JP4196857B2 - Heat exchanger and heat transfer member - Google Patents

Description

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

In a conventional fin for a heat exchanger, by providing slit pieces that form segments arranged in a staggered manner with respect to the air flow, and bending the air flow upstream side of the slit pieces by about 90 ° to provide a bent portion, The heat transfer rate is improved by suppressing the growth of the temperature boundary layer by disturbing the air flow (see, for example, Patent Document 1).

In other heat exchangers, a large number of pin-like (needle-like) fins are arranged in the air flow to improve the heat exchange performance.
JP-A 63-83591

By the way, in the invention described in Patent Document 1, a slit piece is formed by cutting and raising a part of a thin plate-like fin, and the front end (front edge) side of the cut and raised slit piece is bent by about 90 ° and folded. Since the curved portion is formed, it has the following manufacturing problems.

In other words, in the invention described in Patent Document 1, since all the bent portions are formed by bending the front end side of the slit pieces, the bending force in the same direction continuously acts on the thin plate-like fin material. Therefore, when the bent portion is formed, the fin material is deformed so as to gather in one direction.

Moreover, although it is necessary to provide the slit pieces regularly with a constant pitch dimension, as described above, in the invention described in Patent Document 1, since the fin material tends to gather in one direction,
It is difficult to reduce the variation in pitch dimension between the slit pieces. And when the variation in the pitch dimension between the slit pieces increases, there is a high possibility that the heat transfer rate is lowered and the desired heat exchange capability cannot be obtained.

In addition, in a heat exchanger with a large number of pin-shaped (needle-shaped) fins in the air flow, the weight of the heat exchanger is increased by providing fins, that is, a large number of pins, and a large number of pins are heat-exchanged. Productivity is deteriorated due to the placement on the vessel, and it is difficult to mass-produce.

Also, if a large number of pins are formed by cutting out between pins, a large amount of material that must be discarded when cutting out is generated, so the yield of the material deteriorates. Therefore, it is still difficult to mass-produce.

  An object of this invention is to improve productivity by a simple fin shape in view of the said point.

  Another object of the present invention is to improve the heat exchange performance with a simple fin shape.

The present invention has been devised to achieve the above object. In the invention according to claim 1, the tube (1) through which a fluid flows, and the tube (1) provided on the outer surface of the tube (1) are provided. (1) A heat exchanger comprising fins (2) for increasing the heat exchange area with the air flowing around,
The fin (2) includes a flat plate portion (2a) , a collision wall (2c) formed by cutting a part of the flat plate portion (2a) at a right angle, and the flat plate portion (2a). A slit piece (2d) composed of a portion continuously connected to the base of the collision wall (2c) ,
The cut and raised height (H) of the collision wall (2c) is in the range of 0.02 mm or more and 0.4 mm or less,
A plurality of heat exchange parts (2e) composed of the collision wall (2c) and the slit piece (2d) are provided in the air flow direction,
The pitch dimension (P) between the heat exchange parts (2e) adjacent in the air flow direction is in the range of 0.02 mm or more and 0.75 mm or less,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. Range of
Furthermore, the L-shaped cross-sectional shape is comprised by the said collision wall (2c) and the said slit piece (2d),
The L-shaped cross-sectional shape on the upstream side of the air flow and the L-shaped cross-sectional shape on the downstream side of the air flow are disposed symmetrically with respect to a virtual plane orthogonal to the flat plate portion (2a). It is characterized by that.

As a result, bending forces in directions that cancel each other when the collision wall (2c) is formed continuously act on the thin plate-like fin material. Therefore, when forming the collision wall (2c),
Since it is possible to prevent the fin material from being deformed so as to gather in one direction, the dimensional variation of the collision wall (2c) can be reduced.

As a result, the heat transfer efficiency between the air and the fin (2) is increased by the turbulent flow effect due to the collision wall (2c), and the heat exchange efficiency is enhanced, while the fin (2) is simplified in shape and the fin productivity. Can be improved.
In particular, the height (H) of the collision wall (2c) is set to a range of 0.02 mm to 0.4 mm, and the pitch dimension (P) between the heat exchange parts (2e) adjacent in the air flow direction (P ) Within a range of 0.02 mm to 0.75 mm and the ratio (H / L) within a range of 0.5 to 2.2, which will be described later with reference to FIGS. As shown in FIG. 12, a high range of heat exchange performance can be set effectively.

In the invention according to claim 2, the tube (1) through which the fluid flows and the fin (2) which is provided on the outer surface of the tube (1) and increases the heat exchange area with the air flowing around the tube (1) A heat exchanger comprising:
The fin (2), said flat plate portion and (2a), said plate and (2a) of formed by cutting and raising a portion the collision wall (2c), of said plate (2a) A slit piece (2d) composed of a portion continuously connected to the base of the collision wall (2c) ;
The cut and raised height (H) of the collision wall (2c) is in the range of 0.02 mm or more and 0.4 mm or less,
A plurality of heat exchange parts (2e) composed of the collision wall (2c) and the slit piece (2d) are provided in the air flow direction,
The pitch dimension (P) between the heat exchange parts (2e) adjacent in the air flow direction is in the range of 0.02 mm or more and 0.75 mm or less,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. Range of
A ratio (D / C) of a length dimension (C) perpendicular to the air flow direction of the fin (2) and a length dimension (D) perpendicular to the air flow direction of the collision wall (2c). ) As the cutting length ratio (E),
The cut length ratio (E) is in the range of 0.775 or more and 0.995 or less.

By the way, according to the study by the present inventor, it has been found that the wind speed of the passing air on the collision wall (2c) varies greatly depending on the cut length ratio (E) (see FIGS. 21 to 23 described later). Therefore, in the invention described in claim 2, by setting the cut length ratio (E) in the appropriate range, the wind speed of the passing air on the collision wall (2c) is raised to a predetermined range near the maximum wind speed. (See FIG. 21). As a result, the effect of improving the fin heat transfer performance by the collision wall (2c) can be effectively exhibited.
In the invention according to claim 2, as in the invention according to claim 1, the cut-and-raised height (H) of the collision wall (2c) is set in the range of 0.02 mm to 0.4 mm, and The pitch dimension (P) between the heat exchange portions (2e) adjacent in the air flow direction is in the range of 0.02 mm or more and 0.75 mm or less, and the ratio (H / L) is 0.5 or more. By setting the range to 2.2 or less, a range with high heat exchange performance can be effectively set as shown in FIGS.

  As in the third aspect of the invention, in the heat exchanger according to the second aspect, when the cut length ratio (E) is set in the range of 0.810 to 0.980, the collision wall (2c ) It is possible to further improve the fin heat transfer performance by further increasing the wind speed of the passing air.

According to a fourth aspect of the present invention, in the heat exchanger according to the second or third aspect , the collision wall (2c) is formed by cutting the collision wall (2c) perpendicularly from the flat plate portion (2a ). When, L-shaped cross section is constituted by said slit pieces (2d),
The L-shaped cross-sectional shape on the upstream side of the air flow and the L-shaped cross-sectional shape on the downstream side of the air flow are disposed symmetrically with respect to a virtual plane orthogonal to the flat plate portion (2a). It is characterized by that.

  Thus, more specifically, the collision wall (2c) can be suitably implemented in a form that forms an L-shaped cross-section with the slit piece (2d).

According to a fifth aspect of the present invention, in the heat exchanger according to any one of the first to fourth aspects, a part of the plurality of collision walls (2c) located on the upstream side of the air flow. The collision wall (2c) is cut and raised (H) higher than the other collision walls (2c),
Further, among the plurality of collision walls (2c), the plurality of collision walls (2c) located on the downstream side of the air flow are all cut and raised (H) having the same size. .

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 excessive increase in pressure loss (ventilation resistance) due to excessive flow disturbance on the downstream side of the air flow.

According to a sixth aspect of the present invention, in the heat exchanger according to any one of the first to fifth aspects, among the plurality of collision walls (2c), a plurality of the plurality of collision walls (2c) positioned on the upstream side of the air flow. The raised height (H) of the collision wall (2c) is higher toward the downstream side of the air flow,
Further, among the plurality of collision walls (2c), the cut-and-raised height (H) of the plurality of collision walls (2c) located on the downstream side of the air flow is the plurality of the plurality of collision walls (2c) located on the upstream side of the air flow. It is characterized by being lower than the cut-and-raised height (H) of the collision wall (2c) located at the most downstream portion of the collision wall (2c).

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 excessive increase in pressure loss (ventilation resistance) due to excessive flow disturbance on the downstream side of the air flow.

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

  As in the invention described in claim 8, the fin (2) may specifically be constituted by a plate fin formed in a flat plate shape.

In a ninth aspect of the present invention, in the heat exchanger according to any one of the first to eighth aspects, the fin (2) protrudes upstream of the tube (1) in the air flow direction. A protruding portion (2j) is formed,
The protruding wall (2j) is also formed with the collision wall (2c).

Thereby, the range of the turbulent flow area of the high heat transfer coefficient in the portion in contact with the wall surface of the tube (1) in the fin (2) can be increased (see FIG. 25 (a) described later), and the fin heat transfer performance is effectively improved. I can .
As in the invention according to claim 10, in the heat exchanger according to claim 9, it is preferable that at least two or more collision walls (2c) are formed in the protrusion (2j).

  In invention of Claim 11, in the heat exchanger of Claim 9 or 10, the downstream end part of the air flow direction of the fin (2) is connected to the air flow direction of the tube (1). The arrangement is such that it does not protrude downstream from the downstream end.

  Thereby, the ventilation resistance increase by the protrusion of the downstream edge part of the air flow direction of a fin (2) can be suppressed, and the performance ensuring as the whole heat exchanger can be performed effectively.

The invention according to claim 12 is a heat transfer member that is formed of a thin plate member and is exposed to the fluid to transfer heat to and from the fluid,
A plurality of heat exchanging portions (2e) comprising a cut and raised portion (2c) cut and raised from the thin plate member and a slit piece (2d) continuously connected to the root portion of the cut and raised portion (2c). A flat plate portion (2a) having
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,
Further, the heat exchanging portion adjacent to each other in the flow direction of the fluid (2e) pitch dimension between (P), or 0.02 mm, Ri following ranges der 0.75 mm,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. It is the range of these.

As a result, as shown in FIGS . 8 , 9 and 12, which will be described later, the fin shape can be simplified and the fin productivity can be improved while effectively setting the high heat exchange performance range. .

In invention of Claim 13, in the heat-transfer member of Claim 12, the cut-and-raised height (H) of the cut-and-raised part (2c) is in the range of 0.06 mm or more and 0.36 mm or less. ,
Furthermore , the pitch dimension (P) between the heat exchange parts (2e) is in the range of 0.08 mm or more and 0.68 mm or less.

Thereby, as shown in FIG. 8 and FIG. 9 to be described later, an even higher range of the heat exchange performance can be set effectively .

  As in the invention described in claim 14, in the heat transfer member according to claim 12 or 13, the cut-raised angle (θ) of the cut-raised portion (2c) is specifically 40 degrees or more, 140 It may be in the range below the degree.

  As in the invention according to claim 15, in the heat transfer member according to any one of claims 12 to 14, the cut and raised portion (2c) is specifically cut from the thin plate member in a curved shape. The shape may be raised.

As in the invention according to claim 16 , in the heat transfer member according to any one of claims 12 to 15 , the heat exchange member (2e) is located upstream of the fluid flow. What is necessary is just to arrange | position the cross-sectional shape of the said heat exchange part (2e), and the cross-sectional shape of the said heat exchange part (2e) located in the said fluid flow downstream side mutually symmetrically.

As in the invention described in claim 17 , in the heat transfer member according to any one of claims 12 to 16 , the heat exchanging portion (2e) is a flow of the fluid in the flat plate portion (2a). What is necessary is just to form in a line in the direction.

As in the invention described in claim 18, in the heat transfer member according to claim 17, the number of the heat exchanging portion (2e) is parallel portion and the fluid flow direction of said plate (2a) The number of dimensions may be larger than the value obtained by dividing the value (B) when the unit of length is millimeters by 0.75.

According to a nineteenth aspect of the present invention, in the heat transfer member according to any one of the twelfth to eighteenth aspects, at least one of the cuts is provided in the heat exchange section (2e) adjacent in the fluid flow direction. A flat portion (2f) not provided with the raising portion (2c) is provided.

  Thereby, the flow resistance of the fluid can be reduced.

In the invention according to claim 20 , in the heat transfer member according to claim 19 , the dimension (B) of the portion parallel to the fluid flow direction in the flat plate portion (2a) is 5 mm or more and 25 mm or less. Range,
Furthermore, the dimension (Cn) of the part parallel to the fluid flow direction in the flat part (2f) is a predetermined dimension smaller than 1 mm.

  Thereby, the flow resistance of the fluid can be reduced.

In a twenty-first aspect of the present invention, in the heat transfer member according to the nineteenth aspect , a dimension (B) of a portion of the flat plate portion (2a) parallel to the fluid flow direction is greater than 25 mm and not greater than 50 mm. Range,
Furthermore, the dimension (Cn) of the portion parallel to the fluid flow direction in the flat portion (2f) is in the range of 1 mm or more and 20 mm or less.

  Thereby, the flow resistance of the fluid can be reduced.

According to a twenty-second aspect of the present invention, in the heat transfer member according to any one of the twelfth to twenty- first aspects, a length dimension (C) of the thin plate member in a direction orthogonal to the fluid flow direction and the cut-and-raised portion. When the ratio (D / C) between the flow direction of the fluid of the portion (2c) and the length dimension (D) in the orthogonal direction is the cut length ratio (E),
The cut length ratio (E) is in the range of 0.775 or more and 0.995 or less.

  According to this, similarly to the second aspect, the cutting length ratio (E) is appropriately set, and the wind speed of the passing air on the cut-and-raised portion (2c) can be raised to a predetermined range near the maximum wind speed. The heat transfer performance improvement effect by the cut and raised portion (2c) can be effectively exhibited.

As in the invention described in claim 23 , in the heat transfer member described in claim 22 , if the cut length ratio (E) is set in a range of 0.810 or more and 0.980 or less, a cut and raised portion ( 2c) It is possible to further improve the heat transfer performance by further increasing the wind speed of the passing air.

Note that the term “symmetric” in claim 1, claim 4 and claim 16 refers to the collision wall (2c), the L-shaped cross-sectional shape including the collision wall (2c), and the cut-and-raised part (2c). The arrangement of the heat exchange part (2e) is basically symmetrical with respect to the air (fluid) flow direction. However, as will be described in detail in the embodiments described later, the shape is very small in shape. When there are asymmetric parts, or the number of collision walls (2c), cut-and-raised parts (2c), and heat exchange parts (2e) is slightly different between upstream and downstream in the direction of air (fluid) flow It is used in the meaning including.

  In other words, the term “symmetric” is not limited to a perfect symmetrical relationship, but is substantially symmetric (substantially symmetric) to the extent that fin material can be prevented from gathering in one direction during fin molding. Used to include relationships.

Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.

(First embodiment)
In this 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 this embodiment, that is, a radiator. These are the principal part perspective views of the heat exchanger by this embodiment, (b) is AA sectional drawing of (a).

Incidentally, a radiator is a high-pressure side heat exchanger of a vapor compression refrigerator that cools the heat of the refrigerant discharged from the compressor. If the discharge pressure is less than the critical pressure of the refrigerant, While the refrigerant condenses, it dissipates the heat absorbed by the evaporator, and when the discharge pressure is higher than the critical pressure of the refrigerant, the refrigerant does not condense in the radiator, while dissipating the heat absorbed by the evaporator. The temperature is lowered.

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.

  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.

By the way, as shown in FIG. 2A, the tube 1 is a flat multi-hole tube in which a plurality of refrigerant passages are formed by extruding or drawing a metal material.

  The fin 2 is a corrugated fin formed in a wave shape so as to have a flat plate portion 2a and a curved portion 2b curved so as to connect the adjacent flat plate portions 2a. The sheet metal material is formed by applying 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.

  In the flat plate portion 2a of the fin 2, a part of the flat plate portion 2a is cut and raised at right angles to form a plurality of cut and raised portions 2c. Here, cutting up at right angles means, specifically, cutting up a part of the flat plate portion 2a at an angle of 90 ° with respect to the surface of the flat plate portion 2a. The angle may be an angle in the vicinity of 90 °, which is increased or decreased by a minute 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. ing. 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 slit piece 2d. The slit piece 2d and the cut-and-raised portion 2c form an L-shaped cross-sectional shape. The L-shaped cross-sectional shape is formed so as to be symmetrical with respect to a virtual surface Lo orthogonal to the flat plate portion 2a on the air flow upstream side and the air flow downstream side.

Specifically, in the air flow direction, when the flat plate portion 2a is divided into two equal parts by the virtual plane Lo on the upstream side and the downstream side, the number of the upstream raised portions 2c and the downstream raised portions 2c. The air flow upstream side of the slit piece 2d is cut and raised at a right angle on the upstream side of the air flow, while the air flow upstream side of the slit piece 2d is cut at a right angle on the downstream side of the air flow. It has been cut up.

  Next, the outline of the manufacturing method of the fin 2 is described. FIG. 3 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 applies 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 (FIG. 2) to make the fin material 11 wavy, and to the flat plate portion 2a. This is a fin forming apparatus that forms the cut-and-raised portion 2c at a corresponding portion.

The fin forming apparatus 13 includes a pair of gear-shaped forming rollers 13a and a cutter that is provided on the tooth surface of the forming roller 13a and forms the cut-and-raised portion 2c. When passing between the forming rollers 13a, it 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 to a predetermined length so that a predetermined number of the curved portions 2b have one fin 2, and the fin material 11 cut to a predetermined length is fed to the feeding device 1.
5 is sent to the correction device 16 described later.

  The feeding device 15 includes a pair of gear-shaped 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. 2B, the fin pitch Pf has a size twice the distance between the adjacent flat plate portions 2a.

  Incidentally, 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 drawn out from the material roll 10 (drawing step), and the drawn-out fin material 1
1 is given a predetermined tension 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).

Then, feeding toward the straightening unit 16 at the predetermined length of the fin material 11 is cut to the feed device 15 (feeding step), to correct the unevenness by pressing the curved portion 2b in correction device 16 (straightening At the same time, the fin material 11 is shrunk so that the adjacent curved portions 2b are in contact with each other in the brake device 17 (shrinking 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 plurality of cut and raised portions 2c are provided so as to be symmetrical with each other in the air flow direction, the bending force in such a direction as to cancel each other during the fin forming process is continuously thin plate-like fin material. 11 acts.

  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, it is possible to improve fin productivity by simplifying the shape of the fin 2 while increasing the heat transfer efficiency by increasing the heat transfer coefficient between the air and the fin 2 by the turbulent flow effect by the cut and raised portion 2c. it can.

  According to the study by the present inventors, the thickness of the fin 2 is set to 0.01 mm to 0.1 mm, and the cut and raised height H (see FIG. 2B) is set to 0.1 mm to 0.5 mm. It is desirable to cut and raise the pitch dimension P (see FIG. 2B) between the portions 2c to be 1.5 to 5 times the height H.

  More specifically, in the present embodiment, the thickness of the fin 2 is 0.05 mm, the cut-and-raised height H is 0.2 mm, and the pitch dimension P between the cut-and-raised portions 2 c is cut and raised. Five times. The cut-and-raised height H is a height dimension including the thickness of the fin 2 as clearly shown in FIGS. 7, 14, and 15 described later.

(Second Embodiment)
In the second embodiment, as shown in FIG. 4, the cut-and-raised height H of the plurality of cut-and-raised portions 2c located on the upstream side of the air flow is gradually changed so as to increase toward the downstream side of the air flow. ing.

  On the other hand, the cut-and-raised heights H of the plurality of cut-and-raised portions 2c located on the downstream side of the air flow have the same dimensions, and the highest height among the plurality of cut-and-raised portions 2c located on the upstream side of the air flow. The predetermined dimension is lower than the cut-and-raised height H of the cut-and-raised part 2c located in the downstream portion.

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

Even if the height of the cut-and-raised stream on the downstream side of the air flow is increased to enhance the turbulent flow effect, the number of fins 2 to be heat exchanged is small. )
There is a high possibility that the amount of decrease in the heat exchange amount due to the increase will increase and the heat exchange efficiency will deteriorate.

  In the second embodiment, the cut and raised height H of the plurality of cut and raised portions 2c located on the upstream side of the air flow is gradually changed so as to increase toward the downstream side of the air flow. The cut-and-raised portion 2c on the side of the air flow and the cut-and-raised portion 2c on the downstream side of the air flow are not in a symmetric relationship in a complete sense, but the cut-and-raised portion 2c on the upstream side of the air flow and the cut-and-raised portion 2c on the downstream side of the air flow Are common in that they have an L-shaped cross-sectional shape and constitute a substantially symmetrical relationship. Therefore, the arrangement of the cut-and-raised portions 2c according to the second embodiment is also referred to as “symmetrical” in the present invention. "Relationship".

  In the first and second embodiments, the number of the cut-and-raised portions 2c on the upstream side of the air flow and the number of cut-and-raised portions 2c on the downstream side of the air flow are both set to the same number (each 9). Even if the number of the cut-and-raised portion 2c on the side and the cut-and-raised portion 2c on the downstream side of the air flow is slightly shifted (for example, 1), it is included in the “symmetrical relationship” in the present invention.

(Third embodiment)
In the first and second embodiments described above, the heat exchanger including the corrugated fins 2 bent into a wave shape has been described. However, the third embodiment is formed into a flat plate shape as shown in FIG. The present invention is applied to a heat exchanger having plate-like fins 2.

(Fourth embodiment)
In the above-described embodiment, the cut-and-raised portions 2c are formed so as to be symmetrical with each other with respect to the virtual surface Lo. However, in the example of FIG. The portion 2c and the cut-and-raised portion 2c on the downstream side of the air flow are formed symmetrically with respect to the flat plate portion 2a.

  In the example of FIGS. 6B and 6C, a pair of symmetrically raised portions 2c are arranged in the air flow direction as one set.

  Moreover, in the example of FIG.6 (d), the cut-and-raised part 2c is formed in the site | part opposite to 1st Embodiment with respect to the slit piece 2d. It goes without saying that the shape shown in FIG. 6 and the second embodiment (FIG. 4) may be combined.

(Fifth embodiment)
FIG. 7 is a fin cross-sectional view for explaining the fifth embodiment, and 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. Further, the pitch dimension P between the heat exchanging portions 2e formed by the cut and raised portions 2c and the slit pieces 2d continuously connected to the root portions of the cut and raised portions 2c is set to a range of 0.02 mm or more and 0.75 mm or less. Yes.

  Here, as shown in FIG. 7, the pitch dimension P between the heat exchanging parts 2e is a dimension indicating the distance between the adjacent heat exchanging parts 2e in the air flow direction. It is equal to the dimension of the part parallel to the direction orthogonal to the air flow direction among the parts 2e.

8 is a numerical simulation result showing the relationship between the pitch dimension P between the heat exchange parts 2e and the heat exchange performance, and FIG. 9 is a numerical simulation showing the relationship between the cut-and-raised height H and the heat exchange performance. It is a result. As is clear from FIGS. 8 and 9, the cut-and-raised height H of the cut-and-raised portion 2c is set to 0.02 mm or more and 0.4 mm or less, and the pitch dimension P between the heat exchange portions 2e is set to 0.02 mm or more. When the thickness is 0.75 mm or less, it can be seen that the heat exchange performance is improved.

  The heat exchange performance is determined based on the product of the heat transfer coefficient and the heat transfer area. In FIGS. 8 and 9, the heat exchange performance of the fins of the current heat exchanger provided with a so-called louver is shown. The change of the heat exchange performance by the pitch dimension P and the cut-and-raised height H is shown by the ratio as a reference.

Further, when the height H of the cut-and-raised portion 2c or the pitch P between the heat exchange portions 2e is changed,
Since the pressure loss (ventilation resistance) of the air flowing around the fin 2, that is, the flat plate portion 2 a also changes, in the numerical simulation shown in FIGS. 8 and 9, the height H of the cut-and-raised portion 2 c or between the heat exchange portions 2 e In response to the change, the fin pitch Pf (see FIG. 2b and FIG. 4), which is twice the distance between the adjacent flat plate portions 2a, is changed in accordance with the change so that the pressure loss (ventilation resistance) becomes substantially the same. The heat exchange performance is calculated by changing the height H of the part 2c and the pitch P between the heat exchange parts 2e.

  Incidentally, when the fin pitch Pf is increased, as shown in FIGS. 10 and 11, although the pressure loss (ventilation resistance) is reduced, the number of the flat plate portions 2a is reduced and the heat transfer area and the heat transfer coefficient are also reduced. Conversely, when the fin pitch Pf is reduced, the number of the flat plate portions 2a is increased and the heat transfer area and the heat transfer coefficient are increased, but the pressure loss (ventilation resistance) is increased.

FIG. 10 shows a numerical simulation result using the pitch P between the heat exchange parts 2e as a parameter, and FIG. 11 shows a numerical simulation result using the height H of the cut-and-raised part 2c as a parameter.

Further, 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 heat exchange portion 2e parallel to the air flow direction is the height H of the cut-and-raised portion 2c. And it changes according to the pitch P between the heat exchange parts 2e.

  Therefore, based on FIGS. 8 and 9, the height H of the cut-and-raised portion 2c with respect to the dimension L of the portion parallel to the air flow direction (that is, the heat exchange portion 2e is parallel to the direction perpendicular to the air flow direction). FIG. 12 shows a summary of the relationship between the ratio of the dimension H) (= H / L) and the heat exchange performance.

  Therefore, by setting the ratio of the cut and raised height H to the dimension L of the portion parallel to the air flow direction in the heat exchange part 2e (= H / L) in the range of 0.5 to 2.2. High heat exchange performance can be obtained.

(Sixth embodiment)
In the fifth embodiment, the height H of the cut-and-raised portion 2c and the heat exchanging portion 2e are obtained so that the heat exchanging performance equal to or higher than the heat exchanging performance of the fins of the current heat exchanger provided with so-called louvers can be obtained. The pitch P is set in between, but the actual product has dimensional variations and the like.

  Therefore, in the sixth embodiment, considering that the heat exchange performance fluctuates by 20%, the cut-and-raised height H of the cut-and-raised portion 2c is set to a range of 0.06 mm to 0.36 mm, and the heat exchange portion The pitch P between 2e is in the range of 0.08 mm or more and 0.68 mm or less.

(Seventh embodiment)
In the above-described embodiment, as shown in FIG. 13A, the heat exchange performance (heat transfer coefficient) is achieved by the air flow meandering in the cut-and-raised portion 2c, particularly the cut-and-raised portion 2c on the downstream side of the air flow. Therefore, the cut-and-raised angle θ of the cut-and-raised portion 2c is not limited to the above-mentioned value of about 90 degrees, but as shown in FIG. It is only necessary that a part of the flat plate portion 2a is cut and raised.

  Therefore, in the seventh embodiment, specifically, the cut-and-raised angle θ of the cut-and-raised portion 2c is set in the range of 40 degrees or more and 140 degrees or less.

  Therefore, the cross-sectional shape of the heat exchange part 2e is not limited to the L-shaped cross-sectional shape, and may be various cross-sectional shapes as shown in FIGS. 14 and 15, 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 raised.

FIG. 14A shows an example in which the cut-and-raised angle θ is about 40 degrees, and FIG.
Is an example in which the cut-and-raised angle θ is about 140 degrees, and FIGS. 14C and 14D show the slit piece 2d in the flat plate portion 2a with the cut-and-raised angle θ set to about 40 degrees. This is an example of bending to raise.

FIG. 15A shows an example in which the slit piece 2d is bent on the opposite side to the cut and raised portion 2c so as to be raised in the same direction as the cut and raised portion 2c. FIG. 15B shows an example in which the cut and raised portion 2c is cut and raised so as to form a smooth arcuate curved surface from the slit piece 2d to the cut and raised portion 2c.

  FIG. 15 (c) shows a smooth arcuate curved surface from the slit piece 2d to the cut-and-raised portion 2c, and the opposite side of the slit piece 2d to the cut-and-raised portion 2c has the same orientation as the cut-and-raised portion 2c. It is an example bent into a curved surface. Furthermore, FIG.15 (d) changes the direction which the cut-and-raised part 2c cuts up every other.

(Eighth embodiment)
The eighth embodiment relates to the number of heat exchanging portions 2e, that is, the cut-and-raised portions 2c. That is, as shown in FIG. 16, B is a dimension of a portion of the flat plate portion 2a parallel to the air flow direction, and is represented by a value when the unit of length is millimeter. The number n of the heat exchanging portions 2e is larger than the value obtained by dividing the value of the dimension B (unit: millimeter) of the portion parallel to the air flow direction by 0.75.

  That is, the number n (n is a natural number) of the heat exchange units 2e is expressed by the following formula (1).

n> (B / 0.75) (1)
(Ninth embodiment)
In the ninth embodiment, as shown in FIG. 17, at least one flat portion 2 f not provided with the cut-and-raised portion 2 c is provided in the heat exchanging portions 2 e adjacent in the air flow direction. And the dimension B of the part parallel to the air flow direction in the flat plate part 2a is 5 mm or more and 25 mm or less, and the dimension Cn of the part parallel to the air flow direction in the flat part 2f is smaller than 1 mm. It is set as a predetermined dimension (in this embodiment, 0.5 mm). Thereby, the flow resistance of air can be reduced.

(10th Embodiment)
In the tenth embodiment, as shown in FIG. 18, a plurality of flat portions 2f (three in the illustrated example) where the cut-and-raised portions 2c are not provided are provided in the heat exchange portions 2e adjacent in the air flow direction. Yes.

  The dimension B of the portion parallel to the air flow direction in the flat plate portion 2a is set to a range larger than 25 mm and 50 mm or less, and the dimension Cn of the portion parallel to the air flow direction in the flat portion 2f is set to The predetermined dimension is 1 mm or more and 20 mm or less (in this embodiment, 5 mm). Thereby, the flow resistance of air can be reduced.

(Eleventh embodiment)
FIGS. 19 to 23 illustrate the eleventh embodiment. In the eleventh embodiment, as shown in FIG. 19, the length dimension of the fin 2 in the direction perpendicular to the air flow direction is C, and the cut-and-raised portion 2c. When the length dimension in the direction perpendicular to the air flow direction is D and the ratio of both length dimensions (D / C) is the cut length ratio E, the cut length ratio E is used to improve the heat exchange performance. Therefore, the optimum range is set.

  In addition, the length dimension C of the fin 2 in the direction orthogonal to the air flow direction is a dimension that coincides with the interval between the adjacent tubes 1 as shown in FIG. 20 is a cross-sectional view taken along the line AA in FIG.

  FIG. 21 is a graph showing the relationship between the average wind speed of the air flow passing over the cut-and-raised portion 2c (see FIG. 13) and the cut length ratio E, and shows the calculation result of numerical simulation by the present inventor. ing.

  As the main conditions of this numerical simulation, the pitch dimension P between adjacent heat exchange parts 2e shown in FIG. 20 is 0.5 mm, the height H is 0.25 mm, and the air flow direction of the heat exchange part 2e is The dimension L = 0.25 mm, the fin pitch Pf of the corrugated fin 2 is 2.5 mm, and the wind speed on the front surface of the heat exchanger is set to 4 m / S.

  In this numerical simulation, the cut and raised length D is fixed to 4.5 mm, the fin length C is changed, and the change in the average wind speed of the air flow based on the change in the cut length ratio E is calculated. .

  Here, the phenomenon in which the average wind speed of the air flow changes based on the change in the cut length ratio E will be described with reference to FIGS. 22 and 23. FIGS. 22 (b) and 22 (c) are enlarged views of the Z portion in FIG. 22 (a). 22 (b) shows the air flow when the cut length ratio E (D / C) = 0.69, and FIG. 22 (c) shows the cut length ratio E (D / C) = 0. The air flow when set to 81 is shown.

  Non-cut portions 2g and 2h are formed on both side surfaces of the cut-and-raised portion 2c in the flat surface portion 2a of the fin 2, and the bypass air of the cut-and-raised portion 2c on the non-cut portions 2g and 2h is shown by the arrows in FIG. It flows like G. At this time, FIG. 22B shows a state in which the length F of the non-cut portions 2g and 2h is increased and the cut length ratio E (D / C) is reduced to 0.69.

  When the cut length ratio E is thus reduced, the detour air flow of the arrow G passing over the non-cut portions 2g and 2h is generated at a considerable rate as shown in FIG. 22 (b). As a result, the wind velocity of the air flow in the case of the cut length ratio E = 0.69 is the non-cut portion 2g, 2h, which is the outside in the length direction of the cut and raised portion 2c, as shown by the broken line in FIG. In association with this, the wind speed of the passing air on the cut and raised portion 2c decreases.

  In addition, the horizontal axis of Fig.23 (a) represents the length C of the fin 2 in the direction orthogonal to the air flow direction by the ratio. That is, the center of the fin length C is represented by 0, and the length from the center 0 to the side end of the fin 2 is represented by ± 1. Therefore, on the horizontal axis of FIG. 23A, the total length of the length C of the fin 2 is represented as “2”.

  By the way, as shown in FIG. 22 (c), when the cut length ratio E is increased to 0.81, the length F of the non-cut portions 2g and 2h decreases, and the detour air flow passing through the non-cut portions 2g and 2h. Almost disappears. Thereby, the wind speed distribution is made uniform, and the wind speed of the passing air on the cut-and-raised portion 2c can be increased as shown by a one-dot chain line in FIG.

  Further, when the cut length ratio E is increased to near 0.94, the wind speed of the passing air on the cut and raised portion 2c can be further increased as shown by the solid line in FIG. When the cut length ratio E is made closer to “1”, both end portions in the length direction of the cut-and-raised portion 2c approach the wall surface of the tube 1 (or the fin curved portion 2b). Since the influence of the resistance due to the wall surface of 2b) increases and the wind speed decreases, the average wind speed of the passing air on the cut-and-raised portion 2c decreases.

  Since there is a correlation that the heat transfer performance (air-side heat transfer coefficient) of the fin 2 increases as the average wind speed of the passing air on the cut-and-raised portion 2c increases, the cut length ratio E should be selected within the optimum range. Thus, the heat transfer performance of the fin 2 can be effectively improved.

  FIG. 21 shows the relationship between the cut length ratio E and the average wind speed of the passing air on the cut-and-raised portion 2c, and this average wind speed becomes maximum near the cut length ratio E = 0.90. Therefore, in order to improve the heat transfer performance of the fin 2, it is most effective to set the cut length ratio E in the vicinity of 0.90, but considering the variation in the cut length ratio E as a product, etc. It can be said that it is practical that the decrease in the wind speed from the maximum wind speed is within about 10% as a range in which the performance degradation can be allowed.

  Therefore, a range of 0.775 or more and 0.995 or less is set as the range of the cut length ratio E. Thereby, the heat transfer performance of the fin 2 can be improved effectively. Even within this set range, if the cut length ratio E is set within the range of 0.810 or more and 0.980 or less, the wind speed decrease from the maximum wind speed is within approximately 6%, and the heat transfer performance of the fin 2 is improved. Therefore, it is more preferable.

(Twelfth embodiment)
FIG. 24 shows a twelfth embodiment. In the twelfth embodiment, the fin 2 is provided with a protruding portion 2i protruding to the upstream side of the air flow from the tube 1, and the protruding portion 2i is also provided with a cut-and-raised portion 2c. It is formed continuously. This is for the following reason.

FIG. 25 (b) shows a comparative example of the twelfth embodiment. In this comparative example, the air flow upstream end and the air flow downstream end of the fin 2 and the tube 1 are made to coincide with each other as in the first embodiment. ing. Therefore, the protrusion 2i of the fin 2 according to the twelfth embodiment is not formed.

  The cut-and-raised portion 2c turbulent airflow to improve the fin heat transfer performance. According to the detailed experimental study by the present inventors, even if the cut-and-raised portion 2c is formed, the air in the fin 2 As shown in FIG. 25 (b), a laminar flow region is formed in the inlet region on the upstream side of the flow, and a turbulent region, that is, a region having a high heat transfer coefficient is formed on the downstream side of the laminar flow region. .

  In the twelfth embodiment, paying attention to this point, the fin 2 is formed with a protruding portion 2i protruding upstream of the air flow from the tube 1, and the protruding portion 2i is continuously formed with a raised portion 2c. Yes.

  According to the twelfth embodiment, since the disturbance of the air flow due to the cut-and-raised portion 2c is started also in the projecting portion 2i of the fin 2 on the upstream side of the air flow, as shown in FIG. The turbulent flow region can be shifted to the air flow upstream side of the comparative example of FIG. Thereby, the fin 2 can increase the heat transfer performance effectively by increasing the high heat transfer coefficient region in the portion in contact with the wall surface of the tube 1 from the range indicated by the broken line arrow in the comparative example of FIG. .

  According to the inventor's study, the protrusion length of the protrusion 2i is set to a length that can form at least two cut-and-raised portions 2c within the range of the protrusion 2i. It is preferable for improvement.

  FIG. 25C shows another comparative example, in which a projecting portion 2j projecting to the air flow downstream side of the tube 1 is formed on the fin 2. According to this other comparative example, a turbulent region having a high heat transfer coefficient can be formed also in the projecting portion 2j on the downstream side of the air flow. The range can be increased from the arrow range to the solid arrow range.

  However, since the protrusion 2j to the downstream side of the air flow is a part away from the wall surface of the tube 1, the heat of the high-temperature fluid in the tube 1 does not easily reach the protrusion 2j. As a result, according to another comparative example of FIG. 25C, the turbulent flow region having a high heat transfer rate due to the protrusion 2j on the downstream side of the air flow cannot be effectively used for improving the fin heat transfer performance. On the contrary, the formation of the projecting portion 2j increases the ventilation resistance, which causes the heat exchanger heat dissipation performance to deteriorate due to this defect.

  Accordingly, the fin 2 is arranged so as not to protrude downstream from the air flow downstream end portion of the tube 1, that is, the air flow downstream end portion of the fin 2 and the air flow downstream end portion of the tube 1 in the air flow direction. The arrangement (FIG. 25 (a)) that coincides with each other is advantageous for ensuring the heat dissipation performance of the heat exchanger.

  Here, the arrangement in which the end of the fin 2 on the downstream side of the air flow and the end of the tube 1 on the downstream side of the air flow coincide with each other, which means a substantial coincidence including a minute shift between both ends due to assembly variation or the like. is doing.

(Other embodiments)
Moreover, in the above-mentioned embodiment, although the heat exchange part 2e, ie, the cut-and-raised part 2c, was formed in a line in the air flow direction in the flat plate part 2a, the present invention is limited to this. Instead, for example, two or more rows may be used.

  Further, in the above-described embodiment, the present invention is applied to the radiator of the vehicle air conditioner. However, the application of the present invention is not limited to this, for example, a heater core for heating of the vehicle air conditioner, a vapor compression type, and the like. The present invention can also be applied to heat exchangers such as evaporators and condensers of refrigerators and radiators that cool engine cooling water.

  Moreover, in the above-mentioned embodiment, although the fin 2 was manufactured by the roller molding method, this invention is not limited to this, For example, you may manufacture the fin 2 by press work.

In the above-described embodiment, the tube 1 and the fin 2 are brazed, but the present invention is not limited to this. For example, by expanding the tube 1, the tube 1 and the fin 2 are machined. May be combined.

It is a front view of the heat exchanger by embodiment of this invention. (A) is a principal part perspective view of the heat exchanger by 1st Embodiment of this invention, (b) is AA sectional drawing of (a). It is a schematic diagram of the roller shaping | molding apparatus by 1st Embodiment. It is sectional drawing which shows the fin by 2nd Embodiment of this invention. It is a principal part perspective view of the heat exchanger by 3rd Embodiment of this invention. It is sectional drawing which shows the fin by 4th Embodiment of this invention. It is fin part sectional drawing explaining the definition of the pitch dimension P between the cut and raised height H and the heat exchange part 2e. It is a graph which shows the numerical simulation result which shows the relationship between the pitch dimension P between the heat exchange parts 2e, and heat exchange performance. It is a graph which shows the numerical simulation result which shows the relationship between the cutting height H and heat exchange performance. It is a graph which shows the numerical simulation result which made pitch P between the heat exchange parts 2e a parameter. It is a graph which shows the numerical simulation result which made height H of the cut and raised part 2c a parameter. It is the graph which put together the relationship between ratio (= H / L) of the dimension H of the part parallel to the direction orthogonal to the flow direction of air among heat exchange parts 2e, and heat exchange performance. It is a schematic diagram which shows the air flow on the cut and raised part 2c. It is fin part sectional drawing which shows the cut and raised part by 7th Embodiment of this invention. It is fin part sectional drawing which shows the cut and raised part by 7th Embodiment of this invention. It is a principal part perspective view of the heat exchanger by 8th Embodiment of this invention. It is fin part sectional drawing of the heat exchanger by 9th Embodiment of this invention. It is fin part sectional drawing of the heat exchanger by 10th Embodiment of this invention. It is a principal part perspective view of the heat exchanger by 11th Embodiment of this invention. It is AA sectional drawing of FIG. It is a graph which shows the relationship between the cut length ratio E by 11th Embodiment, and the average wind speed of a raising part. (A) is a principal part top view for operation | movement description of 11th Embodiment, (b), (c) is the Z section enlarged view of (a). (A) is a graph which shows the wind speed distribution of a fin length direction, (b) is a principal part top view which shows the corresponding structure in the fin length direction of the horizontal axis of (a). It is a principal part perspective view of the heat exchanger by 12th Embodiment of this invention. (A) is a principal part top view of the heat exchanger by 12th Embodiment of this invention, (b), (c) is a principal part top view of the comparative example of 12th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Tube, 2 ... Fin, 2a ... Flat plate part, 2b ... Curved part, 2c ... Cut-and-raised part,
2d: slit piece.

Claims (23)

A heat exchanger comprising a tube (1) through which a fluid flows, and fins (2) provided on an outer surface of the tube (1) to increase a heat exchange area with air flowing around the tube (1). ,
The fin (2) includes a flat plate portion (2a) , a collision wall (2c) formed by cutting a part of the flat plate portion (2a) at a right angle, and the flat plate portion (2a). A slit piece (2d) composed of a portion continuously connected to the base of the collision wall (2c) ,
The cut and raised height (H) of the collision wall (2c) is in the range of 0.02 mm or more and 0.4 mm or less,
A plurality of heat exchange parts (2e) composed of the collision wall (2c) and the slit piece (2d) are provided in the air flow direction,
The pitch dimension (P) between the heat exchange parts (2e) adjacent in the air flow direction is in the range of 0.02 mm or more and 0.75 mm or less,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. Range of
Further, L-shaped cross section is constituted by said deflector and (2c) the slit piece and (2d),
The L-shaped cross-sectional shape on the upstream side of the air flow and the L-shaped cross-sectional shape on the downstream side of the air flow are disposed symmetrically with respect to a virtual plane orthogonal to the flat plate portion (2a). A heat exchanger characterized by that. A heat exchanger comprising a tube (1) through which a fluid flows, and fins (2) provided on an outer surface of the tube (1) to increase a heat exchange area with air flowing around the tube (1). ,
The fin (2), said flat plate portion and (2a), said plate and (2a) of formed by cutting and raising a portion the collision wall (2c), of said plate (2a) A slit piece (2d) composed of a portion continuously connected to the base of the collision wall (2c) ;
The cut and raised height (H) of the collision wall (2c) is in the range of 0.02 mm or more and 0.4 mm or less,
A plurality of heat exchange parts (2e) composed of the collision wall (2c) and the slit piece (2d) are provided in the air flow direction,
The pitch dimension (P) between the heat exchange parts (2e) adjacent in the air flow direction is in the range of 0.02 mm or more and 0.75 mm or less,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. Range of
A ratio (D / C) of a length dimension (C) perpendicular to the air flow direction of the fin (2) and a length dimension (D) perpendicular to the air flow direction of the collision wall (2c). ) As the cutting length ratio (E),
The heat exchanger characterized in that the cut length ratio (E) is in the range of 0.775 or more and 0.995 or less.   The heat exchanger according to claim 2, wherein the cut length ratio (E) is in a range of 0.810 to 0.980. By cutting and raising the collision wall (2c) at a right angle shape from said plate (2a), by the collision wall and (2c) the slit piece and (2d) is L-shaped cross section is constituted,
The L-shaped cross-sectional shape on the upstream side of the air flow and the L-shaped cross-sectional shape on the downstream side of the air flow are disposed symmetrically with respect to a virtual plane orthogonal to the flat plate portion (2a). The heat exchanger according to claim 2 or 3 , wherein Among the plurality of collision walls (2c), a part of the collision walls (2c) located on the upstream side of the air flow is cut and raised higher than the other collision walls (2c). And
Further, among the plurality of collision walls (2c), the plurality of collision walls (2c) located on the downstream side of the air flow are all cut and raised (H) having the same size. The heat exchanger according to any one of claims 1 to 4. Among the plurality of collision walls (2c), the cut and raised height (H) of the plurality of collision walls (2c) located on the upstream side of the air flow is higher toward the downstream side of the air flow,
Further, among the plurality of collision walls (2c), the cut-and-raised height (H) of the plurality of collision walls (2c) located on the downstream side of the air flow is the plurality of the plurality of collision walls (2c) located on the upstream side of the air flow. The heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger is lower than a cut-and-raised height (H) of a collision wall (2c) located at the most downstream portion of the collision wall (2c) of the heat exchanger. .   The heat exchanger according to any one of claims 1 to 6, wherein the fin (2) is a corrugated fin formed in a wave shape.   The heat exchanger according to any one of claims 1 to 6, wherein the fin (2) is a plate fin formed in a flat plate shape. The fin (2) is formed with a protruding portion (2j) protruding to the upstream side in the air flow direction from the tube (1),
The heat exchanger according to any one of claims 1 to 8, wherein the collision wall (2c) is also formed in the protruding portion (2j).   The heat exchanger according to claim 9, wherein at least two collision walls (2c) are formed in the protrusion (2j).   The downstream end of the fin (2) in the air flow direction is arranged so as not to protrude downstream from the downstream end of the tube (1) in the air flow direction. The heat exchanger according to 9 or 10. A heat transfer member that is formed from a thin plate member, is exposed to a fluid and transfers heat to and from the fluid,
A plurality of heat exchanging portions (2e) comprising a cut and raised portion (2c) cut and raised from the thin plate member and a slit piece (2d) continuously connected to the root portion of the cut and raised portion (2c). A flat plate portion (2a) having
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,
Further, the heat exchanging portion adjacent to each other in the flow direction of the fluid (2e) pitch dimension between (P), or 0.02 mm, Ri following ranges der 0.75 mm,
A ratio (H / L) of the cut and raised height (H) to a dimension (L) of a portion parallel to the air flow direction in the heat exchange part (2e) is 0.5 or more and 2.2 or less. A heat transfer member characterized by being in the range . The cut and raised height (H) of the cut and raised portion (2c) is in the range of 0.06 mm or more and 0.36 mm or less,
Furthermore , the pitch dimension (P) between the said heat exchange parts (2e) is the range of 0.08 mm or more and 0.68 mm or less, The heat-transfer member of Claim 12 characterized by the above-mentioned .   The heat transfer member according to claim 12 or 13, wherein the cut and raised angle (θ) of the cut and raised portion (2c) is in a range of 40 degrees or more and 140 degrees or less.   The heat transfer member according to any one of claims 12 to 14, wherein the cut and raised portion (2c) is cut and raised from the thin plate member in a curved shape. Among the plurality of heat exchange parts (2e), the cross-sectional shape of the heat exchange part (2e) located on the upstream side of the fluid flow and the cross section of the heat exchange part (2e) located on the downstream side of the fluid flow The heat transfer member according to any one of claims 12 to 15 , wherein the shapes are arranged symmetrically with each other. The heat exchanging portion (2e), at said plate (2a), according to any one of claims 12 to 16, characterized in being formed in a row in the flow direction of the fluid Heat transfer member. The number of the heat exchanging portions (2e) is the dimension of the portion of the flat plate portion (2a) parallel to the fluid flow direction, and the value (B) when the unit of length is millimeter is 0. The heat transfer member according to claim 17 , wherein the number is larger than the value divided by 75. The at least one heat exchange part (2e) adjacent in the flow direction of the fluid is provided with a flat part (2f) not provided with the cut and raised part (2c). The heat transfer member according to any one of 12 to 18 . The dimension (B) of the portion parallel to the fluid flow direction in the flat plate portion (2a) is in the range of 5 mm or more and 25 mm or less,
Furthermore, the dimension (Cn) of the site | part parallel to the flow direction of a fluid among the said flat parts (2f) is a predetermined dimension smaller than 1 mm, The heat-transfer member of Claim 19 characterized by the above-mentioned. The dimension (B) of the portion parallel to the fluid flow direction in the flat plate portion (2a) is in the range of more than 25 mm and 50 mm or less,
Furthermore, the dimension (Cn) of the site | part parallel to the fluid flow direction among the said flat parts (2f) is the range of 1 mm or more and 20 mm or less, The heat-transfer member of Claim 19 characterized by the above-mentioned. The ratio (D / C) of the length dimension (C) of the thin plate member in the direction perpendicular to the fluid flow direction and the length dimension (D) of the cut and raised portion (2c) in the direction perpendicular to the fluid flow direction. ) As the cutting length ratio (E),
The Broken length ratio (E) of 0.775 or more, 0.995 or less 12 claims, characterized in that the range of heat transfer member according to any one of 21. The heat transfer member according to claim 22 , wherein the cut length ratio (E) is in the range of 0.810 to 0.980.

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