JP2007278571A - Heat transfer member and heat exchanger using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat transfer member capable of improving productivity, and a heat exchanger using the same. <P>SOLUTION: This heat transfer member composed of a thin sheet member, and exposed in the fluid to give and receive heat with the fluid, is provided with a flat plate portion 2a having a louver 20 composed of a cut and risen portion 2c cut and risen from the thin sheet member, and a strip piece 2d continuously connected to a base portion of the cut and risen portion 2c, the cut and risen portions 2c are respectively disposed at both end portions in the fluid flowing direction of the strip piece 2d, and two cut and risen portions 2c disposed at both end portions of the strip piece 2d are cut and risen in the same direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat transfer member and a heat exchanger that improve performance by turbulent air flow, and is suitable for, for example, a vehicle.

  As this type of heat exchanger, a heat exchanger capable of improving the heat exchange performance with a simple fin shape is known (see Patent Document 1).

This heat exchanger is provided with a cut-and-raised portion obtained by cutting and raising a part of the flat plate portion at a right angle on the flat plate portion of the fin, and an L-shape is formed by the cut-and-raised portion and a strip piece connected to the cut and raised portion of the flat plate portion. A cross-sectional shape is formed. Then, the heat exchange efficiency is increased by increasing the heat transfer coefficient between the air and the fin by the turbulent flow effect by the cut and raised portion.
JP 2005-121348 A

  However, in the configuration described in Patent Document 1, since all the cut-and-raised parts are formed by raising only one end side of the belt-like piece, the belt-like piece is formed when the cut-and-raised part is formed. Only a moment in a certain direction, that is, a direction in which the cut-and-raised portion is cut is applied, and twisting occurs at the boundary between the strip-shaped piece and the cut-and-raised portion.

  Furthermore, when a plurality of heat exchanging portions composed of strip-shaped pieces and cut-and-raised portions are arranged on the plate portion, there is a problem that the entire plate portion is twisted. As a result, undesired deformation appears in the heat transfer member that provides the heat exchange part, and it has been difficult to achieve a desired shape with high accuracy. In particular, when trying to form a strip-shaped piece or cut-and-raised portion having a fine size, it has been difficult to stably provide a desired shape.

  In view of the above problems, an object of the present invention is to provide a heat transfer member that can stably obtain a desired shape.

  Another object is to provide a heat transfer member capable of improving productivity and a heat exchanger using the heat transfer member.

  In order to achieve the above object, the present invention is a heat transfer member that is formed of a thin plate member and that is placed in a fluid and transfers heat to and from the fluid, the strip (2d), and the strip (2d) is provided at both ends in the fluid flow direction, and has a cut-and-raised portion (2c) that is cut and raised in the same direction.

  Thereby, when the cut-and-raised portion (2c) is cut and raised, moments in directions that cancel each other act on the strip-like piece (2d). Therefore, when the cut-and-raised portion (2c) is formed, it is possible to prevent the joining portion (the root portion of the cut-and-raised portion (2c)) between the strip (2d) and the cut-and-raised portion (2c) from being twisted in advance. The processing accuracy of the heat exchange part (20) can be improved. As a result, a desired shape can be obtained stably. Furthermore, productivity can be improved.

  In addition, a plurality of heat exchanging portions (20) having a strip (2d) and the cut and raised portions (2c) provided on both sides thereof can be provided.

  In the present invention, in the plurality of heat exchanging parts (20), the cut and raised height (H), which is the height from the plate surface of the strip (2d) at the tip of the cut and raised part (2c), is approximately. The second feature is that they have the same dimensions.

  Thereby, in all the heat exchange parts (20), the magnitude of the moment applied when the upstream cut-and-raised part (21c) is cut up and the magnitude of the moment applied when the downstream cut-and-raised part (22c) is cut up are reduced. Can be the same. Therefore, when the cut-and-raised part (2c) is formed, it is possible to more reliably prevent the joint portion (the root part of the cut-and-raised part (2c)) between the strip-like piece (2d) and the cut-and-raised part (2c) from being twisted. Therefore, the processing accuracy of the heat exchange part (20) can be further improved. As a result, a desired shape can be obtained more stably. Further, productivity can be further improved.

In the present invention, a plurality of heat exchanging portions (20) each having a strip (2d) and the cut and raised portions (2c) provided on both sides thereof are arranged along the fluid flow direction. The cut-and-raised height (H ₁ ) of the cut-and-raised part (21c) on the upstream side of the fluid flow is the cut-and-raised part on the downstream side of the fluid flow only in the heat exchange part (20) located on the upstream side of the fluid flow. The third feature is that it is higher than the cut and raised height (H ₂ ) of (22c).

  As a result, only the plurality of heat exchanging portions (20) located on the upstream side of the air flow has a cut-and-raised portion (2c) whose cut-and-raised height (H) is higher than that of the other cut-and-raised portions (2c). As a result, the heat transfer rate is increased by disturbing the flow on the upstream side of the air flow, and the flow loss is excessively disturbed on the downstream side of the air flow, thereby preventing an increase in pressure loss (ventilation resistance).

  A plurality of heat exchanging portions (20) having a strip (2d) and cut and raised portions (2c) provided on both sides thereof are arranged along the fluid flow direction, and the fluid flow upstream The heat exchange part (20) located on the side has a cut-and-raised part (21c) having a cut-and-raised height higher than that of the heat exchange part (20) on the downstream side of the fluid flow.

  Thereby, it is possible to prevent heat flow rate from being increased by disturbing the flow on the upstream side of the air flow, and to prevent pressure flow (ventilation resistance) from increasing due to excessive flow disturbance on the downstream side of the air flow.

  Further, the cut and raised portion (2c) can be cut and raised at a right angle to the plate surface of the strip (2d).

  Moreover, it is good also considering the cut-and-raised angle of the cut-and-raised part (2c) as the range of 40 to 120 degree | times.

  Moreover, in this invention, it is further provided with a plate part (2a), and the plate part (2a) has a plurality of heat exchange parts each having a strip (2d) and cut-and-raised parts (2c) provided on both sides thereof. (20) is provided, and the plurality of heat exchange sections (20) are arranged linearly and symmetrically about a predetermined reference position on the plate surface of the strip (2d). Is the fifth feature.

  Thereby, the bending force of the direction which mutually cancels at the time of a shaping | molding process acts on a thin plate-shaped heat-transfer member material (11) continuously. Therefore, when the cut-and-raised portion (2c) is formed, the heat transfer member material (11) can be prevented from being deformed so as to gather in one direction, so that the strip-shaped piece (2d) and the cut-and-raised portion can be prevented. The variation in (2c) can be reduced. As a result, productivity can be improved.

  In the present invention, the ratio (H / L) of the cut and raised height (H) to the dimension (L) of the portion parallel to the fluid flow direction in the heat exchange section (20) is 0.9 or more and 1. The sixth feature is that the range is 25 or less.

  Thereby, as shown in FIG. 11 and FIG. 12 described later, it is possible to improve the productivity while improving the heat exchange performance.

  The ratio (H / L) of the cut and raised height (H) to the dimension (L) of the portion parallel to the fluid flow direction in the heat exchange section (20) is in the range of 0.95 to 1.2. Then, productivity can be improved while further improving the heat exchange performance.

  And the ratio (H / L) of the cut and raised height (H) to the dimension (L) of the portion parallel to the fluid flow direction in the heat exchange section (20) is in the range of 1.0 to 1.15. Then, productivity can be improved while further improving the heat exchange performance.

  In the present invention, the cut-and-raised height (H) of the cut-and-raised portion (2c) is in the range of 0.02 mm or more and 0.4 mm or less, and the pitch between adjacent heat exchange portions (20) in the fluid flow direction. The seventh feature is that the dimension (P) is in the range of 0.04 mm or more and 0.75 mm or less.

  Thereby, as shown in FIG. 7 and FIG. 8 described later, it is possible to improve the productivity while improving the heat exchange performance.

  The cut and raised height (H) of the cut and raised portion (2c) is in the range of 0.1 mm to 0.35 mm, and the pitch dimension (P) between the heat exchange portions (20) adjacent in the fluid flow direction is set. When the thickness is in the range of 0.2 mm to 0.7 mm, the productivity can be improved while further improving the heat exchange performance.

  The cut and raised height (H) of the cut and raised portion (2c) is in the range of 0.2 mm to 0.3 mm, and the pitch dimension (P) between the heat exchange portions (20) adjacent in the fluid flow direction is set. When the thickness is in the range of 0.4 mm to 0.6 mm, productivity can be improved while further improving the heat exchange performance.

  Moreover, in a heat exchanger provided with the tube (1) through which a heat medium flows, and the fin (2) which is provided in the outer surface of the tube (1) and increases the heat exchange area with the fluid which flows around the tube (1) The fin (2) can be the heat transfer member according to any one of claims 1 to 13.

  Further, the thickness of the fin (2) can be specifically set in a range of 0.01 mm or more and 0.1 mm or less.

  Further, the fin (2) can be specifically constituted by a corrugated fin formed in a wave shape.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the heat exchanger according to the present invention is applied to a radiator of a vehicle air conditioner, and FIG. 1 is a front view of the heat exchanger according to the first embodiment, that is, the radiator.

  The radiator is a high-pressure side heat exchanger of a vapor compression refrigerator that dissipates heat of the refrigerant discharged from the compressor. The radiator is also called a refrigerant condenser. In a refrigeration cycle using carbon dioxide or the like as a refrigerant, when the discharge pressure is less than the critical pressure of the refrigerant, the heat absorbed in the evaporator is radiated while the refrigerant is condensed in the radiator. On the other hand, when the discharge pressure is equal to or higher than the critical pressure of the refrigerant, the refrigerant is not condensed in the radiator, and the temperature is lowered while radiating the heat absorbed by the evaporator.

  Further, as shown in FIG. 1, the radiator is joined to a plurality of tubes 1 through which the refrigerant flows and the outer surface of the tubes 1 to increase the heat transfer area with the air and promote heat exchange between the refrigerant and the air. The reinforcing member of the core part which consists of the fin 2, the header tank 3 which extends in the direction orthogonal to the longitudinal direction of the tube 1 on both ends in the longitudinal direction of the tube 1 and communicates with each tube 1, and the tube 1 and the fin 2, etc. It consists of a side plate (insert) 4 formed. The radiator has a refrigerant inlet in one header tank 3 and a refrigerant outlet in the other header tank 3. A separator may be provided in the header tank 3 to provide a meandering refrigerant flow, and one header tank may be provided with a refrigerant inlet and outlet. Note that the fin 2 corresponds to the heat transfer member of the present invention.

  In this embodiment, the tube 1, the fin 2, the header tank 3, and the side plate 4 are all made of metal (for example, aluminum alloy), and these members 1 to 4 are joined by brazing.

  FIG. 2 is a perspective view showing the fin 2 of the heat exchanger according to the first embodiment, and FIG. 3 is a partially enlarged perspective view thereof. As shown in FIGS. 2 and 3, the fin 2 is a corrugated fin formed in a wave shape so as to have a plate-like plate portion 2 a and a top portion 2 b that positions and talks adjacent plate portions 2 a for a predetermined distance. The plate part 2a provides a surface that extends along the flow direction of air as a heat exchange fluid. The plate portion 2a can be provided by a flat plate, and is also referred to as a flat plate portion 2a in the following description. The top portion 2b has a flat top plate portion that provides a narrow-width plane to face the outside. Between the top plate portion and the flat plate portion 2a, a substantially right-angled bent portion is provided. The top plate portion is joined to the tube 1, and the fin 2 and the tube 1 are joined so that heat can be transferred. The top portion 2b can be viewed as a curved portion that is curved as a whole when the width of the top plate portion is sufficiently narrow and the bent portion is formed with a large radius. Therefore, in the following description, the top portion 2b is also referred to as a curved portion 2b. In the present embodiment, the corrugated corrugated fin 2 is formed by subjecting a thin plate metal material to a roller forming method. The curved portion 2 b of the fin 2 is brazed to the flat portion (flat portion) of the tube 1.

  4 is a sectional view taken along the line IV-IV in FIG. 2, and FIG. 5 is a partially enlarged sectional view thereof. As shown in FIGS. 2 to 5, a plurality of raised portions 2 c are formed on the flat plate portion 2 a of the fin 2 by cutting and raising a part of the flat plate portion 2 a at a right angle. As a result of the plurality of cut-and-raised portions 2c being formed, a plurality of slit-like openings are opened in the flat plate portion 2a. Each cut-and-raised portion 2 c has a height that can be recognized as clearly rising from the flat plate portion 2 a that is the base portion of the fin 2. The height of the cut-and-raised portion 2c is also referred to as the width of the cut-and-raised portion 2c. The plurality of cut and raised portions 2c have the same height. One slit-shaped opening is formed by making an H-shaped cut in the flat plate portion 2a and pushing it open from one side. Therefore, two cut-and-raised portions 2c belonging to the two louvers 20 are provided on both sides of one slit-like opening. Since these two cut-and-raised portions 2c are formed by bending the material of the flat plate portion 2a, the total height of these two cut-and-raised portions 2c is approximately equal to the width of the slit-shaped opening opened between them. equal.

  Each cut-and-raised part 2c is a long and narrow rectangle, and can be called a strip shape. Each cut-and-raised portion 2c is formed so as to extend along the height direction of the fin 2, that is, along the direction intersecting the air flow direction. In the present embodiment, each cut-and-raised portion 2c extends in parallel to the height direction of the fin 2, that is, along a direction intersecting at right angles to the air flow direction. In this embodiment, the cut-and-raised portion 2c extends over almost the entire height in the height direction of the flat plate portion 2a. That is, the cut-and-raised portion 2c is formed from a position close to one bent portion of the flat plate portion 2a to a position close to the other bent portion. As a result, the slit-like opening also extends over the entire height of the flat plate portion 2a. Here, “cutting up at right angles” specifically refers to cutting up a part of the flat plate portion 2a at an angle of 90 ° with respect to the plate surface of the flat plate portion 2a. The cut-and-raised angle may be an angle around 90 °, which is increased or decreased by a small amount from 90 °.

  The air flowing on the surface of the fin 2, that is, the flat plate portion 2 a is collided with the cut and raised portion 2 c to disturb the flow of air flowing on the surface of the flat plate portion 2 a to increase the heat transfer coefficient between the fin 2 and the air. Therefore, the cut-and-raised portion 2c serves as an air flow collision wall.

  Here, among the flat plate portions 2a of the fins 2, a flat plate portion connected to the root portion of the cut and raised portion 2c is referred to as a strip-shaped piece 2d. One cut-and-raised portion 2c is formed at each end of the strip 2d in the air flow direction. That is, the cut-and-raised portions 2 are continuously connected to both ends of the strip-shaped piece 2d in the air flow direction. At this time, the two cut-and-raised portions 2c provided at both ends of the strip 2d are cut and raised in the same direction.

  In the present embodiment, the two cut-and-raised portions 2c extend from both sides of the slip piece 2d toward one side of the slit piece 2d. That is, the direction in which one cut-and-raised portion 2c belonging to one slit piece 2d extends and the direction in which the other cut-and-raised portion 2c extends are the same direction. Such a shape can be formed by bending one of the two raised portions 2c connected to one slit piece 2d in the clockwise direction and the other in the counterclockwise direction.

  For this reason, the cross-sectional shape which can be called a substantially U shape or bracket shape is formed by the strip | belt-shaped piece 2d and the two cut-and-raised part 2c continuously connected to the both ends of the strip | belt-shaped piece 2d. Hereinafter, a portion having a substantially U-shaped cross section including the strip-shaped piece 2d and the two cut-and-raised portions 2c in the fin 2 is referred to as a louver 20. In this embodiment, all the cut-and-raised portions 2c formed on one flat plate portion 2a extend in the same direction.

  In this embodiment, end portions of the plurality of raised portions 2c are arranged in rows on both sides of the flat plate portion 2a. For this reason, the rigidity of the flat plate portion 2a is increased on both sides of the flat plate portion 2a, and the difference in rigidity from the top portion 2b where the cut-and-raised portion 2c is not provided is remarkable. Such a difference in rigidity enables sharp bending at the bending portion.

  The plurality of louvers 20, that is, the plurality of raised portions 2c, are formed so as to extend in parallel to each other. The plurality of louvers 20 are arranged side by side along the air flow direction so as to collide with the air flow one after another, and are arranged symmetrically around a predetermined reference position C on the plate surface of the flat plate portion 2a. ing. Specifically, when the upstream side and the downstream side of the flat plate portion 2a are equally divided at the reference position C in the air flow direction, the number of the upstream cut-and-raised portions 2c and the downstream cut-and-raised portion 2c. And the height from the plate surface of the flat plate portion 2a of all the cut and raised portions 2c (hereinafter referred to as the cut and raised height H) are made equal.

  In the above description, it has been described that the cut-and-raised portions 2c are formed on both sides of one slit piece 2d. The fin 2 has two end flat plate portions and one intermediate flat plate portion, which are sufficiently wider than the slit piece 2d, at the upstream end, the central portion, and the downstream end in the air flow direction. The cut and raised portions 2c extending from these wide flat plate portions have the same shape as the cut and raised portions 2c belonging to the slit pieces 2d. Considering these shapes, it can also be seen that the plurality of cut-and-raised portions 2c employed in this embodiment are provided on both sides of one slit-like opening. In this embodiment, cut-and-raised portions 2c are formed on both sides of all slit-like openings. Therefore, all the slit pieces 2d provided between the two slit-shaped openings are formed with two cut-and-raised portions 2c extending in the same direction regardless of the width.

  Next, the outline of the manufacturing method of the fin 2 is described. FIG. 6 is a schematic diagram of a roller forming apparatus. A thin plate-like fin material 11 taken out from a material roll (uncoiler) 10 is given a tension by a tension device 12 that gives a predetermined tension to the fin material 11.

  The tension device 12 includes a weight tension portion 12a that applies a constant tension to the fin material 11 by gravity, a roller 12b that rotates as the fin material 11 advances, and a spring that applies a predetermined tension to the fin material 11 via the roller 12b. It comprises a roller tension part 12d comprising means 12c.

  The reason why a predetermined tension is applied to the fin material 11 by the tension device 12 is to keep the fin height of the fin bent by the fin forming device 13 described later constant.

  The fin forming device 13 bends the fin material 11 given a predetermined tension by the tension device 12 to form a large number of curved portions 2b (see FIG. 2) to make the fin material 11 corrugated, and the flat plate portion 2a. The cut-and-raised portion 2c is formed at a portion corresponding to the above.

  The fin forming device 13 includes a pair of gear-shaped forming rollers 13a and a cutter (not shown) provided on the tooth surface of the forming roller 13a to form the cut-and-raised portion 2c. When the material 11 passes between the pair of forming rollers 13a, the material 11 is bent along the teeth 13b of the forming roller 13a to be formed into a wave shape, and the cut and raised portion 2c is formed.

  The cutting device 14 cuts the fin material 11 into a predetermined length so that the curved portion 2b has a predetermined number in one fin 2, and the fin material 11 cut into the predetermined length is fed by the feeding device 15. It is sent to the correction device 16 described later.

  The feeding device 15 is composed of a pair of gear-like feeding rollers 15 a having a reference pitch substantially equal to the distance between adjacent curved portions 2 b formed by the fin forming device 13. Here, in the corrugated fin 2 bent into a wave shape, the distance between the adjacent curved portions 2b is generally referred to as a fin pitch Pf. As shown in the fin cross-sectional view of FIG. 4, the fin pitch Pf is twice as large as the distance between the adjacent flat plate portions 2 a.

  When the fin pitch Pf (distance between adjacent curved portions 2b) in the finished state of the fin 2 is reduced, the pressure angle of the forming roller 13a is increased, and when the fin pitch Pf is increased, the pressure angle is decreased. At this time, if the difference between the modules of the forming roller 13a and the feed roller 15a is within 10%, the fins can be formed without changing the feed roller 15a.

  The straightening device 16 is a straightening device that pushes the curved portion 2b from a direction substantially perpendicular to the ridge direction of the curved portion 2b to correct the unevenness of the curved portion 2b. The straightening device 16 sandwiches the fin material 11 therebetween. It is formed of a pair of straightening rollers 16a and 16b that rotate following the progress of the fin material 11. The correction rollers 16 a and 16 b are arranged so that the line connecting the rotation centers of the correction rollers 6 a and 6 b is perpendicular to the traveling direction of the fin material 11.

  The brake device 17 is a brake device having brake surfaces 17a and 17b that are in contact with the plurality of curved portions 2b and generate a frictional force toward the opposite side of the fin material 11 in the traveling direction. 16, the fin material 11 is arranged on the traveling direction side of the fin material 11, and the curved portion 2 b of the fin material 11 is in contact with each other by the feeding force generated by the feeding device 15 and the frictional force generated by the brake surfaces 17 a and 17 b. The material 11 is compressed.

  The brake shoe 17c formed with the brake surface 17a is rotatably supported at one end side, and a spring member 17d constituting a frictional force adjusting mechanism is disposed at the other end side. The frictional force generated on the brake surfaces 17a and 17b is adjusted by adjusting the amount of bending of the spring member 17d. In addition, the plate part 17e which forms the brake shoe 17c and the brake surface 17b is a material excellent in abrasion resistance, for example, die steel.

  Next, the operation of the fin forming apparatus according to the present embodiment will be described in the order of steps performed in the fin forming apparatus.

  The fin material 11 is pulled out from the material roll 10 (drawing step), and a predetermined tension is applied to the drawn fin material 11 in the traveling direction of the fin material 11 (tension generating step). And the curved part 2b and the cut-and-raised part 2c are shape | molded in the fin material 11 with the fin shaping | molding apparatus 13 (fin shaping | molding process), and it cut | disconnects to predetermined length with the cutting device 14 (cutting process).

  Next, the fin material 11 cut to a predetermined length by the feeding device 15 is fed toward the correction device 16 (feeding step), and the curving portion 2b is pressed by the correction device 16 to correct the irregularities (correction step). ) And the fin material 11 is contracted so that the adjacent curved portions 2b are in contact with each other in the brake device 17 (contracting step).

  Then, the fin material 11 that has finished the shrinking process is stretched by its own elastic force to a predetermined fin pitch Pf, and the corrugated fin molding is completed through an inspection process such as dimensional inspection.

  Next, the function and effect of this embodiment will be described.

  In the present embodiment, since the cut-and-raised portion 2c is provided in the same direction on both sides of the strip-shaped piece 2d in the air flow direction, when the cut-and-raised portion 2c is formed, moments in directions that cancel each other are formed. Acts on 2d.

  Accordingly, the boundary portion between the strip 2d and the cut-and-raised portion 2c (the root portion of the cut-and-raised portion 2c) can be prevented from being twisted, so that the processing accuracy of the louver 20 can be improved. As a result, a desired shape can be stably obtained, and the productivity of the fins 2 can be improved.

  In the present embodiment, since the cut-and-raised height H of the cut-and-raised portion 2c is substantially the same in all the louvers 20, when the upstream-side cut-and-raised portion 21c is raised in all the strips 2d. And the magnitude of the moment applied when the downstream cut-and-raised portion 22c is raised are substantially the same.

  Therefore, when the cut-and-raised portion 2c is formed, the boundary between the strip-like piece 2d and the cut-and-raised portion 2c can be more reliably prevented from being twisted, so that the processing accuracy of the strip-like piece 2d and the cut-and-raised portion 2c is further improved. be able to. As a result, the productivity of the fins 2 can be further improved.

  Further, in the present embodiment, since the plurality of louvers 20 are arranged symmetrically around a predetermined reference position C, the bending force in such a direction as to cancel each other during the fin forming process is continuously thin plate-like fins. Acts on the material 11.

  Therefore, when the cut-and-raised portion 2c is formed, the fin material 11 can be prevented from being deformed so as to be gathered in one direction, so that variations in the strip-like piece 2d and the cut-and-raised portion 2c can be suppressed to be small. it can. As a result, the productivity of the fin 2 can be further improved.

  Furthermore, since both sides of the strip 2d in the air flow direction are cut and raised, it is possible to secure the interval between the adjacent louvers 20 without cutting out the fin material 11 when the louvers 20 are formed. For this reason, it becomes possible to ensure the yield of the fin material 11.

  Furthermore, by cutting and raising both sides of the strip-shaped piece 2d in the air flow direction, the interval between the adjacent louvers 20 can be increased while suppressing the height of the cut and raised portion 2c. Therefore, the heat transfer performance can be improved because the turbulent flow promoting effect can be enhanced and the heat transfer rate can be enhanced while preventing an increase in pressure loss (ventilation resistance).

  In addition, according to examination of the present inventors, it is desirable that the thickness of the fin 2 be 0.01 mm to 0.1 mm.

  7 is a numerical simulation result showing the relationship between the pitch dimension P between the louvers 20 and the heat exchange performance, and FIG. 8 is a numerical simulation result showing the relationship between the cut-and-raised height H and the heat exchange performance.

  Here, as shown in FIG. 5, the pitch dimension P between the louvers 20 is a dimension that indicates the distance between adjacent louvers 20 in the air flow direction. It is equal to the dimension of the part parallel to the direction orthogonal to the flow direction. The heat exchange performance is determined based on the product of the heat transfer coefficient and the heat transfer area.

  As is apparent from FIGS. 7 and 8, the cut-and-raised height H (see FIG. 5) is 0.02 mm to 0.4 mm, and the pitch dimension P (see FIG. 5) between the cut-and-raised portions 2c is 0. It can be seen that heat exchange performance is improved when the thickness is 04 mm to 0.75 mm.

  Furthermore, it can be seen that the heat exchange performance is further improved if the cut and raised height H is set to 0.1 mm to 0.35 mm and the pitch dimension P between the cut and raised portions 2c is set to 0.2 mm to 0.7 mm. . Moreover, if the cut and raised height H is 0.2 to 0.3 mm and the pitch dimension P between the cut and raised portions 2c is 0.4 to 0.6 mm, the heat exchange performance can be further improved. Recognize. The cut-and-raised height H is a height dimension including the thickness of the fin 2 as clearly shown in FIG.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  In this embodiment, the plurality of louvers 20 formed on one plate portion 2a include an upstream louver group including a plurality of louvers 20 located on the upstream side of the air flow, and a plurality of louvers located on the downstream side of the air flow. Is divided into two groups of downstream louvers. The shape of the louver 20 belonging to the downstream louver group is symmetrically arranged with respect to the upstream louver group and a predetermined reference position C on the plate surface.

FIG. 9 is a fin cross-sectional view showing the louver 20 belonging to the upstream louver group located on the upstream side of the air flow according to the second embodiment. As shown in FIG. 9, in the present embodiment, only the plurality of louvers 20 located on the upstream side of the air flow cuts and raises the cut and raised portion 2c on the upstream side of the air flow (hereinafter referred to as upstream cut and raised portion 21c). the height H _1, the air flow downstream cut-and-raised portion 2c (hereinafter, referred to as the downstream cut-and-raised parts 22c) is higher than the cut-and-raised height H ₂ of.

  As a result, the plurality of louvers 20 positioned on the upstream side of the air flow have cut and raised portions 2c having a height H higher than that of the other raised portions 2c. It is possible to increase the heat transfer rate by disturbing the flow, and to prevent the flow from being disturbed excessively on the downstream side of the air flow and the pressure loss (ventilation resistance) from increasing.

Even by increasing the height H ₁ cut and raised on the upstream side cut-and-raised portion 21c of the plurality of louvers 20 positioned in the air flow downstream side increases the turbulence effect, since the fin 2 to be heat exchanged running low, Compared with the increase in heat transfer coefficient due to the turbulent flow effect, the amount of decrease in the heat exchange amount due to the increase in pressure loss (ventilation resistance) is greater, and there is a high possibility that the heat exchange efficiency will deteriorate.

In the second embodiment, the plurality of louvers 20 positioned in the air flow upstream side, the cut-and-raised height H ₁ of the upstream cut-and-raised parts 21c, the cut-and-raised height of the downstream cut-and-raised parts 22c H ₂ The louver 20 on the upstream side of the air flow and the louver 20 on the downstream side of the air flow are not in a symmetric relationship in a complete sense. Since both louvers 20 have a substantially U-shaped cross-sectional shape and are in a substantially symmetrical relationship, the arrangement of the cut-and-raised portions 2c according to the second embodiment is also referred to in the present invention. It is arranged symmetrically.

  In the first and second embodiments, the number of louvers 20 on the upstream side of the air flow and the number of louvers 20 on the downstream side of the air flow are set to the same number. Even if the number of louvers 20 is shifted by a small number (for example, one), it is included in the “symmetrical relationship” referred to in the present invention.

  Further, in the present embodiment, since the plurality of louvers 20 are arranged symmetrically around a predetermined reference position C, the bending force in such a direction as to cancel each other during the fin forming process is continuously thin plate-like fins. Acts on the material 11.

  Accordingly, when the cut and raised portion 2c is formed, the fin material 11 can be prevented from being deformed so as to be gathered in one direction, so that variations in the slit piece 2d and the cut and raised portion 2c can be suppressed to be small. it can. As a result, the productivity of the fin 2 can be further improved.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  In this embodiment, the plurality of louvers 20 formed on one plate portion 2a include an upstream louver group including a plurality of louvers 20 located on the upstream side of the air flow, and a plurality of louvers located on the downstream side of the air flow. Is divided into two groups of downstream louvers. The shape of the louver 20 belonging to the downstream louver group is the same as that of the first embodiment.

FIG. 9 is a fin cross-sectional view showing the louvers 20 belonging to the upstream louver group located on the upstream side of the air flow according to the third embodiment. As shown in FIG. 9, in the present embodiment, only the plurality of louvers 20 located on the upstream side of the air flow cuts and raises the cut and raised portion 2c on the upstream side of the air flow (hereinafter referred to as upstream cut and raised portion 21c). the height H _1, the air flow downstream cut-and-raised portion 2c (hereinafter, referred to as the downstream cut-and-raised parts 22c) is higher than the cut-and-raised height H ₂ of.

  In the louver 20 belonging to the downstream louver group, the height of the upstream cut-and-raised portion and the height of the downstream cut-and-raised portion are both H and the same. Therefore, the louver 20 belonging to the upstream louver group has a cut-and-raised part (21c) having a higher cut-and-raised height than the louver 20 belonging to the downstream louver group. In this embodiment, H1> H> H2. The height H and the height H2 can be substantially equal. Further, H1 + H2> 2 × H may be set.

  As a result, the plurality of louvers 20 positioned on the upstream side of the air flow have cut and raised portions 2c having a height H higher than that of the other raised portions 2c. It is possible to increase the heat transfer rate by disturbing the flow, and to prevent the flow from being disturbed excessively on the downstream side of the air flow and the pressure loss (ventilation resistance) from increasing.

Even by increasing the height H ₁ cut and raised on the upstream side cut-and-raised portion 21c of the plurality of louvers 20 positioned in the air flow downstream side increases the turbulence effect, since the fin 2 to be heat exchanged running low, Compared with the increase in heat transfer coefficient due to the turbulent flow effect, the amount of decrease in the heat exchange amount due to the increase in pressure loss (ventilation resistance) is greater, and there is a high possibility that the heat exchange efficiency will deteriorate.

  Further, a cut-and-raised portion higher than the cut-and-raised height of the louver belonging to the downstream louver group may be adopted only for some louvers belonging to the upstream louver group. Furthermore, the cut and raised height may be set so that the average cut and raised height of the upstream louver group is higher than the average cut and raised height of the downstream louver group.

In the third embodiment, the plurality of louvers 20 positioned in the air flow upstream side, the cut-and-raised height H ₁ of the upstream cut-and-raised parts 21c, the cut-and-raised height of the downstream cut-and-raised parts 22c H ₂ The louver 20 on the upstream side of the air flow and the louver 20 on the downstream side of the air flow are not in a symmetric relationship in a complete sense. Since both louvers 20 have a substantially U-shaped cross-sectional shape and are in a substantially symmetrical relationship, the arrangement form of the cut-and-raised portions 2c according to the third embodiment is also referred to in the present invention. It is arranged symmetrically.

  In the first and second embodiments, the number of louvers 20 on the upstream side of the air flow and the number of louvers 20 on the downstream side of the air flow are set to the same number. Even if the number of louvers 20 is shifted by a small number (for example, one), it is included in the “symmetrical relationship” referred to in the present invention.

(Fourth embodiment)
Next, 4th Embodiment of this invention is described based on FIGS. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

Figure 10 is a fin cross-sectional view for explaining a fourth embodiment, the cut-and-raised height of the upstream cut-and-raised parts 21c (hereinafter, referred to as height H ₁ raised upstream cut) over 0.02 mm 0. The range is 4 mm or less. Further, the pitch dimension P between the louvers 20 composed of the cut-and-raised portion 2c and the strip-shaped piece 2d continuously connected to the root portion of the cut-and-raised portion 2c is set to a range of 0.02 mm to 0.75 mm. In the present embodiment, the height H ₂ cutting and raising of the downstream cut-and-raised parts 22c is equal to the height H ₁ raised upstream cut.

Since the cut-and-raised portion 2c is cut and raised from the flat plate portion 2a, the dimension L (see FIG. 7) of the portion (band-like piece 2d) parallel to the air flow direction in the heat exchanging portion 2e is the upstream cut-and-raised height. It changes according to the pitch P between the height H ₁ and the louver 20.

Therefore, the ratio (= H) of the upstream cut-and-raised height H ₁ (that is, the dimension H ₁ of the part of the louver 20 parallel to the direction perpendicular to the air flow direction) to the dimension L of the part parallel to the air flow direction. ₁ / L) and the heat exchange performance are summarized as shown in FIG.

As is clear from FIG. 11, the ratio of the upstream cut height H ₁ to the dimension L of the portion of the louver 20 parallel to the air flow direction (= H ₁ / L) is 0.9 or more and 1.25. By setting it as the following range, high heat exchange performance can be obtained.

Incidentally, the ratio (= H) of the upstream cut-and-raised height H ₁ (that is, the dimension H ₁ of the part of the louver 20 parallel to the direction perpendicular to the air flow direction) to the dimension L of the part parallel to the air flow direction. ₁ / L) and pressure loss (ventilation resistance) are summarized as shown in FIG.

As apparent from FIG. 12, the ratio (= H ₁ / L) of the upstream cut-and-raised height H ₁ to the dimension L of the portion of the louver 20 parallel to the air flow direction is 1.2 or less. By doing so, pressure loss (ventilation resistance) can be reduced.

Therefore, in consideration of heat exchange performance and pressure loss (ventilation resistance), the ratio of the upstream cut height H ₁ to the dimension L of the portion of the louver 20 parallel to the air flow direction (= H ₁ / L) It is desirable that the range be 0.9 or more and 1.25 or less, more preferably 0.95 or more and 1.2 or less, and still more preferably 1.0 or more and 1.15 or less.

(Fifth embodiment)
In each of the above-described embodiments, the heat flow performance (heat transfer coefficient) is improved by meandering the air flow at the cut-and-raised portion 2c. Therefore, the cut-and-raised angle θ of the cut-and-raised portion 2c is about 90 degrees as described above. It is not limited to the value, and it is sufficient that a part of the flat plate portion 2a is cut and raised at an angle such that the air flow meanders.

  Therefore, in the fifth embodiment, specifically, the cut-and-raised angle θ of the cut-and-raised portion 2c is set in a range of 40 degrees to 140 degrees. Therefore, the cross-sectional shape of the louver 20 is not limited to the U-shaped cross-sectional shape, and may be various cross-sectional shapes as shown in FIGS. 11 and 12, for example. Incidentally, the cut-and-raised angle θ of the cut-and-raised portion 2c refers to an angle that has been cut and raised with reference to the state before the flat-plate portion 2a is cut and raised.

  FIG. 13A shows an example in which both the cut-and-raised angle θ of the upstream cut-and-raised portion 21c and the downstream cut-and-raised portion 22c are about 40 degrees. FIG. 13B is an example in which both the cut-and-raised angle θ of the upstream cut-and-raised portion 21c and the downstream cut-and-raised portion 22c are about 140 degrees.

  FIG. 13C shows an example in which the cut-and-raised angle θ of the upstream cut-and-raised portion 21c is about 90 degrees, and the cut-and-raised angle θ of the downstream-side cut and raised portion 22c is about 40 degrees.

  FIG. 14A shows an example in which the joint between the cut-and-raised portion 2c and the strip-shaped piece 2d and the strip-shaped piece 2d are bent so as to be raised with respect to the flat plate portion 2a. FIG. 14B shows an example in which the cut-and-raised portion 2c is cut and raised so as to form a smooth arc-shaped curved surface from the belt-like piece 2d to the cut-and-raised portion 2c.

  14C shows an example in which the end of the upstream cut-and-raised portion 21c is bent toward the upstream side of the air flow and the end of the downstream cut-and-raised portion 22c is bent toward the downstream side of the air flow. is there.

(Other embodiments)
In each of the above embodiments, the present invention is applied to a radiator of a vehicle air conditioner. However, the application of the present invention is not limited to this, and for example, a heater core for heating of a vehicle air conditioner, a vapor compression type, etc. The present invention can also be applied to heat exchangers such as evaporators and condensers of refrigerators and radiators that cool engine cooling water.

  Further, in each of the above embodiments, the fin 2 is wave-shaped, but the present invention is not limited to this, and may be a plate fin formed in a flat plate shape, a pin fin formed in a needle shape, or the like.

  Moreover, in each said embodiment, although the louver 20, ie, the cut-and-raised part 2c, was formed in 1 row in the air flow direction in the flat plate part 2a, this invention is not limited to this. For example, two or more rows may be used.

  Further, the plurality of cut-and-raised portions 2c may be formed to be inclined at a predetermined angle with respect to the height direction of the fin 2, that is, the direction perpendicular to the air flow direction.

  In the above embodiments, a plurality of louvers 20 are formed in the flat plate portion 2a of the fin 2. However, the present invention is not limited to this, and may be one, for example.

It is a front view of the heat exchanger by a 1st embodiment. It is a perspective view which shows the fin 2 of the heat exchanger by 1st Embodiment. It is a fragmentary perspective view of the fin 2 shown in FIG. It is IV-IV sectional drawing of FIG. It is a principal part expanded sectional view of FIG. It is a schematic diagram of the roller shaping | molding apparatus by 1st Embodiment. It is a numerical simulation result which shows the relationship between the pitch dimension P between the louvers 20, and heat exchange performance. It is a numerical simulation result which shows the relationship between the cutting height H and heat exchange performance. It is fin part sectional drawing which shows the louver 20 located in the airflow upstream by 2nd and 3rd embodiment. It is fin part sectional drawing explaining the definition of the height H cut and raised and the pitch dimension P between the louvers 20. FIG. 4 is a graph summarizing the relationship between the ratio (= H ₁ / L) of the upstream cut and raised height H ₁ to the dimension L of the portion of the louver 20 parallel to the air flow direction and the heat exchange performance. 4 is a graph summarizing the relationship between the ratio (= H ₁ / L) of the upstream cut-and-raised height H ₁ to the dimension L of the portion of the louver 20 parallel to the air flow direction and the pressure loss (ventilation resistance). It is fin part sectional drawing which shows the louver 20 by 5th Embodiment. It is fin part sectional drawing which shows the louver 20 by 5th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Tube, 2 ... Fin (heat transfer member), 2a ... Plate part, 2c ... Cut-and-raised part, 2d ... Strip piece, 20 ... Louver (heat exchange part).

Claims (17)

A heat transfer member that is formed from a thin plate member and is placed in a fluid to transfer heat to and from the fluid,
A strip-shaped piece (2d) and a cut-and-raised portion (2c) provided at both ends of the strip-shaped piece (2d) in the fluid flow direction and cut and raised in the same direction. Heat transfer member. 2. The heat transfer member according to claim 1, comprising a plurality of heat exchange portions (20) having the strip (2 d) and the cut and raised portions (2 c) provided on both sides thereof. . The cut-and-raised height (H), which is the height from the plate surface of the strip-like piece (2d), at the tip of the cut-and-raised portion (2c) is substantially the same size. Heat exchanger. A plurality of heat exchanging portions (20) having the strip (2d) and the cut and raised portions (2c) provided on both sides thereof are arranged along the fluid flow direction, Only in the heat exchange part (20) located on the upstream side, the cut-and-raised height (H ₁ ) of the cut-and-raised part (21c) on the upstream side of the fluid flow is equal to the cut-off part (22c) on the downstream side of the fluid flow. The heat transfer member according to any one of claims 1 to 3, wherein the heat transfer member is higher than a raising height (H ₂ ). A plurality of heat exchanging portions (20) having the strip (2d) and the cut and raised portions (2c) provided on both sides thereof are arranged along the fluid flow direction, The heat exchanging part (20) located on the upstream side has a cut and raised part (21c) having a higher cut and raised height than the heat exchange part (20) on the downstream side of the fluid flow. The heat transfer member according to any one of 1 to 3. The heat transfer member according to any one of claims 1 to 4, wherein the cut and raised portion (2c) is cut and raised at a right angle to the plate surface of the strip (2d). The heat transfer member according to any one of claims 1 to 4, wherein a cut and raised angle of the cut and raised portion (2c) is in a range of 40 degrees to 120 degrees. Furthermore, a plate part (2a) is provided,
The plate portion (2a) is provided with a plurality of heat exchange portions (20) having the strips (2d) and the cut and raised portions (2c) provided on both sides thereof, and the plurality of heat exchange portions. The part (20) is arranged linearly and symmetrically arranged around a predetermined reference position on the plate surface of the strip (2d). The heat-transfer member as described in any one. The ratio (H / L) of the cut and raised height (H) to the dimension (L) of the portion parallel to the fluid flow direction in the heat exchange part (20) is in the range of 0.9 to 1.25. The heat transfer member according to claim 1, wherein the heat transfer member is provided. In the heat exchange part (20), the ratio (H / L) of the cut and raised height (H) to the dimension (L) of the part parallel to the fluid flow direction is in the range of 0.95 to 1.2. The heat transfer member according to claim 1, wherein the heat transfer member is provided. The ratio (H / L) of the cut and raised height (H) to the dimension (L) of the portion parallel to the fluid flow direction in the heat exchange section (20) is in the range of 1.0 or more and 1.15 or less. The heat transfer member according to claim 1, wherein the heat transfer member is provided. The cut and raised height (H) of the cut and raised portion (2c) is in the range of 0.02 mm to 0.4 mm,
The pitch dimension (P) between the heat exchange parts (20) adjacent in the fluid flow direction is in a range of 0.04 mm or more and 0.75 mm or less, according to any one of claims 1 to 10, The heat transfer member described. The cut-and-raised height (H) of the cut-and-raised portion (2c) is in the range of 0.1 mm to 0.35 mm,
The pitch dimension (P) between the heat exchange parts (20) adjacent in the fluid flow direction is in the range of 0.2 mm or more and 0.7 mm or less, according to any one of claims 1 to 10, The heat transfer member described. The cut-and-raised height (H) of the cut-and-raised portion (2c) is in the range of 0.2 mm to 0.3 mm,
The pitch dimension (P) between the heat exchange parts (20) adjacent in the fluid flow direction is in a range of 0.4 mm or more and 0.6 mm or less, according to any one of claims 1 to 10, The heat transfer member described. A heat exchanger comprising a tube (1) through which a heat medium flows and fins (2) provided on an outer surface of the tube (1) to increase a heat exchange area between a fluid flowing around the tube (1). There,
The heat exchanger according to any one of claims 1 to 13, wherein the fin (2) is a heat transfer member according to any one of claims 1 to 13. The heat exchanger according to claim 14, wherein a thickness of the fin (2) is in a range of 0.01 mm to 0.1 mm. The heat exchanger according to claim 14 or 15, characterized in that the fin (2) is a corrugated fin formed in a wave shape.

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