JP2005315567A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator having further reduced uneven temperature distribution. <P>SOLUTION: In an inlet side heat exchange portion 10 where a degree of drying is lower and the flow distribution of refrigerant easily deviates, the number of heat exchange passages of an upward flow path 10b is reduced than that of a downward flow path 10a. Thus, liquid phase refrigerant flowing on the upstream side in the longitudinal direction of a tank where liquid phase refrigerant in the upward flow path 10b is liable to lack is increased and regions where the liquid phase refrigerant lacks are reduced, thus reducing uneven temperature distribution. In an outlet side heat exchange portion 20 having a high degree of drying and causing little partial circulation distribution of the refrigerant, the number of heat exchange passages of the lowest flow path 20c where the volume of the distributed refrigerant most expands is greater than that of a path 20b right before the lowest flow. Thus, an increase in distribution resistance in the lowest flow path 20c is suppressed and the distribution resistance in the outlet side heat exchange portion 20 is kept lower. As a result, the evaporator has reduced uneven temperature distribution and lower distribution resistance. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an evaporator in which heat exchange units are arranged side by side on the windward and leeward sides.

  For example, as disclosed in Patent Documents 1 to 3, there is an evaporator in which two heat exchange units are conventionally arranged on the windward side and the leeward side. FIG. 13 shows an example of an evaporator in which two heat exchangers of this type are arranged in parallel on the windward side and the leeward side. The evaporator 100 shown in FIG. 13 includes an upper tank 111, a lower tank 112, and a leeward heat exchange unit 110 including a plurality of heat exchange passages connected to both the tanks 111, 112. A tank 122 and an upwind heat exchanging unit 120 including a plurality of heat exchange passages connected in communication between the tanks 121 and 122 are arranged so as to overlap each other in the air blowing direction.

  The leeward side heat exchanging part 110 is provided with an evaporator inlet 107 at the right end of the upper tank 111, and the upper tank 111 is partitioned into an upper first tank part 111a and an upper second tank part 111b by a partition part 114, The lower tank 112 is partitioned by a partition 115 into a lower first tank portion 112a and a lower second tank portion 112b. As a result, the heat exchange passage groups stacked in multiple stages are partitioned in order from the right to the left into the first path 110a, the second path 110b, and the third path 110c. The refrigerant introduced into the exchange unit 110 is the upper first tank unit 111a → the first pass 110a → the lower first tank unit 112a → the second pass 110b → the upper second tank unit 111b → the third pass 110c → the lower second tank. It flows in the order of part 112b. Then, the refrigerant is introduced from the lower second tank part 112b as the most downstream part of the leeward heat exchange part 110 into the lower first tank part 122a as the most upstream part of the windward heat exchange part 120 through the communication path 109. It has come to be.

  On the other hand, in the windward side heat exchanging unit 120, the lower tank 122 is partitioned into a lower first tank unit 122a and a lower second tank unit 122b by a partition unit 124, while the upper tank 121 is partitioned into an upper first tank unit by a partition unit 125. 121a and the upper 2nd tank part 121b are divided. As a result, the heat exchange passage groups stacked in a plurality of stages are partitioned into the first path 120a, the second path 120b, and the third path 120c in order from the left to the right. The refrigerant introduced into the section 120 is the lower first tank section 122a → the first path 120a → the upper first tank section 121a → the second path 120b → the lower second tank section 122b → the third path 120c → the upper second tank section. It flows in the order of 121b. And this refrigerant | coolant is derived | led-out from the evaporator 100 from the evaporator exit 108 provided in the right end of the upper 2nd tank part 121b as the most downstream part of the windward heat exchange part 120. FIG.

  Here, the paths superimposed on the windward side and the leeward side overlap in the direction of ventilation. Also, the paths (10a and 20c) (10b and 20b) (10c and 20a) superimposed on the windward side and the leeward side have the refrigerant flow directions opposite to each other including the flow in the upstream and downstream tank portions. It has become. In the figure, the circled numbers are numbers added to the paths in the order in which the refrigerant flows.

FIG. 14a shows the distribution of the liquid-phase refrigerant in each of the heat exchange units 110 and 120, and FIG. 14b shows the distribution of the liquid-phase refrigerant as an entire evaporator obtained by superimposing these. Note that the distribution of the liquid-phase refrigerant almost coincides with the temperature distribution. As shown in FIG. 14b, in the evaporator 100 in which the two heat exchange units 110 and 120 are stacked in the wind flow direction, the two heat exchange units 110 and 120 can complement each other to exchange heat. As compared with the evaporator, the temperature distribution unevenness can be reduced.
JP-A-6-74679 Japanese Patent Laid-Open No. 10-238896 JP 2000-105091 A

  However, unevenness is still produced. A region where the liquid-phase refrigerant does not flow, that is, a region where only the gas-phase refrigerant circulates causes temperature unevenness because the air flowing through cannot be sufficiently cooled.

  The present invention has been made in view of the above points, and an object of the present invention is to provide an evaporator in which a heat exchanging portion is laminated in two layers in the direction of ventilation, and further can reduce temperature distribution unevenness.

  As a result of research, the present inventor has found that in the upward flow path (in this specification, the upward flow path refers to a path in which the circulating refrigerant becomes an upward flow), the gas-liquid mixed refrigerant flowing from the lower tank is transferred to the tank of the lower tank. It has been found that the liquid flow refrigerant is biased to the downstream side in the tank longitudinal direction and short on the upstream side in the tank longitudinal direction because the upward flow path rises when the pressure is pushed downstream and reaches a predetermined pressure. Moreover, the present inventor shows that the above phenomenon appears remarkably in the inlet-side heat exchange section through which refrigerant (gas-liquid mixed refrigerant) having a low dryness (= high wetness) flows (= wetness). However, it does not appear so conspicuously in the outlet side heat exchange section through which the refrigerant (gas phase refrigerant) flows, but rather in the outlet side heat exchange section, the volume expansion of the refrigerant causes a problem of flow resistance, and the volume of the refrigerant is the largest. At the same time, we found out that the distribution resistance in the most downstream path becomes larger.

  FIG. 15 is a supplementary explanatory diagram showing the temperature distribution when all the rooms 130a to 130f are used as upward flow paths. As shown in FIG. 15, it can be seen that as the downstream path increases, the degree of dryness of the refrigerant increases and the flow rate of the refrigerant increases, so that the temperature distribution is less uneven.

  Therefore, the present inventor has increased the amount of liquid-phase refrigerant on the upstream side in the longitudinal direction of the tank by reducing the number of heat exchange passages of the upflow bath in the inlet side heat exchanger, and reduced the temperature unevenness, and the outlet side heat. In the exchanger, the technical idea of preventing an increase in the flow resistance was conceived by increasing the number of heat exchange passages in the most downstream path than the number of heat exchange passages in the immediately downstream pass.

In the first aspect of the present invention, a heat exchange passage that extends in the vertical direction and is laminated in a plurality of stages in the lateral direction and flows the refrigerant therein, and a heat exchange path provided at both upper and lower ends of the plurality of heat exchange paths in the plurality of stages. And a tank for merging and distributing the refrigerant from
Two heat exchange parts are connected so that the heat exchange part is arranged in two layers in the direction of the air flow and the refrigerant is circulated through one heat exchange part and then the refrigerant is circulated through the other heat exchange part. An evaporator,
Setting the heat exchange part on the inlet side of the refrigerant to two or more paths, setting the heat exchange part on the outlet side of the refrigerant to two or more paths,
In the inlet side heat exchange unit, the number of heat exchange passages in the upward flow path in which the refrigerant becomes an upward flow is smaller than the number of heat exchange passages in the downward flow path in which the refrigerant becomes a downward flow, and in the outlet side heat exchange unit Is characterized in that the number of heat exchange passages in the most downstream path is larger than the number of heat exchange passages in the immediately downstream pass.

  The invention according to claim 2 is the evaporator according to claim 1, wherein the number of passes is equal in both heat exchanging portions, and the flow direction of the refrigerant in the opposite windward path and the leeward path is reversed. It is characterized by having become.

  The invention of claim 3 is the evaporator of claim 1, characterized in that the number of passes of the outlet side heat exchange section is smaller than the number of passes of the inlet side heat exchange section.

  Invention of Claim 4 is an evaporator of any one of Claims 1-3, Comprising: The said exit side heat exchange part is set to 3 paths or more, and the refrigerant | coolant downstream path | pass in the said exit side heat exchange part The feature is that the number of heat exchange passages is increased.

  Invention of Claim 5 is an evaporator of any one of Claims 1-4, Comprising: The said exit side heat exchange part is set to 3 or more paths, The said most downstream path | pass in the said exit side heat exchange part The number of heat exchange passages in the upward flow path is made smaller than the number of heat exchange passages in the downward flow path.

  The invention according to claim 6 is the evaporator according to any one of claims 1 to 5, wherein the inlet side heat exchange section is set to three or more passes.

  Invention of Claim 7 is an evaporator of any one of Claims 1-6, Comprising: The said inlet side heat exchange part has been arrange | positioned in the leeward side, and the said outlet side heat exchange part has been arrange | positioned in the leeward side. It is characterized by.

  According to the first aspect of the present invention, in the inlet side heat exchange section, the number of heat exchange passages in the upward flow path where the refrigerant becomes an upward flow is smaller than the number of heat exchange passages in the downward flow path. Can be reduced. Moreover, in the outlet side heat exchanging section, the number of heat exchange passages in the most downstream path where the volume of circulation refrigerant expands most is larger than the number of heat exchange passages in the path immediately before the most downstream, so that an increase in circulation resistance can be suppressed. it can. As a result, an evaporator with low temperature distribution unevenness and low flow resistance can be realized.

  According to the invention of claim 2, in addition to the effect of the invention of claim 1, a state in which the temperature distributions of the two heat exchange parts are superposed or predicted is compared with an evaporator having two heat exchange parts with different paths. Easy to manage because it is easy to simulate. In addition, in invention of Claim 1, an evaporator with which the number of passes differs in two heat exchange parts, and especially an evaporator in which the number of passes differs in two heat exchange parts like this preferable.

  According to the invention of claim 3, in addition to the effect of the invention of claim 1, the number of passes of the outlet side heat exchange unit is smaller than the number of passes of the inlet side heat exchange unit. The total passage cross-sectional area at (the sum of the passage cross-sectional areas of the heat exchange passages in each pass) increases. Therefore, the passage cross-sectional area in each path is increased and the passage resistance is reduced. As a result, it is suitable when it is required to further reduce the passage resistance of the outlet side heat exchange section.

  According to the invention of claim 4, in addition to the effect of the invention of any one of claims 1 to 4, the outlet side heat exchange section has a structure in which the number of heat exchange passages is increased toward the downstream side, that is, the refrigerant Since the total passage cross-sectional area of the path is enlarged along the volume expansion of the path, the passage resistance at the outlet side heat exchange section can be minimized.

  According to the invention of claim 5, in addition to the effect of any one of claims 1 to 3, the outlet side heat exchanging section has an upward flow path that is larger than the number of heat exchange passages of the downflow path except for the most downstream path. Because the number of heat exchange passages is reduced, the temperature distribution in the outlet side heat exchange section can be further improved (refer to claim 1), and in the outlet side heat exchange section, it is desired to prioritize the temperature distribution uniformity over the passage resistance reduction. This is an effective structure.

  In particular, in the structure in which claim 5 and claim 4 are combined, the uniformity of the temperature distribution can be further improved while the passage resistance is extremely reduced in the outlet side heat exchange section.

  According to the invention of claim 6, in addition to the effects of the invention of any one of claims 1 to 5, since the inlet-side heat exchange part is set to three or more passes, the temperature distribution unevenness of the inlet-side heat exchange part is further reduced. it can.

  According to the invention of claim 7, in addition to the effects of any one of claims 1 to 6, the inlet side heat exchange part is arranged on the leeward side and the outlet side heat exchange part is arranged on the leeward side. Then, the air that is ventilated by the outlet side heat exchanger is cooled, and then this cooled air can be further cooled by the inlet side heat exchange section at a lower temperature than the outlet side heat exchange section. That is, the air can be cooled stepwise by the heat exchange section on the leeward side and the leeward side. As a result, the windward and leeward heat exchange sections can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  1st Embodiment: FIGS. 1-6 is a figure explaining the evaporator of 1st Embodiment of this invention.

  The evaporator 1 according to the first embodiment is an evaporator interposed in a refrigeration cycle of an automotive air conditioner, and is installed in an air conditioning case arranged inside an instrument panel, and flows through the refrigerant. Heat is exchanged with the air passing through the outside, and the refrigerant is evaporated to cool the air. The evaporator of the present invention is not limited to a vehicle air conditioner and can be used in other fields.

  First, the overall structure in the evaporator will be described with reference to FIG.

  The evaporator 1 is an evaporator in which a heat exchange section 10 on the refrigerant inlet side and a heat exchange section 20 on the refrigerant outlet side are arranged in parallel on the windward side and the leeward side.

  The inlet-side heat exchange unit 10 includes an upper tank 11, a lower tank 12, and a plurality of heat exchange passages connected in communication between the tanks 11 and 12. On the other hand, the outlet side heat exchanging unit 20 includes an upper tank 21 and a lower tank 22 and a plurality of heat exchange passages connected in communication between the tanks 21 and 22.

  In the inlet-side heat exchange unit 10, the upper tank 11 is partitioned into an upper first tank unit 11 a and an upper second tank unit 11 b by a partition unit 51, while the lower tank 12 is partitioned by the partition unit 51 into the lower first tank unit 12 a and It is partitioned into a lower second tank portion 12b. An evaporator inlet 7 is provided at the right end of the upper tank 11, and a plurality of heat exchange passage groups stacked in multiple stages are divided into a first path 10a, a second path 10b, and a third path 10c in order from right to left. Will be. As a result, the refrigerant introduced from the evaporator inlet 7 to the outlet side heat exchange unit 20 is the upper first tank part 11a → the first path 10a → the lower first tank part 12a → the second path 10b → the upper second tank part 11b. → The third path 10c → the lower second tank portion 12b flows in this order. Then, the refrigerant is introduced from the most downstream part (lower second tank part 12b) of the outlet side heat exchange part 20 into the most upstream part (lower first tank part 22a) of the outlet side heat exchange part 20 through the communication path 9. Is done.

  On the other hand, in the outlet-side heat exchange unit 20, the lower tank 22 is partitioned into a lower first tank portion 22 a and a lower second tank portion 22 b by a partition portion 51, while the upper tank 21 is partitioned into an upper first tank portion by a partition portion 51. The evaporator outlet 8 is provided at the right end of the upper tank 21, which is partitioned into 21 a and an upper second tank portion 21 b. As a result, the heat exchange passage groups stacked in multiple stages are partitioned into a first path 20a, a second path 20b, and a third path 20c in order from left to right. The refrigerant introduced from the communication path 9 to the outlet side heat exchanging unit 20 is the lower first tank unit 22a → first path 20a → upper first tank unit 21a → second path 20b → lower second tank unit 22b → third. It flows in the order of the path 20c → the upper second tank portion 21b. Then, this refrigerant is led out from the evaporator 1 from an evaporator outlet 8 provided at the right end of the upper second tank portion 21b as the most downstream part of the windward heat exchange part (heat exchange part downstream of the refrigerant) 20. The

  The evaporator 1 includes a plurality of (three in this example) paths (10a, 10b, 10c, 20a, 20b) in which each of the heat exchange units 10, 20 has the same number of meanders in both the heat exchange units 10, 20. , 20c), and the paths that are overlapped on the windward side and the leeward side (for example, the first path 10a of the inlet-side heat exchange unit 10 and the third path 20c of the outlet-side heat exchange unit 20). The refrigerant flows in opposite directions including the flow in the upstream and downstream tank portions.

  Next, the manufacturing process of the evaporator 1 according to the first embodiment will be supplemented. In this evaporator 1, tubes 30 arranged in the vertical direction are stacked in a plurality of stages in the horizontal direction with outer fins 33 interposed therebetween, and the strength is strengthened on the outermost side in the tube stacking direction (outermost in the horizontal direction). The side plates 35 and 37, the pipe connector 36, etc. are attached to be in a predetermined evaporator shape, and are manufactured by brazing together (see FIGS. 1, 2, and 3). 1 and 2, reference numeral 34 denotes an outermost metal thin plate.

  As shown in FIG. 3, the tube 30 to be used is formed by joining the pair of thin metal plates 40A and 40B in the middle with the inner fins 61 and 61 sandwiched between the pair of thin metal plates 40A and 40B. In the tube 30, two heat exchange passages 31, 31 are formed inside the tube 30 to flow the refrigerant across the central partition portion 30 a, and the tube 30 wall is outward from both ends of each heat exchange passage 31. The tank parts 32 and 32 which protrude in a cylinder shape toward are formed. The thin metal plates 40A and 40B forming the tube 30 correspond to the two passages 31 and 31 of the tube 30 and the four tank portions 32 and 32, and the two heat exchange passage recesses 41 and 42, respectively. And four tank parts 43, 44, 45, 46. Moreover, the metal thin plate 40A and the metal thin plate 40B have the same shape, and the thin metal plate 40A is the metal thin plate 40B, and the thin metal plate 40B is the thin metal plate 40A.

  The partition part 51 formed in the tanks 11, 12, 21, and 22 of each of the heat exchange parts 10 and 20 described above is a metal thin plate 50 provided with a blocking part for constituting the partition part 51 shown in FIG. It is formed by using instead of the metal thin plates 40A and 40B at the stacking position.

"Feature point"
Next, features of the first embodiment will be described with reference to FIGS. 2 and 6. The first embodiment is characterized by a path section set by the arrangement position of the metal thin plate 50.

  First, in the inlet-side heat exchange unit 10, the number of heat exchange passages in the second path 10b as the upward flow path is made smaller than the number of heat exchange passages in the first path 10a and the third path 10c as the downward flow path. is there. In other words, the relationship between the total passage sectional area S10c of the upward flow path 10b and the total passage sectional areas S10a, S10c of the downward flow paths 10a, 10c is set to satisfy S10a, S10c> S10b, and at the same time, the upward flow path 10b. The relationship between the size L10b in the tank longitudinal direction (horizontal direction) and the size L10a and L10c in the tank longitudinal direction (horizontal direction) of the downflow paths 10a and 10c is such that L10a, L10c> L10b. In the present specification, the “total passage cross-sectional area of the path” means (the number of heat exchange paths of the path) × (the cross-sectional area of the heat exchange path).

  For this reason, in the inlet-side heat exchange unit 10 through which the gas-liquid mixed refrigerant having a low dryness (= high wetness) flows, as shown in FIG. 6a, the upstream side in the tank longitudinal direction in the upward flow path 10b (FIG. 6). The amount of the liquid refrigerant on the middle left side increases, and the region where the liquid refrigerant is insufficient in the upward flow path 10b decreases. Thereby, the temperature nonuniformity in the inlet side heat exchange part 10 becomes small.

  On the other hand, in the outlet side heat exchange section 20, the number of heat exchange passages is increased in the downstream path. In other words, the relationship between the total passage sectional area S20a of the first path 20a, the total passage sectional area S20b of the second path, and the total passage sectional area S20c of the third path 20c becomes S20c> S20b> S20a, and at the same time A tank longitudinal direction (horizontal direction) size L20a of 20a, a tank longitudinal direction (horizontal direction) size L20b of the second pass 20b, and a tank longitudinal direction (horizontal direction) size L20c of the third pass 20c. The relationship is L20c> L20b> L20a.

  For this reason, in the outlet-side heat exchange unit 20 through which the gas-liquid mixed refrigerant or the gas-phase refrigerant having a high degree of dryness (= low degree of wetness) and volume expansion flows, the third downstream path as a problem of flow resistance. The flow resistance in the path 20c is reduced, and the passage resistance in the outlet side heat exchange unit 20 is reduced.

  In this embodiment, the number of heat exchange passages in the upflow path 20a is smaller than the number of heat exchange passages in the downflow path 20b except for the most downstream path 20c. Therefore, the total passage sectional area S20a of the first path 20a as the upward flow path is smaller than the total passage sectional area S20b of the second path 20b as the downward flow path except for the third path 20c as the most downstream path. Yes. As a result, the amount of liquid-phase refrigerant on the upstream side in the longitudinal direction of the tank in the upward flow path 20a is increased, and the region where the liquid-phase refrigerant in the upward flow path is insufficient is reduced. Thereby, the temperature nonuniformity in the exit side heat exchange part 20 is further reduced.

"effect"
Next, the effects of the evaporator 1 of the first embodiment will be summarized.

  (I) According to the first embodiment, in the inlet-side heat exchange unit 10 where the dryness of the refrigerant is low and the flow distribution of the liquid-phase refrigerant is easily biased, the number of heat exchange passages of the upflow path 10b is reduced. Since the number of heat exchange passages in the paths 10a and 10c is smaller (S10a, S10c> S10b), the liquid-phase refrigerant that flows to the upstream side in the longitudinal direction of the tank where the liquid-phase refrigerant tends to be insufficient in the upward flow path 10b (see FIG. 6 middle dotted line portion) increases, the liquid-phase refrigerant shortage region decreases, and the temperature distribution unevenness decreases.

  Further, in the outlet side heat exchanging unit 20 that has a high degree of dryness and the distribution distribution of the refrigerant (gas-liquid mixed refrigerant or gas phase refrigerant) is less likely to be biased, the heat exchange passage of the most downstream path 20c in which the volume of the circulating refrigerant expands most. Since the number of heat exchange passages is greater than the number of heat exchange passages in the immediately downstream path 20b (S20c> S20b), an increase in the flow resistance in the most downstream path 20c is suppressed, and the flow resistance in the outlet side heat exchange section 20 is low. It can be suppressed.

  As a result, it is possible to realize an evaporator with small temperature distribution unevenness and low flow resistance.

  (II) In particular, according to the first embodiment, the outlet side heat exchanging unit 20 is set to three or more passes, and the downstream pass where the refrigerant volume expands has a structure in which the number of heat exchange passages is increased. Since the structure is S20c> S20b> S20a, the structure is most suitable for reducing the passage resistance in the outlet-side heat exchange unit 20.

  (III) Moreover, according to this 1st Embodiment, the number of paths (three in this example) of both the heat exchange parts 10 and 20 is set identically, and the paths (10a and 20c) which face each other toward the ventilation direction Since (10b and 20b) (10c and 20a) have a structure in which the refrigerant flow directions are reversed, evaporators having different numbers of passes between the two heat exchange units 10 and 20 (e.g., evaporation in the fourth embodiment) Compared to the evaporator 400 and the evaporator 700) of the seventh embodiment, it is easier to predict or simulate the state in which the temperature distributions of the two heat exchanging units 10 and 20 are overlapped and manage.

  (IV) Further, according to the first embodiment, the number of heat exchange passages in the upflow path 20a is made smaller than the number of heat exchange passages in the downflow path 20b except for the most downstream path 20c in the outlet side heat exchange section 20. Because of the structure, that is, the structure of S20b> S20a, the temperature distribution at the outlet side heat exchanging unit 20 can be further improved.

  (V) Further, according to the first embodiment, since the inlet side heat exchanging unit 10 is configured to have three or more passes, the structure is less than two passes (for example, the second embodiment and the third embodiment). Since the total passage sectional areas S10a, S10b, and S10c of the paths 10a, 10b, and 10c are reduced, the temperature distribution unevenness of the inlet side heat exchange unit 10 can be further reduced.

  (VI) Also, according to the first embodiment, the inlet side heat exchange unit 10 is arranged on the leeward side and the outlet side heat exchange unit 20 is arranged on the leeward side. The air is cooled at 20, and the cooled air can be further cooled at the inlet-side heat exchange unit 10, which is at a lower temperature than the leeward-side outlet-side heat exchange unit 20. That is, the air can be cooled stepwise by the outlet side heat exchange unit 20 and the inlet side heat exchange unit 10. As a result, the heat exchange units 20 and 10 on the windward side and the leeward side can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Hereinafter, other embodiments of the present invention will be described. In the following embodiments, detailed drawings are omitted, and the same or similar configurations as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  Second Embodiment: FIG. 7 shows an evaporator according to a second embodiment.

  In the evaporator 200 of the second embodiment, the inlet side heat exchange unit 10 has two passes and the outlet side heat exchange unit 220 has two passes by setting the partition 51. It differs from the evaporator 1 of 1st Embodiment which is 3 passes and the exit side heat exchange parts 20 are 3 passes.

  Since the second embodiment has the following configuration, the same effects (I), (III), and (VI) as those in the first embodiment except for (II), (IV), and (V) can be obtained.

  (I) In the evaporator 200 of the second embodiment, the number of heat exchange passages of the second path (upflow path) 210b is changed to the first path (downflow) in the inlet-side heat exchange unit 210, as in the first embodiment. (Path) 210a is less than the number of heat exchange passages (S210b <S210a), and in the outlet side heat exchange section 220, the number of heat exchange passages of the second path (the most downstream path) 220b is the first path. This is a structure (S220a <S220b) that is larger than the number of heat exchange passages in the most downstream downstream path 220a. Therefore, in the inlet side heat exchanging section 210, the liquid phase refrigerant that tends to be short of the liquid phase refrigerant in the upstream flow path 210b increases on the upstream side in the longitudinal direction of the tank, the liquid phase refrigerant shortage region is reduced, and the temperature distribution unevenness is reduced. . Further, in the outlet side heat exchange unit 220, the increase in the flow resistance in the most downstream path 220b is suppressed, and the flow resistance in the outlet side heat exchange unit 220 is suppressed low. As a result, an evaporator with low temperature distribution unevenness and low flow resistance can be realized.

  (III) Moreover, 2nd Embodiment sets the number of the paths (two in this example) of both the heat exchange parts 210 and 220 similarly to 1st Embodiment, and the paths which face toward the ventilation direction (210a and 220b) (210b and 220a) is a structure in which the flow direction of the refrigerant is reversed. Therefore, compared with the evaporators (for example, the evaporator 400 of the fourth embodiment and the evaporator 700 of the seventh embodiment) in which the number of passes is different between the two heat exchange units 210 and 220, the temperatures of the two heat exchange units 210 and 220 are different. It is easy to predict or simulate the superposition of distributions and to manage them.

  (VI) Moreover, this 2nd Embodiment is the structure which has arrange | positioned the entrance side heat exchange part 210 in the leeward side, and has arrange | positioned the exit side heat exchange part 220 in the leeward side like 1st Embodiment. Therefore, the air is first cooled by the outlet-side heat exchange unit 220 on the windward side, and then the cooled air can be further cooled by the inlet-side heat exchange unit 210 having a temperature lower than that of the outlet-side heat exchange unit 220. That is, the air can be cooled stepwise by the outlet side heat exchange unit 220 and the inlet side heat exchange unit 210. As a result, the heat exchange units 220 and 210 on the windward side and the leeward side can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Third Embodiment: FIG. 8 shows a third embodiment of the present invention.

  The evaporator 300 according to the third embodiment has the same configuration as that of the evaporator 200 according to the second embodiment except that the flow direction of the refrigerant is upside down from the evaporator 200 according to the second embodiment. As will be described below, the same effect as the evaporator 200 of the second embodiment can be obtained.

  (I) In the evaporator 300 of the third embodiment, the number of heat exchange passages in the first path 310a as the upward flow path in the inlet side heat exchange unit 310 is the number of heat exchange passages in the second path 310b as the downward flow path. And the number of heat exchange passages in the second path 320b as the most downstream path in the outlet side heat exchange section 320 of the first path 320a as the most downstream immediately preceding path is smaller (S310a <S310b). The structure is larger than the number of heat exchange passages (S320b> S320a). Therefore, in the inlet side heat exchanging section 310, the liquid phase refrigerant that tends to be short of the liquid phase refrigerant in the upstream flow path 310a increases on the upstream side in the longitudinal direction of the tank, the liquid phase refrigerant shortage region is reduced, and the temperature distribution unevenness is reduced. . Further, in the outlet side heat exchange unit 320, the increase in the flow resistance in the most downstream path 320b is suppressed, and the flow resistance in the outlet side heat exchange unit 320 is suppressed low. As a result, an evaporator with low temperature distribution unevenness and low flow resistance can be realized.

  (III) Moreover, the evaporator 300 of this 3rd Embodiment sets the number of paths (two in this example) of both the heat exchange parts 310 and 320 to the same, and the path | passes (310a and 310a) which opposes toward a ventilation direction. 320b) (310b and 320a) has a structure in which the flow direction of the refrigerant is reversed. Therefore, compared with the evaporators (for example, the evaporator 400 of the fourth embodiment and the evaporator 700 of the seventh embodiment) in which the number of passes is different between the two heat exchange units 310 and 320, the temperatures of the two heat exchange units 310 and 320 are different. It is easy to predict or simulate the superposition of distributions and to manage them.

  (VI) Further, the evaporator 300 of the third embodiment has a structure in which the inlet side heat exchange unit 310 is arranged on the leeward side and the outlet side heat exchange unit 320 is arranged on the leeward side. Therefore, the air is first cooled by the outlet side heat exchange unit 320 on the windward side, and then the cooled air can be further cooled by the inlet side heat exchange unit 310 that is lower in temperature than the outlet side heat exchange unit 320. That is, the air can be cooled stepwise by the outlet side heat exchange unit 320 and the inlet side heat exchange unit 310. As a result, the windward and leeward heat exchange units 320 and 310 can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Fourth Embodiment: FIG. 9 shows a fourth embodiment of the present invention.

  The evaporator 400 according to the fourth embodiment is different from the evaporator 1 according to the first embodiment in that the outlet side heat exchanging section 420 has two passes, and the other configurations are substantially the same as those in the first embodiment. It has become. According to the evaporator 400 of this 4th Embodiment, since it is the following structures, (I) (V) (VI) similar to 1st Embodiment except (II) (III) (IV) In addition, the effect of (VII) is also obtained.

  (I) In the fourth embodiment, in the inlet side heat exchanging section 410, the number of heat exchange passages in the second path 410b as the upflow path is the heat of the first path 410a and the third path 410c as the downflow path. The number of exchange passages is smaller (S410a, S410c> S410b), and in the outlet side heat exchange section 420, the heat exchange passage of the second path 420b as the most downstream path in which the volume of the circulating refrigerant expands most. This is a structure (S420b> S420a) in which the number is larger than the number of heat exchange passages of the first path 420a as the immediately downstream path.

  Therefore, in the inlet side heat exchanging section 410 that has a low dryness and tends to be biased in the distribution of refrigerant, the amount of liquid phase refrigerant that flows upstream in the longitudinal direction of the tank, which tends to be insufficient in the upward flow path 410b, increases. The liquid-phase refrigerant shortage area is reduced, and the temperature distribution is less uneven. Further, in the outlet side heat exchanging section 420, which has a high degree of dryness and the distribution distribution of the refrigerant is less likely to be biased, an increase in the distribution resistance in the most downstream path 420b where the volume of the circulating refrigerant expands is suppressed, and the outlet side heat exchange is performed. The distribution resistance in the part 420 is kept low. As a result, it is possible to realize an evaporator with small temperature distribution unevenness and low flow resistance.

  (V) Moreover, this 4th Embodiment is the structure which set the entrance side heat exchange part 410 to 3 or more passes. Therefore, the total passage cross-sectional areas S410a, S410b, and S410c of each of the paths 410a, 410b, and 410c are smaller than the structure of two paths or less (for example, the second embodiment and the third embodiment). The unevenness of the temperature distribution can be further reduced.

  (VI) Moreover, this 4th Embodiment is the structure which has arrange | positioned the inlet side heat exchange part 410 in the leeward side, and has arrange | positioned the outlet side heat exchange part 420 in the leeward side. Therefore, the air is first cooled by the outlet side heat exchange unit 420 on the windward side, and then the cooled air can be further cooled by the inlet side heat exchange unit 410 having a temperature lower than that of the outlet side heat exchange unit 420. That is, the air can be cooled stepwise by the outlet side heat exchange unit 420 and the inlet side heat exchange unit 410. As a result, the heat exchange units 420 and 410 on the windward side and the leeward side can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  (VII) Further, according to the evaporator 400 of the fourth embodiment, the number of passes of the outlet side heat exchange unit 420 (two in this example) is more than the number of passes of the inlet side heat exchange unit 410 (three in this example). ). Therefore, in the outlet side heat exchange section 420, the total passage sectional areas S410a and S410b in the paths 410a and 410b are increased. As a result, it is suitable when it is required to further reduce the passage resistance of the outlet side heat exchanging section 420.

  Fifth Embodiment: FIG. 10 shows an evaporator 500 according to a fifth embodiment.

  In the evaporator 500 of the fifth embodiment, the refrigerant flow direction is reversed upside down from that of the evaporator 1 of the first embodiment, and the outlet side heat exchange unit 520 is lowered except for the most downstream path 520c. The structure is the same as that of the first embodiment except that the number of heat exchange passages in the upward flow path 520b is not larger than the number of heat exchange passages in the flow path 520a. Since the fifth embodiment has the following configuration, the same effects (I), (II), (III), (V), and (VI) as those in the first embodiment except for (IV) can be obtained.

  (I) In the evaporator 500 of the fifth embodiment, in the inlet-side heat exchange unit 510, the number of heat exchange passages of the first path 510a and the third path 510c as the upflow path is the second as the downflow path. The number of heat exchange passages in the path 510b is smaller (510a, S510c <S510b), and the outlet side heat exchange section 520 has a third path 520c as the most downstream path in which the volume of the circulating refrigerant expands most. The number of heat exchange passages is larger than the number of heat exchange passages of the second path 520b as the immediately downstream pass (S520c> S520b). Therefore, in the inlet side heat exchanging portion 510 having a low dryness and a tendency to be biased in the distribution of refrigerant, the liquid phase refrigerant flowing upstream in the longitudinal direction of the tank, which tends to be short of the liquid phase refrigerant in the upward flow paths 510c and 510a. It increases and the liquid-phase refrigerant shortage area decreases, and the temperature distribution unevenness decreases. Further, in the outlet side heat exchange section 520 that has a high degree of dryness and the distribution distribution of the refrigerant is less likely to be biased, an increase in circulation resistance in the most downstream path 520c in which the volume of the circulation refrigerant expands most is suppressed, and the outlet side heat exchange section. The flow resistance at 520 is kept low. As a result, it is possible to realize an evaporator with small temperature distribution unevenness and low flow resistance.

  (II) Further, according to the evaporator 500 of the fifth embodiment, the outlet side heat exchange section 520 is set to three or more passes, and the number of heat exchange passages is increased in the downstream pass where the refrigerant volume expands ( S520c> S520b> S520a). Therefore, it becomes the most suitable structure for reducing the passage resistance in the outlet side heat exchange section 20.

  (III) According to the fifth embodiment, the number of paths (three in this example) of both the heat exchanging units 510 and 520 are set to be the same, and the paths facing each other in the ventilation direction (510a and 520c). (510b and 520b) (510c and 520a) is a structure in which the flow direction of the refrigerant is reversed. Therefore, compared with the evaporators (for example, the evaporator 400 of the fourth embodiment and the evaporator 700 of the seventh embodiment) in which the number of passes is different between the two heat exchange units 510 and 520, the temperatures of the two heat exchange units 510 and 520 are different. It is easy to predict or simulate the superposition of distributions and to manage them.

  (V) Moreover, since the evaporator 500 of this 5th Embodiment is the structure which set the inlet side heat exchange part 510 to 3 or more paths, it is a structure of 2 paths or less (for example, 2nd Embodiment or 3rd Embodiment). Since the total passage cross-sectional areas S510a, S510b, and S510c of the paths 510a, 510b, and 510c are smaller than the above, the temperature distribution unevenness of the inlet-side heat exchange unit 510 can be further reduced.

  (VI) Further, the evaporator 500 of the fifth embodiment has a structure in which the inlet side heat exchange unit 510 is arranged on the leeward side and the outlet side heat exchange unit 520 is arranged on the leeward side. Therefore, the air is first cooled by the outlet side heat exchange unit 520 on the windward side, and the cooled air can be further cooled by the inlet side heat exchange unit 510 having a temperature lower than that of the outlet side heat exchange unit 520. That is, the air can be cooled stepwise by the outlet side heat exchange unit 520 and the inlet side heat exchange unit 510. As a result, the windward and leeward heat exchange units 520 and 510 can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Sixth Embodiment: FIG. 11 shows an evaporator 600 according to a sixth embodiment of the present invention. The evaporator 600 of this sixth embodiment is different from the first embodiment in that it is set to four paths at the inlet-side heat exchange unit 610 and the outlet-side heat exchange unit 620, and other than that of the first embodiment. The configuration is almost the same. Since the sixth embodiment has the following configuration, the same effects (I), (II), (III), (V), and (VI) as those of the evaporator 1 of the first embodiment except for (IV) are obtained. can get.

  (I) In the evaporator 600 of the sixth embodiment, in the inlet-side heat exchange unit 610, the number of heat exchange passages of the second path 610b and the fourth path 610d as the upflow path is the first as the downflow path. It is a structure (S610a, S610c> S610b, 610d) in which the number of heat exchange passages of the path 610a and the third path 610c is reduced, and the most downstream of the outlet side heat exchange unit 620 where the volume of the circulating refrigerant expands In this structure, the number of heat exchange passages in the fourth path 620d as the path is larger than the number of heat exchange passages in the third path 620c as the immediately downstream path (S620d> S620c). Therefore, in the inlet-side heat exchange unit 610 that has a low degree of dryness and tends to be biased in the distribution of refrigerant, the liquid-phase refrigerant that flows to the upstream side in the longitudinal direction of the tank, where the liquid-phase refrigerant tends to be insufficient in the upward flow paths 610b and 610d. It increases and the liquid-phase refrigerant shortage area decreases, and the temperature distribution unevenness decreases. Further, in the outlet side heat exchange unit 620 that has a high degree of dryness and the distribution distribution of the refrigerant is less likely to be biased, an increase in circulation resistance in the most downstream path 620d in which the volume of the circulation refrigerant expands is suppressed, and the outlet side heat exchange unit The distribution resistance at 620 is kept low.

  (II) In particular, the evaporator 600 of the sixth embodiment has a structure in which the outlet side heat exchange section 620 is set to three or more passes, and the number of heat exchange passages is increased in the downstream pass where the refrigerant volume expands (S620d> Since S620c> S620b> S620a), the structure is most suitable for reducing the passage resistance in the outlet side heat exchange section 620.

  (III) Further, the evaporator 600 of the sixth embodiment sets the same number of paths (four in this example) for both the heat exchangers 610 and 620, and faces the paths (610a and 610a) facing each other in the ventilation direction. 620d) (610b and 620c) (610c and 620b) (610d and 620a) are configured such that the refrigerant flow directions are reversed. Therefore, compared with the evaporators (for example, the evaporator 400 of the fourth embodiment and the evaporator 700 of the seventh embodiment) in which the number of passes is different between the two heat exchange units 610 and 620, the temperatures of the two heat exchange units 610 and 620 are different. It is easy to predict or simulate the superposition of distributions and to manage them.

  (V) Moreover, the evaporator 600 of this 6th Embodiment is the structure which set the entrance side heat exchange part 610 to 3 or more passes. Therefore, the total passage cross-sectional area S610a, S610b, S610c, 610d of each path 610a, 610b, 610c, 610d is smaller than the structure of two paths or less (for example, the second embodiment or the third embodiment), so that the entrance side Unevenness in the temperature distribution of the heat exchange unit 610 can be further reduced.

  (VI) Moreover, the evaporator 600 of this 6th Embodiment is the structure which has arrange | positioned the inlet side heat exchange part 610 in the leeward side, and has arrange | positioned the outlet side heat exchange part 620 in the leeward side. Therefore, the air is first cooled by the outlet side heat exchange unit 620 on the windward side, and then the cooled air can be further cooled by the inlet side heat exchange unit 610 having a temperature lower than that of the outlet side heat exchange unit 620. That is, the air can be cooled stepwise by the outlet side heat exchange unit 620 and the inlet side heat exchange unit 610. Thereby, the heat exchange units 620 and 610 on the windward side and the leeward side can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  Seventh Embodiment: FIG. 12 shows an evaporator 700 according to a seventh embodiment of the present invention. The evaporator 700 of the seventh embodiment has substantially the same configuration as that of the sixth embodiment, except that the outlet side heat exchange unit 720 is configured with two passes.

  According to the seventh embodiment, since it has the following configuration, in addition to the same effects (I), (V), and (VI) as in the first embodiment except (II), (III), and (IV), The effect of (VII) described later can also be obtained.

  (I) In the evaporator 700 of the seventh embodiment, in the inlet-side heat exchange unit 710, the number of heat exchange passages of the second path 710b and the fourth path 710d as the upward flow path is the first as the downward flow path. The structure S710a, S710c> S710b, 710d) in which the number of heat exchange passages of the path 710a and the third path 710c is smaller than that of the path 710a and the third path 710c. The number of heat exchange passages in the second path 720b as the number of heat exchange passages is larger than the number of heat exchange passages in the first path 720a as the most immediately downstream path (S720b> S720a). Therefore, in the inlet-side heat exchange unit 710 that has a low dryness and tends to be biased in the refrigerant distribution, the liquid-phase refrigerant that flows to the upstream side in the tank longitudinal direction, where the liquid-phase refrigerant tends to be insufficient in the upward flow paths 710b and 710d, It increases and the liquid-phase refrigerant shortage area decreases, and the temperature distribution unevenness decreases. Further, in the outlet side heat exchange unit 720 that has a high degree of dryness and is less likely to be biased in the distribution of refrigerant, an increase in circulation resistance in the most downstream path 720b in which the volume of the circulating refrigerant expands is suppressed, and the outlet side heat exchange unit The distribution resistance at 720 is kept low.

  (V) Moreover, the evaporator 700 of this 7th Embodiment is the structure which set the entrance side heat exchange part 710 to 3 or more passes. Therefore, since the total passage cross-sectional areas S710a, S710b, S710c, and 710d of each path 710a, 710b, 710c, and 710d are smaller than the structure of two paths or less (for example, the second embodiment or the third embodiment), the entrance side Unevenness in the temperature distribution of the heat exchange unit 710 can be further reduced.

  (VI) Further, the evaporator 700 of the seventh embodiment has a structure in which the inlet side heat exchange unit 710 is arranged on the leeward side and the outlet side heat exchange unit 720 is arranged on the leeward side. Therefore, the air is first cooled by the outlet side heat exchange unit 720 on the windward side, and then the cooled air can be further cooled by the inlet side heat exchange unit 710 having a temperature lower than that of the outlet side heat exchange unit 720. That is, the air can be cooled stepwise by the outlet side heat exchange unit 720 and the inlet side heat exchange unit 710. As a result, the heat exchange units 720 and 710 on the windward side and the leeward side can be efficiently used without waste, and the heat exchange efficiency can be further improved.

  (VII) In the seventh embodiment, the number of paths (two in this example) of the outlet side heat exchange section 720 is smaller than the number of paths of the inlet side heat exchange section 710 (four in this example). is there. Therefore, in the outlet side heat exchange unit 720, the total passage cross-sectional areas S720a and S720b in the paths 720a and 720b are increased. As a result, it is suitable when it is required to further reduce the passage resistance of the outlet side heat exchange section 720.

  In short, the present invention has a structure in which the number of heat exchange passages in the upflow path is smaller than the number of heat exchange passages in the downflow path in the inlet-side heat exchange section that has a low dryness and tends to be biased in the distribution of refrigerant. Therefore, the liquid phase refrigerant that tends to run out of liquid phase refrigerant in the upward flow path increases in the upstream side in the longitudinal direction of the tank, the liquid phase refrigerant shortage region decreases, and the temperature distribution unevenness is reduced. In addition, in the outlet side heat exchange section where the degree of dryness is high and the distribution of refrigerant is less likely to be biased, the number of heat exchange passages in the most downstream path where the volume of circulation refrigerant expands is more than the number of heat exchange passages in the immediately downstream path. Therefore, the increase in the flow resistance in the most downstream path is suppressed, and the flow resistance in the outlet side heat exchange section is suppressed to a low level. Thereby, it becomes an evaporator with small nonuniformity of temperature distribution and low flow resistance.

FIG. 1 is a front view of the evaporator according to the first embodiment as viewed from the windward side. FIG. 2 is a top view of the evaporator. FIG. 3 is a perspective view showing the structure of the tube. FIG. 4 is a perspective view showing a thin metal plate having a closing portion that constitutes a partition portion of the tank. FIG. 5 is a schematic view showing the flow of the refrigerant in the evaporator. FIG. 6 is a schematic diagram showing the distribution of the liquid refrigerant in the evaporator. FIG. 7 is a schematic view showing an evaporator according to the second embodiment. FIG. 8 is a schematic view showing an evaporator according to a third embodiment. FIG. 9 is a schematic view showing an evaporator according to a fourth embodiment. FIG. 10 is a schematic view showing an evaporator according to a fifth embodiment. FIG. 11 is a schematic view showing an evaporator according to a sixth embodiment. FIG. 12 is a schematic view showing an evaporator according to a seventh embodiment. FIG. 13 is a schematic view showing an example of a conventional evaporator. FIG. 14 is a schematic view showing a distribution of the liquid refrigerant in the evaporator of FIG. FIG. 15 is a schematic diagram showing the temperature distribution when all the rooms are used as upward flow paths.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Evaporator 10 ... Inlet side heat exchange part 10 ... Outlet side heat exchange part 10a ... 1st path | pass (downflow path)
10b ... 2nd pass (upflow path)
10c 3rd pass (downflow pass)
DESCRIPTION OF SYMBOLS 11 ... Upper tank 12 ... Lower tank 20 ... Outlet side heat exchange part 20a ... 1st path | pass (upflow path)
20b ... 2nd pass (pass immediately before the most downstream, downward flow pass)
20c ... 3rd pass (the most downstream pass)
DESCRIPTION OF SYMBOLS 21 ... Upper tank 22 ... Lower tank 31 ... Heat exchange passage 51 ... Partition part S10a, b, c ... Total passage sectional area of path S20a, b, c ... Total passage sectional area of path 200 ... Evaporator 210 ... Inlet side heat Exchanger 210a ... 1st pass (downflow path)
210b ... 2nd pass (upflow path)
220 ... Outlet side heat exchanging part 220a ... 1st pass (pass immediately before the most downstream)
220b ... 2nd path (downstream path)
S210a, b ... total passage cross-sectional area of path S220a, b ... total path cross-sectional area of path 300 ... evaporator 310 ... inlet side heat exchange section 310a ... first path (upflow path)
310b ... 2nd pass (downward flow pass)
320 ... exit side heat exchange section 320a ... first pass (pass immediately before the most downstream)
320b ... 2nd path (downstream path)
S310a, b ... total passage cross-sectional area of the path S320a, b ... total passage cross-sectional area of the path 400 ... evaporator 410 ... inlet side heat exchange section 410a ... first path (downflow path)
410b ... 2nd pass (upflow path)
410c ... 1st path | pass (downflow path)
420: outlet side heat exchanging section 420a: first pass (pass immediately before the most downstream)
420b ... 2nd path (downstream path, upflow path)
S410a, b, c: total passage cross-sectional area of the path S420a, b: total cross-sectional area of the path 500 ... evaporator 510 ... inlet side heat exchange section 510a ... first path (upflow path)
510b ... 2nd pass (downward flow pass)
510c 3rd pass (upflow path)
520 ... Outlet side heat exchange section 520a ... First pass 520b ... Second pass (pass immediately before the most downstream)
520c ... 3rd pass (the most downstream pass)
S510a, b, c: total passage cross-sectional area of the path S520a, b, c ... total path cross-sectional area of the path 600 ... evaporator 610 ... inlet side heat exchange section 610a ... first path (downflow path)
610b ... 2nd pass (upflow path)
610c ... 3rd pass (downflow path)
610d 4th pass (upflow path)
620 ... Outlet side heat exchange section 620a ... 1st pass 620b ... 2nd pass 620c ... 3rd pass (pass immediately before the most downstream)
620d ... Fourth path (the most downstream path)
S610a, b, c, d: total passage cross-sectional area of the path S620a, b, c, d: total cross-sectional area of the path 700 ... evaporator 710 ... inlet side heat exchange section 710a ... downflow path 710b ... upflow path 720 ... Exit side heat exchange part 720 ... Heat exchange part 720c ... 3rd pass (pass immediately before the most downstream)
720d: the most downstream path S710a, b, c, d: the total passage sectional area of the path S720a, b: the total passage sectional area of the path

Claims (7)

A heat exchange passage (31) that extends in the vertical direction and is laminated in a plurality of multi-stages in the horizontal direction and allows refrigerant to flow inside, and heat exchange provided at both upper and lower ends of the multi-stage heat exchange passages (31, 31,...) A heat exchange section (10, 20) having a tank (11, 12, 21, 22) for merging and distributing the refrigerant from the passage (31, 31, ...),
The heat exchange part (10, 20) is arranged in two layers in the direction of ventilation,
An evaporator in which both heat exchanging parts (10, 20) are connected so that the refrigerant is circulated to the other heat exchanging part (20) after the refrigerant is circulated to any one of the heat exchanging parts (10). Because
Set the heat exchange section (10) on the refrigerant inlet side to two or more paths (10a, 10b,...)
Set the heat exchange part (20) on the outlet side of the refrigerant in two or more paths (20a, 20b, ...),
In the inlet-side heat exchange section (10), the number of heat exchange passages in the upflow path where the refrigerant becomes an upward flow is smaller than the number of heat exchange passages in the downflow path where the refrigerant becomes a downward flow,
In the outlet side heat exchange section (20), the number of heat exchange passages in the most downstream path is greater than the number of heat exchange passages in the immediately downstream pass, and the evaporators (1) (200) (300) ( 400) (500) (600) (700). The evaporator according to claim 1, comprising:
Make the number of passes the same in both heat exchange parts (10, 20),
The evaporators (1), (200), (300), (500), and (600), wherein the refrigerant flow directions in the opposite windward path and the leeward path are opposite to each other. The evaporator according to claim 1, comprising:
The evaporator (400) (700), wherein the number of passes of the outlet side heat exchange part (20) is smaller than that of the inlet side heat exchange part (10). The evaporator according to any one of claims 1 to 3,
The outlet side heat exchange part (20) is set to 3 passes or more,
The evaporator (1) (500) (600), wherein the number of heat exchange passages is gradually increased toward the downstream path in the outlet side heat exchange section (20). The evaporator according to any one of claims 1 to 4,
The outlet side heat exchange part (20) is set to 3 passes or more,
In the outlet side heat exchange section (20), the number of heat exchange passages in the upflow path is smaller than the number of heat exchange passages in the downflow path except for the most downstream path. ). The evaporator according to any one of claims 1 to 5,
The evaporator (1) (400) (500) (600) (700), wherein the inlet side heat exchange section (10) is set to three or more passes. The evaporator according to any one of claims 1 to 6,
The evaporator (1) (200) (300) (400) characterized in that the inlet side heat exchange part (10) is arranged on the leeward side and the outlet side heat exchange part (20) is arranged on the leeward side. (500) (600) (700).

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