JP2008304116A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator capable of improving an overheat degree without increasing the number of part items. <P>SOLUTION: This evaporator has a heat exchange part formed by laminating a plurality of tubes 30 and fins and connecting a tank part of both upper-lower ends by a refrigerant passage extended in the tubes 30, and is constituted so that this heat exchange part is formed by two layers of a first heat exchange part and a second heat exchange part in the ventilation direction, and a first passage part 101 for the first heat exchange part and a second passage 102 for the second heat exchange part are partitioned by a partition part 40a in the tubes 30. The evaporator is characterized by arranging a heat transfer restraining part 103 in the partition part 40a for restraining heat transfer between both passages 101 and 102 by reducing the cross-sectional area between the first passage 101 and the second passage 102. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an evaporator provided with a two-layer heat exchange section in the direction of ventilation.

Conventionally, an evaporator in which heat exchange units are arranged in two layers on the windward and leeward sides in the ventilation direction is known (for example, see Patent Document 1).
In this conventional technique, by forming two layers of heat exchanging portions, it is possible to eliminate uneven temperature distribution compared to an evaporator composed of one heat exchanging portion by supplementing air cooling with each other. .

Moreover, in this prior art, in forming a two-layer heat exchange part, the 1st channel | path and the 2nd channel | path are arranged in parallel by partitioning one tube by a partition part, and both heat exchange part The number of parts can be reduced as compared with a structure in which each is formed of independent tubes.
JP 2006-242406 A

However, the present inventor has found that in the above-described evaporator, one tube has a first passage and a second passage that form a two-layer heat exchanging portion, so that the heat of both passages passes through both passages. It has been found that due to the fact that the refrigerant is transmitted through the partitioning section, the refrigerant has an adverse effect on the degree of superheat, which is the degree to which the refrigerant is vaporized at high pressure.
Thus, if both passages are formed independently, the degree of superheat is improved, but in that case, the number of parts is increased.

  The present invention has been made paying attention to the conventional problems as described above, and an object thereof is to provide an evaporator capable of improving the degree of superheating without causing an increase in the number of parts.

  In order to achieve the above-mentioned object, the invention according to claim 1 is formed by laminating a plurality of tubes and fins, and connecting tank portions at both upper and lower ends with a refrigerant passage extending in the tube. The heat exchange part is formed in two layers of the first heat exchange part and the second heat exchange part in the ventilation direction, and in the tube, for the first heat exchange part An evaporator in which a first passage and a second passage for the second heat exchanging section are partitioned by a partition section, wherein the partition section has a cross-sectional area between the first passage and the second passage. The evaporator is characterized in that it is provided with a heat transfer suppression unit that reduces heat transfer between the two passages.

  Moreover, the invention of claim 2 is the evaporator according to claim 1, wherein the tube is formed on the outer periphery of the joint and on the inner side of the joint to form the first passage. A pair of outer plates each including a first passage recess and a second passage recess that forms the second passage, and a partition formed between the two passage recesses, The evaporator is characterized in that it is formed by joining, and the heat transfer suppressing portion is provided with a concave groove in at least one of the pair of partition portions in the extending direction of the partition portions.

  According to a third aspect of the present invention, in the evaporator according to the first or second aspect of the present invention, the tube is formed at a joint portion formed on an outer periphery and on the inner side of the joint portion. A pair of outer plates each including a first passage recess that forms a passage, a second passage recess that forms the second passage, and a partition formed between the passage recesses, The heat transfer suppression portion is formed on at least one of the pair of partition portions, and the partition portion is provided on the first passage recess side and the first passage recess side. It was set as the evaporator characterized by providing the division part to divide | segment.

In the evaporator of the present invention, the partition portion that partitions the first passage and the second passage of the tube is provided with the heat transfer suppressing portion that reduces the cross-sectional area between the two passages and suppresses heat transfer between the two passages. Heat transfer between the passage and the second passage is suppressed, and the degree of superheat can be improved.
Moreover, since only the heat transfer suppression part is formed in a part of the existing tube, it can be implemented without increasing the number of parts.
Accordingly, the present invention can provide an evaporator that can improve the degree of superheat without causing an increase in the number of parts.

Moreover, in the invention according to claim 2, since the heat transfer suppressing portion is provided with a concave groove in the partition portion, it is easy to secure the workability of brazing at the time of joining by securing the area of the partition portion. is there.
Moreover, in the invention according to claim 3, since the heat transfer suppressing portion includes the divided portion obtained by dividing the partition portion, the heat transfer by the partition portion can be cut off, and the superheat characteristic can be further improved.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The evaporator of this embodiment is formed by laminating a plurality of tubes (30) and fins (33), and tank portions (11, 12, 21, 22) at both upper and lower ends are placed in the tubes (30). The heat exchange unit is connected to the extended refrigerant passage, and the heat exchange unit has two layers of a first heat exchange unit (10) and a second heat exchange unit (20) in a ventilation direction. In the tube (30), the first passage (101) for the first heat exchange part and the second passage (102) for the second heat exchange part are partitioned (40a, 40a). The evaporator is partitioned by the partition portion (40a), and the sectional area between the first passage (101) and the second passage (102) is reduced in the partition portion (40a) to suppress heat transfer between both passages. It is an evaporator provided with the heat transfer suppression part (103).

Below, based on FIGS. 1-7, the evaporator A of Example 1 of the best embodiment of this invention is demonstrated.
First, the configuration will be described.
The evaporator A according to the first embodiment is installed in an air conditioning case inside an instrument panel (not shown) that is interposed in a refrigeration cycle of an automotive air conditioner, and passes through the refrigerant flowing outside and the outside. Heat is exchanged with the air to be cooled, and the refrigerant is evaporated to cool the air.

As shown in the front view of FIG. 3 and the plan view of FIG. 4, the evaporator A is configured by alternately stacking tubes 30 and outer fins 33 extending in the vertical direction indicated by the arrows above and below in the horizontal direction indicated by the arrows left and right. And it is formed by brazing. Note that the outermost metal thin plate 34, strength reinforcing side plates 35 and 37, a pipe connector 36, and the like are attached to the left and right ends of the evaporator A.
Then, in the evaporator A, as shown in FIG. 6, the upper first tank portion 11 and the upper second tank portion 12 that extend in parallel in the left-right direction at the upper end portion of the evaporator A, A plurality of lower first tank portions 21 and lower second tank portions 22 that extend in parallel in the vehicle width direction at the lower end of the container A, and the upper first tank portion 11 and the lower first tank portion 21 communicated with each other. The first path 10a, the second path 10b, and the third path 10c formed from the first passage 101 (see FIG. 1) of the tube 30 are communicated with the upper second tank portion 12 and the lower second tank portion 22. A fourth path 20a, a fifth path 20b, and a sixth path 20c formed from the second passages 102 (see FIG. 1) of the plurality of tubes 30 are provided, and the refrigerant is circulated from the evaporator inlet 7 to the evaporator outlet 8. A refrigerant flow dew RW is formed.

  The refrigerant flow path RW includes an inlet-side heat exchange unit (first heat exchange unit) 10 formed by the upper first tank unit 11, the first to third passes 10 a, 10 b, 10 c, and the lower first tank unit 21. , An upper second tank part 12, fourth to sixth paths 20 a, 20 b, 20 c, and an outlet side heat exchange part (second heat exchange part) 20 formed by the lower second tank part 22. And the exit side heat exchange part 20 is arrange | positioned in the windward with respect to the ventilation direction shown by arrow AIR in FIG.

  That is, when the refrigerant is introduced from the evaporator inlet 7 to the inlet side heat exchanging unit 10, the upper first tank unit 11 → the first pass 10a → the lower first tank unit 21 → the second pass 10b → the upper first tank unit 11 → The flow passes in the order of the third path 10c → the lower first tank portion 21, and is finally introduced into the most upstream portion (lower second tank portion 22) of the outlet side heat exchange portion 20 through the communication portion 9.

  On the other hand, the refrigerant introduced from the communication part 9 into the outlet side heat exchange part 20 is the lower second tank part 22 → the fourth path 20a → the upper second tank part 12 → the fifth path 20b → the lower second tank part 22 → The flow passes in the order of the sixth path 20c → the upper second tank portion 12, and is finally led out from the evaporator A through the evaporator outlet 8.

The first to third passes 10a, 10b, and 10c are formed by the first passages 101 of the plurality of tubes 30, and the fourth to sixth passes 20a, 20b, and 20c are the second passages 102 of the plurality of tubes 30. The relationship between the numbers of heat exchange passages in the first pass 10a to the sixth pass 20c is set so that the following relationships (a) to (d) are established.
(A) Number of first pass passages <number of second pass passages to number of sixth pass passages (b) Number of second pass passages ≧ number of third pass passages (c) Number of third pass passages> number of fourth pass passages (d ) Number of 5th path passage> Number of 6th path passage ≥ Number of 4th path passage

Each of the tank parts 11, 12, 21, 22 and the paths 10a, 10b, 10c, 20a, 20b, and 20c described above is formed by the tube 30, and the structure thereof will be described below.
As shown in FIG. 1, the tube 30 is formed by joining and brazing together with a pair of corrugated inner fins 61, 61 sandwiched between a pair of plate-like outer plates 40, 40. ing. The outer plates 40 and 40 and the inner fins 61 and 61 are made of a highly conductive metal plate such as aluminum.

The outer plate 40 is formed in a substantially rectangular thin plate shape, and a joint portion 40b formed on the outer peripheral edge, and a first passage recess portion 41a and a second passage recess portion arranged in parallel in the longitudinal direction inside the joint portion 40b. 41b, a partition portion 40a formed between the concave portions 41a and 41b and extending in the longitudinal direction, and tank portion portions 42 and 42 for tank portions formed at both longitudinal ends of the concave portions 41a and 41b for both passages. It is equipped with.
Then, by brazing the pair of outer plates 40, 40 between the joint portions 40b, 40b and the partition portions 40a, 40a, the first passage 101 sandwiched between the pair of first passage recesses 41a, 41a is formed. The second passage 102 formed between the pair of second passage concave portions 41b and 41b is formed. The first passage 101 and the second passage 102 form paths 10a, 10b, 10c, 20a, 20b, and 20c.

  Further, both the passages 101 and 102 are communicated with the tank portion cylinder portion 42, and when the outer plate 40 is laminated, the tank portion cylinder portions 42 are brazed so as to be coaxial with each other. The tank portions 11 and 12 are formed, the upper first tank portion 11 and the lower first tank portion 21 are communicated with each other through the first passage 101, and the upper second tank portion 12 and the lower second tank portion 22 are connected to each other. The two passages 102 communicate with each other.

  Further, the hole for the tank portion 42 for the tank portion at a predetermined position is closed by the shielding plate 51 shown in FIG. 6, and the shielding plate 51 allows the first path 10 a and the second path in the upper first tank portion 11. Section with path 10b, Section with second path 10b and third path 10c in lower first tank section 21, Section with fourth path 20a and fifth path 20b in lower second tank section 22, Upper second tank The section 12 is divided into a fifth path 20b and a sixth path 20c.

Furthermore, in the first embodiment, the heat transfer suppression unit 103 that suppresses heat transfer between the inlet side heat exchange unit 10 and the outlet side heat exchange unit 20 via the partition unit 40a to the partition unit 40a of the outer plate 40. Is formed.
That is, as shown in FIG. 2, in each of the pair of partition portions 40a, 40a, concave grooves 40d, 40d having a plate thickness substantially reduced by a half by re-strike processing are formed extending in the longitudinal direction. The heat transfer suppressing portion 103 is formed by the both concave grooves 40d and 40d.

Next, the operation of the first embodiment will be described.
In the evaporator A, heat is exchanged between the refrigerant flowing through the inside and the air passing through the outside, and the refrigerant is evaporated to cool the air.
Here, in the present Example 1, it is set as the two-layer structure by the leeward side inlet side heat exchange part 10 and the leeward side outlet side heat exchange part 20, and each heat exchange part 10 and 20 is made into several path | pass 10a-10c, Comparing to 20a to 20c, the two heat exchange units 10 and 20 supplement the cooling of the air to each other, and the unevenness of the temperature distribution can be reduced compared to an evaporator composed of one heat exchange unit.

  In addition, the inventor of the present application, in the evaporator A, in order to ensure the refrigerant superheat performance (superheat) performance that prevents the liquid refrigerant from returning to the compressor side without vaporizing the refrigerant, 10 and the heat-transfer interruption | blocking in the exit side heat exchange part 20 discovered that there existed an effect.

  That is, FIG. 7 is a superheat degree characteristic diagram, and the characteristic (a) is a characteristic in a case where heat transfer between the heat exchange units 10 and 20 is not performed with the heat exchange units 10 and 20 being independent. On the other hand, the characteristics (b) and (c) show the case where the heat exchange units 10 and 20 are not independent, the characteristic (b) is the characteristic of the first embodiment, and the characteristic (c) is This is a characteristic of the conventional product in which the heat transfer suppressing portion 103 is not formed in the partition portion 40a of the outer plate 40.

  As shown in this characteristic diagram, when both the heat exchange parts 10 and 20 are made independent, the superheat characteristic is good. However, in this case, it is necessary to divide the tube 30, and the number of parts is nearly doubled compared to the first embodiment, and the number of brazing steps is also doubled, resulting in a significant cost increase.

  On the other hand, since the thing of this Example 1 only forms the heat-transfer suppression part 103 by the concave groove 40d in the partition part 40a, while the number of parts and brazing man-hours are not different from a conventional product, The degree is higher than the conventional product.

  As described above, in the first embodiment, the number of components is not increased by a simple configuration in which the heat transfer suppressing portion 103 is formed in the partition portion 40a of the outer plate 40 by the concave groove 40d by the wrist-like process. In addition, the refrigerant superheat characteristic can be improved, and the performance can be improved as compared with the conventional case. If the performance is equivalent, the size can be reduced.

(Other examples)
Other embodiments will be described below. However, since these other embodiments are modifications of the first embodiment, only the differences will be described, and the configuration and operational effects similar to those of the first embodiment will be described. Is omitted.

In the tube 230 used in the evaporator according to the second embodiment shown in FIG. 8, a concave groove 40d is formed only in one partition 40a of the pair of outer plates 40, 240, and a concave groove 40d is formed in the other partition 240a. This is an example in which the heat transfer suppressing portion 203 is formed without being formed.
Even in the second embodiment, the degree of superheat can be improved by suppressing the heat transfer by the amount by which the sectional area of the partition portion 40a is reduced.

The tube 330 used in the evaporator of the third embodiment shown in FIG. 9 is formed with a concave groove 40d in the partition portion 40a of one outer plate 40 of the pair of outer plates 40, 340 as in the first embodiment. The partition portion 340a of the other outer plate 340 is formed with a split portion 340d that divides the partition portion 340a into the first passage recess portion 41a side and the second passage recess portion 41b side. The heat transfer suppressing portion 303 is formed by the groove 40d and the dividing portion 340d.
As shown in FIG. 10, a plurality of division parts 304d are intermittently formed in the longitudinal direction of the outer plate 340, and the first part of the partition part 340a is provided between the division part 304d and the division part 340d. A connecting portion 340e that connects the passage recess 41a side and the second passage recess 41b side is formed.

  According to the third embodiment, the partitioning portion 340a is divided by the dividing portion 340d, and the first passage concave portion 41a side and the second passage concave portion 41b side are separated from each other, so that the heat transfer suppression performance is further improved. be able to.

  A tube 430 used in the evaporator of the fourth embodiment shown in FIG. 11 is an example in which the outer plate 340, 340 shown in the third embodiment is used and the heat transfer suppressing portion 403 is formed by a pair of divided portions 340d, 340d.

  According to the fourth embodiment, since the divided portions 340d are formed in the both partition portions 340a, the heat transfer suppression performance can be further improved.

  The evaporator of Example 5 shown in FIG. 12 is the example which formed the division | segmentation part 540d in each partition part 540a and 540a of a pair of outer plates 540 and 540 similarly to Example 5, and formed the heat transfer suppression part 503. However, the structure of the dividing unit 540d is different from that of the fourth embodiment.

  That is, in the fifth embodiment, the partition portions 540a and 540a are cut, and the cut portions are caulked with respect to the other partition portion 540a to join both the partition portions 540a and 540a. Both passage recesses 41a and 41b are divided.

  Therefore, even in the fifth embodiment, the same heat transfer suppression performance improvement as in the fourth embodiment can be achieved.

  A tube 630 used in the evaporator of the sixth embodiment shown in FIG. 13 is formed using the outer plate 340 shown in the third embodiment and the outer plate 240 shown in the second embodiment, and one partition 340a. This is an example in which the heat transfer suppressing portion 603 is formed by the divided portion 340d formed in the above.

  Also in the sixth embodiment, since the cross-sectional areas of both partition portions 240a and 340a can be halved, the thermal conductivity can be suppressed.

  As mentioned above, although embodiment and Example 1-6 of this invention were explained in full detail with reference to drawings, the concrete structure is not restricted to this embodiment and Example 1-6, and the present invention. Design changes that do not depart from the gist are included in the present invention.

  For example, in the first to sixth embodiments, the relationship between the numbers of heat exchange passages of the first pass 10a to the sixth pass 20c is set so that the above relationships (a) to (d) are established. This makes it possible to set the relationship between the flow path cross-sectional area to expand the flow path cross-sectional area as the gas refrigerant ratio increases in the downward flow, and the refrigerant push-up energy in the previous pass in the upward flow. It becomes the relation setting of the channel cross-sectional area according to the size, and the area where the refrigerant flow rate causing the unevenness of the temperature distribution is reduced can be minimized as the whole of the first pass 10a to the sixth pass 20c. Although a synergistic effect with the effect is obtained and preferable, the relationship between the first pass 10a to the sixth pass 20c is not limited to this in carrying out the present invention.

  In Examples 1 to 6, in forming the tube 30, the outer plate 40 includes the first passage recess 41a and the second passage recess 41b, but is not limited thereto. For example, like the tube 730 shown in FIG. 14, one outer plate 740 is formed in a flat shape, and both concave portions 41 a and 41 b as shown in the first to sixth embodiments are formed in the other outer plate. A thing may be used (the figure shows an example using the outer plate 340 used in the third embodiment).

  Moreover, in Examples 1-6, although what showed a pair of outer plates 40 and 40 in the middle as a tube was shown, it is not limited to this, For example, extrusion molding like the tube 830 shown in FIG. It is also possible to use those formed by the above. In the figure, reference numeral 803 denotes a heat transfer suppressing portion.

  In Example 1, although the example which applied the evaporator of this invention to the evaporator of a vehicle air conditioner was shown, it is not restricted to this, It can apply as an evaporator of the air conditioner which uses the refrigerating cycle in another technical field. .

It is a figure which shows the tube 30 used for the evaporator A of Example 1 of the best form of this invention, Comprising: (a) is a disassembled perspective view, (b) is a perspective view. 3 is a cross-sectional view of a main part of a tube 30 used in the evaporator A of Example 1. FIG. It is a front view of the evaporator A of Example 1. FIG. It is a top view of the evaporator A of Example 1. FIG. It is sectional drawing of the principal part of the evaporator A of Example 1, Comprising: The state cut | disconnected by the S5-S5 line | wire of FIG. 3 is shown. It is explanatory drawing which shows the refrigerant | coolant flow dew RW inside the evaporator A of Example 1. FIG. It is the superheat degree characteristic figure which showed the superheat degree characteristic of the evaporator A of Example 1 with the other comparative example. It is sectional drawing of the principal part which shows the tube 230 used for the evaporator of Example 2. FIG. It is sectional drawing of the principal part which shows the tube 330 used for the evaporator of Example 3. FIG. It is a perspective view of the outer plate 340 of the tube 330 used for the evaporator of Example 3. FIG. It is sectional drawing of the principal part which shows the tube 430 used for the evaporator of Example 4. FIG. It is sectional drawing of the principal part which shows the tube 530 used for the evaporator of Example 5. FIG. It is sectional drawing of the principal part which shows the tube 630 used for the evaporator of Example 6. FIG. It is sectional drawing of the principal part which shows the tube 730 of another example. It is sectional drawing of the principal part which shows the tube 830 of another example.

Explanation of symbols

A Evaporator 10 Inlet side heat exchange section (first heat exchange section)
11 Upper first tank part 12 Upper second tank part 20 Outlet side heat exchange part (second heat exchange part)
21 Lower first tank portion 22 Lower second tank portion 30 Tube 33 Outer fin 40 Outer plate 40a Partition portion 40b Joint portion 40d Concave groove 101 First passage 102 Second passage 103 Heat transfer suppression portion 203 Heat transfer suppression portion 230 Tube 240 Outer Plate 240a partitioning part 340a partitioning part 303 Heat transfer suppressing part 304d dividing part 330 Tube 340 Outer plate 340a partitioning part 340d dividing part 340e connecting part 403 Heat transfer suppressing part 430 Tube 503 Heat transfer suppressing part 530 Tube 540 Outer plate 540a Partitioning part 540d Dividing part 603 Heat transfer suppressing part 630 Tube 730 Tube 740 Outer plate 830 Tube

Claims (3)

It is formed by laminating a plurality of tubes and fins,
The heat exchanging unit includes a heat exchanging unit that connects the upper and lower tank units with a refrigerant passage extending into the tube, and the heat exchanging unit has a first heat exchanging unit and a second heat exchanging unit in the ventilation direction. And two layers are formed,
In the tube, an evaporator in which a first passage for the first heat exchange part and a second passage for the second heat exchange part are partitioned by a partition part,
An evaporator, wherein the partition portion is provided with a heat transfer suppressing portion that reduces a cross-sectional area between the first passage and the second passage and suppresses heat transfer between the two passages. The tube includes a joint portion formed on the outer periphery, a first passage recess portion that forms the first passage and a second passage recess portion that forms the first passage, A pair of outer plates provided with a partition formed between the recesses for the passage, and formed by joining the joint and the partition,
2. The evaporator according to claim 1, wherein the heat transfer suppression unit includes a concave groove in at least one of the pair of partition portions in an extending direction of the partition portion. The tube includes a joint portion formed on the outer periphery, a first passage recess portion that forms the first passage and a second passage recess portion that forms the first passage, A pair of outer plates provided with a partition formed between the recesses for the passage, and formed by joining the joint and the partition,
The heat transfer suppression part includes a dividing part that divides the partition part into the first passage recess side and the first passage recess side in at least one of the pair of partition parts. The evaporator according to claim 1 or 2.

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