WO2021015272A1 - Heat exchanger and air conditioning device - Google Patents

Abstract

This heat exchanger comprises: a heat dissipation unit (20) that is provided with a heat exchange core (230) that dissipates heat from a high-pressure refrigerant into a first air flow by heat exchange between the first air flow and the high-pressure refrigerant; and an evaporator (22) that is disposed above the heat dissipation unit and evaporates a low-pressure refrigerant by causing the low-pressure refrigerant to absorb heat from a second air flow by heat exchange between the second air flow and the low-pressure refrigerant. In this heat exchanger, the condensed water generated from the evaporator by the heat exchange in the evaporator is guided to the windward side of the first air flow in the heat exchange core of the heat dissipation unit, and the guided condensed water is applied to the heat exchange core to dissipate heat from the high-pressure refrigerant into the condensed water and vaporize the condensed water.

Description

Heat exchanger and air conditioner Cross-reference to related applications

This application is based on Japanese Patent Application No. 2019-135404 filed on July 23, 2019 and Japanese Patent Application No. 2020-54811 filed on March 25, 2020. The description is incorporated by reference.

This disclosure relates to heat exchangers and air conditioners.

Conventionally, in an air conditioner, it has been proposed that the evaporation part is arranged above the heat dissipation part and a water guiding flow path for guiding the condensed water generated in the evaporation part to the heat dissipation part is provided (see, for example, Patent Document 1).

In this product, the aim is to improve the cooling efficiency of cooling the refrigerant in the heat dissipation part by applying condensed water to the heat dissipation part and vaporizing the condensed water in the heat dissipation part to remove the heat of vaporization from the refrigerant.

International release 2018/235765

The above-mentioned Patent Document 1 does not describe how to apply the condensed water generated in the evaporation part to the heat dissipation part in the air conditioner. For example, if the condensed water is allowed to flow down to the upper tank of the heat radiating portion, the condensed water may flow to the leeward side along the upper tank of the heat radiating portion.

Therefore, the condensed water is not vaporized in the heat radiating part and flows to the leeward side of the heat radiating part as it is. Therefore, there is a high possibility that a sufficient cooling effect of the refrigerant cannot be obtained in the heat radiating portion.

The present disclosure provides a heat exchanger provided with an evaporation unit and a heat dissipation unit, the heat exchanger in which the condensed water generated in the evaporation unit is used to improve the cooling effect of the refrigerant in the heat dissipation unit, and an air conditioner. The purpose.

In order to achieve the above object, according to one aspect of the present disclosure, a heat radiating unit including a heat exchange core that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant.
It is provided on the upper side with respect to the heat radiating section, and includes an evaporating section which absorbs heat from the second air stream and evaporates the low pressure refrigerant by heat exchange between the second air stream and the low pressure refrigerant.
The condensed water generated from the evaporation part by the heat exchange of the evaporation part is guided to the wind side of the first air flow in the heat exchange core in the heat dissipation part, and this guided condensed water is applied to the heat exchange core to change from the high pressure refrigerant to the condensed water. It dissipates heat and vaporizes condensed water.

Therefore, since the heat of vaporization can be transferred from the high-pressure refrigerant to the condensed water, the high-pressure refrigerant can be cooled by using the condensed water. This makes it possible to provide a heat exchanger in which the condensed water generated in the evaporation section is used to improve the cooling effect of the refrigerant in the heat dissipation section.

Note that the reference reference numerals in parentheses attached to each component or the like indicate an example of the correspondence between the component or the like and the specific component or the like described in the embodiment described later.

It is a refrigerant circuit diagram which showed the refrigerating cycle circuit which has the heat exchanger of 1st Embodiment. It is sectional drawing which shows typically the schematic structure of the heat exchanger in 1st Embodiment. FIG. 5 is a cross-sectional view showing a cross section of III-III of FIG. 2 in the first embodiment, and is an excerpt of a third plate on one side of a side plate portion on one side. It is the arrow view of FIG. 2 in the IV direction in 1st Embodiment, and is the figure which showed the 2nd plate of the other side of the other side plate part by the alternate long and short dash line. In the first embodiment, of the pair of plate members constituting the condensation component and the evaporation component, the second plate member arranged on the other side in the stacking direction is viewed as an arrow in the direction indicated by the arrow V in FIG. It is a visual view. In the first embodiment, of the pair of plate members constituting the condensation component and the evaporation component, the first plate member arranged on one side in the stacking direction is an arrow viewed in the direction indicated by the arrow IV in FIG. It is a visual view. In the first embodiment, it is the cross-sectional view which showed the cross section of VII-VII of FIG. 2, and is the figure which shows typically the refrigerant flow in a condensed part by an arrow. It is sectional drawing which showed the cross section of VIII-VIII of FIG. 2 in 1st Embodiment, and is the figure which shows typically the refrigerant flow in the evaporation part by an arrow. It is sectional drawing which showed the cross section of IX-IX of FIG. 4 in 1st Embodiment, and is the figure which showed typically the structure of the internal heat exchange part. In the first embodiment, it is an arrow view of the second plate on one side of the side plate portion on one side as viewed in the direction indicated by the arrow V in FIG. In the first embodiment, it is an arrow view of the first plate on one side of the side plate portion on one side as viewed in the direction indicated by the arrow V in FIG. It is a figure corresponding to FIG. 5, and is the figure which showed the structure in which the 1st communication hole of the condensing plate part on the other side of the 2nd plate member of FIG. 5 is not provided. It is a figure corresponding to FIG. 6, and is the figure which showed the structure which the 1st communication hole of one side evaporation plate part was not provided in the 1st plate member of FIG. It is sectional drawing which showed the cross section of XIV-XIV of FIG. 4 in 1st Embodiment, and is the figure which showed typically the internal heat exchange part and the water guide plate. It is sectional drawing which shows typically the schematic structure of the heat exchanger in inverse proportion. It is an enlarged view of the XVI part in FIG. 15, and is the figure which showed the structure of the water storage part, the drain pipe, and the condensation part. It is a refrigerant circuit diagram which showed the refrigerating cycle circuit which has the heat exchanger of 2nd Embodiment, and is the figure which corresponds to FIG. It is sectional drawing which shows typically the schematic structure of the heat exchanger in 2nd Embodiment, and is the figure which corresponds to FIG. FIG. 18 is an arrow view in the XIX direction of FIG. 18, showing a side plate portion on one side of the second embodiment. It is sectional drawing which showed the XX-XX cross section of FIG. 18 in 2nd Embodiment, and is the figure which showed the other side side plate part of 2nd Embodiment. It is sectional drawing which showed the XXI-XXI cross section of FIG. 18 in 2nd Embodiment, and is the figure which showed the one-side condensing plate part and one-side evaporation plate part excerpted. It is sectional drawing which showed the cross section of XXII-XXII of FIG. 18 in 2nd Embodiment, and is the figure which showed the one-side condensing plate part and one-side evaporation plate part excerpted. It is a cross-sectional view corresponding to FIG. 22 showing the cross section of XXIII-XXIII of FIG. 18, and is the first communication hole of the condensing plate portion on the other side and the second communication plate portion of the evaporation plate portion on the other side of the second plate member of FIG. It is a figure which showed the structure which the communication hole is not provided. It is a cross-sectional view corresponding to FIG. 22 showing the cross section of XXIV-XXIV of FIG. 18, and is the first communication hole of the other side condensing plate portion and the first of the other side evaporation plate portion of the second plate member of FIG. It is a figure which showed the structure which the communication hole is not provided. FIG. 5 is a schematic diagram schematically showing an evaporation unit, a water storage unit, a drain pipe, a condensing unit, and a distributor in the heat exchanger in the third embodiment. In the third embodiment, it is an arrow view in the direction of XXVI of FIG. 25, and is a schematic view schematically showing a drain pipe, a condensing part, and a distributor. It is a perspective view which shows typically the state which disassembled the condensing part and a distributor in 3rd Embodiment. It is the figure corresponding to FIG. 21 in 4th Embodiment, and is the figure which showed the one-side condensing plate part and one-side evaporation plate part excerpted. FIG. 5 is an overall configuration diagram of an air conditioner including a heat exchanger, a duct, and a blower unit according to a fifth embodiment as viewed from above in the vertical direction. It is a figure which showed the structure of the blower unit of 5th Embodiment. It is sectional drawing which showed the cross section of XXXI-XXXI of FIG. 29, and is the figure which showed the arrangement relation of the heat exchanger and the duct of 5th Embodiment. 6 is an overall configuration diagram of an air conditioner including a heat exchanger, a duct, and a blower unit according to a sixth embodiment as viewed from above in the vertical direction. It is sectional drawing which showed the sectional view of XXXIII-XXXIII of FIG. 32, and is the figure which showed the structure of the blower unit of 6th Embodiment. FIG. 5 is an overall configuration diagram of an air conditioner including a heat exchanger, a duct, and a blower unit according to a seventh embodiment as viewed from above in the vertical direction. It is an overall block diagram which showed the arrangement relation of the heat exchanger and the duct of 8th Embodiment. It is an overall block diagram which showed the arrangement relation of the heat exchanger and the duct of 9th Embodiment. It is an overall block diagram which showed the arrangement relation of the heat exchanger and the duct of the tenth embodiment. It is an overall block diagram which showed the arrangement relation of the heat exchanger and the duct of 11th Embodiment. It is a refrigerant circuit diagram which showed the refrigerating cycle circuit which has a heat exchanger in the modification of 1st Embodiment. In the modified example of the first embodiment, it is the cross-sectional view which showed the cross section corresponding to the VIII-VIII cross section of FIG. 2, and is the figure which corresponds to FIG. It is a refrigerant circuit diagram which showed the refrigerating cycle circuit in the modification of 2nd Embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the figures. In each of the following embodiments, the same or equal parts are designated by the same reference numerals in the drawings in order to simplify the description.

(First Embodiment)
As shown in FIG. 1, the heat exchanger 10 of the present embodiment constitutes a part of the refrigeration cycle circuit 12 in which the refrigerant circulates. That is, in the refrigeration cycle circuit 12, the refrigerant compressed by the compressor 14 included in the refrigeration cycle circuit 12 flows into the heat exchanger 10, and the refrigerant flowing into the heat exchanger 10 flows through the heat exchanger 10. Then, it is sucked into the compressor 14.

The heat exchanger 10 exchanges heat between the air flowing into the air-conditioned space where cooling or heating is performed and the refrigerant. For example, when the air-conditioned space is cooled, the heat exchanger 10 cools the air flowing to the air-conditioned space with a refrigerant. Further, when the air-conditioned space is heated, the heat exchanger 10 heats the air flowing to the air-conditioned space with a refrigerant.

As shown in FIGS. 1 and 2, the heat exchanger 10 of the present embodiment is configured by brazing and joining a plurality of constituent members made of a metal such as an aluminum alloy to each other.

The heat exchanger 10 of the present embodiment includes a condensing unit 20 as a heat radiating unit, an evaporation unit 22, an internal heat exchange unit 28, one side plate portion 30, the other side plate portion 32, and a tubular inlet. It includes a pipe 34 and a tubular outlet pipe 36. The heat exchanger 10 includes a water guide plate 50 as a second water guide for guiding the condensed water to the upper side of the outer cylinder 281.

As shown in FIGS. 2 to 4, the one-side side plate portion 30 and the other-side side plate portion 32 form a substantially plate shape with a predetermined stacking direction Ds as a thickness direction and a vertical direction Dg as a longitudinal direction. There is.

The stacking direction Ds is a direction intersecting the vertical direction Dg, strictly speaking, a direction orthogonal to the vertical direction Dg. Note that FIG. 2 shows a cross section of II-II of FIG. Further, in the present embodiment, the direction orthogonal to both the stacking direction Ds and the vertical direction Dg is referred to as the heat exchanger width direction Dw.

The one side plate portion 30 is arranged at one end of the heat exchanger 10 in the stacking direction Ds, and the other side plate portion 32 is arranged at the other end of the heat exchanger 10 in the stacking direction Ds. Has been done. The condensing portion 20, the evaporating portion 22, and the internal heat exchange portion 28 are arranged between the one side side plate portion 30 and the other side side plate portion 32 in the stacking direction Ds. That is, the one-side side plate portion 30 is arranged on one side of the stacking direction Ds with respect to the condensing portion 20, the evaporating portion 22, and the internal heat exchange portion 28, and the other side side plate portion 32 is the condensing portion 20, the evaporating portion, and the evaporating portion. It is arranged on the other side of the stacking direction Ds with respect to 22 and the internal heat exchange portion 28. Then, the one side side plate portion 30 and the other side side plate portion 32 have a condensing portion 20, an evaporation portion 22, and an internal heat exchange portion 28 between the one side side plate portion 30 and the other side side plate portion 32. The water guide plate 50 is sandwiched between them.

The condensing portion 20 has a laminated structure in which a plurality of condensed constituent portions 201 having the laminating direction Ds in the thickness direction and the vertical direction Dg in the longitudinal direction are laminated in the laminating direction Ds. That is, the condensing unit 20 has a plurality of condensed components 201, and the plurality of condensed components 201 are laminated in the stacking direction Ds and joined to each other.

Then, as shown in FIGS. 2, 5, and 6, inside the plurality of condensing components 201, one side condensing tank space 201a, the other side condensing tank space 201b, and the condensing flow path 201c (that is, high-pressure refrigerant), respectively. An internal space consisting of a flow path) is formed. The one-side condensing tank space 201a, the other-side condensing tank space 201b, and the condensing flow path 201c are spaces through which the refrigerant flows.

One side condensing tank space 201a is connected to one end of the condensing flow path 201c, and the other side condensing tank space 201b is connected to the other end of the condensing flow path 201c. The condensing flow path 201c extends, for example, along a corrugated path that reciprocates a plurality of times in the vertical direction Dg. In the present embodiment, the condensing flow path 201c extends along a corrugated path that reciprocates three times in the vertical direction Dg.

The condensing flow path 201c is arranged above the one-sided condensing tank space 201a and the other-side condensing tank space 201b in the vertical direction Dg. Further, the one-sided condensing tank space 201a is arranged on one side of the heat exchanger width direction Dw with respect to the other-side condensing tank space 201b.

Further, as shown in FIGS. 2 and 7, at least one side condensing tank space 201a or the other side condensing tank space 201b communicates with each other between the condensing components 201 adjacent to each other.

The refrigerant compressed and discharged by the compressor 14 (see FIG. 1) flows into the condensing section 20 through the inlet pipe 34 as shown by arrows Fi and F1a, and the refrigerant flows into the condensing flow path of each condensing component 201. It flows to 201c. Then, the condensing unit 20 exchanges heat between the air around the condensing unit 20 and the refrigerant flowing in the condensing flow path 201c, thereby dissipating heat from the refrigerant and condensing the refrigerant.

The arrows F2a, F2b, and F2c in FIG. 7 indicate the refrigerant flow in the plurality of one-sided condensing tank spaces 201a adjacent to each other in the stacking direction Ds and connected to each other. Further, arrows F3a and F3b each indicate a refrigerant flow in a plurality of other side condensing tank spaces 201b adjacent to each other in the stacking direction Ds and connected to each other. Further, arrows F4a to F4h each indicate a refrigerant flow in the condensation flow path 201c.

The evaporation unit 22 has a laminated structure in which a plurality of evaporation components 221 having the lamination direction Ds in the thickness direction and the vertical direction Dg in the longitudinal direction are laminated in the lamination direction Ds. That is, the evaporation component 22 has a plurality of evaporation components 221 and the plurality of evaporation components 221 are laminated in the stacking direction Ds and joined to each other.

Then, as shown in FIGS. 2, 5 and 6, inside the plurality of evaporation components 221 respectively, one side evaporation tank space 221a, the other side evaporation tank space 221b and the evaporation flow path 221c (that is, low pressure refrigerant). An internal space consisting of a flow path) is formed. The one-side evaporation tank space 221a, the other-side evaporation tank space 221b, and the evaporation flow path 221c are spaces through which the refrigerant flows.

The one-side evaporation tank space 221a is connected to one end of the evaporation flow path 221c, and the other side evaporation tank space 221b is connected to the other end of the evaporation flow path 221c. The evaporation flow path 221c extends, for example, along a corrugated path that reciprocates a plurality of times in the vertical direction Dg. In the present embodiment, the evaporation flow path 221c extends along a corrugated path that reciprocates twice in the vertical direction Dg. The evaporation flow path 221c is formed so that the flow path cross-sectional area is larger than that of the condensation flow path 201c.

The evaporation flow path 221c is arranged below the one-side evaporation tank space 221a and the other-side evaporation tank space 221b in the vertical direction Dg. Further, the one-side evaporation tank space 221a is arranged on one side of the heat exchanger width direction Dw with respect to the other-side evaporation tank space 221b.

Further, as shown in FIGS. 2 and 8, at least one side evaporation tank space 221a or the other side evaporation tank space 221b communicate with each other between the evaporation components 221 adjacent to each other.

The evaporation unit 22, the internal heat exchange unit 28, and the condensing unit 20 are arranged side by side in the vertical direction Dg in the order of the evaporation unit 22, the internal heat exchange unit 28, and the condensing unit 20. Specifically, the evaporation unit 22, the internal heat exchange unit 28, and the condensing unit 20 are arranged side by side in the vertical direction Dg from the upper side in the order of description. That is, the internal heat exchange unit 28 is arranged so as to overlap the evaporation unit 22 on the lower side. The condensing unit 20 is arranged so as to overlap the evaporation unit 22 and the internal heat exchange unit 28 on the lower side.

The refrigerant flowing out of the condensing section 20 passes through the internal heat exchange section 28 and the throttle section 321e included in the other side plate section 32 in the order of description thereof, and is decompressed by the throttle section 321e (that is, the decompression section). Flows into the evaporation unit 22. The refrigerant flow from the condensing portion 20 to the evaporating portion 22 is represented by, for example, arrows F1b to F1f in FIG.

The refrigerant that has flowed into the evaporation section 22 from the drawing section 321e flows into the evaporation flow path 221c of each evaporation component section 221. Then, the evaporation unit 22 exchanges heat between the air around the evaporation unit 22 and the refrigerant flowing in the evaporation flow path 221c, thereby causing the refrigerant to absorb heat and evaporate the refrigerant.

The arrows F5a and F5b in FIG. 8 indicate the refrigerant flow in the plurality of one-sided evaporation tank spaces 221a adjacent to each other in the stacking direction Ds and connected to each other. Further, the arrows F6a and F6b each indicate the refrigerant flow in the plurality of other side evaporation tank spaces 221b adjacent to each other in the stacking direction Ds and connected to each other. Further, arrows F7a to F7g each indicate a refrigerant flow in the evaporation flow path 221c.

As shown in FIG. 2, the one-side side plate portion 30 has a one-sided first plate 301, a one-sided second plate 302, and a one-sided third plate 303, which are plate-shaped members. The one-side side plate portion 30 is configured such that the one-side first plate 301, the one-side second plate 302, and the one-side third plate 303 are laminated and joined to each other. The one-sided first plate 301, the one-sided second plate 302, and the one-sided third plate 303 are arranged in the order of the one-sided first plate 301, the one-sided second plate 302, and the one-sided third plate 303 in the stacking direction Ds. It is stacked from one side to the other.

The condensing portion 20 and the evaporating portion 22 are fixed to the one side side plate portion 30, respectively. Specifically, the condensing portion 20 and the evaporating portion 22 are joined in parallel to the other side of the first plate 301 on one side in the stacking direction Ds. That is, the plurality of condensation constituents 201 and the plurality of evaporation constituents 221 are respectively laminated on the other side of the stacking direction Ds with respect to the one side plate portion 30.

The other side side plate portion 32 has a plate-shaped member, the other side first plate 321 and the other side second plate 322, and the other side first plate 321 and the other side second plate 322 are laminated. It is composed of being joined to each other. The other side first plate 321 and the other side second plate 322 are laminated from one side to the other side in the stacking direction Ds in the order of the other side first plate 321 and the other side second plate 322.

The condensing portion 20 and the evaporating portion 22 are fixed to the other side plate portion 32, respectively. Specifically, the condensing portion 20 and the evaporating portion 22 are joined in parallel to one side of the other side first plate 321 in the stacking direction Ds. That is, the plurality of condensation constituents 201 and the plurality of evaporation constituents 221 are respectively laminated on one side of the stacking direction Ds with respect to the other side plate portion 32.

As shown in FIGS. 2, 4, and 9, the internal heat exchange section 28 flows out from the refrigerant flowing out from the condensing section 20 (that is, the condensing flow path 201c) and from the evaporating section 22 (that is, the evaporation flow path 221c). The heat is exchanged with the refrigerant. That is, the internal heat exchange unit 28 transfers heat from the high-pressure refrigerant that has passed through the condensing unit 20 to the low-pressure refrigerant that has passed through the evaporation unit 22.

Therefore, the internal heat exchange portion 28 has a double-tube structure extending in the stacking direction Ds, and has a tubular outer cylinder portion 281 and a tubular inner cylinder inserted into the outer cylinder portion 281. It has a portion 282. The internal heat exchange section 28 is arranged side by side with the condensing section 20 and the evaporation section 22 between the first plate 301 on one side and the first plate 321 on the other side, and the first plate 301 on one side and the first plate on the other side thereof. It is joined to 321 respectively.

The outer cylinder portion 281 has a plurality of outer cylinder constituent portions 281a and 281b. The outer cylinder portion 281 has a tubular shape formed so as to extend in the stacking direction Ds by connecting the plurality of outer cylinder constituent portions 281a and 281b in series in the stacking direction Ds and joining them to each other. Specifically, the outer cylinder portion 281 includes a plurality of first outer cylinder constituent portions 281a and a plurality of second outer cylinder constituent portions 281b having a shape different from that of the first outer cylinder constituent portion 281a. It has as cylinder constituent parts 281a and 281b.

For example, whichever the first outer cylinder constituent portion 281a (that is, the first and second internal heat exchange portion forming portions) and the second outer cylinder constituent portion 281b (that is, the second and fourth internal heat exchange portion forming portions) Also has a tubular shape extended in the stacking direction Ds.

The second outer cylinder constituent portion 281b has a shape symmetrical to the stacking direction Ds with respect to the first outer cylinder constituent portion 281a. The plurality of first outer cylinder constituent portions 281a and the plurality of second outer cylinder constituent portions 281b are alternately connected in series in the stacking direction Ds and brazed to each other. In this way, the outer tubular portion 281 is configured.

In the present embodiment, as shown in FIGS. 2 and 4, the outer tubular portion 281 has an upper outer surface 283 formed toward the upper side of the outer surface in the vertical direction Dg (that is, the ventilation flow path 22a). I have. The outer cylinder portion 281 is an upper portion of the upper outer surface 283, and heat exchangers the condensed water flowing along the water guide plate 50 and the condensed water dropped from the ventilation flow path 22a (that is, the second air flow path). It serves as a first water conveyance portion that leads to one side of Dw in the width direction.

The inner cylinder portion 282 is composed of a pipe member formed so as to extend in the stacking direction Ds. As shown in FIGS. 2 and 10, one end of the inner tubular portion 282 is inserted into a through hole 302a for one end formed in the second plate 302 on one side, and the second through hole 302a on one side is used for the through hole 302a for one end. It is brazed to the plate 302. Further, as shown in FIGS. 2 and 9, the other end of the inner cylinder portion 282 is inserted into the other end through hole 321a formed in the other side first plate 321 and the other end through hole 321a. It is brazed and joined to the side first plate 321.

With such a configuration, the internal heat exchange section 28 has two flow paths extending in the stacking direction Ds, specifically, an outer flow path 28a through which the refrigerant flowing out from the evaporation section 22 flows, and a condensing section 20. An inner flow path 28b through which the refrigerant flowing out of the water flows is formed.

The outer flow path 28a is arranged inside the outer cylinder portion 281, and the inner flow path 28b is arranged inside the outer flow path 28a with the cylinder wall of the inner cylinder portion 282 interposed therebetween. There is. Therefore, in the internal heat exchange unit 28, the refrigerant flowing in the outer flow path 28a and the refrigerant flowing in the inner flow path 28b exchange heat with each other via the cylinder wall of the inner cylinder portion 282.

In the present embodiment, the water guide plate 50 is a second water guide portion arranged between the one side side plate portion 30 and the other side side plate portion 32. The water guide plate 50 is arranged below the plurality of ventilation flow paths 22a. The water guide plate 50 is arranged on the other side of the heat exchanger width direction Dw (that is, the leeward side of the air flow in the ventilation flow path 22a) with respect to the outer cylinder portion 281 of the internal heat exchange portion 28.

The water guide plate 50 is arranged so that its thickness direction intersects the vertical direction Dg. The upper surface of the water guide plate 50 is arranged so as to face the ventilation flow path 22a. One side of the upper surface of the water guide plate 50 in the heat exchanger width direction Dw is located at the same portion in the vertical direction Dg as the other side of the heat exchanger width direction Dw of the upper outer surface 283 of the outer cylinder portion 281.

The water guide plate 50 is formed in an inclined shape so that its upper surface advances in the vertical direction Dg toward the other side in the heat exchanger width direction Dw. The water guide plate 50 of the present embodiment plays a role of guiding the condensed water dropped from the plurality of ventilation flow paths 22a to the upper outer surface 283.

As shown in FIGS. 4, 7, and 9, in addition to the above-mentioned through hole 321a for the other end, the through hole 321b for the inlet and the through hole 321c for the exit are formed in the first plate 321 on the other side. There is. A diaphragm hole 321d that functions as an orifice hole is also formed in the first plate 321 on the other side. That is, the other side side plate portion 32 has a portion of the other side first plate 321 in which the throttle hole 321d is formed as the throttle portion 321e. The throttle hole 321d is an orifice.

An inlet pipe 34 is inserted into the inlet through hole 321b, and the inlet pipe 34 is brazed to the other side first plate 321 at the inlet through hole 321b. As a result, the inlet pipe 34 is connected to the condensing portion 20 so as to communicate with the condensing portion 20.

An outlet pipe 36 is inserted into the outlet through hole 321c, and the outlet pipe 36 is brazed to the other side first plate 321 at the outlet through hole 321c. As a result, the outlet pipe 36 is connected to the internal heat exchange section 28 so as to communicate with the outer flow path 28a of the internal heat exchange section 28.

As shown in FIGS. 2, 4, and 9, in the other side plate portion 32, the other side second plate 322 is brazed and joined to the other side first plate 321 on the other side in the stacking direction Ds. As a result, the other side relay flow path 32a is formed between the other side first plate 321 and the other side relay flow path 32a.

The other side relay flow path 32a extends in the vertical direction Dg, and is provided between the inner flow path 28b of the internal heat exchange portion 28 and the throttle hole 321d in the refrigerant flow. That is, the other side relay flow path 32a is a flow path connecting the refrigerant outlet side of the inner flow path 28b and the refrigerant inlet side of the throttle hole 321d.

As shown in FIGS. 2 and 8, the inlet position evaporation component 222 located at the other end of the stacking direction Ds among the plurality of evaporation components 221 has the evaporation section 22 from the throttle hole 321d as the throttle flow path. An evaporation unit inlet 222a for allowing the refrigerant to flow into the inside is provided. The evaporation unit inlet 222a is included in the one-side evaporation tank space 221a of the inlet position evaporation component 222. The throttle hole 321d of the other side plate portion 32 is connected to the evaporation portion inlet 222a.

Further, the hole diameter of the throttle portion 321e of the other side plate portion 32 is set so as to cause a predetermined depressurizing action on the refrigerant passing through the throttle hole 321d. That is, the throttle hole 321d is a fixed throttle that throttles the flow of the refrigerant, and functions as a decompression unit that decompresses the refrigerant flowing out from the condensing unit 20 and then flows it to the evaporation unit 22. Since the internal heat exchange section 28 is provided in the present embodiment, more specifically, the throttle hole 321d of the throttle section 321e flows out of the condensing section 20 and flows out from the condensing section 20 to the inner flow path 28b of the internal heat exchange section 28 and the other. The refrigerant that has passed through the side relay flow path 32a flows in.

As shown in FIG. 11, a through hole 301b for a condensing portion and a through hole 301c for gas-liquid separation are formed in the first plate 301 on one side of the one-side side plate portion 30. The through hole 301b for the condensing portion is located below the through hole 301c for gas-liquid separation.

Further, as shown in FIG. 10, in addition to the above-mentioned through hole 302a for one end, the through hole 302b for the condensing portion and the through hole 302c for gas-liquid separation are formed in the second plate 302 on one side. The through hole 302b for the condensing portion is located below the through hole 302a for one end and the through hole 302c for gas-liquid separation, and is arranged so as to be concentric with the through hole 301b for the condensing portion of the first plate 301 on one side. Has been done.

Further, as shown in FIGS. 2 and 3, the one-side third plate 303 has a flow path cover portion 303a and a gas-liquid separation cover portion 303c arranged above the flow path cover portion 303a. ing.

As shown in FIGS. 2 and 7, the outlet position of the plurality of condensed components 201 located at one end of the stacking direction Ds is the outlet of the condensed section in which the refrigerant flows out from the inside of the condensed section 20. 202a is provided. The condensing portion outlet 202a is included in the one-sided condensing tank space 201a of the outlet position condensing component 202. Then, the through hole 301b for the condensing portion of the first plate 301 on one side and the through hole 302b for the condensing portion of the second plate 302 on the one side are connected to the outlet 202a of the condensing portion.

Further, the one-side third plate 303 is brazed to one side of the stacking direction Ds with respect to the one-side second plate 302, whereby the flow path cover portion 303a of the one-side third plate 303 is unilaterally first. A one-sided relay flow path 30a is formed between the two plates 302.

The one-side relay flow path 30a extends in the vertical direction Dg, and is provided between the through hole 302b for the condensing portion of the one-side second plate 302 and the inner flow path 28b of the internal heat exchange portion 28 in the refrigerant flow. There is. That is, the one-side relay flow path 30a is a flow path connecting the condensing part outlet 202a of the condensing part 20 and the refrigerant inlet side of the inner flow path 28b. Due to such a flow path configuration of the refrigerant, the throttle hole 321d of the other side plate portion 32 is provided between the condensing portion outlet 202a and the evaporation portion inlet 222a in the refrigerant flow.

As shown in FIG. 11, the gas-liquid separation through hole 301c of the first plate 301 on one side is composed of a penetration portion 301d on one side, a penetration portion 301e on the other side, and a connecting portion 301f. The one-side penetrating portion 301d and the other-side penetrating portion 301e are formed so as to extend in the vertical direction Dg.
The other side penetrating portion 301e is arranged on the other side opposite to one side in the heat exchanger width direction Dw, slightly away from the one side penetrating portion 301d with respect to the one side penetrating portion 301d. The connecting portion 301f is arranged between the one-side penetrating portion 301d and the other-side penetrating portion 301e, and connects the upper end portion of the one-side penetrating portion 301d and the upper end portion of the other-side penetrating portion 301e.
Further, as shown in FIGS. 8 and 11, the evaporation unit 22 is provided with an evaporation unit outlet 22b that allows the refrigerant to flow out from the inside of the evaporation unit 22. The evaporation portion outlet 22b is an opening hole opened in the stacking direction Ds. The gas-liquid separation through hole 301c is formed so that the other side through hole 301e of the gas-liquid separation through hole 301c exclusively overlaps one side of the stacking direction Ds with respect to the evaporation part outlet 22b.

As shown in FIG. 10, the gas-liquid separation through hole 302c of the second plate 302 on one side is formed so as to extend in the vertical direction Dg. The gas-liquid separation through hole 302c is arranged so as to overlap the other side penetrating portion 301e of the one side first plate 301. On the other hand, the gas-liquid separation through hole 302c of the second plate 302 on one side is arranged away from the one side through portion 301d of the first plate 301 on one side toward the other side in the heat exchanger width direction Dw. Has been done.

As shown in FIGS. 2 and 3, the gas-liquid separation cover portion 303c of the third plate 303 on one side has a shape recessed to one side in the stacking direction Ds, and is inside the cover between the second plate 302 on one side. It forms the space 303d. The cover inner space 303d is a space connected to the gas-liquid separation through hole 302c of the second plate 302 on one side.

The gas-liquid separation cover portion 303c, the first gas-liquid separation component 301g in which the gas-liquid separation through hole 301c is formed in the first plate 301 on one side, and the gas-liquid separation portion 302 in the second plate 302 on one side for gas-liquid separation. The second gas-liquid separation component 302d in which the through hole 302c is formed constitutes the gas-liquid separation unit 26. That is, the one-side side plate portion 30 has a gas-liquid separation portion 26. Refrigerant flows into the gas-liquid separation unit 26 from the evaporation unit 22 as shown by arrows F8 (see FIGS. 2 and 8). Then, the gas-liquid separation unit 26 functions as an accumulator that separates the gas-liquid of the refrigerant flowing in from the evaporation unit 22. The gas-liquid separation unit 26 is formed in the gas-liquid separation unit 26 while allowing the gas-phase refrigerant out of the gas-liquid separated refrigerants to flow out from the gas-liquid separation unit 26 to the outer flow path 28a of the internal heat exchange unit 28. The liquid phase refrigerant is stored in the liquid storage space 26a.

As shown in FIGS. 3, 10, and 11, the liquid storage space 26a includes the gas-liquid separation through hole 302c of the one-side first plate 301, the other-side penetration portion 301e, and the one-side second plate 302, and the inside of the cover. It is composed of space 303d. In FIGS. 2, 10, 10 and 11, the state in which the liquid phase refrigerant is accumulated in the lower part of the liquid storage space 26a is shown by hatching.

The inner tubular portion 282 of the internal heat exchange portion 28 is inserted through the one-side penetrating portion 301d of the one-sided first plate 301 and then reaches the one-side through hole 302a of the one-sided second plate 302. Then, the one-side penetrating portion 301d of the one-sided first plate 301 communicates with the outer flow path 28a of the internal heat exchange portion 28 at the lower portion thereof. Therefore, the one-side penetrating portion 301d and the connecting portion 301f of the one-side first plate 301 function as a refrigerant lead-out flow path that guides the gas phase refrigerant from the liquid storage space 26a to the outer flow path 28a as shown by arrows F9a and F9b. ..

To elaborate on the configuration of the condensing unit 20, as shown in FIGS. 2 and 7, each of the plurality of condensing components 201 has a pair of plate-shaped condensing plate portions 201d and 201h, respectively. In each of the plurality of condensing components 201, the pair of condensing plate portions 201d and 201h are laminated in the stacking direction Ds. Then, the plurality of condensing components 201 are provided with each other so that the pair of condensing plate portions 201d and 201h form the condensing flow path 201c and the condensing tank spaces 201a and 201b between the pair of condensing plate portions 201d and 201h, respectively. It is composed by being joined.

Specifically, the pair of condensing plate portions 201d and 201h are the one-side condensing plate portion 201d and the other-side condensing plate portion 201h arranged on the other side of the stacking direction Ds with respect to the one-side condensing plate portion 201d. Is.

As shown in FIGS. 2, 5 and 6, one of the pair of condensing plate portions 201d and 201h, one side condensing plate portion 201d, is a first condensing tank forming portion recessed to one side in the stacking direction Ds. It has a 201e, a second condensation tank forming portion 201f, and a condensing flow path forming portion 201g.

Further, the other side condensing plate portion 201h, which is the other of the pair of condensing plate portions 201d and 201h, condenses with the first condensing tank forming portion 201i and the second condensing tank forming portion 201j recessed toward the other side in the stacking direction Ds. It has a flow path forming portion 201k.

The one-side condensed tank space 201a is formed between both of the first condensed tank forming portions 201e and 201i, and the other side condensed tank space 201b is formed between both the second condensed tank forming portions 201f and 201j. ing. Further, the condensed flow path 201c is formed between both condensed flow path forming portions 201g and 201k.

Further, in the one-side condensing plate portion 201d, the width of the first condensing tank forming portion 201e and the width of the second condensing tank forming portion 201f are the same in the stacking direction Ds, which is larger than the width of the condensing flow path forming portion 201g. Is also getting bigger. Similarly, in the condensing plate portion 201h on the other side, the width of the first condensing tank forming portion 201i and the width of the second condensing tank forming portion 201j are the same in the stacking direction Ds, and the condensing flow path forming portion 201k It is larger than the width of. Therefore, in the condensing portion 20, the first condensing tank forming portions 201e and 201i are joined to each other and the second condensing tank forming portions 201f and 201j are also joined to each other between the condensing constituent portions 201 adjacent to each other in the condensing portion 20. There is.

On the other hand, among the condensing components 201 adjacent to each other, the ventilation flow path 20a (that is, the first air flow) through which the air flow (that is, the first air flow) passes between the condensate flow path forming portions 201g and 201k. 1 air flow path) is formed.

As a result, the condensing portion 20 is provided with a plurality of ventilation flow paths 20a. Therefore, the condensing portion 20 is provided with a plurality of pairs of condensing flow path forming portions 201g and 201k.

The plurality of pairs of condensing flow path forming portions 201g and 201k, and the plurality of condensing portion fins 203 form a condensing portion heat exchange core 230 that exchanges heat between the air flow and the refrigerant in the condensing portion 20. A plurality of the ventilation flow paths 20a are formed side by side in the stacking direction Ds, and the plurality of ventilation flow paths 20a are condensed, which are corrugated fins brazed to the outside of the condensation flow path forming portions 201g and 201k, respectively. The part fin 203 is arranged. Then, the condensing portion fin 203 promotes heat exchange between the air passing through the ventilation flow path 20a and the refrigerant in the condensing portion 20.

As shown in FIGS. 2 and 7, among the plurality of condensed components 201, the condensed components 201 located at one end and the other end of the stacking direction Ds are located between them. The shape is different from that of the condensed component 201. For example, the condensing component 201 located at the end on one side thereof is composed of a condensing plate portion 201h on the other side and a portion 301h of the first plate 301 on the one side facing the condensing plate portion 201h on the other side. There is. Further, the condensing component 201 located at the other end is composed of one side condensing plate portion 201d and a portion 321f of the other side first plate 321 facing the one side condensing plate portion 201d. There is.

Further, as shown in FIGS. 5 to 7, in the one-sided condensing plate portion 201d, the first condensing tank forming portion 201e is formed with the first communication hole 201m penetrating in the stacking direction Ds, and the second condensing tank forming portion 201m is formed. A second communication hole 201n penetrating in the stacking direction Ds is formed in 201f. Similarly, in the other side condensing plate portion 201h, the first condensing tank forming portion 201i is formed with the first communication hole 201o penetrating in the stacking direction Ds, and the second condensing tank forming portion 201j is formed with the stacking direction Ds. A second communication hole 201p is formed through the hole.

The condensing tank space 201a on one side of each of the condensing components 201 adjacent to each other communicates with each other by arranging the first communication holes 201m and 201o so as to overlap each other. Further, the condensing tank space 201b on the other side of the condensing component 201 adjacent to each other communicates with each other by arranging the second communication holes 201n and 201p so as to overlap each other.

However, some of the plurality of condensing components 201 are not provided with any of the first communication holes 201m and 201o and the second communication holes 201n and 201p. As a result, a plurality of condensed constituent groups 204a to 204d having one or more condensed constituents 201 are configured. In the present embodiment, as the plurality of condensed constituent groups 204a to 204d, the first condensed constituent group 204a, the second condensed constituent group 204b, the third condensed constituent group 204c, and the fourth condensed constituent group 204d are used. It is configured.

In the condensing unit 20, the first condensed component group 204a, the second condensed component group 204b, the third condensed component group 204c, and the fourth condensed component group 204d are arranged in the order of description from the other side in the stacking direction Ds. They are arranged side by side. Then, in the refrigerant flow of the condensing unit 20, the first condensed component group 204a, the second condensed component group 204b, the third condensed component group 204c, and the fourth condensed component group 204d are on the upstream side in the order of description. It is connected in series from to the downstream side.

Further, in the condensation configuration unit group having a plurality of condensation configuration units 201 among the plurality of condensation configuration unit groups 204a to 204d, the plurality of condensation flow paths 201c are connected in parallel in the refrigerant flow.

In order to realize such a flow path of the refrigerant, as shown in the C1 portion of FIG. 7, the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the second condensing component group 204b Is not provided with the first communication hole 201o. Further, as shown in the C2 portion, the second communication hole 201n is not provided in the one-sided condensing plate portion 201d located at one end of the stacking direction Ds in the second condensing component group 204b. Further, as shown in the C3 portion, the first communication hole 201o is not provided in the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the fourth condensing component group 204d. For example, the other side condensing plate portion 201h in which the second communication hole 201p is provided but the first communication hole 201o is not provided is shown in FIG.

The configuration of the evaporation unit 22 is basically the same as the configuration of the condensation unit 20 described above. That is, as shown in FIGS. 2 and 8, each of the plurality of evaporation components 221 has a pair of plate-shaped evaporation plate portions 221d and 221h. In each of the plurality of evaporation components 221 the pair of evaporation plate portions 221d and 221h are laminated in the stacking direction Ds. Then, the plurality of evaporation components 221 are provided with each other so that the pair of evaporation plates 221d and 221h form the evaporation flow path 221c and the evaporation tank spaces 221a and 221b between the pair of evaporation plates 221d and 221h, respectively. It is composed by being joined.

Specifically, the pair of evaporation plate portions 221d and 221h are the one-side evaporation plate portion 221d and the other-side evaporation plate portion 221h arranged on the other side of the stacking direction Ds with respect to the one-side evaporation plate portion 221d. Is.

As shown in FIGS. 2, 5 and 6, one of the pair of evaporation plate portions 221d and 221h, one side evaporation plate portion 221d, is a first evaporation tank forming portion recessed to one side in the stacking direction Ds. It has 221e, a second evaporation tank forming portion 221f, and an evaporation channel forming portion 221g.

Further, the other side evaporation plate part 221h, which is the other of the pair of evaporation plate parts 221d and 221h, evaporates with the first evaporation tank forming part 221i and the second evaporation tank forming part 221j recessed toward the other side in the stacking direction Ds. It has a flow path forming portion 221k.

The one-side evaporation tank space 221a is formed between the two first evaporation tank forming portions 221e and 221i, and the other side evaporation tank space 221b is formed between both the second evaporation tank forming portions 221f and 221j. ing. Further, the evaporation channel 221c is formed between both evaporation channel forming portions 221g and 221k.

Further, in the one-side evaporation plate portion 221d, the width of the first evaporation tank forming portion 221e and the width of the second evaporation tank forming portion 221f are the same in the stacking direction Ds, and the evaporation flow path forming portion 221g (that is, that is). It is larger than the width of the first and third low-pressure refrigerant flow path forming portions). Further, the widths of the evaporation tank forming portions 221e and 221f in the stacking direction Ds are the same as the widths of the condensing tank forming portions 201e and 201f of the one-side condensing plate portion 201d.

Similarly, in the other side evaporation plate portion 221h, the width of the first evaporation tank forming portion 221i and the width of the second evaporation tank forming portion 221j are the same in the stacking direction Ds. It is larger than the width of the evaporation channel forming portion 221k (that is, the second and fourth low pressure refrigerant channel forming portions). Further, the widths of the evaporation tank forming portions 221i and 221j in the stacking direction Ds are the same as the widths of the condensing tank forming portions 201i and 201j of the condensing plate portion 201h on the other side.

Therefore, in the evaporation unit 22, the first evaporation tank forming portions 221e and 221i are joined to each other, and the second evaporation tank forming portions 221f and 221j are also joined to each other between the evaporation constituent parts 221 adjacent to each other. There is.

On the other hand, among the evaporation constituent parts 221 adjacent to each other, a ventilation flow path 22a through which air passes is formed between the evaporation flow path forming portions 221g and 221k. As a result, the evaporation section 22 is provided with a plurality of ventilation flow paths 22a.

A plurality of the ventilation flow paths 22a are formed side by side in the stacking direction Ds, and each of the plurality of ventilation flow paths 22a (that is, the second air flow path) is brazed to the outside of the evaporation flow path forming portions 221g and 221k. The evaporation part fin 223, which is a brazed corrugated fin, is arranged. Then, the evaporation section fin 223 promotes heat exchange between the air flow passing through the ventilation flow path 22a (that is, the second air flow) and the refrigerant in the evaporation section 22.

As shown in FIGS. 2 and 8, the evaporation component 221 located at the other end of the stacking direction Ds among the plurality of evaporation components 221 has a different shape from the other evaporation components 221. For example, the evaporation component 221 located at the other end is composed of a one-side evaporation plate portion 221d and a portion 321g of the other-side first plate 321 facing the one-side evaporation plate portion 221d. There is.

As shown in FIGS. 5, 6 and 8, in the one-side evaporation plate portion 221d, the first evaporation tank forming portion 221e is formed with a first communication hole 221m penetrating in the stacking direction Ds to form a second evaporation tank. A second communication hole 221n penetrating in the stacking direction Ds is formed in the portion 221f. Similarly, in the other side evaporation plate portion 221h, the first evaporation tank forming portion 221i is formed with the first communication hole 221o penetrating in the stacking direction Ds, and the second evaporation tank forming portion 221j is formed with the stacking direction Ds. A second communication hole 221p is formed through the hole.

The evaporation tank space 221a on one side of each of the evaporation components 221 adjacent to each other communicates with each other by arranging the first communication holes 221m and 221o so as to overlap each other. Further, the evaporation tank space 221b on the other side of each of the evaporation components 221 adjacent to each other communicates with each other by arranging the second communication holes 221n and 221p so as to overlap each other.

However, some of the plurality of evaporation components 221 are not provided with any of the first communication holes 221m and 221o and the second communication holes 221n and 221p. As a result, a plurality of evaporation constituent groups 224a to 224c having one or more evaporation constituents 221 are configured. In the present embodiment, the first evaporation constituent group 224a, the second evaporation constituent group 224b, and the third evaporation constituent group 224c are configured as the plurality of evaporation constituent groups 224a to 224c.

In the evaporation unit 22, the first evaporation component group 224a, the second evaporation component group 224b, and the third evaporation component group 224c are arranged side by side from the other side to one side in the stacking direction Ds in the order of description. .. Then, in the refrigerant flow of the evaporation unit 22, the first evaporation component group 224a, the second evaporation component group 224b, and the third evaporation component group 224c are connected in series from the upstream side to the downstream side in the order of description. ing.

Further, in the evaporation component group having the plurality of evaporation components 221 out of the plurality of evaporation components groups 224a to 224c, the plurality of evaporation flow paths 221c are connected in parallel in the refrigerant flow.

In order to realize such a flow path of the refrigerant, as shown in the E1 part of FIG. 8, the one-side evaporation plate part 221d located at one end of the stacking direction Ds in the first evaporation component group 224a Is not provided with the first communication hole 221 m. Further, as shown in the E2 portion, the second communication hole 221p is not provided in the other side evaporation plate portion 221h located at the other end of the stacking direction Ds in the third evaporation component group 224c. Further, as shown in the E3 portion, the one-side evaporation plate portion 221d located at one end of the stacking direction Ds in the third evaporation component group 224c is not provided with the first communication hole 221m. For example, the one-side evaporation plate portion 221d in which the second communication hole 221n is provided but the first communication hole 221m is not provided is shown in FIG.

As shown in FIGS. 2, 5, and 6, one one-side condensing plate portion 201d, one one-side evaporation plate portion 221d, and one first outer cylinder constituent portion 281a are configured as a single component. .. That is, the one-side condensing plate portion 201d, the one-side evaporation plate portion 221d, and the first outer cylinder constituent portion 281a constitute one first plate member 381 (that is, the first and third heat exchange plates). .. Among the first plate members 381, the one-side condensing plate portion 201d, the first outer cylinder constituent portion 281a, and the one-side evaporation plate portion 221d are arranged in this order from the lower side to the upper side in the vertical direction Dg. It is arranged in.

Therefore, the first plate member 381 has a first outer cylinder constituent portion 281a, which is a portion constituting a part of the internal heat exchange portion 28, between the one-side condensing plate portion 201d and the one-side evaporation plate portion 221d. doing. In short, the first plate member 381 constitutes a part of the internal heat exchange unit 28.

Similarly, one other side condensing plate portion 201h, one other side evaporation plate portion 221h, and one second outer cylinder constituent portion 281b are configured as a single component. That is, the other side condensing plate portion 201h, the other side evaporating plate portion 221h, and the second outer cylinder forming portion 281b constitute one second plate member 382 (that is, the second and fourth heat exchange plates). .. Among the second plate members 382, the other side condensing plate portion 201h, the second outer cylinder constituent portion 281b, and the other side evaporation plate portion 221h are arranged in this order from the lower side to the upper side in the vertical direction Dg. It is arranged in. Therefore, the second plate member 382 has a second outer cylinder constituent portion 281b, which is a portion constituting a part of the internal heat exchange portion 28, between the other side condensing plate portion 201h and the other side evaporation plate portion 221h. doing. In short, the second plate member 382 constitutes a part of the internal heat exchange portion 28.

In the present embodiment, the first plate member 381 is formed so that the outer cylinder forming portion 281a is convex toward one side of the stacking direction Ds (that is, one side in the predetermined direction) with respect to the evaporation flow path forming portion 221g. The second plate member 382 is formed so that the outer cylinder constituent portion 281b is convex toward the other side of the stacking direction Ds (that is, the other side in the predetermined direction) with respect to the evaporation flow path forming portion 221k.

Both the first plate member 381 and the second plate member 382 are made of a metal having good thermal conductivity such as an aluminum alloy. Further, the plurality of first plate members 381 and the plurality of second plate members 382 are alternately laminated and arranged in the stacking direction Ds, and are brazed to each other. In the present embodiment, the first plate member 381 and the second plate member 382 are joined to a plate member located at one end of the stacking direction Ds, that is, the first plate 301 on one side. The plate member is a second plate member 382. The plate member located at the other end of the laminated structure in the stacking direction Ds, that is, the plate member joined to the first plate 321 on the other side is referred to as the first plate member 381.

Further, in the present embodiment, the second plate member 382 has the front and back surfaces of the stacking direction Ds with respect to the first plate member 381, except for the presence or absence of the communication holes 201m, 201n, 201o, 201p, 221m, 221n, 221o, and 221p. It is said that the shape is inverted. Both the first plate member 381 and the second plate member 382 have a shape symmetrical with respect to the heat exchanger width direction Dw. Therefore, parts are standardized between at least a part of the plurality of first plate members 381 and at least a part of the plurality of second plate members 382.

Further, in the pair of the first plate member 381 and the second plate member 382, the internal space of the condensation component 201, the internal space of the evaporation component 221 and the outer flow path 28a of the internal heat exchange unit 28 are mutually connected. It is an independent space. That is, the first plate member 381 is formed so as to separate the condensing flow path 201c, the outer flow path 28a, and the evaporation flow path 221c formed by the first plate member 381 from each other. Similarly to this, the second plate member 382 is also formed so as to separate the condensing flow path 201c, the outer flow path 28a, and the evaporation flow path 221c formed by the second plate member 382 from each other.

In the heat exchanger 10 configured as described above and the refrigeration cycle circuit 12 including the heat exchanger 10, the refrigerant flows as follows. First, as shown in FIGS. 1, 2, and 7, the refrigerant discharged from the compressor 14 passes through the inlet pipe 34 as shown by arrows Fi and F1a, and the first condensed component group 204a of the condensed portion 20 Of these, a plurality of one-sided condensing tank spaces 201a flow into the upstream space in which they are connected.

The refrigerant that has flowed into the upstream space of the first condensing component group 204a is distributed to the plurality of condensing flow paths 201c while flowing to one side of the stacking direction Ds as shown by the arrow F2a in the upstream space.

Here, an air flow from one side of the heat exchanger width direction Dw flows to the other side of the heat exchanger width direction Dw through the circumference of the condensing component 201 (that is, a plurality of ventilation flow paths 20a) as shown by the arrow FB2 in FIG.

The refrigerant (that is, high-pressure refrigerant) flowing through the plurality of condensing flow paths 201c flows in parallel with each other as shown by arrows F4a, F4b, and F4c, and the air flow around the condensing component 201 (that is, the plurality of ventilation flow paths 20a). It exchanges heat with the air flow inside) and dissipates heat to that air flow.

Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of condensing tank spaces 201b on the other side are connected. Further, the refrigerant is transferred from the downstream space of the first condensing component group 204a to the upstream space in which a plurality of other side condensing tank spaces 201b of the second condensing component group 204b are connected as shown by an arrow F3a. Inflow. The refrigerant that has flowed into the upstream space of the second condensed component group 204b is distributed to the plurality of condensed flow paths 201c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing through the plurality of condensed flow paths 201c exchanges heat with the air flow around the condensed component 201 (that is, the air flow in the plurality of ventilation flow paths 20a) while flowing in parallel with each other as shown by arrows F4d and F4e. It is made to dissipate heat to the air flow.

Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of one-sided condensing tank spaces 201a are connected. Further, the refrigerant flows from the downstream space of the second condensed component group 204b into the one-sided condensed tank space 201a as the upstream space of the third condensed component group 204c as shown by an arrow F2b. The refrigerant that has flowed into the upstream space of the third condensed component group 204c flows from the upstream space to the condensed flow path 201c. The refrigerant flowing in the condensing flow path 201c exchanges heat with the air flow around the condensing component 201 (that is, the air flow in the plurality of ventilation flow paths 20a) while flowing as shown by the arrow F4f, and dissipates heat to the air. ..

Then, the refrigerant flows from the condensing flow path 201c into the condensing tank space 201b on the other side as a downstream space. Further, the refrigerant is transferred from the downstream space of the third condensed component group 204c to the upstream space in which a plurality of other side condensed tank spaces 201b of the fourth condensed component group 204d are connected as shown by an arrow F3b. Inflow.

The refrigerant that has flowed into the upstream space of the fourth condensed component group 204d is distributed to the plurality of condensed flow paths 201c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of condensing flow paths 201c exchanges heat with the air flow around the condensing component 201 (that is, the air flow in the plurality of ventilation flow paths 20a) while flowing in parallel with each other as shown by arrows F4g and F4h. It is made to dissipate heat to the air flow.

Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of one-sided condensing tank spaces 201a are connected. The refrigerant that has flowed into the space on the downstream side of the fourth condensing component group 204d is, as shown by arrows F1b and F2c, from the condensing portion outlet 202a to the condensing portion through hole 301b of the first plate 301 on one side and the second on one side. It flows into the one-side relay flow path 30a through the through hole 302b for the condensing portion of the plate 302.

In the one-side relay flow path 30a, the refrigerant flows from the lower side to the upper side of the vertical Dg as shown by the arrow F1c in FIG. 2, and the refrigerant flows from the one-side relay flow path 30a to the internal heat exchange portion as shown by the arrow F1d. It flows into the inner flow path 28b of 28. In the inner flow path 28b, the refrigerant flows from one side of the stacking direction Ds to the other side, and the refrigerant flows from the inner flow path 28b to the other side relay flow path 32a as shown by the arrow F1e.

In the other side relay flow path 32a, the refrigerant flows from the lower side to the upper side in the vertical direction Dg, and the refrigerant flows from the other side relay flow path 32a through the throttle hole 321d of the other side first plate 321 into the evaporation unit 22. Inflow to. At this time, the refrigerant flow is throttled in the throttle hole 321d, so that the refrigerant pressure after passing through the throttle hole 321d is lower than the refrigerant pressure before passing through the throttle hole 321d.

As shown in FIGS. 2 and 8, the refrigerant that has passed through the throttle hole 321d of the throttle section 321e flows into the evaporation section 22 from the evaporation section inlet 222a. Therefore, all of the plurality of condensing flow paths 201c formed in the condensing portion 20 evaporate the evaporating portion 22 through the condensing portion outlet 202a (see FIG. 7), the throttle hole 321d, and the evaporating portion inlet 222a in the order of description. It is connected to the flow path 221c.

The refrigerant flowing into the evaporation unit 22 from the evaporation unit inlet 222a first flows into the upstream space in which a plurality of one-side evaporation tank spaces 221a of the first evaporation component group 224a are connected. The refrigerant that has flowed into the upstream space of the first evaporation component group 224a is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds as shown by the arrow F5a in the upstream space.
Here, an air flow from one side of the heat exchanger width direction Dw flows to the other side of the heat exchanger width direction Dw through the evaporation component 221 (that is, a plurality of ventilation flow paths 22a) as shown by the arrow FB1 in FIG.

The refrigerant flowing through the plurality of evaporation flow paths 221c exchanges heat with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a) while flowing in parallel with each other as shown by arrows F7a and F7b. It is made to absorb heat from the air flow.

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of other side evaporation tank spaces 221b are connected. Further, the refrigerant is transferred from the downstream space of the first evaporation component group 224a to the upstream space in which a plurality of other side evaporation tank spaces 221b of the second evaporation component group 224b are connected as shown by an arrow F6a. Inflow.

The refrigerant that has flowed into the upstream space of the second evaporation component group 224b is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing through the plurality of evaporation flow paths 221c exchanges heat with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a) while flowing in parallel with each other as shown by arrows F7c and F7d. It is made to absorb heat from the air flow.

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of one-side evaporation tank spaces 221a are connected. Further, the refrigerant is transferred from the downstream space of the second evaporation component group 224b to the upstream space in which a plurality of one-side evaporation tank spaces 221a of the third evaporation component group 224c are connected as shown by an arrow F5b. Inflow.

The refrigerant that has flowed into the upstream space of the third evaporation component group 224c is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of evaporation channels 221c flows in parallel with each other as shown by arrows F7e, F7f, and F7g, exchanges heat with the air flow around the evaporation component 221 and absorbs heat from the air flow.

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of other side evaporation tank spaces 221b are connected. The refrigerant that has flowed into the downstream space of the third evaporation component group 224c flows from the evaporation part outlet 22b to the liquid storage space 26a of the gas-liquid separation part 26 of the one-side side plate part 30 as shown by arrows F6b and F8. Flow to.

In the gas-liquid separation unit 26, the refrigerant is gas-liquid separated, and among the gas-liquid separated refrigerants, the gas-phase refrigerant flows to the outer flow path 28a of the internal heat exchange unit 28 as shown by arrows F9a and F9b. On the other hand, among the gas-liquid separated refrigerants, the liquid-phase refrigerant accumulates in the liquid storage space 26a.

The refrigerant flowing in the outer flow path 28a of the internal heat exchange unit 28 exchanges heat with the refrigerant flowing in the inner flow path 28b while flowing from one side to the other side of the stacking direction Ds as shown by arrows FA1 and FA2 in FIG. Be made to. Then, the refrigerant flowing through the outer flow path 28a flows out from the outlet pipe 36 to the outside of the heat exchanger 10 as shown by the arrow Fo. The refrigerant flowing out of the outlet pipe 36 is sucked into the compressor 14 as shown in FIG. As described above, the refrigerant flows in the heat exchanger 10 and the refrigeration cycle circuit 12.

In the present embodiment, as described above, in the evaporation unit 22, the refrigerant flowing in the plurality of evaporation flow paths 221c absorbs heat from the air flow around the evaporation component unit 221 (that is, the air flow in the plurality of ventilation flow paths 22a). .. Therefore, in the plurality of ventilation flow paths 22a, condensed water is generated on the surface exposed on the ventilation flow path 22a side and the evaporation part fin 223 in each of the plurality of evaporation components 221.

The condensed water generated in this way is dropped onto the upper outer surface 283 of the water guide plate 50 and the outer cylinder portion 281 as shown by arrows W1 and W2 in FIG. The condensed water dropped on the water guide plate 50 flows to the upper outer surface 283 of the outer cylinder portion 281 along the water guide plate 50 as shown by the arrow W3 in FIG.

Here, on the upper outer surface 283 of the outer cylinder portion 281, the condensed water flowing from the water guide plate 50 merges with the condensed water dropped from the surfaces of the plurality of ventilation flow paths 22a and the evaporation portion fin 223. The merged condensed water is a heat exchanger between the one side plate portion 30 and the other side plate portion 32 with respect to the outer cylinder portion 281 along the upper outer surface 283 as shown by the arrow W3 in FIG. It flows to one side of the width direction Dw.

After that, between the one side plate portion 30 and the other side plate portion 32, the condensed water passes through one side of the heat exchanger width direction Dw with respect to the outer tubular portion 281 and the plurality of ventilation flow paths 20a of the condensing portion 20. Drop into.

That is, the condensed water is guided to the upstream side of the air flow in the condensing part heat exchange core 230 of the condensing part 20 by the water guiding plate 50 and the upper outer surface 283 of the outer cylinder part 281. Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation flow paths 20a and the condensed portion fins 203 in the plurality of condensed constituent portions 201.

The refrigerant flowing in the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

According to the present embodiment described above, the heat exchanger 10 has an internal heat exchange with a condensing unit 20 including a heat exchange core 230 that dissipates heat from the refrigerant to an air flow in a plurality of ventilation flow paths 20a, an evaporation unit 22, and an internal heat exchanger. A unit 28 is provided.

The evaporation section 22 is arranged on the Dg upper side in the vertical direction with respect to the condensing section 20, and is a refrigerant by heat exchange between the air flow in the plurality of ventilation flow paths 22a and the refrigerant (that is, the low pressure refrigerant) in the evaporation flow path 221c. Is absorbed from the air flow in the plurality of ventilation flow paths 22a and evaporated.

The internal heat exchange unit 28 is arranged between the condensing unit 20 and the evaporation unit 22. The internal heat exchange portion 28 includes an upper outer surface 283 of the outer tubular portion 281.

The above-mentioned Patent Document 1 describes that a water storage unit for storing condensed water generated in the evaporation unit is provided in a case, and the condensed water in the water storage unit is hung on the heat dissipation unit.

For example, as shown in FIGS. 15 and 16, when the condensed water generated in the evaporation section 22 is hung on the condensing section 20 from above, the condensed water is hung on the heat exchange section of the condensing section 20 along the upper tank. Instead, it just flows downwind. Therefore, the condensed water may not be useful for cooling the high-pressure refrigerant in the heat exchange section of the condensing section 20.

On the other hand, the internal heat exchange unit 28 of the present embodiment includes the upper outer surface 283 of the outer cylinder portion 281 as described above. The upper outer surface 283 guides the condensed water generated from the evaporation unit 22 by the heat exchange of the evaporation unit 22 to the wind side of the air flow in the plurality of ventilation passages 22a of the heat exchange cores 230 in the condensation unit 20. The condensed water to be collected is hung on the heat exchange core 230. Therefore, the refrigerant (that is, the high-pressure refrigerant) in the condensing flow path 201c dissipates heat to the condensed water to vaporize the condensed water.

According to this, the heat of vaporization can be transferred from the refrigerant in the condensing flow path 201c to the condensed water. Therefore, the refrigerant in the condensing flow path 201c can be cooled by the condensed water. Therefore, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensing unit 20. it can.

Specifically, the condensing unit 20 and the evaporation unit 22 are configured to have a plurality of pairs of the first plate member 381 and the second plate member 382. Hereinafter, for convenience of explanation, as shown in FIG. 14, the first plate member 381, the second plate member 382, the first plate member 381, and the second plate member 382 arranged in the stacking direction Ds are referred to as the first plate member 381A. , 2nd plate member 382A, 1st plate member 381B, 2nd plate member 382B.

The first plate member 381A is a first heat exchange plate arranged on one side of the stacking direction Ds with respect to the second plate member 382A. The first plate member 381B is a third heat exchange plate arranged on one side of the stacking direction Ds with respect to the second plate member 382B. The second plate member 382A is a second heat exchange plate arranged on one side in a predetermined direction with respect to the first plate member 381B (that is, the fourth heat exchange plate).

The first plate member 381 and the second plate member 382 are arranged so as to be paired with each other, and the evaporation flow path 221c and the condensation flow path 221c and the condensation flow path are arranged between the first plate member 381 and the second plate member 382. 201c is formed. Ventilation channels 20a and 22a are formed between the second plate member 382A and the first plate member 381B.

The first plate member 381B and the second plate member 382B are arranged so as to form a pair and meet each other, and ventilation passages 20a and 22a are formed between the first plate member 381B and the second plate member 382B. Has been done. The first plate members 381A and 381B and the second plate members 382A and 382B each constitute an internal heat exchange unit 28.

The internal heat exchange section 28 is arranged between the evaporation flow path 221c and the condensation flow path 201c and exchanges heat between the refrigerant that has passed through the condensation section 20 and the refrigerant that has passed through the evaporation section 22. The upper outer surface 283 of the internal heat exchange section 28 serves as a water guiding section that guides the condensed water to the windward side of the air flow in the heat exchange core 230.

In the present embodiment, the first plate members 381A and 381B are formed so that the outer cylinder forming portion 281a is convex toward one side of the stacking direction Ds with respect to the evaporation flow path forming portion 221g, respectively. The second plate members 382A and 382B are formed so that the outer cylinder forming portion 281b is convex toward the other side of the stacking direction Ds with respect to the evaporation flow path forming portion 221k, respectively. Therefore, the condensed water generated on the outer surface of the evaporation channel forming portions 221g and 221k can be satisfactorily received by the outer cylinder constituent portions 281a and 281b.

In the present embodiment, the water guide plate 50 is arranged between the one side side plate portion 30 and the other side side plate portion 32. The water guide plate 50 has a heat exchanger width with respect to the internal heat exchange portion 28. Direction Dw is arranged on the other side. The water guide plate 50 guides the condensed water dropped from the ventilation flow path 22a to the upper outer surface 283 of the outer cylinder portion 281 of the internal heat exchange portion 28.

Therefore, a large amount of condensed water can be collected and guided to the windward side of the air flow in the plurality of ventilation channels 22a of the heat exchange cores 230 in the condensing portion 20. In the present embodiment, the water guide plate 50 is formed so as to be inclined so that the upper surface thereof advances in the vertical direction Dg toward the other side in the heat exchanger width direction Dw. Therefore, the water guide plate 50 suppresses the condensed water dropped from the plurality of ventilation flow paths 22a from flowing to the leeward side of the air flow in the plurality of ventilation flow paths 20a, and the condensed water is transferred to the internal heat exchange unit 28. It can be satisfactorily guided to the upper outer surface 283 of the outer cylinder portion 281.

(Second Embodiment)
Next, the second embodiment will be described. In this embodiment, the differences from the above-described first embodiment will be mainly described. In addition, the same or equivalent parts as those in the above-described embodiment will be omitted or simplified. This also applies to the description of the embodiment described later.
As shown in FIGS. 17 and 18, the heat exchanger 10 of the present embodiment includes a condensing unit 20, an evaporation unit 22, and a drawing unit 321e, as in the first embodiment. However, unlike the first embodiment, the heat exchanger 10 of the present embodiment does not include the gas-liquid separation unit 26 (see FIG. 2) and the internal heat exchange unit 28.

In FIG. 18, the cross sections of the first plate member 381, the second plate member 382, the condensing part fin 203, and the evaporation part fin 223 are shown by thick lines instead of hatching. Further, in order to make the illustration easy to see, FIG. 18 shows a deliberate spacing (that is, actually) between the first plate member 381, the second plate member 382, the one-side side plate portion 30, and the other-side side plate portion 32. It is displayed with a space (no interval).

The refrigeration cycle circuit 12 of the present embodiment includes a gas-liquid separator 40 corresponding to the gas-liquid separation unit 26 of the first embodiment as a device different from the heat exchanger 10. The gas-liquid separator 40 is an accumulator having the same function as the gas-liquid separator 26, and is provided on the downstream side of the refrigerant flow with respect to the outlet pipe 36 of the heat exchanger 10 and on the upstream side of the refrigerant flow with respect to the compressor 14. ..

As shown in FIGS. 18 and 19, in the present embodiment, the one-side side plate portion 30 has a single-layer structure rather than a laminated structure in which a plurality of plates are laminated. That is, the one-sided side plate portion 30 of the present embodiment is composed of the one-sided first plate 301, and corresponds to the one-sided second plate 302 and the one-sided third plate 303 (see FIG. 2) of the first embodiment. Does not have.

The inlet pipe 34 is inserted into a lower through hole 30b formed in the lower part of the one side side plate portion 30, and is brazed to the one side side plate portion 30 at the lower through hole 30b. As a result, the inlet pipe 34 is connected to the condensing portion 20 so as to communicate with the condensing portion 20.

Further, the outlet pipe 36 is inserted into the upper through hole 30c formed in the upper part of the one side side plate portion 30, and is brazed to the one side side plate portion 30 at the upper through hole 30c. .. As a result, the outlet pipe 36 is connected to the evaporation unit 22 so as to communicate with the evaporation unit 22.

As shown in FIGS. 18 and 20, the other side plate portion 32 has the other side first plate 321 and the other side second plate 322, and the other side first plate 321 and the other side second plate thereof. It is configured by laminating 322 and joining to each other.

The first plate 321 on the other side has a diaphragm portion 321e as in the first embodiment. In addition, the first plate 321 on the other side is formed with a condensing portion outlet hole 321h which is a through hole provided in the lower part of the first plate 321 on the other side. The condensing portion outlet hole 321h communicates with the condensing portion outlet 202a.

The second plate 322 on the other side has a groove portion 322a that is recessed from one side of the stacking direction Ds to the other side and extends in the vertical direction Dg. The other side second plate 322 is brazed to the other side of the stacking direction Ds with respect to the other side first plate 321 so that the groove portion 322a of the other side second plate 322 is joined to the other side first plate 321. A side relay flow path 322b is formed between the two.

This side relay flow path 322b extends in the vertical direction Dg, and is provided between the condensing portion outlet hole 321h and the throttle portion 321e of the other side first plate 321 in the refrigerant flow. That is, the side relay flow path 322b is a flow path that connects the condensing portion outlet 202a of the condensing portion 20 and the throttle hole 321d. Due to such a flow path configuration of the refrigerant, the throttle hole 321d of the other side plate portion 32 is provided between the condensing portion outlet 202a and the evaporation portion inlet 222a in the refrigerant flow.

As shown in FIG. 18, in the present embodiment as in the first embodiment, one condensing component 201 and one evaporation component 221 arranged in the vertical direction Dg have a pair of plate members 381 and 382 in the stacking direction. It is configured by being laminated on Ds and joined to each other. Then, of the pair of plate members 381 and 382, the first plate member 381 is arranged on one side of the stacking direction Ds with respect to the second plate member 382.

However, in the present embodiment, as shown in FIGS. 18 and 21, one side condensing tank space 201a is arranged below the condensation flow path 201c in the vertical direction Dg, and the other side condensing tank space 201b is the condensing flow path 201c. It is arranged above the vertical Dg. Further, the one-side evaporation tank space 221a is arranged below the evaporation flow path 221c in the vertical direction Dg, and the other side evaporation tank space 221b is arranged above the evaporation flow path 221c in the vertical direction Dg.
As shown in FIG. 18, the condensing unit 20 of the present embodiment includes a first condensed component group 204a, a second condensed component group 204b, a third condensed component group 204c, and a fourth condensed component group 204d. doing. The first condensed component group 204a, the second condensed component group 204b, the third condensed component group 204c, and the fourth condensed component group 204d are arranged from one side to the other side in the stacking direction Ds in the order of description. Have been placed.

Then, in the refrigerant flow of the condensing unit 20, the first condensed component group 204a, the second condensed component group 204b, the third condensed component group 204c, and the fourth condensed component group 204d are on the upstream side in the order of description. It is connected in series from to the downstream side.

Further, in each of the plurality of condensing components groups 204a to 204d, a plurality of condensing flow paths 201c are connected in parallel in the refrigerant flow.

In order to realize such a refrigerant flow path, as shown in the C4 portion of FIG. 18, in the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the first condensing component group 204a. Is not provided with the first communication hole 201o. Further, as shown in the C5 portion, the second communication hole 201p is not provided in the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the second condensing component group 204b. Further, as shown in the C6 portion, the first communication hole 201o is not provided in the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the third condensing component group 204c.

For example, the other side condensing plate portion 201h in which the second communication hole 201p is provided but the first communication hole 201o is not provided is shown in FIG. 23. Further, the other side condensing plate portion 201h in which the first communication hole 201o is provided but the second communication hole 201p is not provided is shown in FIG. 24.

As shown in FIG. 18, in the present embodiment, the plurality of evaporation constituent groups 224a to 224d included in the evaporation portion 22 are the first evaporation constituent group 224a, the second evaporation constituent group 224b, and the third evaporation constituent group. Group 224c and fourth evaporation component group 224d are configured.

In the evaporation unit 22 of the present embodiment, the first evaporation component group 224a, the second evaporation component group 224b, the third evaporation component group 224c, and the fourth evaporation component group 224d are in the stacking direction Ds in the order of description. They are arranged side by side from the other side to one side. Then, in the refrigerant flow of the evaporation unit 22, the first evaporation component group 224a, the second evaporation component group 224b, the third evaporation component group 224c, and the fourth evaporation component group 224d are on the upstream side in the order of description. It is connected in series from to the downstream side.
Further, in each of the plurality of evaporation components groups 224a to 224d, a plurality of evaporation channels 221c are connected in parallel in the refrigerant flow.

In order to realize such a flow path of the refrigerant, as shown in the E4 part of FIG. 18, the other side evaporation plate part 221h located at the other end of the stacking direction Ds in the second evaporation component group 224b Is not provided with a second communication hole 221p. Further, as shown in the E5 portion, the first communication hole 221o is not provided in the other side evaporation plate portion 221h located at the other end of the stacking direction Ds in the third evaporation component group 224c. Further, as shown in the E6 portion, the second communication hole 221p is not provided in the other side evaporation plate portion 221h located at the other end of the stacking direction Ds in the fourth evaporation component group 224d.

For example, the other side evaporation plate portion 221h in which the first communication hole 221o is provided but the second communication hole 221p is not provided is shown in FIG. 23. Further, the other side evaporation plate portion 221h in which the second communication hole 221p is provided but the first communication hole 221o is not provided is shown in FIG.

In the present embodiment, as shown in FIG. 21, one one-side condensing plate portion 201d and one one-side evaporation plate portion 221d are not configured as a single component, but are configured as separate components. As shown in FIG. 22, one other side condensing plate portion 201h and one other side evaporation plate portion 221h are not configured as a single component, but are configured as separate components. Therefore, in the present embodiment, the first plate member 381 (see FIG. 15) is not configured, and the second plate member 382 is also not configured. In this respect, the present embodiment is different from the first embodiment.

As described above, the one-side condensing plate portion 201d and the one-side evaporation plate portion 221d are configured as separate parts, and the other-side condensing plate portion 201h and the other-side evaporation plate portion 221h are also configured as separate parts. .. Therefore, the condensing portion 20 and the evaporating portion 22 are integrally formed by joining the one-side side plate portion 30 and the other-side side plate portion 32 on both sides of the condensing portion 20 and the evaporating portion 22.

However, as shown in FIG. 18, in the C4 portion of FIG. 18, the first communication hole 201o is formed in the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the first condensing component group 204a. Is not provided. Further, as shown in FIGS. 23 and 27, in the C5 portion of FIG. 23, the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the second condensing component group 204b has a second The communication hole 201p is not provided. Further, as shown in FIGS. 23 and 26, in the C6 portion of FIG. 23, the other side condensing plate portion 201h located at the other end of the stacking direction Ds in the third condensing component group 204c has a first The communication hole 201o is not provided.

Further, as shown in FIG. 18, in the E4 portion of FIG. 18, the second communication hole 221p is provided in the other side evaporation plate portion 221h located at the other end of the stacking direction Ds in the second evaporation component group 224b. Is not provided. Further, as shown in FIG. 18, in the E5 part of FIG. 18, the first communication hole 221o is formed in the other side evaporation plate part 221h located at the other end of the stacking direction Ds in the third evaporation component group 224c. Is not provided. Further, as shown in FIG. 18, in the E6 portion of FIG. 18, the second communication hole 221p is provided in the other side evaporation plate portion 221h located at the other end of the stacking direction Ds in the fourth evaporation component group 224d. Is not provided.

Further, as can be seen from FIGS. 21 to 24, not only between the plurality of one-side condensing plate portions 201d and between the plurality of one-side evaporating plate portions 221d, but also between the one-side condensing plate portion 201d and the one-side evaporating plate portion 201d. Parts are shared with each other with the unit 221d. Similarly, not only between the plurality of other side condensing plate portions 201h and between the plurality of other side evaporative plate portions 221h, but also between the other side condensing plate portion 201h and the other side evaporative plate portion 221h. Parts are standardized.

In the present embodiment, a water guiding section 50A is provided between one condensing component 201 and one evaporation component 221.

The water guide portion 50A includes a partition plate 51 and a closing plate 52. The partition plate 51 is arranged between the evaporation component 221 of the evaporation section 22 and the condensation configuration section 201 of the condensation section 20. The partition plate 51 is formed in a plate shape extending in an intersecting direction in which the evaporation portion 22 and the condensing portion 20 intersect in the line-up direction.

The partition plate 51 is arranged between the one side side plate portion 30 and the other side side plate portion 32. The partition plate 51 is formed in a plate shape over the stacking direction Ds. That is, the partition plate 51 is formed in a plate shape that extends in the stacking direction Ds and the heat exchanger width direction Dw (that is, the intersecting direction in which the evaporation portion 22 and the condensing portion 20 intersect in the line-up direction).

The partition plate 51 is formed so as to cover one side and the center side of the heat exchanger width direction Dw with respect to the evaporation portion 22. Therefore, the partition plate 51 is arranged with respect to the evaporation portion 22 so as to be offset from the other side in the heat exchanger width direction Dw.

The closing plate 52 is formed in a plate shape that is connected to one side of the partition plate 51 in the heat exchanger width direction Dw (that is, the leeward side of the air flow in the ventilation flow path 20a) and extends in the vertical direction Dg. The closing plate 52 is formed so as to close the gap between one condensation component 201 and one evaporation component 221.

The closing plate 52 is a water guiding plate formed so as to prevent the condensed water dropped on the partition plate 51 from flowing to one side of the heat exchanger width direction Dw. That is, the closing plate 52 constitutes a weir portion that prevents condensed water from flowing from the partition plate 51 to the leeward side of the air flow in the ventilation flow path 20a.

In the heat exchanger 10 and the refrigeration cycle circuit 12 of the present embodiment, the refrigerant flows as follows. The broken line arrow shown in FIG. 18 indicates the refrigerant flow in the heat exchanger 10.

First, as shown in FIG. 18, the refrigerant discharged from the compressor 14 is connected to a plurality of one-sided condensing tank spaces 201a among the first condensing component group 204a of the condensing portion 20 via the inlet pipe 34. It flows into the upstream space. The refrigerant that has flowed into the upstream space of the first condensed component group 204a is distributed to the plurality of condensed flow paths 201c while flowing to the other side of the stacking direction Ds in the upstream space.

Here, an air flow from the other side of the heat exchanger width direction Dw flows to one side of the heat exchanger width direction Dw through the condensing component 201 (that is, a plurality of ventilation flow paths 20a) as shown by the arrow FB2 in FIG.

The refrigerant flowing in the plurality of condensed flow paths 201c (that is, high-pressure refrigerant) flows in parallel with each other and exchanges heat with the air flow around the condensed component 201 (that is, the air flow in the plurality of ventilation flow paths 20a). Heat is dissipated to the air flow.

Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of condensing tank spaces 201b on the other side are connected. Further, the refrigerant flows from the downstream space of the first condensing component group 204a into the upstream space in which a plurality of other side condensing tank spaces 201b of the second condensing component group 204b are connected.

The refrigerant that has flowed into the upstream space of the second condensation component group 204b is distributed to the plurality of condensation channels 201c while flowing to the other side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of condensing flow paths 201c is exchanged with the air flow around the condensing component 201 (that is, the air flow in the plurality of ventilation flow paths 20a) while flowing in parallel with each other, and dissipates heat to the air flow. .. Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of one-sided condensing tank spaces 201a are connected. Further, the refrigerant flows from the downstream space of the second condensed component group 204b into the upstream space in which a plurality of one-sided condensed tank spaces 201a of the third condensed component group 204c are connected.

The refrigerant that has flowed into the upstream space of the third condensed component group 204c is distributed to the plurality of condensed flow paths 201c while flowing to the other side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of condensing flow paths 201c is exchanged with the air flow around the condensing component 201 (that is, the air flow in the plurality of ventilation flow paths 20a) while flowing in parallel with each other, and dissipates heat to the air flow. .. Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of condensing tank spaces 201b on the other side are connected. Further, the refrigerant flows from the downstream side space of the third condensed component group 204c into the upstream space in which a plurality of other side condensed tank spaces 201b of the fourth condensed component group 204d are connected.

The refrigerant that has flowed into the upstream space of the fourth condensed component group 204d is distributed to the plurality of condensed flow paths 201c while flowing to the other side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of condensing flow paths 201c is exchanged with the air flow around the condensing component 201 (that is, the plurality of ventilation flow paths 20a) while flowing in parallel with each other, and radiates heat to the air flow.

Then, the refrigerant flows from the plurality of condensing flow paths 201c into the downstream space in which the plurality of one-sided condensing tank spaces 201a are connected. The refrigerant that has flowed into the space on the downstream side of the fourth condensing component group 204d flows into the side relay flow path 322b from the condensing portion outlet 202a through the condensing portion outlet hole 321h of the other side plate portion 32.

In the side relay flow path 322b, the refrigerant flows from the lower side to the upper side in the vertical direction Dg, and the refrigerant flows from the side relay flow path 322b into the evaporation section 22 through the throttle hole 321d of the throttle section 321e. At this time, the refrigerant is depressurized by passing through the throttle hole 321d.

The refrigerant that has passed through the throttle hole 321d of the throttle section 321e flows into the evaporation section 22 from the evaporation section inlet 222a. The refrigerant flowing into the evaporation section 22 from the evaporation section inlet 222a first flows into the upstream space in which the plurality of other side evaporation tank spaces 221b of the first evaporation component group 224a are connected.

The refrigerant that has flowed into the upstream space of the first evaporation component group 224a is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space.

Here, an air flow from the other side of the heat exchanger width direction Dw flows to one side of the heat exchanger width direction Dw through the evaporation component 221 (that is, a plurality of ventilation flow paths 22a) as shown by the arrow FB1 in FIG.

Therefore, the refrigerant flowing in the plurality of evaporation flow paths 221c is exchanged with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a) while flowing in parallel with each other, and the air flow thereof. It absorbs heat from.

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of one-side evaporation tank spaces 221a are connected. Further, the refrigerant flows from the downstream space of the first evaporation component group 224a into the upstream space in which a plurality of one-side evaporation tank spaces 221a of the second evaporation component group 224b are connected. The refrigerant that has flowed into the upstream space of the second evaporation component group 224b is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of evaporation flow paths 221c flows in parallel with each other, exchanges heat with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a), and absorbs heat from the air.

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of other side evaporation tank spaces 221b are connected. Further, the refrigerant flows from the downstream space of the second evaporation component group 224b into the upstream space in which a plurality of other side evaporation tank spaces 221b of the third evaporation component group 224c are connected.

The refrigerant that has flowed into the upstream space of the third evaporation component group 224c is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of evaporation flow paths 221c is exchanged with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a) while flowing in parallel with each other, and absorbs heat from the air flow. ..

Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of one-side evaporation tank spaces 221a are connected. Further, the refrigerant flows from the downstream space of the third evaporation component group 224c into the upstream space in which a plurality of one-side evaporation tank spaces 221a of the fourth evaporation component group 224d are connected.

The refrigerant that has flowed into the upstream space of the fourth evaporation component group 224d is distributed to the plurality of evaporation channels 221c while flowing to one side of the stacking direction Ds in the upstream space. The refrigerant flowing in the plurality of evaporation flow paths 221c flows in parallel with each other, exchanges heat with the air flow around the evaporation component 221 (that is, the air flow in the plurality of ventilation flow paths 22a), and absorbs heat from the air. Then, the refrigerant flows from the plurality of evaporation channels 221c into the downstream space in which the plurality of other side evaporation tank spaces 221b are connected. The refrigerant that has flowed into the space on the downstream side of the fourth evaporation component group 224d flows out from the outlet pipe 36 to the outside of the heat exchanger 10. The refrigerant flowing out of the outlet pipe 36 flows into the gas-liquid separator 40 as shown in FIG. 14, and is sucked into the compressor 14 from the gas-liquid separator 40. As described above, the refrigerant flows in the heat exchanger 10 and the refrigeration cycle circuit 12 of the present embodiment.

In the present embodiment, as described above, in the evaporation unit 22, the refrigerant flowing in the plurality of evaporation flow paths 221c absorbs heat from the air flow around the evaporation component unit 221 (that is, the air flow in the plurality of ventilation flow paths 22a). .. Therefore, in the plurality of ventilation flow paths 22a, condensed water is generated on the surface exposed on the ventilation flow path 22a side and the evaporation part fin 223 in each of the plurality of evaporation components 221.

The condensed water generated in this way is dropped onto the partition plate 51 as shown by the arrow W4 in FIG. 21. The condensed water dropped on the partition plate 51 flows along the partition plate 51 to the other side of the heat exchanger width direction Dw as shown by the arrow W4 in FIG. 21.

After that, the condensed water between the one side plate portion 30 and the other side plate portion 32 passes through the other side of the heat exchanger width direction Dw with respect to the partition plate 51 and enters the plurality of ventilation flow paths 20a of the condensing portion 20. Drop.

That is, the condensed water is guided by the partition plate 51 to the upstream side of the air flow in the condensing part heat exchange core 230 of the condensing part 20. Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation flow paths 20a and the condensed portion fins 203 in the plurality of condensed constituent portions 201.

The refrigerant flowing in the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

Except as described above, this embodiment is the same as the first embodiment. Then, in the present embodiment, the effect obtained from the configuration common to the above-mentioned first embodiment can be obtained in the same manner as in the first embodiment.

(Third Embodiment)
In the first and second embodiments described above, an example in which a water guide portion for guiding the condensed water generated in the evaporation portion to the windward side of the heat exchange portion of the heat dissipation portion has been described in the heat exchanger. However, in addition to this, the third embodiment in which a distributor for distributing and hanging condensed water over the width direction of the heat radiating portion is added will be described with reference to FIGS. 25, 26, and 27. ..

The heat exchanger of the present embodiment includes an upper air-conditioning casing 60, a lower air-conditioning casing 61, a drain pipe 62, and a distributor 63 together with an evaporation unit 22 and a condensing unit 20. The upper air-conditioning casing 60 includes an air flow path 60a for accommodating the evaporation unit 22 and allowing an air flow passing through the evaporation unit 22 to flow, and a water storage unit 60b for temporarily storing the condensed water generated in the evaporation unit 22.

The lower air-conditioning casing 61 is arranged on the lower side in the vertical direction with respect to the upper air-conditioning casing 60. The lower air-conditioning casing 61 includes an air flow path 61a that houses the condensing portion 20 and allows an air flow that passes through the condensing portion 20 to flow. The drain pipe 62 is a pipe for guiding the condensed water in the water storage portion 60b of the upper air conditioning casing 60 to the distributor 63 in the lower air conditioning casing 61.

The distributor 63 includes a water guide unit 64, a distribution unit 65, and a support member 66. The water conducting portion 64 is made of a fiber material and is formed so as to expand in the width direction of the heat exchange core 230. The water guiding portion 64 is arranged on the heavenly region improvement side of the heat exchange core 230 of the condensing portion 20 and on the windward side with respect to the condensing portion 20.

The water guide unit 64 is used to distribute the condensed water from the drain pipe 62 to the distribution unit 65. The water guiding portion 64 of the present embodiment is fitted between the side plates 236 and 237 of the condensing portion 20.

The distribution unit 65 is connected to the water guide unit 64. The distribution unit 65 is composed of a fine fiber material, and guides the condensed water from the water guide unit 64 to a plurality of tubes 231 and heat exchange fins 233 by a capillary phenomenon. The distribution unit 65 includes a plurality of protrusions 65a of the water guide 64 that project from the improvement side to the leeward side.

The plurality of protrusions 65a are arranged in the width direction of the heat exchange core 230, respectively. The plurality of protrusions 65a are respectively arranged between two adjacent tubes 231 of the plurality of tubes 231 of the heat exchange core 230. The plurality of protrusions 65a are respectively arranged above the corresponding heat exchange fins 233 of the heat exchange fins 233.

As a result, the plurality of protrusions 65a come into contact with the upper side of the heat exchange fins 233 and the plurality of tubes 231 of the heat exchange core 230, respectively.

The condensing unit 20 includes an upper tank 234, a heat exchange core 230, and a lower tank 235. The upper tank 234 distributes the high-pressure refrigerant from the compressor 14 to the plurality of tubes 231 of the heat exchange core 230. Each of the plurality of tubes 231 is formed so as to extend in the vertical direction. The plurality of tubes 231 are arranged in the width direction at intervals. Each of the plurality of tubes 231 is a refrigerant pipe for guiding the high-pressure refrigerant from the upper tank 234 to the lower tank 235.

Each of the plurality of tubes 231 circulates a high-pressure refrigerant to dissipate heat from the high-pressure refrigerant to an air flow passing through the air flow path 61a. The lower tank 235 collects the high-pressure refrigerant that has passed through the plurality of tubes 231 and guides it to the decompression section.

A ventilation flow path 20a for circulating an air flow is provided between two adjacent tubes 231 of the plurality of tubes 231. Heat exchange fins 233 are arranged in each of the plurality of ventilation flow paths 20a. The heat exchange fins 233, together with the plurality of tubes 231, exchange heat between the air flow in the plurality of ventilation flow paths 20a and the high-pressure refrigerant.

The distributor 63 configured in this way is arranged below the upper tank 234 of the condensing portion 20 in the vertical direction, on the improving side of the heat exchange core 230, and on the windward side of the heat exchange core 230. ing.

Next, the operation of the heat exchanger 10 of the present embodiment will be described.

First, the refrigerant discharged from the compressor 14 (that is, the high-pressure refrigerant) flows through the plurality of tubes 231 of the heat exchange core 230 of the condensing unit 20. At this time, an air flow flows through the plurality of ventilation passages 20a of the heat exchange core 230 as shown by the arrow FB2 in FIG.

Heat is exchanged between the air flow in the plurality of ventilation flow paths 20a and the refrigerant in the plurality of tubes 231. As a result, the refrigerant dissipates heat to the air flow, so that the refrigerant is cooled.

On the other hand, the refrigerant that has passed through the pressure reducing valve (that is, the low-pressure refrigerant) flows through the evaporation unit 22. Along with this, heat is exchanged between the low-pressure refrigerant flowing in the evaporation unit 22 and the air flow passing through the evaporation unit 22, and the refrigerant absorbs heat from the air flow. At this time, condensed water is generated in the evaporation unit 22.

Condensed water drops from the evaporation unit 22 of this condensed water. Therefore, the condensed water is temporarily stored in the water storage portion 60b of the upper air conditioning casing 60. The condensed water in the water storage portion 60b is guided to the water guide portion 64 of the distributor 63 through the drain pipe 62. The condensed water guided to the water conveyance portion 64 is guided to the windward side in the air flow direction of the heat exchange core 230 through the distribution portion 65 by the capillary phenomenon.

As a result, the condensed water is distributed by the distributor 63 to the heat exchange core 230 in the width direction. Therefore, in the heat exchange core 230, the refrigerant flowing through the plurality of tubes 231 dissipates heat to the condensed water and vaporizes the condensed water. As a result, the condensed water cools the refrigerant in the plurality of tubes 231 together with the air flow. According to the present embodiment described above, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, the refrigerant flowing through the plurality of tubes 231 of the condensing unit 20 radiates heat to the air flow and is cooled. The drain pipe 62 guides the condensed water in the water storage portion 60b of the upper air conditioning casing 60 to the distributor 63 in the lower air conditioning casing 61.

Therefore, the distributor 63 is guided to the lower side of the condensing portion 20 in the vertical direction with respect to the upper tank 234, to the upper side of the heat exchange core 230 to improve the top region, and to the windward side of the heat exchange core 230. The distributor 63 distributes the condensed water to the heat exchange core 230 in the width direction thereof.

In the heat exchange core 230, the refrigerant flowing through the plurality of tubes 231 dissipates heat to the condensed water and vaporizes the condensed water. As a result, the condensed water cools the refrigerant in the plurality of tubes 231 together with the air flow.

From the above, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensation unit 20.

(Fourth Embodiment)
In the first and second embodiments, an example will be described in which the heat exchanger 10 is provided with a water guiding portion 50A for guiding the condensed water generated in the evaporating portion 22 to the windward side of the heat exchange core 230 of the condensing portion 20. did.

However, by flowing the air flow flowing through the condensing unit 20 in the opposite direction to the air flow flowing through the evaporation unit 22 without providing the water conducting unit 50A, the condensed water is flowed upwind of the heat exchange core 230 of the condensing unit 20. The fourth embodiment will be described with reference to FIG. 28.

In the present embodiment, as shown by arrows FB1 and FB2 in FIG. 28, the air flow flowing through the evaporation unit 22 and the air flow flowing through the condensing unit 20 flow in opposite directions.

In the present embodiment, as described above, in the evaporation unit 22, the refrigerant flowing in the plurality of evaporation flow paths 221c absorbs heat from the air flow around the evaporation component unit 221 (that is, the air flow in the plurality of ventilation flow paths 22a). .. Therefore, in the plurality of ventilation flow paths 22a, condensed water is generated in each of the plurality of evaporation components 221.

The condensed water generated in this way flows downward by Dg in the vertical direction along the plurality of evaporation components 221 due to gravity. At this time, the condensed water flows leeward along the plurality of evaporation components 221 by the air flow passing through the evaporation unit 22.

Condensed water drops from one side of the heat exchanger width direction Dw of the evaporation unit 22 onto one side of the heat exchanger width direction Dw of the heat exchange core 230 of the condensation unit 20. That is, the air flow passing through the evaporation unit 22 guides the condensed water of the evaporation unit 22 to the windward side of the heat exchange core 230 of the condensation unit 20.

Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation passages 20a and the condensing part fins 203 in the plurality of condensing components 201.

The refrigerant flowing in the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the condensed water to the refrigerant flowing through the plurality of condensed flow paths 201c. As a result, the condensed water cools the refrigerant in the plurality of tubes 231 together with the air flow.

From the above, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensation unit 20.

(Fifth Embodiment) In the fifth embodiment, in the first embodiment, the condensed water generated from the evaporation unit 22 by arranging the heat exchanger 10 at an angle is air in the heat exchange core 230 of the condensation unit 20. An example of guiding the flow (that is, the first air flow) to the windward side will be described.

FIG. 29 shows the overall configuration of the vehicle air conditioner 70 to which the heat exchanger 10 of the present embodiment is applied.

As shown in FIGS. 29, 30, and 31, the vehicle air conditioner 70 of the present embodiment includes a heat exchanger 10, a blower unit 80, and a blower duct 90. The blower unit 80 is an air flow generator including centrifugal fans 81A and 81B, and a blower case 82.

The centrifugal fan 81A is rotated about the axis S by the rotational force output from the rotating shaft 83a of the electric motor 83. The centrifugal fan 81A is a sirocco fan that sucks in air flow from one side in the axial direction and blows it out in the radial direction by its rotation.

The centrifugal fan 81B is rotated about the axis S by the rotational force output from the rotating shaft 83a of the electric motor 83. The centrifugal fan 81B is a sirocco fan that sucks in air flow from one side in the axial direction and blows it out in the radial direction by its rotation.

The blower case 82 collects the air flow blown from the centrifugal fan 81A and guides it to the upper air flow path 91 of the duct 90, and collects the air flow blown out from the centrifugal fan 81B to the lower air flow path 92 of the duct 90. Lead to.

The air duct 90 forms an upper air flow path 91 and a lower air flow path 92. The upper air flow path 91 and the lower air flow path 92 are formed so as to be separated by a ventilation duct 90. The heat exchanger 10 is arranged so as to straddle the upper air flow path 91 and the lower air flow path 92.

The evaporation unit 22 is arranged in the upper air flow path 91. The condensing portion 20 is arranged in the lower air flow path 92.

In the present embodiment, the main stream of the air flow flowing through the evaporation unit 22 (that is, the second air flow) and the main flow of the air flow flowing through the condensing unit 20 (that is, the first air flow) are parallel and identical to each other. Flows in the direction of.

Here, the main flow of the air flow flowing through the evaporation unit 22 is the air flow having the largest air volume among the plurality of air flows flowing through the evaporation unit 22. The mainstream of the air flow flowing through the condensing portion 20 is the air flow having the largest air volume among the plurality of air flows flowing through the condensing portion 20.

In the present embodiment, the other side of the heat exchanger 10 in the width direction Dw of the heat exchanger is arranged above the one side of the heat exchanger 10 in the width direction Dw of the heat exchanger in the vertical direction (that is, Dg in the vertical direction). There is.

Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged above the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction) with respect to the windward side of the air flow.

Therefore, the condensed water generated in the evaporation section 22 is guided to the windward side of the air flow in the evaporation section 22 along the surface exposed on the ventilation flow path 22a side and the evaporation section fin 223 in each of the plurality of evaporation components 221. ..

This guided condensed water is guided to the upstream side of the air flow in the condensed portion heat exchange core 230 of the condensed portion 20 through the region 400 on one side of the heat exchanger width direction Dw from the heat insulating hole 381a of the heat exchanger 10. Will be killed.

The heat insulating hole 381a is provided between the condensing portion 20 and the evaporating portion 22 in place of the internal heat exchange portion 28. The heat insulating hole 381a is provided to prevent heat transfer between the refrigerant in the condensation component 201 and the refrigerant in the evaporation component 221. The heat insulating hole 381a is formed by communicating the through hole of the first plate member 381 and the through hole of the second plate member 382.

That is, in the present embodiment, the leeward side of the air flow in the evaporation unit 22 is arranged above the windward side of the air flow in the evaporation unit 22, so that the evaporation unit 22 condenses the condensed water by gravity. It will be guided to the upstream side of the air flow in the condensing part heat exchange core 230 of the part 20.

Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation passages 20a and the condensing part fins 203 in the plurality of condensing components 201. As a result, the refrigerant flowing through the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

Thereby, the refrigerant in the condensing flow path 201c can be cooled by the condensed water. Therefore, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensing unit 20. it can.

In this embodiment, a heat insulating hole 381a is formed in place of the internal heat exchange portion 28. The heat insulating hole 381a serves to prevent heat transfer between the refrigerant in the condensation component 201 and the refrigerant in the evaporation component 221.

In the present embodiment, both the one-sided condensing tank space 201a and the other-side condensing tank space 201b are arranged below the vertical Dg with respect to the condensing flow path 201c. Both the one-side evaporation tank space 221a and the other-side evaporation tank space 221b are arranged above the evaporation flow path 221c in the vertical direction Dg.

(Sixth Embodiment)
In the fifth embodiment, an example in which the main stream of the air flow flowing through the evaporation section 22 and the main stream of the air flow flowing through the condensing section 20 flow in parallel and in the same direction as each other has been described.

However, instead of this, the mainstream of the air flow flowing through the evaporation section 22 (that is, the second airflow) and the mainstream of the airflow flowing through the condensing section 20 (that is, the first airflow) are parallel and mutually. The sixth embodiment in which the air flows in the opposite direction will be described with reference to FIGS. 32 and 33.

As shown in FIGS. 32 and 33, the vehicle air conditioner 70 of the present embodiment includes a heat exchanger 10, a blower unit 80, and a blower duct 90. The blower unit 80 is an air flow generator including a centrifugal fan 81C and a blower case 82A.

The centrifugal fan 81C is rotated about the axis by the rotational force output from the rotating shaft of the electric motor. The centrifugal fan 81C is a plug fan that sucks in air flow from one side in the axial direction and blows it out in the radial direction by its rotation.

The blower case 82A guides the air flow blown from the centrifugal fan 81C to the upper air flow path 91 and the lower air flow path 92 of the duct 90.

The air duct 90 forms an upper air flow path 91 and a lower air flow path 92. The upper air flow path 91 and the lower air flow path 92 are formed so as to be separated by a ventilation duct 90. The heat exchanger 10 is arranged so as to straddle the upper air flow path 91 and the lower air flow path 92.

In the present embodiment, the main stream of the air flow flowing through the evaporation section 22 (that is, the second air flow) and the main stream of the air flow flowing through the condensing section 20 (that is, the first air flow) are parallel and opposite to each other. Flow to.

In the present embodiment, the other side of the heat exchanger 10 in the width direction Dw of the heat exchanger is arranged above the one side of the heat exchanger 10 in the width direction Dw of the heat exchanger in the vertical direction (that is, Dg in the vertical direction). There is.

That is, the leeward side of the air flow in the evaporation unit 22 is arranged below the windward side of the air flow in the evaporation unit 22, so that the evaporation unit 22 condenses the condensed water in the condensing unit 20 by gravity. It will be guided to the upstream side of the air flow in the partial heat exchange core 230.

Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged above the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction) with respect to the windward side of the air flow. Therefore, the condensed water generated in the evaporation section 22 is the air in the condensing section heat exchange core 230 of the condensing section 20 along the surface exposed on the ventilation flow path 22a side in each of the plurality of evaporation components 221 and the evaporation section fin 223. It will be guided to the upstream side.

Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation passages 20a and the condensing part fins 203 in the plurality of condensing components 201. As a result, the refrigerant flowing through the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

From the above, the refrigerant in the condensing flow path 201c can be cooled by the condensed water as in the fifth embodiment. Therefore, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensing unit 20. it can.

(7th Embodiment)
In the sixth embodiment, an example in which the air flow blown from one centrifugal fan is divided and flowed to the evaporation unit 22 and the condensation unit 20 has been described. However, instead of this, the seventh embodiment in which the air flow is circulated from the two centrifugal fans 81A and 81B to the evaporation unit 22 and the condensation unit 20 will be described with reference to FIG. 34.

FIG. 34 shows the overall configuration of the vehicle air conditioner 70 to which the heat exchanger 10 of the present embodiment is applied.

As shown in FIG. 34, the vehicle air conditioner 70 of the present embodiment includes a heat exchanger 10, blower units 80A and 80B, and a blower duct 90.

The blower unit 80A includes a centrifugal fan 81A and a blower case 82A. The centrifugal fan 81A is rotated about the axis by the rotational force output from the rotating shaft of the electric motor. The centrifugal fan 81A is a sirocco fan that sucks in air flow from one side in the axial direction and blows it out in the radial direction by its rotation. The blower case 82A collects the air flow generated from the centrifugal fan 81A and guides it to the upper air flow path 91 of the duct 90.

The blower unit 80B includes a centrifugal fan 81B and a blower case 82B. The centrifugal fan 81B is rotated about the axis by the rotational force output from the rotating shaft of the electric motor. The centrifugal fan 81B is a sirocco fan that sucks in air flow from one side in the axial direction and blows it out in the radial direction by its rotation. The blower case 82B collects the air flow generated from the centrifugal fan 81B and guides it to the lower air flow path 92 of the duct 90.

The blower unit 80A and the blower unit 80B of the present embodiment constitute an air flow generation unit that generates an air flow to be circulated in each of the upper air flow path 91 and the lower air flow path 92 of the duct 90.

The blower duct 90 constitutes an upper air flow path 91 that circulates the air flow blown from the blower unit 80A and a lower air flow path 92 that circulates the air flow blown out from the blower unit 80B. The upper air flow path 91 and the lower air flow path 92 are separated by a ventilation duct 90. The heat exchanger 10 is arranged so as to straddle the upper air flow path 91 and the lower air flow path 92.

In the present embodiment, similarly to the sixth embodiment, the main stream of the air flow flowing through the evaporation section 22 (that is, the second air flow) and the main stream of the air flow flowing through the condensing section 20 (that is, the first air flow). Flow parallel and opposite to each other.

In the present embodiment, similarly to the sixth embodiment, the other side of the heat exchanger 10 in the heat exchanger width direction Dw is more vertical than the other side of the heat exchanger 10 in the heat exchanger width direction Dw (that is, vertical). It is arranged on the upper side in the direction Dg).

Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged below the upwind side of the air flow in the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction). As a result, the evaporation unit 22 guides the condensed water to the upstream side of the air flow in the heat exchange core 230 of the condensation unit of the condensation unit 20 by gravity.

Therefore, the condensed water generated in the evaporation section 22 is the air in the condensing section heat exchange core 230 of the condensing section 20 along the surface exposed on the ventilation flow path 22a side in each of the plurality of evaporation components 221 and the evaporation section fin 223. It will be guided to the upstream side.

Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation passages 20a and the condensing part fins 203 in the plurality of condensing components 201. As a result, the refrigerant flowing through the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

Thereby, the refrigerant in the condensing flow path 201c can be cooled by the condensed water. Therefore, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensing unit 20. it can.

(8th Embodiment)
In the sixth and seventh embodiments, an example in which the heat exchanger 10 provided with the heat insulating hole 381a is arranged in an inclined manner has been described. However, instead of this, the eighth embodiment in which the heat exchanger 10 provided with the internal heat exchange portion 28 instead of the heat insulating hole 381a is arranged in an inclined manner will be described with reference to FIG. 35.

Similar to the heat exchanger 10 of the first embodiment, the heat exchanger 10 of the present embodiment is the main stream of the air flow flowing through the evaporation unit 22 (that is, the second air flow) and the air flow flowing through the condensing unit 20 (that is, the second air flow). That is, the main stream of the first air stream) flows in parallel and in the same direction.

In the present embodiment, the other side of the heat exchanger 10 in the width direction Dw of the heat exchanger is arranged above the one side of the heat exchanger 10 in the width direction Dw of the heat exchanger in the vertical direction (that is, Dg in the vertical direction). There is.

Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged above the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction) with respect to the windward side of the air flow. As a result, the evaporation unit 22 guides the condensed water to the upstream side of the air flow in the heat exchange core 230 of the condensation unit of the condensation unit 20 by gravity.

Therefore, the condensed water generated in the evaporation section 22 is the air in the condensing section heat exchange core 230 of the condensing section 20 along the surface exposed on the ventilation flow path 22a side in each of the plurality of evaporation components 221 and the evaporation section fin 223. It will be guided to the upstream side.

Further, a part of the condensed water generated in the evaporation portion 22 is dropped on the upper outer surface 283 of the water guide plate 50 and the outer cylinder portion 281. The dropped condensed water is guided to the upstream side of the air flow in the condensed portion heat exchange core 230 of the condensed portion 20 by the upper outer surface 283 of the water guiding plate 50 and the outer tubular portion 281. Therefore, the condensed water is applied to the surface exposed to the plurality of ventilation flow paths 20a and the condensed portion fins 203 in the plurality of condensed constituent portions 201.

As described above, similarly to the sixth embodiment, the refrigerant flowing in the plurality of condensed flow paths 201c dissipates heat to the condensed water to vaporize the condensed water. Therefore, the heat of vaporization is transferred from the refrigerant flowing in the plurality of condensed flow paths 201c to the condensed water.

Thereby, the refrigerant in the condensing flow path 201c can be cooled by the condensed water. Therefore, in the heat exchanger 10 including the evaporation unit 22 and the condensing unit 20, it is possible to provide the heat exchanger 10 in which the condensed water generated in the evaporation unit 22 is used to improve the cooling effect of the refrigerant in the condensing unit 20. it can.

(9th Embodiment)
In the eighth embodiment, an example has been described in which the main stream of the air flow flowing through the evaporation section 22 and the main stream of the air flow flowing through the condensing section 20 are circulated in parallel and in the same direction. However, instead of this, in the ninth embodiment, as shown in FIG. 36, the main stream of the air flow flowing through the evaporation section 22 and the main stream of the air flow flowing through the condensing section 20 are distributed in parallel and in opposite directions to each other. You may let me.

In the present embodiment, similarly to the eighth embodiment, the other side of the heat exchanger 10 in the heat exchanger width direction Dw is more vertical than the other side of the heat exchanger 10 in the heat exchanger width direction Dw (that is, vertical). It is arranged on the upper side in the direction Dg). Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged below the upwind side of the air flow in the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction).

As a result, the evaporation section 22 guides the condensed water to the upstream side of the air flow in the condensing section heat exchange core 230 of the condensing section 20 by gravity. As a result, the same effect as that of the sixth embodiment can be obtained.

(10th Embodiment)
In the ninth embodiment, the example in which the heat exchanger 10 of the first embodiment is inclined and arranged has been described, but instead of this, the heat exchanger 10 of the second embodiment is arranged by being inclined. The tenth embodiment will be described with reference to FIG. 37.

In the heat exchanger 10 of the present embodiment, the main stream of the air flow flowing through the evaporation section 22 and the main stream of the air flow flowing through the condensing section 20 are circulated in parallel and in opposite directions to each other.

In the heat exchanger 10 of the present embodiment, similarly to the sixth embodiment, the other side of the heat exchanger 10 in the heat exchanger width direction Dw is higher than the other side of the heat exchanger 10 in the heat exchanger width direction Dw. It is arranged on the upper side in the direction (that is, the vertical direction Dg). Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged below the upwind side of the air flow in the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction).

As a result, the evaporation section 22 guides the condensed water to the upstream side of the air flow in the condensing section heat exchange core 230 of the condensing section 20 by gravity. Therefore, the condensed water generated in the evaporation section 22 is the air in the condensing section heat exchange core 230 of the condensing section 20 along the surface exposed on the ventilation flow path 22a side in each of the plurality of evaporation components 221 and the evaporation section fin 223. It will be guided to the upstream side.

From the above, the same effect as that of the sixth embodiment can be obtained.

(11th Embodiment)
In the tenth embodiment, an example in which the air flow flowing through the evaporation unit 22 and the air flow flowing through the condensing unit 20 are circulated in opposite directions has been described. However, instead of this, in the eleventh embodiment, as shown in FIG. 38, the main stream of the air flow flowing through the evaporation section 22 and the main stream of the air flow flowing through the condensing section 20 are parallel and in the same direction as each other. It may be distributed.

In the present embodiment, similarly to the tenth embodiment, the other side of the heat exchanger 10 in the heat exchanger width direction Dw is more vertical than the heat exchanger 10 in the heat exchanger width direction Dw one side (that is, vertical). It is arranged on the upper side in the direction Dg). Therefore, the leeward side of the air flow in the evaporation unit 22 is arranged above the evaporation unit 22 in the vertical direction (that is, Dg in the vertical direction) with respect to the windward side of the air flow.

As a result, the evaporation section 22 guides the condensed water to the upstream side of the air flow in the condensing section heat exchange core 230 of the condensing section 20 by gravity. Therefore, the condensed water generated in the evaporation section 22 is the air in the condensing section heat exchange core 230 of the condensing section 20 along the surface exposed on the ventilation flow path 22a side in each of the plurality of evaporation components 221 and the evaporation section fin 223. It will be guided to the upstream side.

From the above, the same effect as that of the tenth embodiment can be obtained.

(Other embodiments)
(1) In the above-mentioned first embodiment, the heat exchanger 10 includes a gas-liquid separation unit 26 as an accumulator, which is an example. For example, as shown in FIG. 39, the heat exchanger 10 may include a receiver 42 that functions as a gas-liquid separator instead of the gas-liquid separator 26.

The receiver 42 is arranged between the outlet 202a of the condensing portion and the inner flow path 28b of the internal heat exchange portion 28 in the flow of the refrigerant. Then, the receiver 42 stores the refrigerant (specifically, the gas-liquid two-phase refrigerant or the liquid single-phase refrigerant) that has flowed into the receiver 42 from the condensing unit 20, gas-liquid separation, and the gas-liquid separation is performed. The liquid refrigerant flows to the inner flow path 28b of the internal heat exchange section 28.

For example, the receiver 42 may be provided on one side side plate portion 30 by laminating a plurality of plates like the gas-liquid separation portion 26, or may be provided on one side of the stacking direction Ds with respect to the one side side plate portion 30. It may be provided so as to be fixed.

(2) In the above-described first embodiment, the outlet position condensing component 202a provided with the condensing outlet 202a is located at one end of the plurality of condensing components 201 in the stacking direction Ds. This is an example.

Depending on the configuration of the refrigerant flow in the heat exchanger 10, the outlet position condensing component 202 may be located at the other end of the plurality of condensing components 201 in the stacking direction Ds.

(3) In the above-described first embodiment, the inlet position evaporation component 222 provided with the evaporation component inlet 222a is located at the other end of the plurality of evaporation components 221 in the stacking direction Ds. This is an example.

Depending on the configuration of the refrigerant flow in the heat exchanger 10, the inlet position evaporation component 222 may be located at one end of the plurality of evaporation components 221 in the stacking direction Ds.

(4) In the above-described first embodiment, the one-side condensing plate portion 201d, the one-side evaporation plate portion 221d, and the first outer cylinder constituent portion 281a constitute one first plate member 381. At the same time, the condensing plate portion 201h on the other side, the evaporation plate portion 221h on the other side, and the second outer cylinder constituent portion 281b constitute one second plate member 382.

However, this is just an example. The combination of the one-side condensing plate portion 201d, the one-side evaporation plate portion 221d, and the first outer cylinder configuration portion 281a, and the combination of the other-side condensing plate portion 201h, the other side evaporation plate portion 221h, and the second outer cylinder configuration portion 281b. One of the above may be a combination of a plurality of separately configured parts.

(5) In the above-described first embodiment, the pair of condensing plate portions 201d and 201h are laminated in the laminating direction Ds in any of the plurality of condensing components 201, but this is an example.

For example, in a part of the plurality of condensed constituent parts 201 included in the condensed portion 20, the pair of condensed plate portions 201d and 201h may not be laminated in the stacking direction Ds. In short, at least one of the plurality of condensed constituent parts 201 included in the condensed part 20 may have a pair of condensed plate parts 201d and 201h.

(6) In the above-mentioned first embodiment, each of the plurality of evaporation components 221 has a pair of evaporation plate portions 221d and 221h, which is an example. For example, in a part of the plurality of evaporation constituent parts 221 included in the evaporation portion 22, the pair of evaporation plate portions 221d and 221h may not be laminated in the stacking direction Ds. In short, at least one of the plurality of evaporation constituent parts 221 included in the evaporation part 22 may have a pair of evaporation plate parts 221d and 221h.

(7) In the above-described first embodiment, the internal space of the condensing component 201 has a shape in which one side condensing plate portion 201d is recessed to one side of the stacking direction Ds and the other side condensing plate portion to the other side of the stacking direction Ds. 201h is formed by a recessed shape.

However, this is just an example. For example, one of the one-side condensing plate portion 201d and the other-side condensing plate portion 201h may have a flat plate shape without having a recessed shape in the stacking direction Ds. This also applies to the shapes of the one-side evaporation plate portion 221d and the other-side evaporation plate portion 221h.

(8) In the above-mentioned first embodiment, the throttle hole 321d provided in the other side plate portion 32 is an orifice, which is an example. The aperture hole 321d may be a capillary, a capillary and an orifice connected to each other, or a block in which the aperture hole 321d is formed as shown in FIGS. 40 and 41. ..

In the examples of FIGS. 40 and 41, the diaphragm hole 321d is configured as a block-shaped member, is fitted into a hole formed in the first plate 321 on the other side, and is fixed to the first plate 321 on the other side.

(9) In the second embodiment described above, the groove portion 322a of the second plate 322 on the other side does not have a function of throttled the refrigerant flow to reduce the pressure of the refrigerant, but this is an example. For example, the groove portion 322a may be configured as a capillary for narrowing the flow of the refrigerant and may have a function of reducing the pressure of the refrigerant.

(10) In the above-described first embodiment, the evaporation unit 22, the internal heat exchange unit 28, and the condensing unit 20 are arranged side by side in the vertical direction Dg from the upper side in the order of description, but the arrangement order and arrangement thereof. There is no limit to the direction. For example, the evaporation unit 22, the internal heat exchange unit 28, and the condensation unit 20 may be arranged side by side in the horizontal direction, or the condensation unit 20 may be arranged above the evaporation unit 22 in the vertical direction Dg.

(11) In the first embodiment described above, the heat exchanger 10 includes a gas-liquid separation unit 26, an internal heat exchange unit 28, and a throttle hole 321d in addition to the evaporation unit 22 and the condensing unit 20. This is an example. For example, it is possible that the heat exchanger 10 does not include all or any of the gas-liquid separation unit 26, the internal heat exchange unit 28, and the throttle hole 321d.

(12) In the second embodiment described above, the condensation flow path 201c and the evaporation flow path 221c have the same shape as each other, but this is an example. For example, the condensation flow path 201c and the evaporation flow path 221c may have different shapes.

(13) In the second embodiment described above, one of the one-sided condensing tank space 201a and the other-side condensing tank space 201b is arranged above the condensation flow path 201c in the vertical direction Dg. The other side of the condensing tank space 201a on one side and the condensing tank space 201b on the other side is arranged below the Dg in the vertical direction with respect to the condensing flow path 201c.

However, this is just an example. For example, both the one-sided condensing tank space 201a and the other-side condensing tank space 201b may be biased to one of the upper side and the lower side of the vertical Dg with respect to the condensing flow path 201c.

This also applies to the configuration of the evaporation unit 22. That is, both the one-side evaporation tank space 221a and the other-side evaporation tank space 221b may be unevenly arranged on one of the upper side and the lower side of the vertical direction Dg with respect to the evaporation flow path 221c.

(14) In the first to eleventh embodiments described above, an example in which the heat exchanger is applied to the vehicle air conditioner has been described, but the present invention is not limited to this, and the heat exchanger is used for various devices other than the vehicle air conditioner (for example,). It may be applied to a stationary air conditioner (refrigerator).

(15) In the first to eleventh embodiments described above, an example in which the heat radiating unit constitutes the condensing unit 20 for condensing the refrigerant in the refrigeration cycle has been described. However, instead of this, the refrigeration cycle may constitute a supercritical cycle in which carbon dioxide is used as the refrigerant and the pressure of the high-pressure refrigerant is higher than the critical point and the heat radiating portion does not condense the refrigerant.

(16) In the second embodiment described above, the gas-liquid separator 40 as an accumulator is provided as a device different from the heat exchanger 10, but this is an example. For example, as shown in FIG. 31, the gas-liquid separator 40 may be configured as a part of the heat exchanger 10 and integrated with the condensing unit 20, the evaporation unit 22, and the drawing unit 321e.

(17) In the fifth to eleventh embodiments, an example has been described in which the main flow of the air flow flowing through the condensing portion 20 and the main flow of the air flow flowing through the evaporation portion 22 are made to flow in parallel and in the same direction. ..

However, the present invention is not limited to this, and in the fifth to eleventh embodiments, the main stream of the air flow flowing through the condensing section 20 and the main stream of the air flow flowing through the evaporation section 22 may flow in substantially the same direction.

For example, in the error range caused by the manufacturing error of the heat exchanger 10, the relationship between the mainstream of the air flow flowing through the condensing unit 20 and the mainstream of the air flow flowing through the evaporation unit 22 deviates from the parallel relationship. You may.

That is, in the fifth to eleventh embodiments, the main stream of the air flow flowing through the condensing section 20 and the main stream of the air flow flowing through the evaporation section 22 do not necessarily have to flow in parallel.

(18) The present disclosure is not limited to the above-described embodiment, and can be changed as appropriate. Further, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential and when they are clearly considered to be essential in principle. No. Further, in each of the above embodiments, when numerical values such as the number, numerical values, amounts, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and in principle, the number is clearly limited to a specific number. It is not limited to the specific number except when it is done. In addition, in each of the above embodiments, when referring to the shape, positional relationship, etc. of a component or the like, the shape, unless otherwise specified or limited in principle to a specific shape, positional relationship, etc. It is not limited to the positional relationship.

(Summary)
According to the first aspect described in the first to eleventh embodiments and some or all of the other embodiments, the heat exchanger is a high pressure refrigerant by heat exchange between the first air flow and the high pressure refrigerant. A heat radiating unit including a heat exchange core for radiating heat to the first air flow is provided.

The heat exchanger is arranged above the heat radiating section, and includes an evaporating section that absorbs heat from the second air stream and evaporates the low pressure refrigerant by heat exchange between the second air stream and the low pressure refrigerant.

The heat exchanger guides the condensed water generated from the evaporation part by the heat exchange of the evaporation part to the wind side of the first air flow in the heat exchange core in the heat dissipation part, and applies this guided condensed water to the heat exchange core to increase the pressure. The condensed water is vaporized by dissipating heat from the refrigerant to the condensed water.

According to the second aspect, the heat exchanger is arranged between the evaporation part and the heat dissipation part for guiding the condensed water generated from the evaporation part to the wind side of the first air flow in the heat exchange core of the heat dissipation part. Equipped with a water guide.

As a result, the condensed water can be satisfactorily applied to the windward side of the first air flow in the heat exchange core.

According to the third aspect, when the direction in which the heat radiating part and the evaporating part intersect in the line-up direction is the crossing direction, the water guiding part is arranged between the heat radiating part and the evaporating part and is formed so as to expand in the intersecting direction. Has been done.

As a result, the water conveyance portion also serves as a partition portion that prevents the first air flow in the first air flow passage and the second air flow in the second air flow passage from being mixed with each other. Therefore, the physique can be reduced as compared with the case where the water conveyance portion and the partition portion are used respectively.

According to the fourth viewpoint, a weir portion is provided on the leeward side of the first air flow in the headrace portion to prevent condensed water from flowing from the headrace portion to the leeward side of the first air flow.

This makes it possible to satisfactorily guide the condensed water from the headrace to the windward side of the first airflow in the heat exchange core.

According to the fifth viewpoint, the heat exchanger includes a high-pressure refrigerant flow path through which the high-pressure refrigerant flows, and the evaporation part includes a low-pressure refrigerant flow path through which the low-pressure refrigerant flows.

The heat radiating section and the evaporating section are configured to include a first heat exchange plate, a second heat exchange plate, a third heat exchange plate, and a fourth heat exchange plate.

The first heat exchange plate is arranged on one side in a predetermined direction with respect to the second heat exchange plate, and the second heat exchange plate is arranged on one side in a predetermined direction with respect to the third heat exchange plate. The third heat exchange plate is arranged on one side in a predetermined direction with respect to the fourth heat exchange plate. The first heat exchange plate and the second heat exchange plate are arranged so as to meet each other, and a high-pressure refrigerant flow path and a low-pressure refrigerant flow path are formed between the first heat exchange plate and the second heat exchange plate. There is.

Between the second heat exchange plate and the third heat exchange plate, a first air flow path through which the first air flow flows and a second air flow path through which the second air flow flows are formed.

The third heat exchange plate and the fourth heat exchange plate are arranged so as to meet each other, and a high-pressure refrigerant flow path and a low-pressure refrigerant flow path are formed between the third heat exchange plate and the fourth heat exchange plate. There is.

According to the sixth aspect, the first heat exchange plate, the second heat exchange plate, the third heat exchange plate, and the fourth heat exchange plate are arranged between the low pressure refrigerant flow path and the high pressure refrigerant flow path, respectively. It constitutes the internal heat exchange unit. The internal heat exchange unit exchanges heat between the low-pressure refrigerant that has passed through the low-pressure refrigerant flow path and the high-pressure refrigerant that has passed through the high-pressure refrigerant flow path.

The internal heat exchange unit constitutes a water guide unit for guiding the condensed water generated in the second air flow path to the windward side of the first air flow in the heat exchange core.

As a result, the water conveyance section can be satisfactorily configured by the internal heat exchange section.

According to the seventh viewpoint, the internal heat exchange portion includes an outer tubular portion that is formed in a tubular shape extending in a predetermined direction and allows low-pressure refrigerant to flow through the low-pressure refrigerant flow path. The internal heat exchange portion includes an inner cylinder portion that is formed in a tubular shape extending in a predetermined direction inside the outer cylinder portion and allows high-pressure refrigerant that has passed through the high-pressure refrigerant flow path to flow, and the low-pressure refrigerant in the outer cylinder portion and the inside of the inner cylinder portion. Heat is exchanged with the high-pressure refrigerant of. The upper portion of the outer tubular portion formed toward the second air flow path constitutes a water conducting portion.

This makes it possible to satisfactorily configure the water conveyance portion using the outer cylinder portion.

According to the eighth viewpoint, when the water guide portion is the first water guide portion, it is arranged on the lower side with respect to the second air flow path and is provided on the leeward side of the first air flow with respect to the outer cylinder portion. , A second headrace for guiding the condensed water generated in the second air flow path to the first headrace is provided.

As a result, the condensed water generated in the second air flow path can be satisfactorily collected in the first headrace.

According to the ninth viewpoint, the second headrace is formed so as to be inclined upward toward the leeward side of the first air flow in order to guide the condensed water to the first headrace.

According to the tenth viewpoint, the evaporation part and the heat dissipation part form a refrigeration cycle together with the pressure reducing valve and the compressor. The compressor sucks in the low-pressure refrigerant flowing from the evaporation unit, compresses it, and discharges the high-pressure refrigerant. The heat radiating unit exchanges heat between the high-pressure refrigerant discharged from the compressor and the first air flow. The pressure reducing valve decompresses the high pressure refrigerant flowing from the heat radiating unit to discharge the low pressure refrigerant, and the evaporation unit exchanges heat between the low pressure refrigerant flowing from the pressure reducing valve and the second air flow.

According to the eleventh viewpoint, in the heat exchanger, the main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in the same direction.

The evaporation section is arranged at an angle so that the windward side of the second air flow of the evaporation section is arranged below the leeward side of the second air flow of the evaporation section, so that the evaporation section is condensed water. Is guided to the windward side of the first air flow in the heat exchange core in the heat dissipation part by gravity.

According to the twelfth viewpoint, in the heat exchanger, the main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in opposite directions to each other.

The evaporation section is arranged at an angle so that the leeward side of the second air stream of the evaporation section is arranged below the leeward side of the second air flow of the evaporation section, so that the evaporation section collects condensed water. The heat exchange core in the heat dissipation section is guided by gravity to the windward side of the first air flow.

According to the thirteenth viewpoint, the air conditioner includes a heat radiating unit including a heat exchange core that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant. The air conditioner is arranged above the heat dissipation unit, and includes an evaporation unit that absorbs heat from the second air stream and evaporates the low pressure refrigerant by heat exchange between the second air stream and the low pressure refrigerant.

The air conditioner has a duct having a first air flow path through which the first air flow flows and a second air flow path formed separately from the first air flow path and through which the second air flow flows. Be prepared. The main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in the same direction.

Condensation generated from the evaporation part by arranging the evaporation part at an angle so that the leeward side of the second air flow of the evaporation part is arranged below the leeward side of the second air flow of the evaporation part. The evaporation part guides water to the windward side of the first air flow in the heat exchange core in the heat dissipation part by gravity.

According to the fourteenth viewpoint, the air conditioner includes a heat radiating unit including a heat exchange core that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant.

The air conditioner is arranged above the heat dissipation unit, and includes an evaporation unit that absorbs heat from the second air flow and evaporates the low pressure refrigerant by heat exchange between the second air flow and the low pressure refrigerant.

The air conditioner includes a duct having a first air flow path through which the first air flow flows, and a second air flow path formed separately from the first air flow path and through which the second air flow flows. ..

The main flow of the first air flow flowing through the heat dissipation part and the main flow of the second air flow flowing through the evaporation part flow in opposite directions.

Condensed water generated from the evaporation section by arranging the evaporation section at an angle so that the leeward side of the second air flow of the evaporation section is arranged below the leeward side of the second air flow of the evaporation section. The evaporation part guides the heat exchange core in the heat dissipation part to the windward side of the first air flow by gravity.

According to the fifteenth viewpoint, an air flow generating unit for generating a first air flow and a second air flow is provided.

Claims (15)

1. It ’s a heat exchanger,
   A heat radiating unit (20) including a heat exchange core (230) that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant.
   It is provided with an evaporation unit (22), which is arranged above the heat dissipation unit and absorbs heat from the second air flow to evaporate the low pressure refrigerant by heat exchange between the second air flow and the low pressure refrigerant.
   The condensed water generated from the evaporation section by the heat exchange of the evaporation section is guided to the wind side of the first air flow of the heat exchange cores in the heat dissipation section, and the guided condensed water is applied to the heat exchange core. A heat exchanger that evaporates the condensed water by radiating heat from the high-pressure refrigerant to the condensed water.
2. A water guide section (283, 51) arranged between the evaporation section and the heat dissipation section for guiding the condensed water generated from the evaporation section to the wind side of the first air flow in the heat exchange core of the heat dissipation section. The heat exchanger according to claim 1.
3. When the direction in which the heat radiating portion and the evaporating portion intersect is defined as the intersecting direction, the water guiding portion is arranged between the heat radiating portion and the evaporating portion and is formed so as to expand in the intersecting direction. The heat exchanger according to claim 2.
4. A weir portion (52) for suppressing the flow of condensed water from the water guide portion to the leeward side of the first air flow is provided on the leeward side of the first air flow of the water guide portion (51). The heat exchanger according to claim 3.
5. The heat radiating unit includes a high-pressure refrigerant flow path (201c) through which the high-pressure refrigerant flows.
   The evaporation unit includes a low-pressure refrigerant flow path (221c) through which the low-pressure refrigerant flows.
   The heat dissipation unit and the evaporation unit include a first heat exchange plate (381A), a second heat exchange plate (382A), a third heat exchange plate (381B), and a fourth heat exchange plate (382B). Has been
   The first heat exchange plate is arranged on one side in a predetermined direction (Ds) with respect to the second heat exchange plate.
   The second heat exchange plate is arranged on one side in the predetermined direction with respect to the third heat exchange plate.
   The third heat exchange plate is arranged on one side in the predetermined direction with respect to the fourth heat exchange plate.
   The first heat exchange plate and the second heat exchange plate are arranged so as to meet each other, and the high-pressure refrigerant flow path and the low-pressure refrigerant are located between the first heat exchange plate and the second heat exchange plate. A flow path is formed,
   Between the second heat exchange plate and the third heat exchange plate, a first air flow path (20a) through which the first air flow flows and a second air flow path (22a) through which the second air flow flows. Is formed,
   The third heat exchange plate and the fourth heat exchange plate are arranged so as to meet each other, and the high-pressure refrigerant flow path and the low-pressure refrigerant are located between the third heat exchange plate and the fourth heat exchange plate. The heat exchanger according to claim 3, wherein the flow path is formed.
6. The first heat exchange plate, the second heat exchange plate, the third heat exchange plate, and the fourth heat exchange plate are arranged between the low-pressure refrigerant flow path and the high-pressure refrigerant flow path, respectively. An internal heat exchange unit (28) that exchanges heat between the low-pressure refrigerant that has passed through the low-pressure refrigerant flow path and the high-pressure refrigerant that has passed through the high-pressure refrigerant flow path is configured.
   5. The internal heat exchange unit constitutes the water guide unit (283) for guiding the condensed water generated in the second air flow path to the windward side of the first air flow in the heat exchange core. The heat exchanger described in.
7. The internal heat exchange unit
   An outer tubular portion (281) formed in a tubular shape extending in a predetermined direction and allowing the low-pressure refrigerant to flow through the low-pressure refrigerant flow path,
   An inner cylinder portion (282) formed inside the outer cylinder portion in a tubular shape extending in a predetermined direction and allowing the high pressure refrigerant to flow through the high pressure refrigerant flow path is provided, and the low pressure inside the outer cylinder portion is provided. Heat exchange is performed between the refrigerant and the high-pressure refrigerant in the inner cylinder portion.
   The heat exchanger according to claim 6, wherein the upper portion of the outer tubular portion formed toward the second air flow path constitutes the water conducting portion (283).
8. When the water guide portion is used as the first water guide portion, it is arranged below the second air flow path and is provided on the leeward side of the first air flow with respect to the outer cylinder portion. The heat exchanger according to claim 7, further comprising a second water conducting unit (50) for guiding the condensed water generated in the air flow path to the first water conducting unit.
9. The heat exchange according to claim 8, wherein the second headrace is formed so as to be inclined upward toward the leeward side of the first air flow in order to guide the condensed water to the first headrace. vessel.
10. The evaporation unit and the heat dissipation unit form a refrigeration cycle together with the decompression unit (321e) and the compressor (14).
    The compressor sucks in and compresses the low-pressure refrigerant flowing from the evaporation unit, and discharges the high-pressure refrigerant.
    The heat radiating unit exchanges heat between the high-pressure refrigerant discharged from the compressor and the first air flow.
    The depressurizing unit decompresses the high-pressure refrigerant flowing from the heat radiating unit and discharges the low-pressure refrigerant.
    The heat exchanger according to any one of claims 1 to 9, wherein the evaporation unit exchanges heat between the low-pressure refrigerant flowing from the decompression unit and the second air flow.
11. The main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in the same direction.
    By arranging the evaporation portion at an angle so that the windward side of the second air flow of the evaporation portion is arranged below the leeward side of the second air flow of the evaporation portion. The heat exchange according to any one of claims 1 to 10, wherein the evaporation unit guides the condensed water to the windward side of the first air flow in the heat exchange core in the heat dissipation unit by gravity. vessel.
12. The main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in opposite directions.
    The evaporation portion is arranged so as to be inclined so that the leeward side of the second air flow of the evaporation portion is arranged below the leeward side of the second air flow of the evaporation portion. The heat exchanger according to any one of claims 1 to 10, wherein the evaporation unit guides the condensed water to the windward side of the first air flow among the heat exchange cores in the heat dissipation unit by gravity. ..
13. It ’s an air conditioner,
    A heat radiating unit (20) including a heat exchange core (230) that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant.
    An evaporation unit (22), which is arranged above the heat dissipation unit and absorbs heat from the second air flow to evaporate the low pressure refrigerant by heat exchange between the second air flow and the low pressure refrigerant.
    A first air flow path (92) through which the first air flow flows, and a second air flow path (91) formed separately from the first air flow path and through which the second air flow flows. With a duct (90) and
    The main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in the same direction.
    By arranging the evaporation portion at an angle so that the wind side of the second air flow of the evaporation portion is arranged below the leeward side of the second air flow of the evaporation portion. An air conditioner in which the evaporation unit guides the condensed water generated from the evaporation unit to the wind side of the first air flow of the heat exchange cores in the heat dissipation unit by gravity.
14. It ’s an air conditioner,
    A heat radiating unit (20) including a heat exchange core (230) that dissipates heat from the high pressure refrigerant to the first air flow by heat exchange between the first air flow and the high pressure refrigerant.
    An evaporation unit (22), which is arranged above the heat dissipation unit and absorbs heat from the second air flow to evaporate the low pressure refrigerant by heat exchange between the second air flow and the low pressure refrigerant.
    A first air flow path (92) through which the first air flow flows, and a second air flow path (91) formed separately from the first air flow path and through which the second air flow flows. With a duct (90) and
    The main stream of the first air flow flowing through the heat radiating section and the main stream of the second air flow flowing through the evaporation section flow in opposite directions.
    The evaporation portion is arranged so as to be inclined so that the leeward side of the second air flow of the evaporation portion is arranged below the wind side of the second air flow of the evaporation portion. An air conditioner in which the evaporation unit guides the condensed water generated from the evaporation unit to the wind side of the first air flow of the heat exchange cores in the heat dissipation unit by gravity.
15. The air conditioner according to claim 14, further comprising an air flow generating unit (80, 80A, 80B) for generating the first air flow and the second air flow.

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