Sealing structure of heat exchanger

Abstract

[Problem] To improve sealing performance by keeping the compressibility of a packing in a partition part within an appropriate range entirely to suppress partial insufficient compression or excessive compression of the packing. [Solution] In a sealing structure of a heat exchanger 100 provided with a packing 5 between a header plate 3 and a header tank 4, the inequality of t·(1-αmax) ≤ [{t·(1-αn)} 2+x2]1 / 2·cos(φ-θn)≤t·(1-αmin), and the inequality of t·(1-αmax)≤ Rh-Rp≤t·(1-αmin) are satisfied, where the thickness of the packing 5 in a natural state, a constant αmax=0.45, a constant αn=0.33, a constant αmin=0.21, the length Lp of a plate flat surface portion 35b, the length Lh (>Lp) of a tank flat surface portion 47, x calculated as Lh-Lp, the inclination angle φ of a plate side wall portion 33b and a tank side wall portion 46, θ calculated as Arctan [x / {t·(1-αn)], the radius of curvature Rp of a plate curved-surface 36, and the radius of curvature Rh of a tank curved-surface 48 are used.

Description

Heat exchanger sealing structure

[0001] This invention relates to a sealing structure for a heat exchanger.

[0002] Some heat exchangers have a header plate and header tank at the end of the core. In some of these heat exchangers, the interior is divided into multiple sections by a partition provided in the packing that seals the space between the partition wall inside the header tank and the header plate.

[0003] Special table 2017-503992 publication

[0004] Patent Document 1 discloses a header plate having an inclined portion that is tilted by 20° to 65° at a location corresponding to the leg portion of the partition.

[0005] However, in the case of a header plate, if the packing partition is formed with legs that rise up relative to the header plate, it was difficult to keep the compression ratio within an appropriate range across the entire partition.

[0006] In consideration of the above circumstances, the present invention aims to improve sealing performance by keeping the compression ratio of the packing in the partition portion within an appropriate range throughout, thereby suppressing partial under-compression or over-compression of the packing.

[0007] To achieve the above objective, in the present invention, the sealing structure of the heat exchanger 100 comprises a first core 1, a second core 2 provided in parallel with the first core 1, a header plate 3 and a header tank 4 provided at the ends in the direction of fluid flow through the first core 1 and the second core 2, and a packing 5 provided between the header plate 3 and the header tank 4, wherein the header tank 4 is a box-shaped main body having an opening 42 facing the header plate 3. The heat exchanger 100 has a sealing structure comprising a body portion 41 and a partition wall portion 43 that divides the internal space of the body portion 41 into a first core 1 side and a second core 2 side, and the header plate 3 has a groove portion 32 into which the edge portion 45 of the body portion 41 of the header tank 4 is inserted, and a hole portion 31 into which the tubes contained in the first core 1 and the second core 2 are connected, wherein the groove portion 32 is a plate side wall portion 3 that rises inclined toward the center side of the header plate 3 at a position corresponding to the partition wall portion 43 The header plate 3 has a plate flat portion 35b that is continuous from the plate side wall portion 33b via the plate curved surface 36, the partition portion 43 has a tank side wall portion 46 facing the plate side wall portion 33b, a tank flat portion 47 facing the plate flat portion 35b, and a tank curved surface 48 facing the plate curved surface 36, and the packing (5) has a thickness t in its natural state, a constant αmax of 0.45, a constant αn of 0.33, and a constant α of 0.21. Using min, Lp which is the length of the plate flat portion (35b), Lh (>Lp) which is the length of the tank flat portion (47), x calculated as Lh - Lp, φ which is the inclination angle of the plate side wall portion (33b) and the tank side wall portion (46), θ calculated as Arctan[x / {t・(1-αn)}], Rp which is the radius of curvature of the plate curved surface (36), and Rh which is the radius of curvature of the tank curved surface (48), the inequality t・(1-αmax) ≤ [{t・(1-αn)} ２ +x ２ ] 1 / 2 It is characterized by satisfying the inequalities cos(φ-θn)≦t・(1-αmin) and t・(1-αmax)≦Rh-Rp≦t・(1-αmin).

[0008] According to the present invention, the compression ratio of the packing in the partition portion can be kept within an appropriate range throughout, thereby suppressing partial under-compression or over-compression of the packing and improving sealing performance.

[0009] This is an exploded view showing a heat exchanger according to one embodiment of the present invention. This is a plan view showing a header plate according to one embodiment of the present invention. This is an enlarged view showing area A in Figure 2. This is a cross-sectional view showing the section I-I in Figure 3. This is a cross-sectional view showing the section II-II in Figure 3. This is a cross-sectional view showing the section III-III in Figure 3. This is a plan view showing a header tank according to one embodiment of the present invention. This is a front view showing a header tank according to one embodiment of the present invention. This is a bottom view showing a header tank according to one embodiment of the present invention. This is a cross-sectional view showing the section IV-IV in Figure 9. This is a cross-sectional view showing the section V-V in Figure 9. This is a plan view showing a packing according to one embodiment of the present invention. This is an enlarged view showing area B in Figure 12. This is a cross-sectional view showing the section VI-VI in Figure 13. This is a cross-sectional view showing the section VII-VII in Figure 13. This is a cross-sectional view showing the section VIII-VIII in Figure 13. This is a cross-sectional view showing the section IX-IX in Figure 13. This is a cross-sectional view showing the packing and header tank assembled on the header plate according to one embodiment of the present invention. This is a cross-sectional view showing the packing and header tank assembled on the header plate according to one embodiment of the present invention. This is a cross-sectional view showing a sealing structure in which a packing is provided between a header plate and a header tank in a heat exchanger according to one embodiment of the present invention.

[0010] Hereinafter, with reference to the drawings, a heat exchanger 100 having a sealing structure between a header plate 3 and a header tank 4 according to one embodiment of the present invention will be described.

[0011] Figure 1 is an exploded view of the heat exchanger 100. In each figure, U, Lo, L, R, Fr, and Rr indicate top, bottom, left, right, front, and back, respectively.

[0012] In this embodiment, an example of applying the present invention to a vertical-flow type heat exchanger 100 in which the fluid flow direction is vertical is shown, but the present invention may also be applied to a horizontal-flow type heat exchanger 100 in which the fluid flow direction is front-to-back or left-to-right. The heat exchanger 100 has a core divided into a plurality of core sections, and comprises a first core 1 and a second core 2 as a plurality of core sections provided in parallel, and further comprises a header plate 3, a header tank 4 and a packing 5. The header plate 3, header tank 4 and packing 5 are provided at both the upper and lower ends of the heat exchanger 100, but in this embodiment, the upper configuration will be described.

[0013] The first core 1 and the second core 2 each comprise a plurality of tubes whose longitudinal direction is vertical, and fins provided between the tubes (not shown). The plurality of tubes have a flattened cross-sectional shape and are provided at equal intervals in the left-right direction, with the front-to-back direction being the longitudinal direction of the cross-section. The fluid flows through the tubes from top to bottom. The fluid is, for example, a coolant. The header plate 3 is provided at the upper ends of the first core 1 and the second core 2. The header tank 4 is provided above the header plate 3. The packing 5 is provided between the header plate 3 and the header tank 4. The fluid according to this embodiment includes a heat transfer medium for cooling or heating, and may be a liquid or a gas.

[0014] Figure 2 is a plan view showing the header plate 3. Figure 3 is an enlarged view showing region A in Figure 2. Figure 4 is a cross-sectional view showing the section I-I in Figure 3. Figure 5 is a cross-sectional view showing the section II-II in Figure 3. Figure 6 is a cross-sectional view showing the section III-III in Figure 3.

[0015] The header plate 3 is formed in the shape of a rectangular plate with its longitudinal direction running horizontally. The header plate 3 has the same number of holes 31 as there are tubes, and grooves 32. The holes 31 are flat, elongated holes similar to those of the tubes. The edges of the holes 31 protrude upward. One tube is connected to one hole 31. The grooves 32 are provided in an annular shape along the four sides of the header plate 3 and are recessed downwards. The grooves 32 surround the area where the holes 31 are provided.

[0016] Section I-I is a cross-section of the header plate 3 that does not include the hole 31 and does not correspond to the partition wall 43 of the header tank 4, which will be described later. Section II-II is a cross-section of the hole 31 of the header plate 3. Section III-III is a cross-section of the header plate 3 that corresponds to the partition wall 43. In sections I-I and II-II, the plate sidewalls 33a on the central side of the header plate 3 of the front and rear grooves 32 are upright. On the other hand, in section III-III, the plate sidewalls 33b on the central side of the header plate 3 of the front and rear grooves 32 are inclined upward toward the center of the header plate 3 in the front-rear direction.

[0017] For example, the inclination angle φ of the plate sidewall portion 33b (see Figure 20) is between 40 and 50 degrees with respect to a plane normal to the direction of flow. In the header plate 3, the plate plane portion 35b between the front and rear plate sidewall portions 33b in the III-III section is shorter in the front-rear direction than the plate plane portion 35a between the front and rear plate sidewall portions 33a in the I-I section. The plate plane portions 35a and 35b are continuous with the plate sidewall portions 33a and 33b, respectively.

[0018] Figure 7 is a plan view showing the header tank 4. Figure 8 is a front view showing the header tank 4. Figure 9 is a bottom view showing the header tank 4. Figure 10 is a cross-sectional view showing the section IV-IV in Figure 9. Figure 11 is a cross-sectional view showing the section V-V in Figure 9.

[0019] The header tank 4 comprises a main body 41, an opening 42, and a partition wall 43. The main body 41 is box-shaped and has an opening 42 facing the header plate 3. The partition wall 43 divides the internal space of the main body 41 into a first core 1 side and a second core 2 side. The upper surface of the main body 41 is provided with inlets 44 on both the left and right ends for fluid to flow in.

[0020] The partition wall 43 has a tank side wall 46 facing the plate side wall 33b of the header plate 3, and a tank flat surface 47 facing the plate flat surface 35b of the header plate 3 on its lower surface. The tank side wall 46, like the plate side wall 33b, is inclined upward toward the center of the partition wall 43 in the front-rear direction. For example, the inclination angle φ of the tank side wall 46 (see Figure 20) is 40 degrees or more and 50 degrees or less with respect to a plane whose normality is the direction of fluid flow (up and down direction).

[0021] Figure 12 is a plan view showing the packing 5. Figure 13 is an enlarged view showing region B in Figure 12. Figure 14 is a cross-sectional view showing the VI-VI section in Figure 13. Figure 15 is a cross-sectional view showing the VII-VII section in Figure 13. Figure 16 is a cross-sectional view showing the VIII-VIII section in Figure 13. Figure 17 is a cross-sectional view showing the IX-IX section in Figure 13.

[0022] The packing 5 comprises an annular portion 51 and a partition portion 52. The annular portion 51 is an annular sealing member having four sides, similar to the groove portion 32, and is inserted into the groove portion 32, with the edge portion 45 of the opening 42 of the main body portion 41 of the header tank 4 making contact from above. The partition portion 52 has a shape that is elongated in the front-rear direction. The partition portion 52 is positioned in the left-right direction corresponding to the partition wall portion 43, and spans the annular portion 51 in the front-rear direction, with the partition wall portion 43 of the header tank 4 making contact with the partition portion 52 from above. The annular portion 51 and the partition portion 52 are integrally formed.

[0023] The partition section 52 comprises a pair of legs 53 and a beam section 54. The pair of legs 53 are provided at both ends in the front-rear direction, and the beam section 54 is provided between the pair of legs 53. The base ends (lower ends) of the pair of legs 53 are connected to the front and rear portions of the annular section 51 at positions corresponding to the bulkhead section 43 in the left-right direction, and the tips (upper ends) of the pair of legs 53 are connected by the beam section 54. The pair of legs 53 rise inclined upward toward the center of the partition section 52 in the front-rear direction. The inclination angle φ of the pair of legs 53 (see Figure 14) is 40 degrees or more and 50 degrees or less with respect to a plane normal to the direction of fluid flow (up-down direction), similar to the plate side wall section 33b and the tank side wall section 46.

[0024] The girder section 54 has a long shape that is substantially parallel to the front-rear direction. The girder section 54 is provided with projections 55 that protrude in the left-right direction. The projections 55 protrude to the left and right from both the left and right sides of the girder section 54. For example, multiple projections 55 may be provided at intervals in the front-rear direction. In a cross section intersecting the front-rear direction, chamfered edges 56 (C-surfaces) are formed on both the left and right ends of the upper part of the girder section 54. The projections 55 and chamfered edges 56 prevent the girder section 54 from tilting and ensure a sufficient filling rate. Instead of chamfered edges 56, rounded edges (R-processing) may be applied.

[0025] Figure 18 is a cross-sectional view taken along line I-I, corresponding to the position of line I-I in Figure 3, showing the assembly of the packing 5 and header tank 4 onto the header plate 3. The I-I cross-section corresponds to the left and right sides of the partition 52 and represents most of the header plate 3. In the I-I cross-section, the annular portion 51 of the packing 5 is inserted into the groove 32, and with the packing 5 in contact with the edge 45 of the main body 41 of the header tank 4, the outer edge 34 of the header plate 3 is crimped inward, causing the edge 45 to be pressed against the packing 5.

[0026] Figure 19 is a cross-sectional view taken along the line III-III in Figure 3, showing the assembly of the packing 5 and the header tank 4 onto the header plate 3. The III-III section corresponds to the partition portion 52. In the III-III section, as in the I-I section, the annular portion 51 of the packing 5 is inserted into the groove 32, and with the packing 5 in contact with the edge 45 of the main body portion 41 of the header tank 4, the outer edge 34 of the header plate 3 is crimped inward, causing the edge 45 to be pressed against the packing 5. The partition portion 52 of the packing 5 is not inserted into the groove 32 because its legs 53 rise from the annular portion 51. In this case, in the III-III cross section, the plate side wall portion 33b on the central side of the header plate 3 of the groove portion 32 and the leg portion 53 of the partition portion 52 are inclined at the same inclination angle φ, so sufficient surface pressure is ensured on the packing 5 at the leg portion 53.

[0027] Next, the sealing structure of the header plate 3, header tank 4, and packing 5 at the position corresponding to the partition wall 43 will be explained with reference to Figure 20.

[0028] The sealing structure of this embodiment is configured such that the partition portion 52 of the packing 5 is compressed between the header plate 3 and the partition wall portion 43 of the header tank 4 at a predetermined compression ratio α. The partition portion 52 has a uniform natural thickness t throughout the pair of leg portions 53 and the girder portion 54. Specifically, the girder portion 54 has a natural thickness t in the vertical direction, and the pair of leg portions 53 have a natural thickness t in the direction perpendicular to the inclined surface.

[0029] When the partition section 52 is compressed at a compression ratio α, the header plate 3 and header tank 4 are assembled such that the distance between the tank flat surface 47 of the partition wall section 43 and the plate flat surface 35b of the header plate 3 is t・(1-α) relative to the natural thickness t of the girder section 54. In other words, the girder section 54 is compressed to a thickness of t・(1-α) during compression.

[0030] The configuration of the header plate 3 and header tank 4 for compressing the partition 52 at a compression ratio α will now be described. Specifically, the header plate 3 and header tank 4 are configured such that the length Lh in the front-rear direction of the tank's flat surface 47 is longer than the length Lp in the front-rear direction of the plate's flat surface 35b. The front and rear ends of the tank's flat surface 47 are each longer by a difference of x than the front and rear ends of the plate's flat surface 35b.

[0031] With the header plate 3 and header tank 4 assembled (with the packing 5 compressed), the first line segment 60, which passes through the front (or rear) end of the plate's flat surface 35b and is perpendicular to the plane, is the distance t・(1-α) between the tank's flat surface 47 and the plate's flat surface 35b. The angle θ between the first line segment 60 and the second line segment 61, which passes through the front (or rear) end of the plate's flat surface 35b and the front (or rear) end of the tank's flat surface 47, has the relationship tanθ = x / {t・(1-α)}, i.e., θ = Arctan[x / {t・(1-α)}], where α is the compressibility factor. The length of the second line segment 61 is [{t・(1-α)}] in relation to the first line segment 60. ２ +x ２ ] 1 / 2 This is shown.

[0032] Also, a third line segment 62 passing through the front end (or the rear end) of the plate flat portion 35b and perpendicular to the inclined surface of the plate side wall portion 33b forms an inclination angle φ with respect to the first line segment 60 and an angle φ - θ with respect to the second line segment 61. Therefore, from the relationship with the second line segment 61, the length of the third line segment 62 is [{{t·(1 - α)}} ２ + x ２ 1 / 2 ·cos(φ - θ).

[0033] The third line segment 62 indicates the distance between the plate side wall portion 33b and the tank side wall portion 46 in the direction perpendicular to the inclined surface of the plate side wall portion 33b. Here, between the plate side wall portion 33b and the tank side wall portion 46, for the leg portion 53 of the packing 5 to be compressed to the compressed thickness t·(1 - α) similar to the桁部 54 with respect to the natural thickness t, the length of the third line segment 62 [{{t·(1 - α)}} ２ + x ２ 1 / 2 ·cos(φ - θ) and the compressed thickness t·(1 - α) preferably satisfy the following formula (1). t·(1 - α) = [{{t·(1 - α)}} ２ + x ２ 1 / 2 ·cos(φ - θ) ··· (1)

[0034] Therefore, by calculating the difference x that satisfies the formula (1) and setting the length Lh of the tank flat portion 47 and the length Lp of the plate flat portion 35b based on the difference x, and constructing and assembling the header plate 3 and the header tank 4, the partition portion 52 of the packing 5 is compressed with an overall uniform compression ratio α across the pair of leg portions 53 and the桁部 54.

[0035] ​​​Further, in particular in the present embodiment, when the digit portion 54 is compressed at a compression rate αn of a predetermined nominal value, the header plate 3 and the header tank 4 are configured and assembled such that the pair of leg portions 53 are compressed at a compression rate within a predetermined allowable range. In this case, when the lower limit value αmin and the upper limit value αmax of the compression rate are set in advance to predetermined constant values as the allowable range of the compression rate, the allowable range of the thickness at the time of compression of the leg portion 53 is not less than the lower limit value t·(1−αmax) and not more than the upper limit value t·(1−αmin). For example, when the compression rate αn of the nominal value is set to 0.33 for the packing 5, the lower limit value αmin of the compression rate is set to 0.21 and the upper limit value αmax of the compression rate is set to 0.45.

[0036] In order to make the length of the third line segment 62 within the allowable range of the thickness at the time of compression of the leg portion 53 described above, the length Lh of the tank flat portion 47 and the length Lp of the plate flat portion 35b are set so that the difference x satisfies the following mathematical formula (2), and the header plate 3 and the header tank 4 are configured and assembled. Thereby, the partition portion 52 of the packing 5 is compressed at a compression rate within the allowable range as a whole in the pair of leg portions 53 and the digit portion 54. t·(1−αmax)≦[{t·(1−αn)} ２ +x ２ 1 / 2 ·cos(φ−θn)≦t·(1−αmin) ...(2)

[0037] In the present embodiment, due to the seal structure between the header plate 3 and the header tank 4, the length Lp of the plate flat portion 35b and the length Lh of the tank flat portion 47 satisfy the first limitation condition based on the natural state thickness t of the packing 5, the compression rate αn at the digit portion 54, the lower limit value αmin of the compression rate of the packing 5, the upper limit value αmax of the compression rate of the packing 5, and the inclination angles φ of the plate side wall portion 33b and the tank side wall portion 46, and the first limitation condition is defined by the above-described mathematical formula (2).

[0038] As an example, if the natural thickness t of packing 5 is 3.5 mm and the nominal compressibility αn is 0.33, the compressed thickness t・(1-αn) will be 2.345 mm. If the natural thickness t of packing 5 is 3.5 mm and the lower limit of compressibility αmin is 0.21, the compressed thickness t・(1-αmin) will be 2.765 mm. If the natural thickness t of packing 5 is 3.5 mm and the upper limit of compressibility αmax is 0.45, the compressed thickness t・(1-αmax) will be 1.925 mm.

[0039] The inclination angle φ of the leg portion 53 of the packing 5 is set to be the same as the inclination angle φ of the tank side wall portion 46 and the plate side wall portion 33b. In one embodiment, the inclination angle φ of the tank side wall portion 46 and the plate side wall portion 33b is set to 45 degrees (0.79 rad). When the header plate 3 and the header tank 4 are assembled (when the packing 5 is compressed), as described above, the angle θ between the first line segment 60 and the second line segment 61 depends on the difference x between the length Lh of the tank planar portion 47 and the length Lp of the plate planar portion 35b. In the case of a nominal compressibility αn, θn = Arctan[x / {t・(1-αn)}], and in one embodiment, as described above, when the compressed thickness t・(1-αn) is 2.345 mm, θn = Arctan[x / 2.345].

[0040] Applying the values ​​from these examples to formula (2), we get 1.925 ≤ [{2.345} ２ +x ２ ] 1 / 2 - cos(45 - Arctan[x / 2.345]) ≤ 2.765. Calculating the difference x to satisfy this equation (2), for example, we obtain x = 1.45 mm. Furthermore, setting the length Lh of the tank's flat section 47 and the length Lp of the plate's flat section 35b to satisfy this difference x = 1.45 mm, for example, we obtain Lh = 34.4 mm and Lp = 31.5 mm.

[0041] In other words, as one embodiment, the header plate 3 and header tank 4 are configured such that, with respect to a packing 5 having a natural thickness t = 3.5 mm, the plate flat portion 35b has a length Lp = 31.5 mm, the tank flat portion 47 has a length Lh = 34.4 mm, and the tank side wall portion 46 and the plate side wall portion 33b are inclined at an inclination angle φ = 45 degrees. Furthermore, they are assembled such that the gap between the plate flat portion 35b and the tank flat portion 47 is t・(1-αn) = 2.345 mm.

[0042] Furthermore, the header plate 3 may be configured such that the plane of the plate flat portion 35b and the slope of the plate side wall portion 33b are directly continuous, or it is preferable that the plane of the plate flat portion 35b and the slope of the plate side wall portion 33b are continuous via the plate curved surface 36. Similarly, the header tank 4 may be configured such that the plane of the tank flat portion 47 and the slope of the tank side wall portion 46 are directly continuous, or it is preferable that the plane of the tank flat portion 47 and the slope of the tank side wall portion 46 are continuous via the tank curved surface 48. The tank curved surface 48 is provided opposite the plate curved surface 36.

[0043] When the header plate 3 has a corner between the plate flat portion 35b and the plate side wall portion 33b, and the header tank 4 has a corner between the tank flat portion 47 and the tank side wall portion 46, the compression ratio of the partition portion 52 may fall outside the acceptable range at these corners, resulting in an unsuitable configuration. In contrast, as described above, by providing the plate curved surface 36 and the tank curved surface 48, the compression ratio of the partition portion 52 can be kept within the acceptable range.

[0044] In this case, the distance between the plate surface 36 and the tank surface 48 (compression thickness) is expressed as Rh-Rp, based on the radius of curvature Rp of the plate surface 36 and the radius of curvature Rh of the tank surface 48. Between the plate surface 36 and the tank surface 48, the allowable range of the compression thickness of the partition 52 is greater than or equal to the lower limit of thickness t・(1-αmax) and less than or equal to the upper limit of thickness t・(1-αmin). Therefore, the radius of curvature Rp of the plate surface 36 and the radius of curvature Rh of the tank surface 48 are set based on the following formula (3) so that the distance between the plate surface 36 and the tank surface 48 is within the allowable range of the compression thickness of the partition 52 as described above, and the header plate 3 and header tank 4 are constructed and assembled. As a result, the partition 52 is compressed at a compression ratio within the allowable range overall, regardless of the corners between the pair of legs 53 and the beam 54. t・(1-αmax)≦Rh-Rp≦t・(1-αmin)...(3)

[0045] As one embodiment, as described above, for a packing 5 with a natural thickness t = 3.5 mm, when the lower limit of the compressibility ratio αmin is 0.21, the compressed thickness t・(1-αmin) is 2.765 mm, and when the upper limit of the compressibility ratio αmax is 0.45, the compressed thickness t・(1-αmax) is 1.925 mm. Applying the values ​​of this embodiment to formula (3), we get 1.925 ≤ Rh - Rp ≤ 2.765. The radius of curvature Rp of the plate surface 36 and the radius of curvature Rh of the tank surface 48 are calculated to satisfy this formula (3), and the plate surface 36 and the tank surface 48 are constructed based on the radii of curvature Rp and Rh.

[0046] In this embodiment, for the sealing structure between the header plate 3 and the header tank 4, the radius of curvature Rp of the plate surface 36 and the radius of curvature Rh of the tank surface 48 are set to satisfy a second limiting condition based on the natural thickness t of the packing 5, the lower limit of the compressibility of the packing 5 αmin, and the upper limit of the compressibility of the packing 5 αmax, and the second limiting condition is defined by the above-described formula (3).

[0047] Furthermore, in this embodiment, the length Lh of the tank flat portion 47 and the length Lp of the plate flat portion 35b, as well as the radius of curvature Rp of the plate curved surface 36 and the radius of curvature Rh of the tank curved surface 48 are set to simultaneously satisfy the first limiting condition based on formula (2) and the second limiting condition based on formula (3), thereby configuring the header plate 3 and the header tank 4.

[0048] The heat exchanger 100 according to the embodiment described above comprises a first core 1, a second core 2 provided in parallel with the first core 1, a header plate 3 and a header tank 4 provided at the ends in the direction of fluid flow for the fluid flowing through the first core 1 and the second core 2, and a packing 5 provided between the header plate 3 and the header tank 4. In this embodiment, the header tank 4 comprises a box-shaped main body portion 41 having an opening 42 facing the header plate 3, and a partition wall portion 43 that divides the internal space of the main body portion 41 into a first core 1 side and a second core 2 side. The header plate 3 comprises a groove portion 32 into which the edge portion 45 of the main body portion 41 of the header tank 4 is inserted, and a hole portion 31 into which the tubes contained in the first core 1 and the second core 2 are connected. In the sealing structure of the heat exchanger 100 according to this embodiment, the groove portion 32 has a plate side wall portion 33b that rises inclined toward the center of the header plate 3 at a position corresponding to the partition wall portion 43, the header plate 3 has a plate flat portion 35b that is continuous from the plate side wall portion 33b via a plate curved surface 36, and the partition wall portion 43 has a tank side wall portion 46 facing the plate side wall portion 33b, a tank flat portion 47 facing the plate flat portion 35b, and a tank curved surface 48 facing the plate curved surface 36. Here, when the nominal compressibility αn of the packing 5 is set to 0.33, the lower limit of the compressibility αmin of the packing 5 is set to 0.21, and the upper limit of the compressibility αmax of the packing 5 is set to 0.45, the length Lh of the tank flat section 47 is set to be longer by a predetermined difference x at both ends than the length Lp of the plate flat section 35b, and the length Lp of the plate flat section 35b and the length Lh of the tank flat section 47 are set to be the thickness t of the packing 5 in its natural state and the length of the packing 5 (girder section The first limiting condition is set to satisfy the nominal compressibility αn of 54), the lower limit of the compressibility of packing 5 αmin, the upper limit of the compressibility of packing 5 αmax, and the inclination angle φ of the plate side wall portion 33b and the tank side wall portion 46, and the radius of curvature Rp of the plate curved surface 36 and the radius of curvature Rh of the tank curved surface 48 is set to satisfy the second limiting condition based on the natural thickness t of packing 5, the lower limit of the compressibility of packing 5 αmin, and the upper limit of the compressibility of packing 5 αmax.The first limiting condition is based on the fact that the angle θ between the first line segment 60 passing through the end of the plate planar portion 35b and perpendicular to the plane, and the second line segment 61 passing through the end of the plate planar portion 35b and the end of the tank planar portion 47, is tanθ = x / {t * (1 - α)} when the compressibility ratio is α, and is given by the formula t * (1 - α max) ≤ [{t * (1 - α n)}. ２ +x ２ ] 1 / 2 The second limiting condition is defined by the formula t・(1-αmax) ≤ Rh-Rp ≤ t・(1-αmin), based on the radius of curvature Rp of the plate surface 36 and the radius of curvature Rh of the tank surface 48.

[0049] According to this embodiment, at the position where the first core 1 and the second core 2 are separated, the header plate 3 has a plate flat portion 35b and a plate side wall portion 33b, and the header tank 4 has a tank flat portion 47 and a tank side wall portion 46, so that the header plate 3 and the header tank 4 are formed in a trapezoidal shape when viewed from the parallel direction of the first core 1 and the second core 2. In this case, by satisfying the first and second limiting conditions described above, the compression ratio of the partition portion 52 of the packing 5 provided between the header plate 3 and the header tank 4 can be kept within an appropriate range throughout, thereby suppressing partial under-compression or over-compression of the packing 5 and improving sealing performance.

[0050] In the above embodiment, a composite heat exchanger 100 comprising a first core 1 and a second core 2 was described as an example, but the present invention is not limited to this example, and in other examples, it may be applied to a U-turn type heat exchanger in which fluid flows into the core from one compartment of a partitioned header tank and flows out from the other.

[0051] The above-described embodiments of the present invention represent one aspect of the header tank of a heat exchanger according to the present invention, and the technical scope of the present invention is not limited to the above-described embodiments. The present invention may be modified, substituted, or transformed in various ways without departing from the spirit of the technical idea, and the claims include all embodiments that may fall within the scope of the technical idea.

[0052] 1. First core 2. Second core 3. Header plate 4. Header tank 5. Packing 31. Hole 32. Groove 33a. Plate side wall 33b. Plate side wall 34. Outer edge 35a. Plate flat surface 35b. Plate flat surface 36. Plate curved surface 41. Main body 42. Opening 43. Partition 44. Inlet 45. Edge 46. Tank side wall 47. Tank flat surface 48. Tank curved surface 51. Annular section 52. Partition 53. Leg section 54. Beam section 55. Projection 56. Chamfer 100. Heat exchanger

Claims

1. A heat exchanger (100) comprising: a first core (1); a second core (2) provided in parallel with the first core (1); a header plate (3) and a header tank (4) provided at the ends in the direction of fluid flow for the fluid flowing through the first core (1) and the second core (2); and a packing (5) provided between the header plate (3) and the header tank (4), wherein the header tank (4) comprises: a box-shaped main body (41) having an opening (42) facing the header plate (3); a partition wall (43) dividing the internal space of the main body (41) into the first core (1) side and the second core (2) side; and the header plate (3) comprises: a groove (32) into which the edge (45) of the main body (41) of the header tank (4) is inserted. A seal structure for a heat exchanger (100), comprising: a hole (31) through which tubes contained in the first core (1) and the second core (2) are connected, wherein the groove (32) has a plate side wall portion (33b) that rises inclined toward the center of the header plate (3) at a position corresponding to the partition wall portion (43), the header plate (3) has a plate flat portion (35b) that is continuous from the plate side wall portion (33b) via a plate curved surface (36), the partition wall portion (43) has a tank side wall portion (46) facing the plate side wall portion (33b), a tank flat portion (47) facing the plate flat portion (35b), and a tank curved surface (48) facing the plate curved surface (36), the packing (5) having a natural thickness t, αmax being a constant of 0.45, and αn being a constant of 0.

33. Using the constant αmin of 0.21, the length Lp of the plate planar portion (35b), the length Lh (>Lp) of the tank planar portion (47), x calculated as Lh - Lp, the inclination angle φ of the plate sidewall portion (33b) and the tank sidewall portion (46), θ calculated as Arctan[x / {t・(1-αn)}], the radius of curvature of the plate curved surface (36) Rp, and the radius of curvature of the tank curved surface (48) Rh, the inequality t・(1-αmax) ≤ [{t・(1-αn)} ２ +x ２ ] 1 / 2 A sealing structure for a heat exchanger (100) characterized by satisfying the inequalities cos(φ-θn)≦t・(1-αmin) and t・(1-αmax)≦Rh-Rp≦t・(1-αmin).

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