JP2002048491A - Heat exchanger for cooling - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inhibit blowing noise while securing heat transfer performance and the drain property of condensed water in a finless-type heat exchanger for cooling. SOLUTION: A projection part 14 formed at heat transfer plates 12a and 12b is set to a flex shape being extended continuously in upper and lower directions, and the flex shape composes an eddy division means for dividing the connection of eddy along the longitudinal direction of the projection part at the rear end of the air flow of the projection part 14. Since the projection part 14 is in a shape being extended continuously in upper and lower directions, the condensed water of the heat exchanger for cooling can be unloaded downward smoothly along the projection part 14. Also, timing when an eddy is generated at the rear end of the airflow of the projection part 14 is shifted according to the flex shape of the projection part 14, thus dividing the connection of the eddy at the rear end of the airflow of the projection part 14.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a finless type cooling heat exchanger comprising only plate-like members constituting a cooling / heating fluid passage, and is suitable for use in, for example, a vehicle air conditioning evaporator. is there.

[0002]

2. Description of the Related Art In a conventional cooling heat exchanger, for example, a vehicle air conditioner evaporator, an air side is provided between tubes having a flat cross section formed by joining two plates in the middle. Corrugated fins with louvers are interposed to increase the heat transfer area. In this corrugated fin, the heat transfer coefficient on the air side is improved by reducing the thickness of the boundary layer using the tip effect of the louver.

[0003] In order to improve the heat transfer coefficient on the air side, louvers have recently been miniaturized to near the processing limit, and this has led to an increase in the number of processing steps for corrugated fins. Also,
Since the thin corrugated fins are mounted between the two plates constituting the tube, the assemblability is deteriorated.
Therefore, the presence of corrugated fins is a major obstacle to cost reduction and downsizing of the heat exchanger.

Japanese Patent Application Laid-Open No. 11-287580 discloses a finless type cooling heat exchanger which does not require fins such as corrugated fins and can secure the required heat transfer performance only by a heat transfer plate constituting a refrigerant passage. Has been proposed.

In this prior art, a plurality of protrusions are formed on each of a plurality of heat transfer plates, and a refrigerant passage for flowing a refrigerant is formed inside the protrusions. Facing the plate with a gap in between,
The gap constitutes a passage for air flowing outside the heat transfer plate, and the protruding portion acts as a turbulence generator for preventing turbulence of the air flow and causing turbulence.

According to this prior art, the heat transfer coefficient on the air side can be greatly improved by the fact that the projection itself constituting the refrigerant passage acts as a turbulence generator, so that no fin member is provided on the air side. , Required heat transfer performance can be secured.

[0007] Therefore, the heat exchanger can be constituted only by the heat transfer plate having the protruding portion constituting the refrigerant passage, and the heat exchanger is characterized in that the cost can be greatly reduced and the size of the heat exchanger can be reduced.

[0008]

However, the inventors of the present invention have conducted detailed experiments and studies toward the practical use of the above-mentioned prior art, and it has been found that in the above-mentioned prior art, an abnormal air flow occurs in the air-side passage. did.

It has been found that the generation of the abnormal fan noise is caused by a vortex generated on the trailing end side of the air flow of the protrusion constituting the refrigerant passage. In particular, if the protrusions constituting the refrigerant passage are linear and have the same height, vortices are simultaneously separated along the longitudinal direction of the protrusions on the rear end side of the protrusions. The generation and peeling of the air flow are connected along the longitudinal direction of the protruding portion, thereby amplifying the abnormal air flow.

As a countermeasure for reducing the abnormal noise of the blower, it is conceivable that the passage pitch, which is the interval between the refrigerant passages, is widened and the cross-sectional area of the air passage is enlarged to lower the passing wind speed. In such a measure, the heat transfer coefficient on the air side is reduced by lowering the wind speed, and the heat transfer area is reduced by increasing the passage pitch, thereby lowering the heat transfer performance.

In the above prior art, as another embodiment, there is disclosed a configuration in which two heat transfer plates are joined by intersecting a projecting portion inclined at a predetermined angle with respect to the air flow direction. However, according to this configuration, an intersection (cross rib shape) between the convex surfaces of the inclined protrusions is formed, so that in the cooling heat exchanger, condensed water stays at the intersection between the convex surfaces and increases ventilation resistance. The problem described above occurs.

In view of the above, the present invention provides a finless cooling heat exchanger composed of only plate-like members constituting a refrigerant passage, while ensuring heat transfer performance and drainage of condensed water. The purpose is to suppress abnormal ventilation noise.

[0013]

To achieve the above object, according to the first aspect of the present invention, a heat transfer plate (12a) is provided.
To 12c), a plurality of protrusions (14) having a shape extending continuously in the vertical direction are formed, and the protrusions (1) are formed.
4) The cold fluid passage (19, 2) through which the cold fluid flows.
0) to allow air to flow in a direction intersecting the direction of flow of the cooling fluid on the outer side of the protrusion (14), and furthermore, the length of the protrusion on the rear end side of the air flow of the protrusion (14). Vortex dividing means (14) for dividing the connection of vortices along the direction
b, 14c, 14d) to the heat transfer plates (12a-12)
c).

According to this, since the projecting portion (14) has a shape extending continuously in the vertical direction, an intersection (cross rib shape) between the convex surfaces of the inclined projecting portion is not formed. Therefore, there is no problem that the condensed water of the cooling heat exchanger stays at the intersection of the convex surfaces to increase the ventilation resistance.

In addition, the vortex dividing means allows the protrusion (1)
4) Simultaneous separation of vortices on the rear end side of the air flow can be suppressed, so that abnormal noise of the blowing can be reduced.

Specifically, the vortex dividing means can be constituted by providing the protruding portion (14) with a shape that bends in the vertical direction and extends, as in the second aspect of the invention.

According to this, the timing at which the vortex is generated on the rear end side of the air flow of the protruding portion (14) is shifted by the bent shape of the protruding portion (14) to disconnect the connection of the vortex on the rear end side of the air flow on the protruding portion. it can.

In particular, as in the third aspect of the present invention, by shifting the phases of the bent shapes of the plurality of protrusions (14), a change in the distance between the plurality of protrusions (14) can be changed. In this case, the air flow can be largely bent, whereby the effect of dividing the connection of the vortices can be enhanced, and the abnormal air blowing noise can be reduced more effectively.

Further, as in the fourth aspect of the present invention, the vortex dividing means may be constituted by changing the protrusion height of the protrusion (14) in the flow direction of the cooling and heating fluid.

According to this, the timing at which the vortex is generated on the rear end side of the air flow of the protruding portion (14) is shifted by changing the protruding height of the protruding portion (14), so that the vortex is generated on the rear end side of the air flow on the protruding portion. Can break connections.

Further, as in the fifth aspect of the present invention, the vortex dividing means may be constituted by partially providing a projection (14b) at the top of the convex surface of the projection (14).

According to this, the timing at which the vortex is generated on the rear end side of the air flow of the projecting portion (14) is shifted by the partial projection (14b) at the top of the convex surface of the projecting portion (14). The vortex connection on the side can be broken.

Further, as in the invention according to claim 6, the vortex dividing means is constituted by providing the projections (14d) projecting from the projecting portions (14) to at least one of the front and rear sides in the air flow direction at mutually shifted positions. May be.

Since the projections (14d) according to the sixth aspect are provided at positions shifted from each other, the projections (14d) do not abut each other in the air passage and block a part of the air passage. Therefore, even if the projections (14d) are formed, air and condensed water can be passed smoothly, and adverse effects on ventilation resistance and drainage can be reduced.

According to the present invention, the projecting portions (14) of the heat transfer plates (12a to 12c) are provided.
A vortex dividing means may be formed by providing a through hole (14c) through which air passes in the vicinity.

According to this, since the air flows through the through hole (14c) near the protruding portion (14), the generation of the vortex itself can be suppressed.

The reference numerals in the parentheses of the above means indicate the correspondence with the specific means described in the embodiments described later.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) First, a comparative example which is a premise of the first embodiment of the present invention will be described with reference to FIGS. This comparative example is a study of a prototype manufactured by the present inventors, and shows an example in which the present invention is applied to a vehicle air conditioning evaporator 10. Note that this comparative example is based on the above-described Japanese Patent Application Laid-Open No. 11-287.
The configuration is basically the same as that of the 580 publication. FIG. 1 is an exploded perspective view showing a configuration of a heat transfer plate at a refrigerant inlet / outlet side, and FIG. 2 is an exploded perspective view showing a configuration of a refrigerant passage of the entire evaporator. 3 to 5 show specific examples of the heat transfer plate.

The evaporator 10 has a flow direction A for air-conditioning air.
And the cross-flow direction B (the vertical direction shown in FIG. 2) in the heat transfer plate portion is configured as a cross-flow heat exchanger that is substantially orthogonal. In this evaporator 10, a core unit 11 for exchanging heat between air-conditioning air and a refrigerant (cooling fluid) is configured by simply stacking a number of heat transfer plates 12a, 12b, and 12c.

In the configuration example shown in FIGS. 1 and 2, a combination area X of the first heat transfer plate 12a and the second heat transfer plate 12b and a combination area Y of the first heat transfer plate 12a and the third heat transfer plate 12c are provided. Thus, the core unit 11 is constituted.

The heat transfer plates 12a, 12b,
12c is A3000 aluminum core material on both sides of A
It is made of a double-sided clad material in which a 4000 series aluminum brazing material is clad, and has a thickness t = 0.1 to 0.4 mm.
It is formed by press-molding a thin plate of the order. Each of the heat transfer plates 12a, 12b, and 12c has a substantially rectangular plane shape, and has the same outer dimensions. The length in the long side direction is, for example, 245 mm, and the width in the short side direction is, for example,
45 mm.

The specific shape of the heat transfer plates 12a, 12b, 12c is different for reasons such as establishment of a refrigerant passage, ease of assembling an evaporator, brazing, and drainage of condensed water. May have the same shape. Then, next, taking the first and second heat transfer plates 12a and 12b as an example, the specific punching shape will be described with reference to FIGS.
Each of the heat transfer plates 12a and 12b is formed by stamping out a protruding portion (rib) 14 from a flat substrate portion 13. The protruding portion 14 serves as a refrigerant passage (cooling fluid passage) through which the low-pressure side refrigerant after passing through the pressure reducing means (expansion valve or the like) of the refrigeration cycle flows.
19, 20 and the heat transfer plate 12
Longitudinal direction (in other words, a direction substantially orthogonal to the air flow direction A)
And a shape that extends in parallel to the shape. Also, the protrusion 14
Has a substantially trapezoidal shape as shown in FIGS.

As shown in FIGS. 3 to 5, the number of the protrusions 14 is five in each of the heat transfer plates 12a and 12b.
2a, 12c), the projecting positions of the protrusions 14 are shifted from each other in the air flow direction A, and the other heat transfer plate is located at the center position of the protrusion pitch P1, which is the interval between the protrusions 14 of one of the heat transfer plates. Are located.

Therefore, the heat transfer plates 12a, 12b
(Or 12a, 12c) are opposed to each other so that the projections 14 face outward, and the substrates 13 are brought into contact with each other and joined together.
Is sealed by the substrate portion 13 of the heat transfer plate on the other side. Therefore, the refrigerant passages 19 and 20 can be formed between the inner surface side of each protrusion 14 and the substrate portion 13 of the mating heat transfer plate.

That is, each of the heat transfer plates 12a to 12c
In the width direction (air flow direction A), inside the protruding portion 14 located on the windward side from the central portion C (FIGS. 4 and 5),
A refrigerant passage 20 on the windward side is formed, and each heat transfer plate 12a
A refrigerant passage 19 on the leeward side is formed inside the protruding portion 14 located on the leeward side of the central portion C in the width direction of 12c.

As shown in FIGS. 4 and 5, the refrigerant passage 20 on the leeward side and the refrigerant passage 19 on the leeward side are connected to both heat transfer plates 12.
a, 12b (or 12a, 12c)
Each is formed in parallel.

On the other hand, the heat transfer plates 12a to 12c are divided into heat transfer plate width directions (air flow direction A) at both ends in a direction B (longitudinal direction of the heat transfer plate) perpendicular to the air flow direction A. The tank portions 15 to 18 are formed two by two. The tank portions 15 to 18 are stamped in the same direction as the projecting portions 14 and 140 on each of the heat transfer plates 12a to 12c, and the ejection height is the same height h (FIG. 7) as the projecting portions 14 and 140. is there.

As described above, the tank portions 15 to 18 are punched out in the same direction as the projecting portion 14, and the concave portions formed by the punching of the both ends in the longitudinal direction of the projecting portion 14 are formed.
Because it is made to be continuous with the embossed concave shape of 18,
Both ends of the leeward refrigerant passage 20 are located on the leeward tank portion 1.
Both ends of the leeward side refrigerant passage 19 communicate with the leeward side tank portions 15 and 16.

The tank portions 15 and 17 at the upper end of the heat transfer plate and the tank portions 16 and 18 at the lower end of the heat transfer plate.
Is divided into two in the width direction of the heat transfer plate. Although the embossed shapes of the tank portions 15 to 18 are circular in the illustrated example of FIG. 3, each of the tank portions 1 to 18 is similar to the illustrated example of FIGS.
5 to 18 may be formed in a substantially oval shape. Further, the embossed shape of each of the tank portions 15 to 18 may be substantially D-shaped.

Communication holes 15a to 18a are opened at the center of each of the tank portions 15 to 18. These communication holes 15a-1
8a allows the flow paths of the tank portions 15 to 18 to communicate with each other between adjacent heat transfer plates in the left-right direction (heat transfer plate stacking direction) shown in FIGS. That is, the projected top portions of the adjacent tank portions 15 to 18 are in contact with and joined to each other to form the communication holes 15a.
-18a are mutually communicated.

As shown in FIGS. 1 and 3, in each of the heat transfer plates 12a to 12c, the leeward tank portions 15, 16 are compared with the leeward tank portions 17, 18.
Is reduced by a predetermined dimension. As a result, as will be described later, the ventilation area in the leeward side region of the core portion 11 can be enlarged as compared with the leeward side region, and the drainage of condensed water can be improved.

The leeward side refrigerant passage 19 is an inlet side refrigerant passage, as will be described later.
0 is an outlet side refrigerant passage. And windward (exit side)
The refrigerant passage 20 has a higher dryness of refrigerant compared with the refrigerant passage 19 on the leeward side (inlet side) and increases the specific volume of the refrigerant. Enlarging the area from the leeward side (inlet side) tank sections 15, 16 is also advantageous for reducing the pressure loss on the refrigerant side.

Further, small projections 14a projecting in the width direction of the heat transfer plate (air flow direction A) are formed from the side surfaces of the projecting portions 14 of the heat transfer plates 12a to 12c. The plurality of small projections 14a are provided at the same position in the longitudinal direction of each projection 14 (four in the example of FIG. 4).

For this reason, two adjacent heat transfer plates 1
The small projections 14a of the small projections 2a, 12b or 12a, 12c are brought into contact with each other, and the heat transfer plates 12a to 12c are joined to each other with a pressing force in the heat transfer plate laminating direction acting on the contact portions of the small projections 14a. can do.

Thus, the pressing force acts on the intermediate portion (the portion where the refrigerant passages 19 and 20 are formed) of the heat transfer plate 12 except for the tank portions 15 to 18 at both ends in the longitudinal direction. The entire board portions 13 can be reliably brought into contact with each other, and the contact surfaces of the board portions 13 can be satisfactorily brazed. Therefore, leakage of the refrigerant from the refrigerant passages 19 and 20 due to poor brazing can be prevented.

Incidentally, each of the heat transfer plates 12a to 12c
In the width direction (air flow direction A), a plurality of protrusions 1
As shown in FIGS. 4 and 5, as shown in FIGS. 4 and 5, the formation positions of the adjacent heat transfer plates 12 a to 12 c are shifted from the adjacent heat transfer plates 12 a to 12 c. Can be located at the concave portion formed by the substrate portion 13.

As a result, a gap is always formed between the top of the protruding portion 14 on the convex side and the concave portion of the substrate portion 13 of the other adjacent heat transfer plates 12a to 12c. This gap is a gap size minus the plate thickness minutes from launch height h of the protrusions 14 is, by this clearance, as the entire length of the heat transfer plate width direction (air flow direction A) of the arrow A ₁ An air passage meandering in a wave shape is continuously formed.

[0048] Thus, the conditioned air is blown in the direction of arrow A, the air passage arrow A ₁ in as the two while meandering in the corrugated heat transfer plates 12a, 12b or 12a, 1
2c.

Next, a portion for allowing the refrigerant to flow into and out of the core portion 11 will be described. As shown in FIGS.
Heat transfer plates 12 are provided at both ends in the heat transfer plate stacking direction.
End plate 2 having the same size as a to 12c
1, 22 are provided. This end plate 21,
Each of the heat transfer plates 22 abuts on the projecting portion 14 of the heat transfer plate 12a and the convex side of the tank portion 15-18.
It has a flat plate shape to be joined to 2a.

1 and 2, a refrigerant inlet hole 21a and a refrigerant outlet hole 21b are formed near the lower end of the end plate 21, and the refrigerant inlet hole 21a is located downstream of the lower end of the heat transfer plate 12a. The refrigerant outlet hole 21b communicates with the communication hole 16a of the side tank portion 16, and the communication hole 18a of the windward tank portion 18 at the lower end of the heat transfer plate 12a.
Communicate with Also, the refrigerant inlet hole 2 of the end plate 21
A refrigerant inlet pipe 23 and a refrigerant outlet pipe 24 are respectively joined to 1a and the refrigerant outlet hole 21b.

One end plate 21 has a refrigerant inlet,
For joining with the outlet pipes 23 and 24, it is made of a double-sided clad material in which an A4000-based aluminum brazing material is clad on both sides of an A3000-based aluminum core like the heat transfer plates 12a to 12c. The other end plate 22 has an A4000-based aluminum core material on only one surface (the surface on the side joined to the heat transfer plate 12a).
It consists of a single-sided clad material clad with an aluminum brazing material. Further, both end plates 21 and 22 have a plate thickness t larger than the heat transfer plate 12 (for example, the plate thickness t =
(About 1.0 mm) to improve the strength.

A gas-liquid two-phase refrigerant decompressed by a decompression means such as an expansion valve (not shown) flows into the refrigerant inlet pipe 23, and a refrigerant outlet pipe 24 is connected to a compressor suction side (not shown). The gas refrigerant evaporated in the step is guided to the compressor suction side.

In each of the heat transfer plates 12a to 12c,
Since the refrigerant from the refrigerant inlet pipe 23 flows into the leeward-side refrigerant passage 19, the leeward-side refrigerant passage 20 constitutes an inlet-side refrigerant passage in the refrigerant passage of the entire evaporator. The refrigerant passing through the refrigerant passage 19 (side) flows into the refrigerant outlet pipe 24 and flows out to the refrigerant outlet pipe 24, so that an outlet-side refrigerant passage is formed.

Next, the refrigerant passage as the entire evaporator 10 will be described with reference to FIG. 2. First, in the left and right direction (heat transfer plate laminating direction) in FIGS. In the half region Y on the side of the other end plate 22, a large number of sets are laminated with the two heat transfer plates 12 a and 12 c as one set. The core portion 11 is formed by joining the heat transfer plates.

Then, of the tank sections 15 to 18 located at the upper and lower ends of the evaporator 10, the tank section 15 on the leeward side,
16 constitutes a refrigerant inlet side tank part, and the windward side tank parts 17 and 18 constitute a refrigerant outlet side tank part. The lower refrigerant inlet side tank portion 16 on the leeward side is separated from the heat transfer plate 12 by a partition portion 27 disposed at an intermediate position (a boundary portion between the region X and the region Y) in the laminating direction. X side flow path) and FIG. 2 right side flow path (area Y side flow path)
And is divided into.

Similarly, the lower coolant outlet side tank portion 18 on the windward side is also divided by the partition portion 28 disposed at the intermediate position, similarly to the left flow path in FIG. 2 (the flow path on the area X side) and the right flow path in FIG. It is partitioned into a flow path (a flow path on the area Y side). These partition portions 27 and 28 are connected to the heat transfer plates 12a to 12
Of c, only the heat transfer plate located at the corresponding site can be easily configured by using a blind lid-shaped one in which the communication holes 15a and 18a of the tank portions 15 and 18 are closed.

According to the configuration of the refrigerant passage shown in FIG. 2, the low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve enters the lower inlet side tank portion 16 on the leeward side from the refrigerant inlet pipe 23 as shown by an arrow a. Since the flow path of the inlet side tank portion 16 is divided into left and right regions X and Y by the partition portion 27, the refrigerant enters only the flow region of the left side region X of the inlet side tank portion 16.

Then, in the left side region X of FIG. 2, the refrigerant rises as indicated by an arrow b in the refrigerant passage 19 formed by the leeward-side protrusions 14 of the heat transfer plates 12a and 12b, and the upper inlet-side tank 15 to go into. Next, the refrigerant moves the upper inlet side tank portion 15 to the right side area Y in FIG.
And moves down the refrigerant passage 19 formed by the leeward projections 14 of the heat transfer plates 12a and 12c as shown by the arrow d, and enters the flow path in the right region Y of the lower inlet tank 16. .

Here, a communication passage for directly communicating the tank portions 16 and 18 is provided at an intermediate position between the tank portions 16 and 18 below the third heat transfer plate 12c incorporated in the right side area Y. Since the cooling medium 120 (see FIG. 2) is formed, the refrigerant in the right side area Y of the tank section 16 then passes through the communication path 120, and the lower outlet side tank section 18 on the windward side as shown by the arrow e. to go into.

Here, since the flow path of the outlet side tank portion 18 is divided into left and right regions X and Y by the partition portion 28, the refrigerant enters only the flow region of the right side region Y of the outlet side tank portion 18. . Next, in the right side area Y of the tank portion 18, the refrigerant is supplied to the windward projecting portions 1 of the heat transfer plates 12a and 12c.
4 rises in the refrigerant passage 20 as shown by the arrow f and enters the right side region Y of the upper outlet side tank portion 17.

From the right side area Y, the refrigerant moves from the upper outlet side tank portion 17 to the left side area X in FIG. 2 as indicated by an arrow g, and is formed by the windward projection 14 of the heat transfer plates 12a and 12b. Down the refrigerant passage 20 as shown by the arrow h, and enters the flow path in the left region X of the lower outlet side tank portion 18. The refrigerant flows to the left side in the outlet side tank portion 18 as shown by an arrow i, and flows out of the evaporator from the refrigerant outlet pipe 24.

In the evaporator 10 shown in FIGS. 1 and 2, the refrigerant passage is configured as described above, and the components shown in FIGS. 1 and 2 are stacked in a state where they are in contact with each other. The brazed state is held by a suitable jig and carried into a brazing heating furnace, where the assembled body is heated to the melting point of the brazing material to braze the assembled body integrally. Thereby, the assembly of the evaporator 10 can be completed.

In this integral brazing, two adjacent heat transfer plates 12a, 12b or 12a, 12a
The small protrusions 14a of FIG. 3c are brought into contact with each other (see FIG. 5), and the pressing force in the heat transfer plate laminating direction is applied to the contact portions of the small protrusions 14a by the jig.
2a to 12c can be joined to each other.

Next, the operation of the evaporator 10 will be described. The evaporator 10 is housed in an air-conditioning unit case (not shown) with the vertical direction of FIGS. Air is blown in the A direction.

When the compressor of the refrigeration cycle operates, the gas-liquid 2 on the low pressure side, which has been reduced in pressure by an expansion valve (not shown).
The phase refrigerant flows according to the above-described passage configurations indicated by arrows a to i in FIG. On the other hand, the heat transfer plates 12a to 12
The gap formed between the c outer surface protrusion protrudes in a convex shape on the side 14, 140 of the substrate portion 13, the arrow A ₁ in FIG. 4 over the entire length of the heat transfer plate width direction (air flow direction A) An air passage meandering like a wave is formed continuously.

[0066] As a result, conditioned air, between the two heat transfer plates 12a and 12b while meandering the air passage in a wave as indicated by arrow A ₁ or 12 that is blown in the direction of arrow A
a and 12c, and the refrigerant absorbs latent heat of vaporization and evaporates from the flow of the air, so that the conditioned air is cooled and becomes cool air.

At this time, with respect to the flow direction A of the conditioned air,
By disposing the inlet-side refrigerant passage 19 on the leeward side and the outlet-side refrigerant passage 20 on the leeward side, the refrigerant inlet / outlet with respect to the air flow has a counterflow relationship.

Further, on the air side, the air flow direction A is perpendicular to the longitudinal direction of the protrusion 14 of the heat transfer plates 12a to 12c (the refrigerant flow direction B in the refrigerant passages 19 and 20). Since the protruding portions 14 and 140 form a convex surface (heat transfer surface) that protrudes orthogonally to the air flow, the air protrudes orthogonally to the protruding portions 14 and 140.
The straight shape is hindered by the convex shape.

For this reason, the flow of the air flow is turbulent and becomes a turbulent state, so that the heat transfer coefficient on the air side can be remarkably improved. Here, the core portion 11 is formed of the heat transfer plates 12a to 12a.
c, the heat transfer area on the air side is greatly reduced as compared with a normal evaporator having a conventional fin member. Since the efficiency is dramatically improved, the reduction in the air-side heat transfer area can be compensated for by the improvement in the air-side heat transfer coefficient, and the required cooling performance can be secured.

By way of detailed examination of the comparative example described above, as shown in FIG.
The main flow E is located at the rear end D of the air flow of the protrusion 14 constituting
In addition to the generation of a peeling layer peeled from the substrate, a vortex is generated in the peeling layer. Moreover, since the protrusions 14 extend linearly and at the same height in the direction orthogonal to the air flow direction A, vortices are generated at the same timing at the rear end D of the protrusion 14 at the same time. I do. It has been found that vortices connected along the longitudinal direction of the protruding portion 14 are generated at the same time, thereby amplifying abnormal blast noise.

Therefore, in the first embodiment, the timing of the air flowing over the protruding portion 14 is shifted in the longitudinal direction of the protruding portion 14 to cut off the connection of the vortices, thereby reducing the noise of the blowing air. FIGS. 7 to 9 are views of the first embodiment corresponding to FIGS. 3 to 5 of the comparative example described above, in which the shape of the protruding portion 14 is bent in a meandering shape in the longitudinal direction, that is, the refrigerant flow direction B. I have.

According to this, the timing of the air flow over the projecting portion 14 is not the same in the longitudinal direction of the projecting portion 14 and is shifted according to the meandering bent shape, so that the vortex at the rear end D of the air flow of the projecting portion 14 is formed. Generation (peeling)
Timing also shifts. In addition, since the meandering bent shape induces a velocity component in the refrigerant flow direction (vertical direction in FIG. 7) into the air flow, the air flow is disturbed and the cooperation of the vortices is hindered.

As a result, since the connection of the vortices can be cut off to prevent the amplification of the fan noise, the fan noise can be reduced.

Further, according to the first embodiment, it is not necessary to increase the passage pitch P2, which is the distance between the refrigerant passages 19 and 20, so that there is no problem of a decrease in heat transfer performance due to the enlargement of the passage pitch P2.

Next, the drainage of condensed water of the evaporator 10 will be described. In the evaporator 10, as shown in FIGS. 1 and 2, the longitudinal direction of the heat transfer plates 12a to 12c (projection 14) is the vertical direction. It is arranged and actually used. Therefore, when the evaporator 10 is in use, the heat transfer plate 1
A gap (see FIGS. 8 and 9) extending in the longitudinal direction (vertical direction) can be continuously formed between 2a to 12c.

In this case, the projecting portion 14 maintains a continuously extending shape only by bending in a meandering shape in the longitudinal direction (vertical direction). (Cross rib shape) is not formed. Therefore, it is possible to continuously form a path along which the condensed water falls along the longitudinal direction (vertical direction) of the protrusion 14. Therefore, the condensed water generated on the surfaces of the heat transfer plates 12a to 12c can be smoothly dropped downward by a path extending continuously in the vertical direction.

Although a part of the condensed water tends to move to the leeward side due to the wind pressure of the blown air, according to the present embodiment, in any of the heat transfer plates 12a to 12c,
The diameters of the leeward side tank portions 15, 16 are made smaller by a predetermined size than the leeward side tank portions 17, 18. Thereby, the ventilation area in the leeward side region can be enlarged in the core portion 11 as compared with the leeward side region, and the air flow velocity in the leeward side region can be reduced.

Therefore, even if a portion of the condensed water moves to the leeward side, the scattering of the condensed water to the downstream side from the leeward ends of the heat transfer plates 12a to 12c can be effectively prevented by the decrease in the air flow velocity. Can be suppressed.

(Second Embodiment) In the first embodiment, all of the plurality of protrusions 14 are bent in a meandering shape as shown in FIG. In FIGS. 10 to 12, among the plurality of protrusions 14, for example, only the protrusion 14 at the center in the air flow direction A is formed in a meandering shape. Even in this case, the effect of reducing the abnormal noise of the blast can be exhibited.

(Third Embodiment) In the first and second embodiments, the phase of the bent shape of the plurality of projections 14 (the phase of the unevenness)
13 to 14 in the third embodiment.
As shown in (a) and (b), the phases (bent phases) of the bent shapes of the plurality of protrusions 14 are shifted. More specifically, the phases of the bent shapes are shifted (reversed) such that the bent convex portions and the convex portions and the concave portions and the concave portions of the respective projecting portions 14 face each other in the longitudinal direction of the projecting portions.

When the phases of the concave and convex portions of the bent shape are shifted from each other as in the third embodiment, the abnormal noise of the blowing air is further reduced as compared with the case where the phases of the concave and convex portions of the bent shape are matched as in the first embodiment. It can be reduced effectively.

The reason for this will be described with reference to FIGS. 15A to 15D. FIGS. 15A and 15B show the case of the first embodiment, and FIGS. 15C and 15D show the case of the third embodiment. In the case of the embodiment, the bending width W of the bent shape of each projection 14 is the same value (for example, 1 mm).

In the first embodiment shown in FIGS. 15 (a) and 15 (b), since the phases of the concave-convex concave and convex coincide with each other, each of the opposed projections forming an air passage meandering in the heat transfer plate laminating direction. The distance between the portions 14, that is, the projecting portion 1 of the hatched portion
The distance between 4 and the protrusion 14 of the fine dot portion is the same at any portion in the longitudinal direction of the protrusion. For this reason, in the first embodiment, air flows linearly in a direction orthogonal to the longitudinal direction of the protruding portion as indicated by an arrow a1 in FIG. 15B.

On the other hand, the third of FIGS. 15C and 15D
In the embodiment, since the phases of the concave and convex portions of the bent shape are shifted (reversed), an air passage meandering in the heat transfer plate laminating direction is formed.
In other words, the interval between the hatched projections 14 and the small dot projections 14 is not constant in the longitudinal direction of the projections, and the wide portions Y1 and the narrow portions Y2 are alternately formed in the longitudinal direction of the projections.

As a result, the air flow tends to pass through the wide-spaced portion Y1, which is a portion having a small ventilation resistance, so that the air flow also occurs in FIG.
It meanders (bends) as indicated by arrow a2 in (d). By the meandering of the air flow in the longitudinal direction of the protruding portion, the connection of the vortices in the longitudinal direction of the protruding portion, the amplification can be more reliably cut off, and the effect of reducing the abnormal noise of the ventilation can be improved as compared with the first embodiment.

(Fourth Embodiment) In all of the first to third embodiments, the bent shapes of the plurality of protrusions 14 are the same, but in the fourth embodiment, as shown in FIGS. A pair of heat transfer plates 12a, 12b (12c)
Of the heat transfer plate 12a and the protrusion 1 of the other heat transfer plate 12b (12c).
4 is different from the bent shape.

More specifically, one of the heat transfer plates 12
a, the interval between the projections and depressions of the bent portion (solid line shape in FIG. 16) of the other heat transfer plate 12b (12c) is reduced. I have to. Even if the bent shape of the protruding portion 14 is changed in this manner, it is possible to suppress the connection of the vortex at the rear end portion D of the air flow and to exert the effect of reducing the abnormal noise of the blower.

(Fifth Embodiment) In all of the first to fourth embodiments, the side surfaces before and after the air flow in the plurality of protrusions 14 of each heat transfer plate 12a, 12b (12c) are both bent. In the fifth embodiment, as shown in FIGS. 19 to 21, of the side surfaces before and after the air flow in each projection 14, only the side surface on the rear end side of the air flow has a bent shape, and the side surface on the front end side of the air flow has a linear shape. . In this way, even when only the side surface on the rear end side of the air flow is bent, the connection of the vortex at the rear end portion D of the air flow can be suppressed, and the effect of reducing the abnormal noise of the blower can be exhibited.

(Sixth Embodiment) FIGS. 22 and 23 show a sixth embodiment, in which the heat transfer plates 12a and 12b (12c) are used.
A meandering bent shape is provided only in a part of the plurality of protrusions 14 in the longitudinal direction, and the other part in the longitudinal direction is linear. Even with such a bent shape, it is possible to suppress the connection of the vortex at the rear end portion D of the air flow and to exert an effect of reducing the abnormal noise of the blower.

(Seventh Embodiment) FIGS. 24 to 26 show a seventh embodiment in which the heat transfer plates 12a, 12b (12c
The protrusion height of the protrusion 14 is partially changed in the longitudinal direction of the protrusion (the refrigerant flow direction).

More specifically, as shown in the sectional views of FIGS. 25 and 26, the protrusion height of the protrusion 14 of each of the heat transfer plates 12a, 12b (12c) is set to h1 in the longitudinal direction of the protrusion (the refrigerant flow direction). And h2 (h1> h2).

As described above, even if the ejection height of the projecting portion 14 is partially changed, simultaneous generation of vortices at the rear end portion D of the air flow can be suppressed, and the effect of reducing abnormal noise of the blowing can be exhibited.

(Eighth Embodiment) FIGS. 27 to 29 show an eighth embodiment in which the heat transfer plates 12a, 12b (12c
The protrusion 14b is partially provided at the top of the convex surface of the protrusion 14 so that the height of the protrusion 14 is partially changed in the longitudinal direction of the protrusion.

More specifically, the projection 14b is
The projections 14 are elongated rectangles extending in the longitudinal direction of the projections.
The length L1 of b is, for example, about 6 mm, and the predetermined interval L
2 (for example, about 4 mm), and a large number of protrusions 14 b are provided on the convex top of the protrusion 14. As described above, even when the protrusion 14b is partially provided at the top of the convex surface of the protruding portion 14, the connection of the vortex at the rear end D of the air flow can be suppressed, and the effect of reducing the abnormal noise of the blowing can be exhibited.

(Ninth Embodiment) FIGS. 30 and 31 show a ninth embodiment, in which the heat transfer plates 12a, 12b (12c) are used.
A through hole 14c is provided in a portion of the substrate portion 13 on the rear end side of the protruding portion 14 on the air flow side.

More specifically, the through hole 14c is
4 is a long and narrow rectangular shape along the longitudinal direction.
The length L3 of 4c is, for example, about 6 mm, and a large number of through-holes 14c are provided at a portion on the rear end side of the protruding portion 14 in the air flow with a predetermined interval L4 (for example, about 4 mm).
Further, in the arrangement example of FIG. 30, the length L3 of the through hole 14c is larger than the interval L4, and the portion of the through hole 14c and the portion where the through hole 14c is not provided (the portion of the interval L4) in the air flow direction A. The through holes 14c are arranged in a staggered arrangement so as to be alternately formed.

In the portion where the through hole 14c is formed,
Is generated, and the generation of the vortex can be suppressed by the air flow. Therefore, the configuration of the ninth embodiment can also exert the effect of reducing the abnormal noise of the blower.

(Tenth Embodiment) FIGS. 32 to 34 show a tenth embodiment.
In the embodiment, the protrusion 1 protrudes from each protrusion 14 of each heat transfer plate to the rear end side of the air flow or the front end side of the air flow.
4d, and the projections 14d are arranged at positions offset from each other (offset positions) between the opposed heat transfer plates forming the air passage.

By the way, the small projections 14a described in the comparative example of the first embodiment are arranged at positions where they contact each other between the opposed heat transfer plates forming the air passage as shown in the sectional view of FIG. I have. Thus, the small projections 14a apply the pressing force in the heat transfer plate laminating direction to the entire joint surface of the heat transfer plate at the time of brazing, thereby improving the brazing property.

Therefore, the contact portion between the small projections 14a partially blocks the air passage, so that if the number of the formed small protrusions 14a is increased, the ventilation resistance is increased and the drainage property is deteriorated.

On the other hand, the protrusion 14d of the tenth embodiment
Are arranged at positions offset from each other (offset positions) between the opposing heat transfer plates that form the air passages, so that there is no increase in ventilation resistance or deterioration of drainage, and the effect of reducing the abnormal noise of the blower is reduced. Can be demonstrated.

(Other Embodiments) The present invention is not limited to the above-described embodiments, but can be variously modified as follows.

Although the third to tenth embodiments have described the case where the technical means for reducing the abnormal noise of the ventilation is provided corresponding to each of the large number of projections 14, the same as in the second embodiment. Also in the third embodiment to the tenth embodiment, the technical means of each embodiment may be applied to only some of the protrusions 14 among the many protrusions 14.

The first to tenth projections 14
Without uniformly applying any one technical means of the embodiment,
The technical means of each embodiment may be implemented in combination with a plurality of projecting portions 14.

In each of the above embodiments, the heat transfer plate 12
Although the present invention is applied to the evaporator 10 through which the low-temperature refrigerant on the low pressure side of the refrigeration cycle flows through the refrigerant passages 19 and 20, the refrigerant passages (cold heat fluid passages) 19 and 20 of the heat transfer plate 12 are replaced with other refrigerant passages. The present invention can also be applied to a cooling heat exchanger through which a type of cold fluid, for example, cold water flows.

In the field of heat exchangers, it is a well-known technique to bend a single plate material having a size and a shape corresponding to two heat transfer plates to form a cold / hot fluid passage. Also in the present invention, as described above, one plate material is bent to form two heat transfer plates 12a and 12a.
b, forming members corresponding to 12a and 12c, and
Refrigerant passages (cold and hot fluid passages) 19 and 20 may be formed between the bent heat transfer plates.

Further, it is also possible to integrally connect a required number of the bent plate units via a narrow connecting portion.

Therefore, the term “a plurality of heat transfer plates” in the present specification is not limited to a plurality of completely separated heat transfer plates disclosed in each of the above-described embodiments, but may be a single heat transfer plate. It is used to include a plate formed by bending a heat transfer plate.

In each embodiment, the heat transfer plates 12a to 12a
12c and the protruding portion 14 are arranged so as to extend in the up-down direction. However, the up-down direction is not limited to the vertical direction with respect to the horizontal plane. 12c and the protruding portion 14 may be arranged slightly inclined from the vertical direction.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view showing a heat exchanger configuration of a comparative example which is a premise of the first embodiment.

FIG. 2 is an exploded perspective view showing a refrigerant passage of a comparative example of FIG.

FIG. 3 is a plan view of a heat transfer plate in the comparative example of FIG.

FIG. 4 is a sectional view taken along line AA of FIG. 3;

FIG. 5 is a sectional view taken along line BB of FIG. 3;

FIG. 6 is an explanatory diagram of an air flow behavior in the comparative example of FIG.

FIG. 7 is a partial plan view of the heat transfer plate in the first embodiment.

FIG. 8 is a sectional view taken along line AA of FIG. 7;

FIG. 9 is a sectional view taken along line BB of FIG. 7;

FIG. 10 is a partial plan view of a heat transfer plate according to a second embodiment.

11 is a sectional view taken along line AA of FIG.

FIG. 12 is a sectional view taken along line BB of FIG. 10;

FIG. 13 is a partial plan view of a heat transfer plate according to a third embodiment.

14A is a cross-sectional view taken along the line AA of FIG. 13, and FIG. 14B is a cross-sectional view taken along the line BB of FIG.

FIG. 15 is an explanatory diagram of a difference in operation between the first embodiment and the third embodiment.

FIG. 16 is a partial plan view of a heat transfer plate according to a fourth embodiment.

FIG. 17 is a sectional view taken along line AA of FIG. 16;

FIG. 18 is a sectional view taken along line BB of FIG. 16;

FIG. 19 is a partial plan view of a heat transfer plate according to a fifth embodiment.

FIG. 20 is a sectional view taken along line AA of FIG. 19;

21 is a sectional view taken along the line BB of FIG.

FIG. 22 is a partial plan view of a heat transfer plate according to a sixth embodiment.

23 is a sectional view taken along line AA of FIG.

FIG. 24 is a partial plan view of a heat transfer plate according to a seventh embodiment.

25 is a sectional view taken along line AA of FIG. 24.

26A is a sectional view taken along line BB of FIG. 24, and FIG. 26B is an enlarged view of a portion C of FIG.

FIG. 27 is a partial plan view of a heat transfer plate according to the eighth embodiment.

28A is a sectional view taken along line AA of FIG. 27, and FIG. 28B is a sectional view taken along line BB of FIG.

29 (a) is a cross-sectional view taken along the line CC of FIG. 27, (b) is a cross-sectional view taken along the line DD of FIG. 27, (c) is a partially enlarged view of (a),
(D) is a partially enlarged view of (b).

FIG. 30 is a partial plan view of a heat transfer plate according to a ninth embodiment.

31 is a sectional view taken along line AA of FIG. 30.

FIG. 32 is a partial plan view of a heat transfer plate according to the tenth embodiment.

FIG. 33 is a sectional view taken along line AA of FIG. 32;

FIG. 34 is a sectional view taken along line BB of FIG. 32;

[Explanation of symbols]

12a to 12c: heat transfer plate, 14: protrusion, 15 to 15
18: tank part, 19, 20 ... refrigerant passage.

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Hiroshi Hamasaki 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Eiichi Torigoe 1-1-1, Showa-cho, Kariya-shi, Aichi Co., Ltd. Inside DENSO (72) Inventor Yuji Nagata 41, Chukumi Yokomichi, Oji, Nagakute-cho, Aichi-gun Aichi Prefecture Inside Toyota Central R & D Laboratories Co., Ltd. -1 F-term in Toyota Central R & D Laboratories, Inc. (Reference) 3L103 AA35 AA39 BB38 CC18 CC23 DD57

Claims (7)

[Claims] A plurality of protrusions (1) having a shape extending continuously in a vertical direction are formed on heat transfer plates (12a to 12c).
4) and a cooling fluid passage (19, 20) through which a cooling fluid flows inside the projection (14), and a flow direction of the cooling fluid on the outside of the projection (14). Vortex dividing means (14b, 14c, 14d) for allowing air to flow in the direction intersecting, and for breaking the vortex connection along the longitudinal direction of the protruding portion at the rear end side of the air flow of the protruding portion (14). The heat transfer plate (12
a to 12c), wherein the heat exchanger for cooling is provided. 2. The cooling heat exchanger according to claim 1, wherein the vortex dividing means is formed by providing the protrusion (14) with a shape that bends and extends in the vertical direction. 3. The cooling heat exchanger according to claim 2, wherein the phases of the plurality of protrusions are shifted from each other. 4. The heat exchange for cooling according to claim 1, wherein the vortex dividing means is configured by changing a protrusion height of the protrusion (14) in a flow direction of the cooling fluid. vessel. 5. The cooling heat exchanger according to claim 1, wherein the vortex dividing means is constituted by partially providing a projection (14b) on the convex top of the projection (14). . 6. A plurality of projections (14) projecting from the projections (14) to at least one of front and rear directions in the flow direction of the air.
The heat exchanger for cooling according to claim 1, wherein the vortex dividing means is configured by providing d) at positions shifted from each other. 7. The vortex dividing means is provided by providing a through hole (14c) through which air passes in the heat transfer plate (12a to 12c) near the protrusion (14). The cooling heat exchanger according to claim 1.