (6, 7) are stacked, this is a part, and in the plate fin laminate 2, a large number of plate fins (6, 7) Are alternately stacked.

  In the plate fin laminate 2, the outer wall (flat surface) of the header flow passage 10 in the header region H of each of the first plate fins 6 and the second plate fins 7 is the plate fins (6, 7) adjacent in the stacking direction It abuts on the outer wall (flat surface) of the header channel 10 in the stacking direction. In FIG. 6, it is shown that the flat surface of the outer wall of the outer peripheral flow passage 10a is in contact with the flat surface of the outer wall of the outer peripheral flow passage 10a of the adjacent plate fins (6, 7) in the stacking direction. In the present embodiment, a high pressure is applied to the refrigerant flowing through the header flow passage 10 in the header flow passage 10, but the header of the plate fin (6, 7) to which the pipe wall (outer wall) of the header flow passage 10 is adjacent. Because it is fixed to the pipe wall (outer wall) of the flow path 10, the expansion of the pipe wall in the header flow path 10 is restricted, and it has a pressure resistant construction. Therefore, in the configuration of the present embodiment, the pressure of the refrigerant flowing through the header channel 10 can be set high, and highly efficient heat exchange can be performed with high reliability.

  In addition, you may comprise so that only the tube wall of the header flow path 10 in the header area | region H may be formed by the thick part which is thicker than another site | part. FIG. 7 is a cross-sectional view showing a part of a header area H in which plate members having different thicknesses are processed by press forming. As shown in FIG. 7, by forming the tube wall portion of the header flow passage 10 in the header region H with a thick portion which is thicker than the other portions, it is possible to ensure even the refrigerant of a higher pressure. It becomes the composition of the heat exchanger which can respond.

  Further, as shown in FIG. 7, only the tube wall of the refrigerant flow passage 11 in the flow passage region P may be constituted by a thick portion thicker than the other portions. With such a configuration, the refrigerant channel 11 can be adapted to a refrigerant having a higher pressure.

  As shown in FIG. 6, in the plate fin laminate 2 of the present embodiment, the first plate fins 6 and the second plate fins 7 are alternately stacked. The second plate fins 7 have substantially the same configuration and shape as the first plate fins 6, but the refrigerant channel 11 and the projections 12 (the first dowels 12 a and the second dowels 12 b in the channel region P) ) Are different from the first plate fins 6.

  FIG. 8 is a view showing that the plate fin laminate 2 is configured by laminating the first plate fins 6 and the second plate fins 7. As shown in FIG. 8, in the second plate fin 7, the refrigerant channel 11 of the channel region P is at a position facing the second dowel 12 b of the first plate fin 6. That is, the refrigerant flow passage 11 in the flow passage region P of the second plate fin 7 is disposed to face the position between the refrigerant flow passages 11 in the flow passage region P of the first plate fin 6. In the plate fin laminated body 2 in which the first plate fins 6 and the second plate fins 7 are laminated, the pipe wall (outer wall) of the refrigerant flow path 11 opposed to the second dowel 12b which is the flow path supporting portion is reliably engaged. It is the composition which touches.

  In the plate fin laminate 2 of the present embodiment, the refrigerant flow paths in the first plate fins 6 and the second plate fins 7 alternately stacked in a cross section orthogonal to the flow direction of the first fluid A in the flow path region P. 11 are configured to be in a staggered arrangement. As a specific configuration of this staggered arrangement, refer to FIG. 18 described later.

  Further, the first dowels 12 a, which are flow path area supporting portions formed at the edge of the flow path area P of the second plate fins 7, abut on the edge of the flow path area P of the adjacent first plate fins 6. And is fixed. Therefore, the protrusion height of the first dowel 12a, which is the flow passage region support, is higher than the protrusion height of the second dowel 12b, which is the flow passage support, by the height of the refrigerant flow passage 11.

  FIG. 9 is a perspective view showing a cross section of the plate fin laminate 2 shown in FIG. 8 taken along line IX-IX. In the plate fin laminate 2 shown in FIG. 9, only the four first plate fins 6, the second plate fins 7, the first plate fins 6, and the second plate fins 7 are stacked in order from the top. There is. As shown in FIG. 9, the first dowel 12 a of the flow passage area P in the first plate fin 6 abuts on the edge of the flow passage area P in the opposing second plate fin 7. Further, the first dowels 12 a of the flow passage area P in the second plate fins 7 are in contact with the edge of the flow passage area P in the opposing first plate fins 6.

  On the other hand, the second dowel 12 b of the flow passage area P in the first plate fin 6 abuts on the pipe wall (outer wall) of the refrigerant flow path 11 of the flow passage area P in the opposing second plate fin 7. Further, the second dowels 12 b of the flow passage region P in the second plate fin 7 are in contact with the pipe wall (outer wall) of the refrigerant flow passage 11 of the flow passage region P in the opposing first plate fin 6.

  In the present disclosure, the stacked plate fins 2a (6, 7) in the plate fin laminate 2 are described as being fixed by brazing, but the present disclosure is not limited to this configuration, Other heat-resistant fixing methods, such as a mechanical connection method and a fixing method using a chemical bonding member may be used.

  As described above, in the plate fin laminate 2 of the present embodiment, the edge of the flow path area P of the fin plate (6, 7) opposed to the first dowel 12a of the flow path area P is reliably supported, A predetermined gap is secured between the laminations. In the present embodiment, the first dowel 12 a of the flow passage region P serves as the flow passage region supporting portion in the plate fin laminate 2.

  In addition, the second dowels 12b of the flow passage region P are in contact with the pipe wall (outer wall) of the refrigerant flow passage 11 of the facing fin plate (6, 7). A predetermined distance is maintained between the stacks of the plates (6, 7) and the coolant channel 11. In the present embodiment, the second dowels 12 b of the flow passage region P serve as the flow passage supporting portion in the plate fin laminate 2.

  In the above embodiment, the first dowels 12a of the flow passage region P are described as being in contact with the edge of the flow passage region P of the facing fin plates (6, 7), but other configurations are also possible It is. For example, the first dowel 12a, which is a flow path area support portion formed at the edge of the flow path area P, is used as a flow path area convex portion, and the edge of the flow path area P of the opposing fin plate (6, 7) The flow path region concave portion may be formed to fit the flow path region convex portion and the flow path region concave portion.

[Stacking by positioning pin]
In the plate fin laminate 2 of the present embodiment, the positioning pin 9 is mounted so that the plurality of plate fins 2a (6, 7) can be easily and reliably stacked at a predetermined position. . FIG. 10 is a perspective view showing a state in which the positioning pin 9 is attached to the plate fin laminate 2. FIG. 11 is an enlarged cross-sectional view of the plate fin laminate 2 to which the positioning pin 9 is attached. The cross-sectional view of FIG. 11 is a view cut along a plane indicated by reference numeral XI in FIG.

  In the present embodiment, the positioning pin 9 is inserted into the positioning hole 13 which is a through hole formed in the header region H of each plate fin 2a (6, 7) and brazed. For this reason, the plate fin laminate 2 has a mechanical structure reinforced and has a configuration in which the pressure resistance to the refrigerant is remarkably strengthened. In the present embodiment, an aluminum metal rod is used as the positioning pin 9.

  In the present embodiment, as shown in FIG. 2, the first dowel 12 a which is a flow passage area support formed in the flow passage area P and the second dowel 12 b which is a flow passage support are the second fluid B. Are arranged parallel to the air flow direction. As described above, since the plurality of projections are arranged side by side between the laminations, the flow path resistance to the second fluid (air) B flowing between the laminations in the plate fin laminated body 2 can be reduced. With such a configuration, in the plate fin laminate 2 of the present embodiment, it is possible to reduce the sound generated when the second fluid flows between the laminates.

[Modification of plate fin]
In addition, as a modification of the plate fin 2a in the plate fin laminated body 2 of the heat exchanger which concerns on this indication, there exists a structure which changed arrangement | positioning of protrusion 12 (12a, 12b). For example, by arranging the plurality of protrusions 12 (12a, 12b) provided between the stacks in the plate fin stack 2 in a staggered arrangement, turbulent flow is generated in the second fluid B passing between the stacks, and heat exchange efficiency is achieved. May be configured to enhance the FIG. 12 is a plan view of plate fins 2b showing a configuration in which a plurality of protrusions 12 (12a, 12b) are arranged in a staggered arrangement between the layers in the plate fin laminate 2. As shown in FIG. Also in this configuration, the first dowel 12a, which is the flow passage area support, is in contact with the edge of the opposing flow passage area P, and the second dowel 12b, which is the flow passage support, is in the opposite flow passage area P. It is configured to be in contact with the tube wall (outer wall) of the coolant channel 11.

  Further, by forming the plurality of projections 12 between the laminations more leeward than the windward side, turbulent flow may be generated in the second fluid B passing between the laminations to enhance the heat exchange efficiency. In addition, the number of the first dowels 12 a in the protrusions 12 may be at least the number of the protrusions 12 on the downwind side more than the upwind side in the flow direction of the second fluid B (air). Thus, by providing the projections 12 on the downwind side more than the upwind side, it is possible to increase the heat transfer coefficient on the downwind side where the flow velocity is low. FIG. 13 is a plan view of the plate fin 2c showing a configuration in which the protuberance 12 on the downwind side is provided more than the protuberance 12 on the upwind side in the flow direction of the air that is the second fluid B. Also in this configuration, the first dowel 12a, which is the flow passage area support, is in contact with the edge of the opposing flow passage area P, and the second dowel 12b, which is the flow passage support, is in the opposite flow passage area P. Contact the tube wall (outer wall) of the coolant channel.

  As described above, regarding the arrangement configuration of the plurality of projections 12 provided between the laminations of the plate fin laminate 2 in the present embodiment, various configurations can be presented, but the specification, configuration, and use of the heat exchanger The optimal configuration is selected according to the needs of the person.

  Moreover, the further modification of the plate fin laminated body 2 in the heat exchanger 1 is demonstrated. In the plate fin laminate 2 in the above-described embodiment, the inlet pipe 4 and the discharge pipe 5 are respectively connected in the vicinity of both end portions in the longitudinal direction, and the header region H is formed on both sides of each plate fin 2a. And two header openings 8 are provided (see FIG. 2).

  FIG. 14 is a view showing a modification of the plate fin laminate, and is a plan view showing the plate fins 2 d constituting the plate fin laminate. As shown in FIG. 14, the header region H is formed only on one end side (left side in FIG. 14) of the plate fin 2 d, and the other region is the flow passage region P. That is, in the plate fin laminate of this modification, the inlet pipe and the discharge pipe are connected in the region near one end in the longitudinal direction. In the plate fin 2d shown in FIG. 14, both the inlet side header opening 8a and the outlet side header opening 8b are formed in the header area H shown on the left side.

  In the plate fin 2d of FIG. 14, the opening shape of the header opening 8a on the supply side has a larger diameter than the opening shape of the header opening 8b on the discharge side. This is the case where the heat exchanger is used as a condenser, in which case the volume of refrigerant after heat exchange is reduced. Further, the refrigerant from the header opening 8a on the inlet side flows through the plurality of refrigerant channels 11a arranged in parallel in the channel area P, and is turned back in the vicinity of the end of the plate fin 2d (near the right end in FIG. 14) It is a structure. In the flow path region P, a refrigerant flow path 11a into which the refrigerant flows from the inlet opening 8a on the inlet side, and a refrigerant flow path 11b flowing to the outlet opening 8b on the discharge side after the return It is formed. In addition, when the said heat exchanger is used as an evaporator, an inlet / outlet becomes reverse of the above-mentioned.

  Further, as shown in FIG. 14, the number of the refrigerant channels 11b arranged in parallel to the header opening 8b on the discharge side is the same as that of the refrigerant channels 11a arranged in parallel, into which the refrigerant from the header opening 8a on the inlet side flows. It is set smaller than the number. This is the same reason as the different diameters of the header openings 8a and 8b, and the volume of the refrigerant after heat exchange is reduced.

  Further, in the plate fin 2d having the configuration shown in FIG. 14, the region where the refrigerant passage 11a into which the refrigerant from the header opening 8a on the inlet side flows in is formed, and the refrigerant passage 11b flowing to the header opening 8b on the outlet side Between the formed region, a plurality of openings 16 are formed for the purpose of reducing the heat conduction between the refrigerants in the plate fins (insulation).

[end plate]
Next, the end plates (3a, 3b) provided at both ends (upper and lower ends) of the plate fin laminate 2 in the stacking direction in the heat exchanger 1 of the present embodiment will be described. FIG. 15 is a perspective view showing the upper end plate 3a provided on the upper end of the plate fin laminate 2 in the stacking direction, and FIG. 16 is a lower end plate 3b provided on the lower end of the plate fin laminate 2 in the stacking direction. It is a perspective view shown. FIG. 17 is an enlarged perspective view showing a joined state of the header region H and the upper end plate 3 a in the plate fin laminate 2.

  In the present embodiment, as described above, the first plate fins 6 and the second plate fins 7 constituting the plate fin laminate 2 are each two plate members (6a and 6b, 7a and 7b) It is formed by bonding together. That is, the first plate fin 6 is formed by bonding the pressed first plate member 6a and the second plate member 6b, and the second plate fin 7 is formed by pressing the first plate 6 The second member 7a and the second plate member 7b are bonded to each other.

  In the plate fin laminate 2 in the present embodiment, the first plate fins 6 and the second plate fins 7 are alternately stacked, and the uppermost end of the plate fin laminate 2 is one side of the first plate fins 6. Only the second plate member 6b is disposed (see FIG. 17). Therefore, although the uppermost end surface of the plate fin laminate 2 has a recess which is a thin groove for forming a flow passage, most of the uppermost end surface is formed of a flat surface. For this reason, the flat surface at the top end face of the plate fin laminate 2 becomes a bonding surface (braided surface) which is a contact surface with the lower surface of the upper end plate 3a, and the bonding area becomes large.

  As shown in FIG. 17, an end plate convex portion 30 is formed on the surface of the upper end plate 3 a disposed on the uppermost end surface of the plate fin laminate 2 opposite to the plate fin laminate 2. The end plate convex portion 30 has a shape corresponding to a recess for forming a flow path in the facing second plate-like member 6 b. Therefore, when the upper end plate 3a is disposed on the uppermost surface of the plate fin laminate 2, the end plate convex portion 30 of the upper end plate 3a is a recess for forming a flow path in the second plate member 6b. Get stuck.

  In addition, as the end plate convex part 30 formed in the upper end plate 3a, it may be formed only in the recessed part for flow path formation of the wide in the header area | region H. As shown in FIG. This is because the recess (groove) for forming the flow passage in the flow passage region P has a narrow width and a sufficient contact surface is secured. In the present embodiment, as a specific example, an example in which the second plate member 6b of the first plate fin 6 is disposed as the uppermost surface of the plate fin laminate 2 will be described, but this is an example. The uppermost surface of the laminated body 2 may be configured by one side of either the first plate fin 6 or the second plate fin 7 according to the order of lamination.

  FIG. 18 is an enlarged perspective view showing a joined state of the lower end surface of the plate fin laminate 2 and the lower end plate 3b. As shown in FIG. 18, in the present embodiment, only the first plate-like member 7 a which is one side of the second plate fins 7 is disposed at the lowermost end of the plate fin laminate 2. Therefore, the lowermost end face of the plate fin laminate 2 has a recess for channel formation, but most of the lowermost end face is formed of a flat surface. Therefore, a sufficient bonding area is secured between the lower end surface of the plate fin laminate 2 and the lower end plate 3b.

[Modification of plate fin laminate and end plate]
FIGS. 19-25 is a figure which shows the various modification of a plate fin laminated body and an end plate.

  FIG. 19 is an enlarged perspective view showing a bonded state of the lower end surface of the plate fin laminate 2 and the lower end plate 31 b. As shown in FIG. 19, at the lowermost end of the plate fin laminate 2, a first plate member 7 a which is one side of the second plate fins 7 is disposed. The lowermost end surface of the plate fin laminate 2 is a surface having a downward concave surface of the first fluid channel recess 11a constituting the upper half of the refrigerant channel 11 which is the first fluid channel in the first plate member 7a. It is composed of The surface having the concave surface (groove) of the first fluid channel recess 11a is directed downward and is in contact with the upper surface of the lower end plate 31b.

  FIG. 20 is a plan view showing the upper surface of the lower end plate 31 b. As shown in FIGS. 19 and 20, on the upper surface of the lower end plate 31b, there are provided a flow passage area P and a header area H having the same configuration as the first plate-like member 7a facing the lower end plate 31b. That is, the header area H is formed on both sides in the longitudinal direction of the lower end plate 31 b, and the flow path area P is formed in the central portion sandwiched by the header area H.

  As shown in FIG. 20, a header channel recess 32 is formed in the header region H on the upper surface of the lower end plate 31b, and a plurality of linear coolant channel recesses (grooves) 33 are formed in the channel region P. It is formed in parallel. In addition, the recessed part 32 for header flow paths of the header area H in the lower end plate 31b is comprised by the bottomed recessed part which has a circle substantially the same as the circle of the header opening 8 in plate fin (6, 7). The header channel recess 32 blocks the refrigerant at the header opening 8 in communication with the supply and discharge pipe.

  As described above, the refrigerant channel recesses (grooves) 33 in the channel region P formed in the lower end plate 31 b are formed in the first plate member 7 a which is one side of the opposing second plate fins 7. It has the same shape at the same position as the refrigerant channel recess 11a. Therefore, in the lower end plate 31b, a header flow passage serving as a refrigerant reservoir is formed in the header region H by the first plate-like member 7a facing the lower end plate 31b, and a plate fin laminate is formed in the flow passage region P. The same refrigerant flow path as the refrigerant flow path 11 in 2 is formed. As a result, in the heat exchanger configured as described above, a refrigerant flow path is formed by the lower end plate 31b and the lowermost first plate member 7a, and the heat exchange efficiency can be further enhanced. Become.

  With regard to the configurations of the lower end surface and the lower end plate 31b of the plate fin laminate 2 shown in FIGS. 19 and 20, the upper surface of the plate fin laminate 2 and the lower surface of the upper end plate are similarly configured. Thus, it is possible to form a refrigerant flow path between the uppermost end surface of the plate fin laminate 2 and the lower surface of the upper end plate.

  FIGS. 21 and 22 are views showing still another configuration of the plate fin laminate 21 and the lower end plate 34 b. FIG. 21 is an enlarged perspective view showing a joined state of the lower end of the plate fin laminate 21 and the lower end plate 34 b. FIG. 22 is a plan view (a) and a side view (b) showing the upper surface of the lower end plate 34b. In the configuration shown in FIG. 21, the second plate fins 7 are disposed at the lowermost end of the plate fin laminate 21. That is, in this modification, in the plate fin laminate 21, the first plate fins 6 and the second plate fins 7 formed by laminating two plate members (6a and 6b, 7a and 7b) are alternately arranged. It is laminated and constituted. Therefore, in the present modification, at the lowermost end of the plate fin laminate 21, either the first plate fin 6 or the second plate fin 7 is disposed in accordance with the stacking order.

  As shown in FIG. 22, a plurality of projections (35, 36) are formed on the upper surface of the lower end plate 34b, and for example, supports the second plate fins 7 at the lowermost end of the plate fin laminate 21. Is configured as. In the plurality of projections (35, 36) formed on the upper surface of the lower end plate 34 b, the flow path supporting convex portion 35 for supporting the refrigerant flow path 11 of the second plate fin 7 and the flow of the second plate fin 7 It divides into the flow-path area | region support convex part 36 which supports the channel | path area | region P. FIG. As shown in FIG. 21, the flow path support convex portion 35 and the flow path region support convex portion 36 have two types of shapes (in particular, the projection lengths are different).

  The flow path region supporting convex portion 36 of the lower end plate 34 b is configured to abut on the edge portion of the flow path region P in the second plate fin 7. Thus, the distance between the lower end plate 34 b and the second plate fin 7 is predetermined by the abutment of the flow path region supporting convex portion 36 with the edge of the flow path region P of the second plate fin 7. The length is definitely defined.

  The flow path support convex portion 35 is a flow path support portion, and is disposed at the position of the refrigerant flow path 11 arranged in parallel in the flow path region P of the facing second plate fins 7. In the present modification, the flow path support convex portions 35 are arranged along the flow direction of the second fluid (air) together with the flow path region support convex portions 36. The flow path supporting convex portion 35 is disposed to face the refrigerant flow path 11, and abuts on the pipe wall (outer wall) of the refrigerant flow path 11 of the second plate fin 7. As described above, since the flow path supporting convex portion 35 abuts on the pipe wall (outer wall) of the refrigerant flow path 11 of the second plate fin 7, the second plate fin 7 at the upper surface and the lowermost end of the lower end plate 34b The gap between the two is reliably defined to a predetermined length.

  The plurality of projections (35, 36) formed on the upper surface of the lower end plate 34b are disposed in a staggered arrangement in the flow direction of the second fluid (air: B) flowing to the plate fin laminate 21. It is also good. In addition, the plurality of projections (35, 36) may be formed with the leeward side more than the windward side.

  With regard to the configurations of the lower end surface and the lower end plate 34b of the plate fin laminate 21 shown in FIGS. 21 and 22, the same should be applied to the uppermost end surface of the plate fin laminate 21 and the lower surface of the upper end plate. Is possible.

  FIG. 23 and FIG. 24 are diagrams showing a lower end plate 37 b of still another configuration. FIG. 23 is an enlarged perspective view showing a joined state of the lower end of the plate fin laminate 21 and the lower end plate 37b. FIG. 24 is a plan view (a) and a side view (b) showing the upper surface of the lower end plate 37b. In the configuration shown in FIG. 23, the plate fin stack 21 is the same as the configuration of the plate fin stack 21 shown in FIG. 21 described above. That is, in this modification, the plate fin laminate 21 is configured by alternately laminating the first plate fins 6 and the second plate fins 7, and at the lowermost end of the plate fin laminate 21, the first Either of the plate fins 6 or the second plate fins 7 is arranged according to the stacking order.

  As shown in FIG. 24, on the upper surface of the lower end plate 37 b, a plurality of protrusions (38, 39) extended in the longitudinal direction are formed, and for example, at the lowermost end of the plate fin laminate 21, The second plate fins 7 are configured to be supported. In the plurality of projections (38, 39) formed to project in a peak shape on the upper surface of the lower end plate 37 b, a flow path supporting convex portion 38 for supporting the refrigerant flow path 11 of the second plate fin 7, and It divides into the flow-path area | region support convex part 39 which supports the flow-path area | region P of 2 plate fins 7. As shown in FIG. As shown in FIG. 23, the flow path support convex portion 38 and the flow path region support convex portion 39 have two types of shapes (in particular, the protrusion lengths are different).

  The flow path region supporting convex portion 39 of the lower end plate 37 b abuts on the edge portion of the flow path region P in the second plate fin 7. Thus, the distance between the lower end plate 37 b and the second plate fin 7 is predetermined by the abutment of the flow path region supporting convex portion 39 with the edge portion of the flow path region P of the second plate fin 7. The length is definitely defined.

  The flow path support convex portion 38 is a flow path support portion, and is disposed at the position of the refrigerant flow path 11 arranged in parallel in the flow path region P of the facing second plate fins 7. The flow path supporting convex portion 38 is disposed to face the refrigerant flow path 11, and abuts against the pipe wall (outer wall) of the refrigerant flow path 11 of the second plate fin 7 with certainty. Thus, since the flow path supporting convex portion 38 abuts on the pipe wall (outer wall) of the refrigerant flow path 11 of the second plate fin 7, the second plate fin 7 at the upper surface and the lowermost end of the lower end plate 37b The gap between the two is reliably defined to a predetermined length.

  With regard to the configurations of the lower end surface and the lower end plate 37b of the plate fin laminate 21 shown in FIGS. 23 and 24, the same should be applied to the uppermost end surface of the plate fin laminate 21 and the lower surface of the upper end plate. Is possible.

  FIG. 25 is a view showing a lower end plate 40 b of still another configuration. FIG. 25 is an enlarged perspective view showing a joined state of the lowermost end of the plate fin laminate 21 and the lower end plate 40b. In the configuration shown in FIG. 25, the plate fin laminate 21 is the same as the configuration of the plate fin laminate 21 shown in FIG. 21 described above. In the configuration shown in FIG. 25, on the upper surface of the lower end plate 40b, the protrusion 35 which is the flow path supporting convex portion shown in FIG. 21 described above and the projection 36 which is the flow path region supporting convex portion are formed. ing. Further, on the upper surface of the lower end plate 40b, a dowel is disposed at the lowermost end of the plate fin laminate 21, for example, a dowel which is abutted and joined to the second dowel 12b which is a flow path supporting portion in the second plate fin 7. The support convex portion 41 is formed. The dowel supporting convex portion 41 is a ridge-shaped protruding portion extended in the longitudinal direction, and is extended between the refrigerant channels 11 in the opposing second plate fins 7. In addition, the dowel support convex portion 41 has a height that reliably abuts on the second dowel 12 b provided between the refrigerant channels 11 in the second plate fin 7. The first dowels 12a formed at the edges of the plate fins (6, 7) disposed at the lowermost end of the plate fin laminate 21 have a height to abut the upper surface of the lower end plate 40b. There is.

  With regard to the configurations of the lower end surface and the lower end plate 40b of the plate fin laminate 21 shown in FIG. 25, the same can be applied to the uppermost end surface of the plate fin laminate 21 and the lower surface of the upper end plate. Become.

  In addition, as shown in the above-described FIG. 14, even in the configuration example in which the header region H is formed only on one end side (the left side in FIG. 14) of the plate fins in the plate fin laminate. It goes without saying that it is possible to apply the configuration of the modification shown in FIG.

[Side plate]
FIG. 26 shows a modification in which one set of side plates 17 and 18 is provided so as to sandwich the end plates 3a and 3b provided at the upper and lower ends of the plate fin laminate 2 from both sides in the heat exchanger of the present disclosure. It is a perspective view shown. The modified example shown in FIG. 26 is configured such that the side surface side on the side of one header region H to which the inlet pipe 4 is connected in the plate fin laminate 2 is sandwiched by the first side plate 17 from above and below. Further, in the plate fin laminate 2, the side surface side on the side of the other header region H to which the discharge pipe 5 is connected is configured to be vertically held by the second side plate 18. The first side plate 17 is formed with an upper opening 17 a through which the inlet pipe 4 passes and a side opening 17 b so that air as the second fluid B flows into the header region of the plate fin laminate 2. Similarly, the second side plate 18 is formed with an upper opening 18a through which the discharge pipe 5 penetrates and a side opening 18b so that air as the second fluid B flows into the header region H of the plate fin laminate 2 It is done.

  As described above, in the modified example shown in FIG. 26, since the pair of side plates 17 and 18 is provided to sandwich the upper and lower portions of the header region H from both sides of the plate fin laminate 2, the end plate 3a, Even if the thickness as 3b is made thin and simple structure, the pipe wall of the header channel 10 of the header region H in the plate fin 2a constituting the plate fin laminate 2 can be reliably held down by predetermined pressure from above and below It becomes. The plate fin laminate 2 configured as described above can flow a desired high pressure refrigerant to the plate fin laminate 2 and can be configured to be capable of highly efficient heat exchange.

  Although FIG. 26 is described as a configuration example for the plate fin laminate 2 shown in FIG. 1, one set of side plates 17 and 18 is also used in the configuration of the modification described with reference to FIGS. 19 to 25. Can be provided to hold the plate fin laminate vertically. Even in the configuration of such a modification, the plate fin laminate can be reliably pressed from above and below at a predetermined pressure, and a refrigerant of a desired high pressure can be flowed through the plate fin laminate, and heat exchange with high efficiency is achieved. It will be possible configuration.

  As described above, in the configuration of the heat exchanger according to the present disclosure, it is possible to achieve weight reduction, miniaturization, and high efficiency of heat exchange, and a high-pressure refrigerant flows through the plate fins in the plate fin laminate. Even with the configuration, the heat exchanger has high reliability and high heat exchange efficiency.

  The present disclosure is a lightweight and miniaturized device that can perform heat exchange with high reliability and efficiency, and thus becomes a heat exchanger with high market value.

1 heat exchanger 2 plate fin laminate 2a plate fin 3 end plate 4 inlet pipe (inlet header)
5 Exhaust pipe (outlet header)
6 1st plate fin 7 2nd plate fin 8 header opening 9 positioning pin 10 header channel 10a outer peripheral channel 10b bypass channel 10c multiple branch channel 11 refrigerant channel (first fluid channel)
12 projection 12a first dowel (flow passage area support portion)
12b Second dowel (channel support)
13 Positioning hole 13a Positioning outer peripheral part (header area support part)
17 1st side plate 18 2nd side plate

Claims (23)

A plate fin laminate in which plate fins having a flow path through which the first fluid flows are stacked;
And a supply / discharge pipe through which the first fluid flows in the flow path of each plate fin in the plate fin laminate.
A heat exchanger for flowing a second fluid between the stacks of the plate fin stacks to exchange heat between the first fluid and the second fluid,
The plate fins are
A flow passage region having a plurality of linear first fluid flow passages such that the first fluid flows in parallel;
A header area having a header flow path for communicating each first fluid flow path of the flow path area with the supply and discharge pipe;
The outer wall of the header channel is configured to contact the outer wall of the header channel of the plate fin adjacent in the stacking direction in the plate fin laminate ,
In the plate fins provided with the header regions on both sides, each of the header channels includes bypass channels that connect the supply and discharge pipe and the multi-branch channel, and are disposed on both sides of the plate fins The heat exchanger according to claim 1, wherein the bypass flow passage and the multi-branch flow passage have a point-symmetrical shape centered on the center of the plate fin .   The heat exchanger according to claim 1, wherein the header flow path has a multi-branch flow path for flowing the refrigerant of the supply and discharge pipe to each first fluid flow path of the flow path region.   The heat exchanger according to claim 2, wherein the multi-branched flow path is configured to abut on an outer wall of a multi-branched flow path in adjacent plate fins in the stacking direction in the plate fin laminate.   The heat exchanger according to any one of claims 1 to 3, wherein in the header region, a tube wall of the header flow passage is formed thicker than other portions.   The heat exchanger according to any one of claims 1 to 4, wherein in the flow passage area, a pipe wall of the flow passage is formed thicker than other portions. The plate fins Te odor, heat exchanger according to any one of claims 1 to 4, wherein the header channel of the header area of both sides is configured so as to have a symmetrical shape. In the plate fin in which the header area is provided on both sides, a plurality of projecting header area supporting portions different from the flow path are formed in the header area, and the header area supporting portions disposed on both sides of the plate fin The heat exchanger according to any one of claims 1 to 6 , wherein the heat exchanger is configured to have a point-symmetrical shape with the center of the plate fin as the center of symmetry.   The heat exchanger according to any one of claims 1 to 5, wherein in the plate fin, the header region is provided at one end side, and the supply and discharge pipe is provided at a position corresponding to the header region. A plurality of projecting header area supporting portions different from the flow path are formed in the header area of the plate fin, and the header area supporting portion is in contact with the header area of the plate fin adjacent in the stacking direction in the plate fin laminate. The heat exchanger according to any one of claims 1 to 8 , configured to form a predetermined space between the plate fins adjacent in the stacking direction in contact with each other. 10. The heat exchanger according to claim 9 , wherein at least two of the header area support portions provided in the header area have through holes, and the through holes serve as positioning holes. The heat exchanger according to claim 10 , wherein positioning pins are fixed to the positioning holes. The flow path region supporting portion different from the flow path is formed in the flow path region of the plate fin, and the flow path region of the plate fin adjacent to the flow path region supporting portion in the stacking direction of the plate fin laminate The heat exchanger according to any one of the preceding claims , wherein the heat exchanger is configured to abut on to form a predetermined space between the stacks. The heat exchanger according to any one of claims 1 to 12 , wherein the plate fin laminate is configured by laminating the plate fins having different flow channel shapes. The heat exchanger according to any one of claims 1 to 12 , wherein the plate fin laminate is configured by alternately laminating the plate fins having two types of flow path shapes. 15. The plate fin laminate according to claim 14 , wherein the channels in the plate fins alternately stacked are arranged in a zigzag in a cross section orthogonal to the direction in which the first fluid flows in the channel region. Heat exchanger. A projecting flow path support portion different from the flow path is formed in the flow path region of the plate fin, and the flow path support portion is in the flow path region of the plate fin adjacent in the stacking direction in the plate fin laminate. 15. A heat exchanger according to claim 13 or 14 , configured to abut the tube wall of the first fluid flow path. The heat exchanger according to claim 16 , wherein the flow path support portions provided to project in the plate fins are arranged in a staggered arrangement with respect to the flow direction of the second fluid flowing between the stacks of the plate fin laminates. . The heat exchanger according to claim 16 , wherein the number of the flow path support portions provided in the plate fins is greater than the windward side on the leeward side in the flow direction of the second fluid B. In the plate fin having two types of flow path shapes, a protruding flow path area convex portion different from the flow path is formed in the flow path area of one of the plate fins, and in the flow path area of the other plate fin A flow passage region concave portion is formed at a position corresponding to the flow passage region convex portion, and the flow passage region convex portion and the flow passage region concave portion of the plate fin adjacent in the stacking direction in the plate fin laminate engage with each other. The heat exchanger according to claim 14 , wherein the space between adjacent ones of the plate fins is a predetermined space. The heat exchanger according to any one of claims 1 to 19 , wherein at least the flow passage in the flow passage region of the plate fin has a rectangular cross section orthogonal to the direction in which the first fluid flows in the flow passage. . The heat exchanger according to any one of claims 1 to 19 , wherein at least the flow passage in the flow passage region of the plate fin has a circular cross section orthogonal to the flow direction of the first fluid in the flow passage. . The heat exchanger according to any one of claims 1 to 21 , wherein at least the flow passage of the flow passage region in the plate fin is formed so as to protrude only on one side in the stacking direction of the plate fin laminate. The heat exchanger according to any one of claims 1 to 21 , wherein at least the flow passage of the flow passage region in the plate fin is formed to protrude on both sides in the stacking direction of the plate fin laminate.

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