JPH0565788B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a plate-fin type heat exchanger used, for example, in an oil cooler.

In this specification, aluminum is meant to include pure aluminum and aluminum alloys.

Conventional technology Conventionally, for example, an oil cooler made of aluminum has a first fluid passage through which oil flows and a second fluid passage through which air flows in a direction perpendicular to the first fluid passage, which are separated by a flat plate and alternately arranged vertically. A press-formed fin such as a multi-entry fin (offset fin) was housed in the first fluid flow path through which oil circulated.

Problems to be Solved by the Invention However, according to such conventional fins, the intervals between the protrusions provided on the fins are narrow;
Although the amount of heat exchanged is relatively high and the performance is high, the pressure loss is very large, so it is necessary to increase the pump discharge pressure to maintain the oil pressure, which increases equipment and power costs. There was a problem. Therefore, in order to reduce the pressure loss, it has been considered to increase the distance between the protrusions of the conventional fins, but this has resulted in the problem that the heat exchange performance deteriorates.

In addition, because conventional oil coolers have a large number of parts, it takes time to assemble the parts (setting), it is not easy to automate the setting, it is not possible to manufacture oil coolers efficiently, and the weight is high. I had a problem with it being heavy.

The purpose of this invention is to solve the above problems, to be able to sufficiently disturb the flow of fluid such as oil, to have an excellent turbulence effect, to facilitate fluid flow, and to minimize pressure loss. It is small, so it is possible to increase the amount of heat exchanged, and has excellent heat exchange performance. It is not necessary to particularly increase the discharge pressure of the pump, and the equipment costs and power costs for the heat exchanger are low. It is economical, has a small number of parts, is lightweight, can significantly shorten the time for setting parts, and can easily automate the setting. A plate-fin type heat exchanger for use in oil coolers, etc., which can be easily and reliably formed into a flow path forming body with rows, and which can also be easily manufactured. That's what we're trying to offer.

Means for Solving the Problems In order to achieve the above object, the present invention provides an aluminum plate fin type having first fluid channels and second fluid channels separated by a flat plate alternately in the vertical direction. In the heat exchanger, a flow path forming body made of extruded aluminum is interposed between the upper and lower flat plates of at least one of the first fluid flow path and the second fluid flow path. The forming body is made up of left and right side walls and a horizontal connecting wall part that connects these both side walls, and the horizontal connecting wall parts are arranged in the front-rear direction and have a cross section of approximately Λ that protrudes alternately up and down.
A plurality of rows of projections each having a large number of arch-shaped projections each having a substantially V-shaped cross section are provided, and the positions of the arch-shaped projections having a cross section of approximately Λ-shape and the arch-shaped projections having a substantially V-shape cross section of the rows of projections adjacent to each other on the left and right are misaligned. The arch-shaped protrusions having a generally Λ-shaped cross section and the arch-shaped protrusions having a roughly V-shaped cross section are arranged side by side adjacent to each other, and fluid passage holes are formed to face each arch-shaped protrusion. The longitudinal direction of the arch-shaped protrusions is made to match the longitudinal direction of the left and right side walls of the channel forming body, so that the fluid flows in the longitudinal direction of the arch-shaped protrusions of each row of protrusions. The wall thickness (t) of the projections is 0.5 to 1.5 mm, the width (W) is t to 10t, the height (H) is 2 to 10 mm, and the pitch (P) between adjacent projections is 3. The main feature is a plate-fin type heat exchanger with a diameter of ~30 mm.

Function In the above-mentioned plate-fin type heat exchanger, when fluid such as oil flows in the fluid passage formed by the passage forming body consisting of the upper and lower flat plates, the left and right side walls, and the horizontal connecting wall, each protrusion The fluid is caused to flow in the longitudinal direction of the arched protrusion of the row,
Since the wall surface of each protrusion faces the direction of fluid flow, oil etc. The fluid hits the protrusion from the front, and the flow of fluid such as oil is disturbed and goes around both the left and right sides of each protrusion, but there is a wide space equivalent to at least one protrusion on both the left and right sides of each protrusion. Therefore, fluid such as oil can easily flow around both the left and right sides of each protrusion, and therefore the pressure loss is small.
In addition, fluid such as oil that has bypassed the protrusions can sufficiently mix within each space. The oil and other fluids that hit the arch-shaped protrusions and flow around to the left and right sides of these holes flow downward or upward into the fluid passage holes, and as a result, the oil and other fluids eventually become Since the flow is disturbed and moved through the fluid channel while being sufficiently stirred, the heat exchange efficiency is greatly increased.

Further, the flow path forming body of the heat exchanger has left and right side walls thereof, and a horizontal connection having a plurality of protrusion rows connecting these side walls and consisting of a large number of arch-shaped protrusions having approximately Λ-shaped and approximately V-shaped cross sections. Since it is integrally made from extruded aluminum, the number of parts is small, it is lightweight, and the time it takes to set up parts can be significantly shortened, making it easy to automate the setting process. It is.

In addition, the flow path forming body is formed by forming a horizontal connecting wall portion of an extruded aluminum material, which is made up of left and right side walls and a horizontal connecting wall portion connecting these, by press working or forming processing using forming rolls, so that the horizontal connecting wall portion has a cross section of approximately Λ. It is possible to easily form a plurality of protrusion rows consisting of a large number of arch-shaped protrusions each having a substantially V-shape.

Since the thickness (t), width (W), height (H) and pitch (P) of each arch-shaped projection are within a predetermined range, moldability is good, and the arch-shaped projection can be formed easily. can be carried out easily and reliably, and as a result, plate-fin type heat exchangers can be easily manufactured.Plate-fin type heat exchangers have high pressure resistance, and have low pressure loss and low pressure loss as mentioned above. This ensures excellent heat exchange performance.

Embodiments Examples of the present invention will be described below based on the drawings.

In this specification, front, back, left, right, and top and bottom are based on FIG. 3, where "front" refers to the front side of the sheet of paper in FIG.
"Right" refers to the right side of the figure, "top" refers to the upper side of the figure, and "bottom" refers to the lower side of the figure.

Further, the embodiment shows a case where the plate-fin type heat exchanger of the present invention is applied to an oil cooler.

In FIGS. 1 to 5 showing a first embodiment of the present invention, a plate-fin heat exchanger 11 has a first fluid flow path A and a second fluid flow path separated by a flat plate 12 made of an aluminum brazing sheet. It has fluid flow paths B alternately in the vertical direction. Oil flows through the first fluid flow path A, and air flows through the second fluid flow path B. Both channels A and B are arranged so that these fluids flow orthogonally.

The first fluid flow path A includes an upper and lower flat plate 12 and a flat plate 12
It is formed by a channel forming body 13 made of an aluminum extrusion molded material interposed between the two.

Here, the flow path forming body 13 has left and right side walls 14,
14, and a horizontal connecting wall portion 1 that connects these side walls 14, 14. The horizontal connecting wall 1 includes a large number of arch-shaped projections having approximately Λ-shaped and approximately V-shaped cross sections that are arranged in the front-rear direction with the horizontal wall 2 interposed between them and alternately protrude vertically from the horizontal wall 2. It is provided with a plurality of protrusion rows R consisting of 3a and 3b.

In each projection row R of this horizontal connection wall portion 1,
A horizontal wall 2 is formed between an upwardly protruding protrusion 3a having a Λ-shaped cross section and a downwardly protruding protruding protrusion 3b having a V-shaped cross-section.
are arranged alternately in the front-back direction through the arch-shaped protrusions 3a, 3b, and the longitudinal direction of each arch-shaped protrusion 3a, 3b is connected to the first fluid flow path A.
It corresponds to the direction of oil flow, and each protrusion 3
The wall surfaces of a and 3b face each other in the direction of oil flow. The positions of the arch-shaped protrusions 3a having a generally Λ-shaped cross section and the arch-shaped protrusions 3b having a generally V-shaped cross section in adjacent protrusion rows R are shifted from each other by one position.

In each projection row R of the horizontal connecting wall portion 1, fluid passage holes are provided between the front and rear horizontal wall portions 2 adjacent to each other so as to face arch-shaped projections 3a and 3b having approximately Λ-shaped and approximately V-shaped cross sections. 4 is open.

The fluid passage hole 4 facing each arch-shaped projection 3a, 3b communicates with openings on both the left and right sides of the projections 3a, 3b, so that oil can easily flow in from both the left and right sides of the projections 3a, 3b.

The channel forming body 13 has left and right side walls 14, 14.
and a flat horizontal connecting wall 1 that connects these parts.The horizontal connecting wall 1 is formed with a vertically protruding cross section by press working or molding using forming rolls. A large number of Λ-shaped and approximately V-shaped arch-shaped projections 3a, 3b are formed so as to leave a horizontal wall portion 2 of a predetermined width between the projections 3a, 3b, and the same number of fluid passage holes 4 are opened to form a horizontal connecting wall portion. 1. Since the large number of protrusions 3a, 3b are formed by being cut and raised from the flat horizontal connecting wall 1, less material can be used, and the weight of the heat exchanger 11 can be reduced.

Here, the wall thickness (t) of each arch-shaped protrusion 3 is 0.5
The width (W) is t~10t, the height (H) is 2~10mm, and the pitch (P) between the adjacent protrusions 3 is 3~30mm.

In the above, the wall thickness (t) of the arch-shaped protrusion 3 is
If it is less than 0.5mm, it is too thin and the protrusion 3 will be formed due to molding.
There is a risk of it breaking. Also, the wall thickness (t) is 1.5mm
If the thickness exceeds 100, it becomes too thick and difficult to mold, and a large amount of aluminum material is used, resulting in high costs. If the width (W) of the arched protrusion 3 is less than t (wall thickness), it will be too narrow and the heat exchange performance will deteriorate, and if it exceeds 10t (10 times the wall thickness), it will be too wide and the pressure loss will increase. . The height (H) of protrusion 3 is 2mm
If it is less than that, the heat exchange performance will deteriorate and the fluid passage will become narrow, making it difficult for the fluid to flow. If the height (H) of the protrusion 3 exceeds 10 mm, the pressure resistance will decrease, which is not preferable. Furthermore, if the pitch (P) of the protrusions 3 is less than 3 mm, it will be too narrow, resulting in large pressure loss and poor moldability. Moreover, if the pitch (P) exceeds 30 mm, the compressive strength will decrease and the heat exchange performance will deteriorate, which is not preferable.

The distance between adjacent protrusion rows R is zero in the illustration, but by providing a horizontal wall extending in the front-rear direction between the protrusion rows R, the spacing between the protrusion rows R is 10t or less. It may be done as follows.
If this interval exceeds 10 t, the fluid will flow easily and the heat exchange performance will be significantly reduced, which is not preferable.

Note that the cross-sectional dimensions of the arch-shaped projections 3a and 3b may be other shapes such as [shape and] shape or ⌒ shape and ) shape.

On the other hand, the second fluid flow path B includes both upper and lower flat plates 12,
A pair of front and rear spacer bars 15 made of extruded aluminum forming the front and rear side walls, and a louvered corrugate that is arranged between these front and rear spacer bars 15 and has an uneven part parallel to both spacer bars 15. - It is formed by the fins 16.

The plate-fin type heat exchanger 11 has a flat plate 1 made of an aluminum brazing sheet.
2, a flow path forming body 13 comprising a horizontal connecting wall portion 1 having left and right side walls 14, 14 and a large number of arch-shaped protrusions 3a, 3b having a cross section of approximately Λ-shape or approximately V-shape;
It can be manufactured by arranging the front and rear spacer bars 15 and the corrugated fins 16 in a polymerized state and joining them together by, for example, vacuum brazing. Since a brazing sheet is used as the flat plate 12, the tips of each arch-shaped protrusion 3a, 3b of the horizontal connecting wall 1 are connected to the flat plate 1 through the brazing material layer.
2, but in some cases protrusion 3
The tips of a, 3b and the flat plate 12 may be separated without being joined.

In this embodiment, an aluminum brazing sheet is used as the flat plate 12; however, the present invention is not limited to this; an aluminum plate can be used as the flat plate 12, and the left and right side walls 14, 14 of the flow path forming body 13 are It is also possible to form a brazing material layer on the upper and lower surfaces and on the upper and lower surfaces of the front and rear spacer bars 15 by coating with a brush or the like, and to join the entire heat exchanger 11 using this brazing material layer.

In the plate-fin type heat exchanger 11, both ends of the first fluid passage A through which oil flows are communicated with a header tank (not shown), and a pump having a predetermined discharge pressure flows into the passage A. Oil is made to flow in the middle of the left and right side walls 14, 14 of the path forming body 13 in a direction that coincides with the longitudinal direction of the many arch-shaped projections 3a, 3b of each projection row R. On the other hand, a second fluid flow path B through which air flows
Both ends are open so that air can flow through the second fluid flow path B by forced air blowing by a fan or by natural ventilation caused by running a vehicle or the like.

When oil flows in the first fluid flow path A, the oil flows in a direction that coincides with the longitudinal direction of the large number of arch-shaped projections 3a, 3b of each projection row R, so that the horizontal connecting wall of the flow path forming body 13 Oil hits all the arch-shaped protrusions 3a, 3b with a Λ-shaped cross section and a substantially V-shaped cross section provided in each protrusion row R of the part 1 from the front, and the flow of the oil is disturbed and the oil flows on both the left and right sides of each protrusion 3a, 3b. However, in each projection row R, a horizontal wall portion 2 of a predetermined width is interposed between the adjacent projections 3a and 3b as described above, and downward arches are provided on both left and right sides of the upward arch-shaped projection 3a. In addition, upward arch-shaped protrusions 3a are arranged on the left and right sides of the downward arch-shaped protrusion 3b, and one protrusion and two front and rear horizontal walls are provided on the left and right sides of each protrusion 3a, 3b. Since a wide space S corresponding to 100 mm is provided, it is very easy for oil to wrap around both the left and right sides of each protrusion 3a, 3b.
Therefore, pressure loss is small. Conversely, when viewed from the space S, the four sides of each space S are the protrusions 3a or 3b.
It is surrounded by protrusions 3a on the front side and on both left and right sides.
Alternatively, the oil that has bypassed 3b can be sufficiently mixed within each space S. The oil that has come into contact with the arch-shaped protrusion 3a having a roughly Λ-shaped cross section and has flowed around to both the left and right sides of these protrusions passes through the space S and flows downward into the fluid passage hole 4, and vice versa. The oil that hits the arch-shaped protrusion 3b and flows around to both the left and right sides of the arch-shaped protrusion 3b flows into the fluid passage hole 4 as an upward flow.
As a result, the flow of the oil is disturbed and the oil moves through the first fluid flow path A while being sufficiently stirred, thereby significantly increasing the heat exchange efficiency.

When the plate-fin type heat exchanger 11 of the above embodiment was actually used as an oil cooler, the heat dissipation performance (heat exchange performance) was the same or improved by 7% compared to the conventional oil cooler. Pressure drop decreased by 10-30%. Therefore, it is clear that a pump with a low discharge pressure can be used, and equipment costs and power costs can be reduced.

6 and 7 show a second embodiment of the invention. Here, the difference from the first embodiment is that the horizontal wall portion 2 is not provided between the arch-shaped protrusions 3a and 3b adjacent to each other in the front and rear of the protrusion row R. Even in the absence of the horizontal wall portion 2, the arch-shaped projections 3a and 3b of the projection rows R adjacent to each other on the left and right are firmly connected at the intersection F of the X shape when viewed from the side, as shown in FIG. There is.

The other points of the second embodiment are the same as those of the first embodiment, so the same parts are given the same reference numerals in the drawings.

The plate-fin heat exchanger 11 of each of the above embodiments is used as an oil cooler, for example, to cool engine oil, industrial machinery, or oil in various hydraulic systems.

In addition, in the plate-fin type heat exchanger 11 of the above embodiment, only the first fluid flow path A is connected to the upper and lower flat plates 12.
and a flow path forming body 13 having a horizontal connecting wall 1 having a large number of arch-shaped protrusions 3a, 3b having approximately Λ-shaped and approximately V-shaped cross sections and a fluid passage hole 4. The two-fluid flow path B may also be similarly formed by the upper and lower flat plates 12 and the flow path forming body 13. Also, contrary to what is shown in the figure, the first fluid flow path A
may be formed by the flat plate 12, a pair of spacer bars 15, and a corrugated fin 16, and the second fluid flow path B may be formed by the flat plate 12 and the flow path forming body 13.

Further, in the plate-fin heat exchanger 11 of the above embodiment, the first fluid flow path A and the second fluid flow path B are arranged perpendicularly, but both flow paths A, B
may be arranged parallel to each other. In this case, the two types of fluids in both channels A and B are caused to flow in parallel to each other or in opposite directions.

Further, the plate-fin type heat exchanger 11 of the above embodiment is a so-called horizontal oil cooler in which the first fluid flow path A is arranged horizontally.
The heat exchanger 11 may be a vertical oil cooler in which the first fluid flow path A is arranged vertically. Further, the heat exchanger 11 can be used not only for an oil cooler but also for various types of heat exchangers that exchange heat between a plurality of types of gas and fluid.

Effects of the Invention As described above, the present invention provides an aluminum plate/fin type heat exchanger having a first fluid flow path and a second fluid flow path alternately in the vertical direction separated by a flat plate. A flow path forming body made of extruded aluminum is interposed between the upper and lower flat plates of at least one of the flow path and the second fluid flow path, and the flow path forming body is connected to both left and right side walls. , and a horizontal connecting wall that connects these side walls, and the horizontal connecting wall includes a plurality of arch-shaped protrusions arranged in the front-rear direction and vertically protruding alternately and having approximately Λ-shaped and approximately V-shaped cross sections. The positions of the arch-shaped protrusions with approximately Λ-shaped cross sections and the arch-shaped protrusions with approximately V-shaped cross sections of the adjacent protrusion rows on the left and right are shifted, so that the arch-shaped protrusions with approximately Λ-shaped cross sections and the approximately V-shaped cross sections are formed. The arch-shaped protrusions of each row are arranged so as to be adjacent to each other on the left and right, and fluid passage holes are formed facing all the arch-shaped protrusions, and the longitudinal direction of the arch-shaped protrusions of each protrusion row is aligned with the left and right sides of the channel forming body. The fluid is made to flow in the longitudinal direction of the arch-shaped protrusions of each row of protrusions, and the wall thickness (t) of each arch-shaped protrusion is 0.5 to 1.5.
mm, width (W) is t~10t, height (H) is 2~
10 mm, and the pitch (P) between adjacent protrusions is 3 to 30 mm. According to the plate-fin type heat exchanger of this invention, the upper and lower flat plates, the left and right side walls, and the horizontal When fluid such as oil flows in the fluid channel formed by the channel forming body consisting of the connecting wall portion, the fluid such as oil flows in the longitudinal direction of the arched protrusion of each row of protrusions, Since the wall surface of each protrusion faces the direction of flow of fluid such as oil, all the arch-shaped protrusions with Λ-shaped and approximately V-shaped cross sections provided in each protrusion row of the horizontal connecting wall of the flow path forming body Fluid such as oil hits from the front, and the flow of oil and other fluid is disturbed and goes around both the left and right sides of each protrusion, but on both the left and right sides of each protrusion, there is one protrusion and two front and rear horizontal walls. Because a correspondingly wide space is opened,
Fluid such as oil can easily flow around the left and right sides of each protrusion, so pressure loss is small. In addition, fluid such as oil that has bypassed the protrusions can sufficiently mix within each space. The oil and other fluids that hit the arch-shaped protrusions and flow around to the left and right sides of these holes flow downward or upward into the fluid passage holes, and as a result, the oil and other fluids eventually become Because the flow is disturbed and moved through the fluid channel while being sufficiently stirred,
Heat exchange efficiency is significantly increased. Moreover, fluids such as oil flow easily and the pressure loss is very small, so there is no need to particularly increase the pump discharge pressure.
The equipment cost and power cost of the heat exchanger are low, making it very economical.

Further, the flow passage forming body of the heat exchanger has a horizontal side wall having left and right side walls thereof, and a plurality of rows of projections connecting these side walls and having a large number of arch-shaped projections having a cross section of approximately Λ-shape and approximately V-shape. Since it is a connecting wall and is made integrally from extruded aluminum, it has fewer parts, is lightweight, and can significantly shorten the time for setting parts, and can automate the setting. It's easy.

In addition, the flow path forming body is formed by forming a horizontal connecting wall portion of an extruded aluminum material, which is made up of left and right side walls and a horizontal connecting wall portion connecting these, by pressing or molding using a forming roll, so that the horizontal connecting wall portion has a cross section of approximately Λ. It is possible to easily form a plurality of protrusion rows consisting of a large number of arch-shaped protrusions each having a substantially V-shape.

Since the thickness (t), width (W), height (H) and pitch (P) of each arch-shaped projection are within a predetermined range, moldability is good, and the arch-shaped projection can be formed easily. can be carried out easily and reliably, and as a result, plate-fin type heat exchangers can be easily manufactured.Plate-fin type heat exchangers have high pressure resistance, and have low pressure loss and low pressure loss as mentioned above. This has the effect of ensuring excellent heat exchange performance.

[Brief explanation of drawings]

1 to 5 show a first embodiment of the present invention. FIG. 1 is a perspective view of the horizontal connecting wall portion of a plate-fin type heat exchanger, and FIG. FIG. 3 is a vertical partial sectional view of the heat exchanger, FIG. 4 is a sectional view taken along line 3--, and FIG. 5 is a sectional view taken along line 3--. be. FIG. 6 is a perspective view of the horizontal connecting wall portion of the heat exchanger of the second embodiment, and FIG. 7 is a partial sectional view of the same heat exchanger, which corresponds to FIG. 5. 1...Fin, 2...Horizontal wall part, 3a, 3b...
... Arch-shaped protrusion, 4... Fluid passage hole, R... Protrusion row, A... First fluid flow path, B... Second fluid flow path,
DESCRIPTION OF SYMBOLS 11... Heat exchanger, 12... Flat plate, 13... Channel forming body, 14... Left and right side walls, 15... Front and rear spacer bar, 16... Corrugated fin.

Claims (1)

[Claims] 1 In an aluminum plate fin type heat exchanger having a first fluid passage A and a second fluid passage B separated by a flat plate 12 alternately in the vertical direction, the first fluid passage A and the second fluid passage A channel forming body 13 made of extruded aluminum is interposed between the upper and lower flat plates 12, 12 of at least one of the channels B, and the channel forming body 13 is
Left and right side walls 14, 14 and these side walls 14, 1
4, and the horizontal connecting wall 1 is made up of a large number of arch-shaped protrusions 3a, 3b having approximately Λ-shaped and approximately V-shaped cross sections arranged in the front-rear direction and protruding vertically alternately. The positions of the arch-shaped protrusions 3a having a substantially Λ-shaped cross section and the arch-shaped protrusions 3b having a generally V-shaped cross section of the right and left adjacent protrusion rows R are shifted, resulting in an arch having a generally Λ-shaped cross section. The shaped protrusions 3a and the arch-shaped protrusions 3b having a substantially V-shaped cross section are arranged side by side adjacent to each other, and a fluid passage hole 4 is formed to face each of the arch-shaped protrusions 3.
The longitudinal direction of the arch-shaped protrusions 3a, 3b of each protrusion row R is made to match the longitudinal direction of the left and right side walls 14, 14 of the channel forming body 13, and the arch-shaped protrusions 3a, 3b of each protrusion row R are The fluid is made to flow in the longitudinal direction, and the wall thickness (t) of each arch-shaped protrusion 3 is 0.5 to 1.5 mm, the width (W) is t to 10 mm, and the height (H) is 2 to 10 mm. , and a plate-fin type heat exchanger in which the pitch (P) between the front and rear adjacent protrusions 3 is 3 to 30 mm.