JP2001027491A - Heat-exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve heat-exchange performance to uniformly distribute a refrigerant to a refrigerant flow passage and to improve heat-exchange performance by reducing incurring of a pressure loss in the refrigerant flow passage, in a drawn cup type heat-exchanger. SOLUTION: This heat-exchanger is formed such that two flat plates 13 and 14 on which a drawing process is applied are overlapped together and constituted such that a plate-form refrigerant flow passage part 11 in which a refrigerant flow passage R is situated and a cooling fin 12 are alternately laminated together. Opening parts 13a and 14a through which a refrigerant is introduced in the refrigerant flow rate R are formed in two flat plates 13 and 14, respectively. The opening parts 14a and 13a of the adjoining refrigerant flow passages 11 and 11 are butted to each other to form a continuous space Sin on the inlet side. A refrigerant flowing through the space Sin on the inlet side flows in the refrigerant passage R through the opening parts 13a and 14a and is distributed to the respective refrigerant flow parts 11. In this case, protrusions 20 to regulate a flow of a flowing refrigerant an introduce a part of the refrigerant to the opening parts 13a and 14a are formed in the space Sin on the inlet side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger constituting a vehicle air conditioner.

[0002]

2. Description of the Related Art FIG. 9 shows an example of the structure of a heat exchanger used as an evaporator in a vehicle air conditioner. The heat exchanger shown in the drawing is a so-called Dron cup type, which has become mainstream in recent years, and is bent into a wave shape with a plate-like refrigerant flow portion 3 in which substantially rectangular flat plates 1 and 2 that have been subjected to a drawing process are overlapped. The cooling fins 4 are alternately stacked.

[0003] Inside the refrigerant flow part 3, the outer peripheral part and the central part of the flat plates 1 and 2 are brazed to reciprocate from the refrigerant inlet 5 provided at the upper part to the lower part and to be aligned with the refrigerant inlet 5 at the upper part. A U-shaped refrigerant flow path R is formed to pass through a refrigerant outlet 6 provided in the air conditioner.

[0004] In this heat exchanger, the refrigerant is distributed to each refrigerant distribution part 3 at the refrigerant inlet 5, is evaporated and vaporized in the course of flowing through the refrigerant flow path R, merges again at the refrigerant outlet 6 and flows out of the heat exchanger. It is supposed to.

[0005]

However, the following problems have been pointed out in the heat exchanger having the above structure. (1) The refrigerant inlet 5 forms a continuous space as shown in FIG.
The refrigerant that has flowed into the heat exchanger is distributed to the respective refrigerant distribution sections 3 in the process of traveling in the continuous space in the direction of the arrow in the figure. However, in the conventional heat exchanger, the refrigerant flows into the refrigerant distribution unit 3 located downstream of the flow of the refrigerant in a biased manner, and the refrigerant is not uniformly distributed to the refrigerant distribution units 3 and the refrigerant is stagnated. The heat exchange is not sufficiently performed in the refrigerant circulation section 3 on the upstream side, which tends to occur.

(2) The refrigerant that has flowed into the heat exchanger is distributed from the space formed by laminating the refrigerant circulation sections 3 to the respective refrigerant circulation sections 3, but in the conventional heat exchanger, the space has been reduced. Since the beginning of the refrigerant flow path R that is continuous with the air flow path is narrower than the expansion of the space, the refrigerant flow path R suddenly contracts in this part, causing a pressure loss. The same phenomenon is observed in the continuous space formed at the refrigerant outlet 6, and since the expansion of the space is wider than that at the end of the refrigerant flow path R, the refrigerant flow path R sharply increases at this part. Pressure loss occurs in an expanded form.

The present invention has been made in view of the above circumstances, and in a Drone cup type heat exchanger, heat is exchanged by uniformly distributing the refrigerant to the refrigerant flow path and reducing pressure loss in the refrigerant flow path. The purpose is to improve performance.

[0008]

As means for solving the above-mentioned problems, a heat exchanger having the following structure is employed. That is, in the heat exchanger according to claim 1, two drawn flat plates are superimposed, and a plate-shaped refrigerant flow portion having a refrigerant flow path provided therein and cooling fins are alternately laminated. The two flat plates are formed with openings for introducing the refrigerant into the refrigerant flow passages, and the openings of the laminated and adjacent refrigerant flow portions are joined to each other to form a continuous space. The refrigerant flowing through the space is a heat exchanger that flows into the refrigerant flow path from the opening and is distributed to each of the refrigerant distribution portions. It is characterized in that a regulating part for introducing the part into the opening is provided.

In this heat exchanger, the provision of the regulating portion allows a part of the refrigerant flowing through the space to be introduced into the opening and flow into the refrigerant flow path. More refrigerant is distributed to the stagnant refrigerant distribution part, and the refrigerant can be uniformly distributed to any of the plurality of refrigerant distribution parts.

A heat exchanger according to a second aspect is characterized in that, in the heat exchanger according to the first aspect, the restricting portion is a projection formed in a direction opposite to a flow direction of the refrigerant.

[0011] In this heat exchanger, by forming the projections in the direction opposite to the flow direction of the refrigerant, the flow of the refrigerant can be easily regulated. Also, by setting the size of the protrusion arbitrarily, the amount of the refrigerant to be regulated can be adjusted.

According to a third aspect of the present invention, in the heat exchanger according to the first or second aspect, the restricting portion is provided integrally with one of the two flat plates. I have.

In this heat exchanger, workability is enhanced by providing the restricting portion integrally with the flat plate. In addition, it becomes possible to appropriately adjust the direction of the projections and the like when drawing the flat plate.

According to a fourth aspect of the present invention, in the heat exchanger according to the third aspect, the regulating portion is formed by performing burring around the opening.

In this heat exchanger, for example, by performing burring on the periphery of the opening at the time of drawing a flat plate, the regulating portion can be easily formed, thereby improving workability and suppressing an increase in manufacturing cost. Can be

According to a fifth aspect of the present invention, there is provided a heat exchanger.
5. The heat exchanger according to 2, 3 or 4, wherein the refrigerant flow portion has a swelling portion that is depressed from at least one of the two flat plates from the outside and protrudes toward the refrigerant flow path. By contacting the top of the bulging portion with the other, a plurality of elliptical or elliptical columnar portions whose major axis is directed in the flow direction of the refrigerant are provided between the two flat plates. .

In this heat exchanger, the refrigerant collides with the columnar part in the course of flowing through the refrigerant flow path, and the flow of the refrigerant is disturbed, and the heat transfer coefficient is improved by the turbulent flow effect. In addition, by joining the bulging portions to form a columnar portion, the joining strength of the two flat plates forming the coolant channel is increased.

According to a sixth aspect of the present invention, there is provided the heat exchanger according to the fifth aspect, wherein the columnar portions are partially obliquely adjacent to the refrigerant flow direction in the flow direction. It is characterized by being arranged so as to overlap.

In this heat exchanger, the front end of the column located downstream of the rear end of the column located upstream of the flow is located between the column adjoining obliquely to the flow direction of the refrigerant. Is located upstream, the local heat transfer coefficient, which tends to decrease at the rear end of the column located on the upstream side, is compensated for by the front end of the column located on the downstream side.

In the heat exchanger according to the present invention, the two flat plates subjected to the drawing process are overlapped with each other, and a plate-like refrigerant flow portion provided with a refrigerant flow passage therein and cooling fins are alternately laminated. The two flat plates are formed with openings for introducing the refrigerant into the refrigerant flow passages, respectively, and the openings of the adjacent refrigerant flow portions are stacked and abutted against each other to form a continuous inlet side space. Is formed, the refrigerant is a heat exchanger that flows into the opening in the process of flowing through the inlet side space and is distributed to each of the refrigerant flowing portions, and the refrigerant flow path communicates with the inlet side space. It is characterized in that the cross section of the flow path is gradually reduced in the flow direction of the refrigerant.

In this heat exchanger, the passage section of the refrigerant passage communicating with the inlet space is formed so as to be gradually reduced, so that the rapid contraction of the refrigerant passage is alleviated. The pressure loss of the refrigerant flowing into the path is reduced.

In the heat exchanger according to the present invention, two drawn flat plates are overlapped with each other, and a plate-like refrigerant flow portion having a refrigerant flow path provided therein and cooling fins are alternately laminated. The two flat plates are respectively formed with openings through which the refrigerant that has passed through the refrigerant flow path flows out. A side space is formed, wherein the refrigerant is distributed to the respective refrigerant distribution sections, flows through the refrigerant flow path, and then flows out of the opening and is discharged through the outlet side space, wherein the outlet side space is provided. The flow path cross section of the refrigerant flow path communicating with the refrigerant is gradually enlarged in the flow direction of the refrigerant.

In this heat exchanger, the refrigerant flow path communicating with the outlet side space is formed so as to gradually enlarge the flow path cross section, so that rapid expansion of the refrigerant flow path is mitigated, and The pressure loss of the refrigerant flowing into the space is reduced.

[0024]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of a heat exchanger according to the present invention will be described with reference to FIGS. The heat exchanger shown in FIG. 1 is configured by alternately stacking plate-shaped refrigerant circulation portions 11 and corrugated cooling fins 12.

As shown in FIG. 2, the refrigerant flow section 11 is formed by laminating substantially rectangular flat plates 13 and 14 which have been drawn and brazing the outer peripheral portion and the central portion. 15 and a refrigerant outlet 16 are provided side by side. Inside the refrigerant flow portion 11, the outer peripheral portions and the central portions of the flat plates 13 and 14 are brazed to advance downward from the refrigerant inlet 15 provided at the upper portion, turn back at the lower portion, and pass through the refrigerant outlet 16. A refrigerant passage R having a U-shape is formed.

A plurality of dimples 1 are formed in the refrigerant flow section 11 by flattening the flat plates 13 and 14 forming the refrigerant flow path R from the outside.
7 are formed, and a plurality of bulging portions 18 are formed in the refrigerant flow path R by these dimples 17. As shown in FIG. 3, these bulging portions 18 have an elliptical shape whose major axis is the flow direction of the refrigerant when viewed in a plan view, and the top portions 18 a are further brazed by opposing bulging portions 18.
It is provided between the flat plates 13 and 14 to form a columnar portion 19 having an elliptical cross-sectional shape. The shape of the columnar body 19 is not limited to an ellipse, but may be an ellipse.

As shown in FIG. 4, each of the bulging portions 18 is arranged in a staggered manner such that the bulging portions 18 which are obliquely adjacent to the flow direction of the refrigerant partially overlap each other in the flow direction. The columnar portion 19 is also arranged according to this.

The refrigerant inlet 15 comprises openings 13a and 14a formed in the flat plates 13 and 14, and the refrigerant inlet 15 provided in each of the refrigerant flow sections 11 protrudes without sandwiching the cooling fins 12, as shown in FIG. Combined and continuous entrance space S
forming in. Similarly, the refrigerant outlet 16 is connected to the flat plates 13, 1
4, the refrigerant outlets 16 provided in each of the refrigerant flow portions 11 are abutted without sandwiching the cooling fins 12 to form a continuous outlet side space Sout as shown in FIG. are doing.

In the heat exchanger having the above-described structure, the refrigerant is distributed to the respective refrigerant distribution portions 11 in the process of traveling in the inlet side space Sin in the direction of the arrow in the drawing, and is evaporated and vaporized in the process of flowing through the refrigerant flow path R. In the outlet side space Sout, they merge again and flow out.

In the process in which the refrigerant flows through the refrigerant flow path R, the refrigerant collides with the columnar portions 19 provided in the refrigerant flow path R, causing a disturbance in the flow of the refrigerant, and the turbulence effect improves the heat transfer coefficient. . Moreover, between the columnar portions 19 obliquely adjacent to the flow direction of the refrigerant, the columnar portions 1 located on the upstream side of the flow are arranged.
Since the front end of the columnar portion 19 located downstream of the rear end of the column 9 is located on the upstream side, the local heat transfer coefficient, which tends to decrease at the rear end of the columnar portion 19 located on the upstream side, is reduced to the downstream side. Supplemented by the front end of the columnar portion 19 located,
The heat transfer coefficient is improved as a whole.

Further, since the columnar portions 19 are regularly arranged along the flow direction of the refrigerant, and the joint portions between the top portions 18a are widely secured, the refrigerant flow portion 11 has any cross section in the flow direction of the refrigerant. The two flat plates 13 and 14 are bonded to each other by the bulging portions 18 to increase the bonding strength. Thereby, even if the thickness of the flat plates 13 and 14 is thin, sufficient pressure resistance can be obtained in the refrigerant flow portion 11.

By the way, as shown in FIG.
The inlet side space Sin formed on the fifth side is provided with a projection (restriction portion) 20 for restricting the flow of the flowing refrigerant and introducing a part of the refrigerant into the refrigerant inlet 15 formed by the openings 13a and 14a. I have. The projection 20 is provided integrally with the flat plate 13 by performing burring around the opening 13a, and is formed so as to protrude in a direction opposite to the flow direction of the refrigerant, and is formed on the opening 14a of the adjacent refrigerant flow section 11. Are packed together.

As described above, when the protrusion 20 for regulating the flow of the refrigerant is formed in the inlet side space Sin, the flow is regulated so that a part of the refrigerant flowing in the inlet side space Sin is scraped off by the protrusion 20, and the refrigerant inlet is formed. 15 and is introduced into the refrigerant flow path R.
As a result, more refrigerant is distributed to the refrigerant distribution section 11 where the refrigerant is located at the upstream side of the flow and where the refrigerant tends to stagnate, and heat is uniformly distributed in all of the plurality of refrigerant distribution sections 11. Since the exchange is performed, the heat exchange performance of the heat exchanger can be improved.

The projections 20 can be easily formed by performing burring on the periphery of the opening 13a at the time of drawing the flat plate 13, thereby simplifying the manufacturing process and reducing costs.

The amount of the refrigerant regulated by the projections 20 can be appropriately set by arbitrarily setting the size of the projections 20 or adjusting the direction of the projections 20 at the time of drawing the flat plate 13. Thus, the refrigerant can be more uniformly distributed.

In the present embodiment, the projections 20 are provided on one of the flat plates 13, but they may be provided on the other flat plate 14. Further, the projections 20 are formed of separate members, and
May be brazed at the same time as brazing.

Next, a second embodiment of the heat exchanger according to the present invention will be described with reference to FIGS. In addition, the first
The same reference numerals are given to the components already described in the embodiment, and the description is omitted. In the heat exchanger according to the present embodiment, the flow path cross section of the refrigerant flow path R that communicates with the inlet space Sin has a flow direction of the refrigerant at a portion that enters the refrigerant flow path R from the inlet space Sin as shown in FIG. Are formed so as to be gradually reduced as the process proceeds (portion indicated by A in the figure). This shape is given when the flat plates 13 and 14 are subjected to drawing. Although not shown, the outlet side space Sou
The portion passing through t has the same shape, and is formed so as to gradually expand according to the flow direction of the refrigerant.

As described above, by forming the cross section of the refrigerant flow path R communicating with the inlet side space Sin so as to gradually decrease as the flow direction of the refrigerant flows, the rapid reduction of the refrigerant flow path R is alleviated. The pressure loss of the refrigerant flowing from the inlet side space Sin into the refrigerant flow path R is reduced.

Further, by forming the cross section of the refrigerant flow path R communicating with the outlet side space Sout so as to gradually expand as it advances in the flow direction of the refrigerant, the rapid expansion of the refrigerant flow path R is reduced, and the refrigerant flow is reduced. The pressure loss of the refrigerant flowing out of the flow path R into the outlet side space Sout is reduced. Thereby, the pressure loss can be reduced together with the inlet side space Sin side, and the heat exchange performance of the heat exchanger can be improved.

In the present embodiment, the wall surface of the refrigerant passage R is formed in a curved shape. However, the present invention is not limited to this. For example, the wall surface of the refrigerant passage R may be formed in a wedge shape as shown in FIG. Absent.

[0041]

As described above, according to the heat exchanger according to the first aspect of the present invention, the provision of the restricting portion allows a part of the refrigerant flowing through the space to be introduced into the opening, and the refrigerant to flow therethrough. Since the refrigerant flows into the flow path, more refrigerant is distributed to the refrigerant distribution part where the refrigerant is located on the upstream side of the flow and the refrigerant tends to stagnate, and is uniformly distributed to any of the plurality of refrigerant distribution parts. To the refrigerant. This allows
The heat exchange performance of the heat exchanger can be improved.

According to the heat exchanger of the second aspect, the flow of the refrigerant can be easily regulated by forming the projections against the flow direction of the refrigerant. In addition, it is also possible to adjust the amount of the refrigerant to be regulated by arbitrarily setting the size of the projection.

According to the heat exchanger of the third aspect, by providing the regulating portion integrally with the flat plate, the workability can be enhanced, and the manufacturing process can be simplified and the cost can be reduced. In addition, it is also possible to adjust the direction of the projection and the like at the time of drawing the flat plate, and it is also possible to set the amount of the refrigerant regulated by the projection appropriately and distribute the refrigerant more uniformly.

According to the heat exchanger of the fourth aspect, for example, by performing burring on the periphery of the opening at the time of drawing a flat plate, the regulating portion can be easily formed, thereby improving workability and manufacturing cost. Can be reduced.

According to the heat exchanger of the fifth aspect, since the refrigerant collides with the columnar part in the course of flowing through the refrigerant flow path, the flow of the refrigerant is disturbed, and the turbulence effect improves the heat transfer coefficient. In addition, the heat exchange performance of the heat exchanger can be improved.
In addition, the joint strength between the two flat plates forming the coolant flow channel is increased by joining the bulging portions to form the columnar portion, so that the pressure resistance of the coolant circulation portion can be increased.

According to the heat exchanger of the sixth aspect, the columnar portions which are obliquely adjacent to the refrigerant flow direction are located downstream of the rear end of the columnar portion located on the upstream side of the flow. The front end of the columnar portion is arranged on the upstream side, and the local heat transfer coefficient, which tends to decrease at the rear end of the columnar portion located on the upstream side, is supplemented by the front end of the columnar portion located on the downstream side. The heat transfer coefficient can be improved as a whole.

According to the heat exchanger of the present invention, the cross section of the refrigerant flow path communicating with the inlet space is formed so as to be gradually reduced, so that the rapid reduction of the refrigerant flow path is reduced.
Since the pressure loss of the refrigerant flowing into the refrigerant flow path from the inlet space is reduced, the heat exchange performance can be improved.

According to the heat exchanger of the eighth aspect, the refrigerant flow passage communicating with the outlet side space is formed so as to gradually increase the cross section of the refrigerant flow passage, whereby the rapid expansion of the refrigerant flow passage is reduced,
Since the pressure loss of the refrigerant flowing out of the refrigerant channel to the outlet side space is reduced, the heat exchange performance can be improved.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a first embodiment of a heat exchanger according to the present invention.

FIG. 2 is an exploded perspective view showing a refrigerant flow section constituting the heat exchanger of FIG.

FIG. 3 is a sectional view taken along line III-III in FIG.

FIG. 4 is a plan view of the refrigerant flow section as viewed from the side.

FIG. 5 is a cross-sectional view showing an inlet side space and a refrigerant flow path connected thereto.

FIG. 6 is a cross-sectional view showing an outlet side space and a refrigerant flow path connected thereto.

FIG. 7 is a view showing a second embodiment of the heat exchanger according to the present invention, and is a cross-sectional view showing an inlet space and a refrigerant flow path connected thereto.

FIG. 8 is a view showing an embodiment similar to the heat exchanger shown in the second embodiment, and is a cross-sectional view showing an inlet side space and a refrigerant flow path connected thereto.

FIG. 9 is a perspective view showing an example of a conventional evaporator.

FIG. 10 is a cross-sectional view showing an inlet-side space and a refrigerant flow path connected thereto in a conventional evaporator.

[Description of Signs] 11 Refrigerant distribution part 12 Cooling fins 13, 14 Flat plate 13a, 14a Opening part 15 Refrigerant inlet 16 Refrigerant outlet 17 Dimple 18 Swelling part 19 Columnar part 20 Projection (restriction part) R Refrigerant flow path Sin Inlet side space Sout exit space

Claims (8)

[Claims] 1. A two-plate drawing machine comprising: two drawn flat plates which are superimposed on each other and a cooling fin and a plate-like cooling medium circulating portion provided with a cooling medium passage therein are alternately laminated; In the flat plate, openings for introducing a refrigerant into the refrigerant flow path are respectively formed, and a continuous space is formed by abutting the openings of the adjacent refrigerant flow portions which are further laminated, and the refrigerant flowing through the space is formed. Is a heat exchanger that flows into the refrigerant flow path from the opening and is distributed to each of the refrigerant distribution sections. In the space, the flow of the refrigerant is regulated, and a part of the refrigerant is introduced into the opening. A heat exchanger, comprising: 2. The heat exchanger according to claim 1, wherein the restricting portion is a projection formed in a direction opposite to a flow direction of the refrigerant. 3. The heat exchanger according to claim 1, wherein the restricting portion is provided integrally with one of the two flat plates. 4. The heat exchanger according to claim 3, wherein the restricting portion is formed by performing burring around the opening. 5. A swelling portion which protrudes toward the coolant flow channel by depressing at least one of the two flat plates from the outside in the coolant circulating portion, and the top of the swelling portion is connected to the other side. A plurality of elliptical or elliptical columnar portions having a major axis directed in the flow direction of the refrigerant are provided between the two flat plates by contacting the refrigerant. Or the heat exchanger according to 4. 6. The columnar portion, wherein ones obliquely adjacent to the flow direction of the refrigerant are arranged so as to partially overlap each other in the flow direction.
The heat exchanger as described. 7. A squeezed two flat plate is superimposed on each other, and a plate-like refrigerant flow portion having a refrigerant flow path provided therein and cooling fins are alternately stacked, and the two flat plates are formed. The flat plate is formed with an opening for introducing a refrigerant into the refrigerant flow path, and a continuous inlet-side space is formed by abutting the openings of the adjacent refrigerant flow sections which are further laminated, and the refrigerant is In the heat exchanger which flows into the opening in the course of flowing through the inlet side space and is distributed to the respective refrigerant flowing portions, the flow path cross section of the refrigerant flow path communicating with the inlet side space has a cross section of the refrigerant. A heat exchanger characterized in that the heat exchanger is gradually reduced in the flow direction. 8. A squeezed two flat plate is superimposed on each other, and a plate-like refrigerant flow portion having a refrigerant flow path provided therein and cooling fins are alternately stacked, and the two flat plates are formed. In the flat plate, openings through which the refrigerant that has passed through the refrigerant flow passages are formed are formed, and the openings of the laminated refrigerant adjoining portions are abutted against each other to form a continuous outlet-side space, and the refrigerant is formed. Is a heat exchanger that is distributed to each refrigerant flow section, flows through the refrigerant flow path, flows out of the opening, and is discharged through the outlet side space, and is a heat exchanger that communicates with the outlet side space. A heat exchanger characterized in that the cross section of the flow path is gradually enlarged as it proceeds in the flow direction of the refrigerant.