JP6974062B2 - Heat exchanger - Google Patents

Description

The present invention relates to a heat exchanger used in, for example, an air conditioner for a vehicle mounted on an automobile or the like, and particularly belongs to the technical field of a structure having a plurality of paths arranged in an external air flow direction.

Conventionally, a vehicle air conditioner includes an air conditioner casing accommodating a cooling heat exchanger and a heating heat exchanger, a temperature control damper and a blowout direction switching damper arranged inside the air conditioner casing. ing. Then, the amount of air passing through the cooling heat exchanger and the heating heat exchanger is changed by the temperature control damper to adjust the temperature of the conditioned air (blowout air temperature), and the conditioned air is adjusted by the blowout direction switching damper. The blowing direction (defroster, vent, heat, etc.) can be switched.

In this type of vehicle air conditioner, an evaporator, which is an element of the refrigeration cycle, may be used as a cooling heat exchanger (see, for example, Patent Documents 1 and 2). In the heat exchangers of Patent Documents 1 and 2, a plurality of tubes extending in the vertical direction are arranged on the upstream side and the downstream side in the external air flow direction, respectively, and laminated in a direction intersecting the external air flow direction, and the upper end portion of the tubes is formed. The upper and lower header tanks are connected to the lower end and the lower end, respectively. As a result, the path on the upstream side in the external air flow direction (upwind path) and the path on the downstream side (downwind side path) are formed in one heat exchanger. Further, on the upstream side in the external air flow direction, a plurality of windward paths are formed in series, and on the downstream side in the external air flow direction, a plurality of leeward paths are similarly connected in series. It is formed.

When the decompressed refrigerant flows into the heat exchanger from the outside, it flows in order through a plurality of leeward paths formed on the downstream side in the external air flow direction, and then moves to the upstream side in the external air flow direction to multiple upstream sides. It flows in order on the windward path. During this time, the refrigerant exchanges heat with the outside air to cool the outside air.

Japanese Unexamined Patent Publication No. 2015-175562 Japanese Unexamined Patent Publication No. 2009-156532

By the way, in general, the compressor of the refrigeration cycle is controlled according to the surface temperature of the heat exchanger (evaporator). Specifically, when the surface temperature of the heat exchanger drops to near the freezing point, for example, the compressor Stops to suppress freezing of condensed water, while operating the compressor when the surface temperature of the heat exchanger rises.

When the compressor stops, the flow of refrigerant in the heat exchanger will stop, but even if the compressor is stopped, the fan will continue to operate while the air conditioner is on, so the heat exchanger The refrigerant remaining in the path exchanges heat with the external air and evaporates to expand the volume. When the volume of the refrigerant in the windward path expands, the liquid refrigerant that has not yet evaporated may move to the adjacent leeward path. In the leeward path where the liquid refrigerant has moved, the rise in surface temperature will be delayed. That is, in the leeward pass, the cooled external air flows through the leeward pass, so that the delay in the rise of the surface temperature tends to appear remarkably. As a result, the temperature of the air after passing through the heat exchanger will change depending on the part of the heat exchanger through which it passes, and the temperature difference of the air generated by this will be the temperature difference of the air blown out from each outlet of the vehicle. It may be a cause of impairing the comfort of the occupants.

In addition, in a path where the surface temperature rises slowly, the condensed water tends to freeze on the surface, which hinders ventilation and leads to a decrease in cooling performance, and the heat exchanger is deformed or damaged due to the freezing of the condensed water. It is also possible that it will lead to.

The present invention has been made in view of this point, and an object thereof is to partially lower the surface temperature of the heat exchanger even when the flow of the refrigerant in the heat exchanger is stopped. The purpose is to suppress deformation and breakage due to freezing of the heat exchanger while making the temperature of the blown air uniform.

In order to achieve the above object, in the present invention, when the refrigerant expands in volume, it moves to the windward path.

The first invention comprises a plurality of vertically extending tubes arranged on the upstream side and the downstream side in the external air flow direction, respectively, and a header tank communicating with the upper end portion and the lower end portion of the tube. in the heat exchanger between the refrigerant and the outside air is configured to exchange heat flowing to the outside air flow direction upstream of the heat exchanger, the first windward path constituted by the tube, the second The windward pass and the third windward pass are formed, and the first windward pass, the second windward pass, and the third windward pass are arranged so as to be arranged in this order, and the external air in the heat exchanger is arranged. On the downstream side in the flow direction, a first leeward pass , a second leeward pass , a third leeward pass, and a fourth leeward pass composed of the above tubes are formed, and the first leeward pass and the second leeward pass are formed . The leeward pass, the third leeward pass, and the fourth leeward pass are arranged so as to be arranged in order, and the refrigerant flows into the heat exchanger in the first leeward pass and the fourth leeward pass. The downstream side of the first leeward pass and the upstream side of the first leeward pass are connected, and the downstream side of the first leeward path and the upstream side of the second leeward path are connected. The side is connected, and the downstream side of the second leeward pass, the downstream side of the third leeward pass, and the upstream side of the second leeward pass are connected.

According to this configuration, the refrigerant flowing from the refrigerant inflow pipe flows into the first leeward path and exchanges heat with the outside air, and then flows into the first leeward path and exchanges heat with the outside air. After that, it flows into the second leeward path and exchanges heat with the outside air, and then flows into the second leeward path to exchange heat with the outside air.

For example, when the compressor stops and the flow of the refrigerant stops, the liquid refrigerant remaining in the first leeward path exchanges heat with the external air and expands in volume. Due to this volume expansion, the liquid refrigerant in the first windward pass moves to the first windward pass. In the windward path, since the temperature difference between the outside air and the refrigerant is large, the refrigerant evaporates quickly, and the partial temperature rise delay is eliminated.

Further , since the flow of the refrigerant is symmetrical in the heat exchanger, the temperature distribution of the heat exchanger is also symmetrical. As a result, the temperature difference between the left side and the right side of the vehicle is further reduced.

The second invention is characterized in that, in the first invention, the refrigerant inflow pipe is composed of a member different from the header tank.

According to this configuration, since the refrigerant inflow pipe and the header tank are separately configured, the complexity of the header tank is avoided.

The third invention is characterized in that, in the first or second invention, the refrigerant outflow pipe for flowing out the refrigerant from the heat exchanger is provided, and the refrigerant outflow pipe is composed of a member different from the header tank. And.

According to this configuration, since the refrigerant outflow pipe and the header tank are separately configured, the complexity of the header tank is avoided.

A fourth aspect of the invention is characterized in that, in the second or third invention, the refrigerant inflow pipe is arranged inside the header tank.

According to this configuration, since there is no refrigerant inflow pipe outside the heat exchanger, the external shape of the heat exchanger is simplified.

A fifth aspect of the invention is characterized in that, in the third invention, the refrigerant outflow pipe is arranged inside the header tank.

According to this configuration, since there is no refrigerant outflow pipe outside the heat exchanger, the external shape of the heat exchanger is simplified.

A sixth aspect of the invention is characterized in that, in the second or third invention, the refrigerant inflow pipe is arranged outside the header tank.

According to this configuration, since there is no refrigerant inflow pipe inside the heat exchanger, the internal structure of the header tank is simplified. In addition, problems such as refrigerant leakage in the header tank can be avoided.

A seventh aspect of the invention is characterized in that, in the third aspect of the invention, the refrigerant outflow pipe is arranged outside the header tank.

According to this configuration, since the refrigerant outflow pipe is eliminated inside the heat exchanger, the internal structure of the header tank is simplified. In addition, problems such as refrigerant leakage in the header tank can be avoided.

According to the eighth aspect of the invention, in any one of the first to seventh aspects, a partition wall for partitioning the upstream side and the downstream side in the external air flow direction is provided inside the header tank, and the windward path is described above. And the leeward path are connected by a through hole provided in a part of the partition wall.

According to this configuration, it is possible to form a through hole at an arbitrary position according to the diversion state of the refrigerant to connect the leeward path and the leeward path.

According to the ninth aspect of the present invention, in any one of the first to eighth aspects, the tubes constituting each of the above paths are laminated in a direction intersecting the flow direction of the external air, and the portion for flowing the refrigerant into the above paths. The portion where the refrigerant flows out from the path is characterized by being separated in the vertical direction and also in the stacking direction of the tubes.

According to this configuration, the portion where the refrigerant flows into the path and the portion where the refrigerant flows out from the path are located on the diagonal line of the path.

In the tenth invention, in the ninth invention, the most downstream path in the refrigerant flow direction is composed of the second windward path, and the second leeward path and the downstream side of the third leeward path are the second. It is characterized by being connected to the upstream side of the windward path.

According to this configuration, even if there is a difference in the amount of refrigerant between the first leeward pass and the fourth leeward pass, the second leeward pass and the above are the second leeward paths most downstream in the refrigerant flow direction. Since the refrigerants in the third leeward pass merge, the temperature distribution becomes uniform in the second leeward pass. In particular, in the path most downstream in the refrigerant flow direction, the proportion of gas refrigerant is large, and if the flow of the refrigerant is biased, the temperature difference between the parts tends to be large. The temperature difference can be reduced.

First aspect of the invention, in the invention of the first 1 0, in the above refrigerant inflow pipe, evenly and the amount of refrigerant flowing into the refrigerant amount and the fourth leeward path flowing into the first leeward path It is characterized in that a refrigerant diversion control structure is provided for this purpose.

According to this configuration, the temperature distribution of the heat exchanger is symmetrical.

First and second invention, in the first aspect of the invention, the refrigerant inlet pipe, a first tube portion connected to the first downstream side path and a second tube portion connected to the fourth leeward path The refrigerant diversion control structure is characterized by being a throttle portion provided between the first pipe portion and the second pipe portion in the refrigerant inflow pipe.

According to this configuration, the temperature distribution of the heat exchanger can be made symmetrical by a simple structure.

Of the invention the first 3, provided in the first aspect of the invention, the refrigerant inlet pipe, a first tube portion connected to the first downstream side path, the refrigerant flow direction downstream of the first pipe section It has a second pipe portion connected to the fourth leeward path, and the refrigerant diversion control structure is a guide portion for guiding the refrigerant in the refrigerant inflow pipe to the first pipe portion. It is characterized by.

Invention of the first 4, in the invention of the first 1 to 3, between adjacent said tube, characterized in that the cold storage medium is provided.

According to this configuration, cold can be uniformly stored in the cold storage material, and the temperature rise of the refrigerant becomes uniform, so that the temperature distribution becomes symmetrical when the cold storage material releases cold heat.

According to the first invention, when the liquid refrigerant in the leeward pass expands in volume, the liquid refrigerant in the leeward pass can be moved to the leeward pass, so that the partial temperature rise delay of the heat exchanger can be delayed. It can be resolved. As a result, the temperature of the blown air can be made uniform, and deformation and breakage due to freezing of the heat exchanger can be suppressed.

In addition , since the flow of the refrigerant can be made symmetrical in the heat exchanger, the temperature distribution of the heat exchanger becomes symmetrical, and as a result, the temperature difference of the blown air between the left side and the right side of the vehicle becomes larger. It can be made even smaller, and for example, an conditioned air having a uniform temperature can be supplied between the driver's seat side and the passenger seat side.

According to the second invention, since the refrigerant inflow pipe is composed of a member separate from the header tank, the structure of the header tank is not complicated and the productivity can be improved.

According to the third invention, since the refrigerant outflow pipe is composed of a member separate from the header tank, the structure of the header tank is not complicated and the productivity can be improved.

According to the fourth invention, by arranging the refrigerant inflow pipe inside the header tank, the external shape of the heat exchanger can be simplified, and the structure for fixing the heat exchanger to the air conditioning casing can be simplified. can do.

According to the fifth invention, by arranging the refrigerant outflow pipe inside the header tank, the external shape of the heat exchanger can be simplified, and the structure for fixing the heat exchanger to the air conditioning casing can be simplified. can do.

According to the sixth invention, since the refrigerant inflow pipe is arranged outside the header tank, the internal structure of the header tank can be simplified.

According to the seventh invention, since the refrigerant outflow pipe is arranged outside the header tank, the internal structure of the header tank can be simplified.

According to the eighth invention, since the windward path and the leeward path are connected by a through hole provided in a part of the partition wall of the header tank, the leeward path and the leeward side are connected according to the diversion state of the refrigerant. You can connect to the path.

According to the ninth aspect of the invention, the portion where the refrigerant flows into the path and the portion where the refrigerant flows out from the path are located on the diagonal line of the path, so that the refrigerant distribution of each tube is made uniform. be able to.

According to the invention of the first 0. Thus flowing the refrigerant of the two windward side paths for refrigerant flow direction downstream of the path, it is possible to reduce the deviation of the flow of the refrigerant, most refrigerant flow direction The temperature difference between parts can be reduced in the downstream path.

According to a first aspect of the invention, since the amount of refrigerant flowing into the first downstream side path and the amount of refrigerant flowing into the fourth downwind path can be equalized, the temperature distribution of the heat exchanger is symmetrical Therefore, the temperature difference between the left side and the right side of the vehicle can be further reduced.

According to the first and second inventions, the amount of the refrigerant flowing into the first leeward pass and the amount of the refrigerant flowing into the fourth leeward pass can be made equal by the throttle portion, so that the heat exchanger can be easily configured. The temperature distribution can be symmetrical.

According to the invention of the first 3, it is possible to make the temperature distribution of the heat exchanger symmetrically.

According to the invention of the first 4, it is possible to make the temperature distribution symmetric in the case of providing the cold accumulating material between the adjacent tubes.

It is a perspective view which looked at the heat exchanger which concerns on embodiment from the upstream side in the flow direction of outside air. It is the schematic which showed the path split of a heat exchanger and the flow of a refrigerant schematically. It is the schematic which shows the windward side part and the leeward side part of a heat exchanger separately. It is a vertical sectional view of the upper header dunk which shows the connection part of the leeward side path and the leeward side path. It is sectional drawing of the upper header tank which concerns on modification 1. FIG. It is a figure corresponding to FIG. 3 which concerns on modification 2. FIG. It is a figure corresponding to FIG. 3 which concerns on modification 3. FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is essentially merely an example and is not intended to limit the present invention, its application or its use.

FIG. 1 is a perspective view of the heat exchanger 1 according to the embodiment of the present invention as viewed from the upstream side and above in the external air flow direction (indicated by a white arrow). FIG. 2 is different from the actual shape of the heat exchanger 1 (the shape shown in FIG. 1), but this is the paths U1 to U3 and D1 to D4 formed in the heat exchanger 1 (details will be described later). ) And the flow of the refrigerant inside the heat exchanger 1 are shown schematically in an easy-to-understand manner. FIG. 3 also differs from the actual shape of the heat exchanger 1 (the shape shown in FIG. 1), but the paths U1 to U3 and D1 to D4 formed in the heat exchanger 1 by a method different from that of FIG. It is a figure which showed the arrangement and the flow of the refrigerant in the heat exchanger 1 in an easy-to-understand manner schematically. In FIG. 3, the paths U1 to U3 on the upstream side in the external air flow direction and the paths D1 to D4 on the downstream side in the external air flow direction are shown at intervals in the external air flow direction, but are actually shown in FIG. As described above, the paths U1 to U3 on the upstream side in the external air flow direction and the paths D1 to D4 on the downstream side in the external air flow direction are close to each other.

As shown in FIG. 1, the heat exchanger 1 is used as a cooling heat exchanger for, for example, a vehicle air conditioner mounted on an automobile or the like, and in this embodiment, evaporation is an element of a refrigeration cycle. It is composed of vessels. Although not shown, the vehicle air conditioner includes a blower unit having a blower, a resin air conditioner casing connected to the blower unit via a duct or the like, and a temperature control damper and a blower arranged inside the air conditioner casing. It is equipped with a damper for switching directions. In addition to the heat exchanger 1, a heat exchanger for heating made of a heater core or the like, an electric heater made of a PTC heater or the like, and the like are housed inside the air conditioning casing.

The heat exchanger 1 is housed inside the air-conditioning casing, and its outer peripheral portion is held by a holding portion formed in the air-conditioning casing. The heat exchanger 1 is arranged so that its air passage surface extends in the vertical direction and the horizontal direction. Almost all of the air blown from the blower passes through the heat exchanger 1. The amount of air flowing through the heating heat exchanger and the electric heater is set according to the opening degree of the temperature control damper.

The cold air that has passed through the heat exchanger 1 and whose temperature has dropped and the hot air that has passed through the heat exchanger for heating and the electric heater and whose temperature has risen are mixed in the air-conditioning casing to form harmonized air, and this harmonized air is blown out. Depending on the opening of the switching damper, it is distributed to the defroster port, vent port, and heat port and supplied to the passenger compartment. The blowing mode can be a desired mode.

In the description of this embodiment, for convenience of explanation, the left side of the vehicle is simply referred to as "left" and the right side of the vehicle is simply referred to as "right".

The heat exchanger 1 includes a core 4 composed of a plurality of tubes 2 and fins 3, an upper header tank 20, a lower header tank 30, a refrigerant inflow pipe 40, and a refrigerant outflow pipe 50. The tubes 2 and fins 3 of the core 4 are alternately arranged in a direction intersecting the external air flow direction (left-right direction) and integrated by brazing in a laminated state.

Further, the tube 2 extends in the vertical direction. The material of the tube 2 can be, for example, an aluminum alloy. The tube 2 is a flat tube having a flat cross section long in the external air flow direction. The material of the fin 3 can also be, for example, an aluminum alloy. The fin 3 is a corrugated fin formed in a corrugated shape continuous in the vertical direction.

Although not shown, the core 4 may be provided with a cold storage material between the adjacent tubes 2 and 2. The cold storage material can be composed of a member capable of storing cold heat, which has been well known in the past. For example, a cold storage material container for accommodating the cold storage material is provided between the adjacent tubes 2 and 2, and the cold heat of the tube 2 is transferred to the cold storage material by accommodating the cold storage material in the cold storage material container. The cold heat of the material can be transferred to the fins 3 and the like.

As shown in FIG. 3, the tubes 2 are similarly arranged on the upstream side and the downstream side in the external air flow direction of the heat exchanger 1. Fins 3 are also arranged between the tubes 2 and 2 arranged on the downstream side in the external air flow direction in the same manner as on the upstream side. Further, the tube 2 on the upstream side in the external air flow direction and the tube 2 on the downstream side in the external air flow direction can be the same. Further, the tube 2 on the upstream side in the external air flow direction and the tube 2 on the downstream side in the external air flow direction are arranged so as to be aligned on the same straight line in the external air flow direction. Therefore, the external air that has flowed between the tubes 2 and 2 on the upstream side in the external air flow direction will flow as it is between the tubes 2 and 2 on the downstream side in the external air flow direction. The refrigerant flowing through the tube 2 absorbs heat from the outside air by exchanging heat with the outside air.

The upper header tank 20 communicates with the upper end portion of the tube 2 on the upstream side in the external air flow direction and the upper end portion of the tube 2 on the downstream side in the external air flow direction. Further, the lower header tank 30 communicates with the lower end portion of the tube 2 on the upstream side in the external air flow direction and the lower end portion of the tube 2 on the downstream side in the external air flow direction.

That is, as shown in FIG. 1, the upper header tank 20 has a tank body 21 formed in a long cylindrical shape in the left-right direction, a left cap member 22 that closes the left end portion of the tank body 21, and a right end portion of the tank body 21. It is provided with a right side cap member 23 to be closed. The tank body 21, the left side cap member 22, and the right side cap member 23 can be made of, for example, an aluminum alloy. As shown in FIG. 4, a partition wall 24 is provided inside the tank main body 21 for partitioning into a space R1 on the upstream side in the external air flow direction and a space R2 on the downstream side. The partition wall 24 can be made of a plate material that extends in the vertical direction as well as in the horizontal direction, but the partition wall 24 may be integrally molded with the tank body 21. The upper end of the partition wall 24 is joined to the inner surface of the upper wall portion of the tank body 21, and the lower end portion of the partition wall 24 is joined to the inner surface of the lower wall portion of the tank body 21. Further, the left end portion of the partition wall 24 is joined to the inner surface of the left side cap member 22, and the right end portion of the partition wall 24 is joined to the inner surface of the right side cap member 23.

Further, as schematically shown in FIG. 3, a plurality of partition plates 25 to 29 are provided inside the tank main body 21 of the upper header tank 20. The partition plates 25 to 29 extend in the vertical direction and extend in the external air flow direction. The partition plates 25 to 27 are arranged in the space R2 (shown in FIG. 4) on the downstream side in the external air flow direction from the partition wall 24 of the upper header tank 20, and are for partitioning the space R2 into four in the left-right direction. Is. Further, the partition plates 28 and 29 are arranged in the space R1 (shown in FIG. 4) on the upstream side in the external air flow direction from the partition wall 24 of the upper header tank 20, and the space R1 is divided into three in the left-right direction. belongs to.

The lower header tank 30 also includes a tank body 31, a left side cap member 32, and a right side cap member 33. As schematically shown in FIG. 3, a partition wall 34 similar to the upper header tank 20 is provided inside the lower header tank 30, and the partition wall 34 causes the inside of the tank body 31 to be upstream in the external air flow direction. It is divided into a space on the side and a space on the downstream side.

Further, a plurality of partition plates 35 to 38 are provided inside the tank body 31 of the lower header tank 30. The partition plates 35 to 38 extend in the vertical direction and extend in the external air flow direction. The partition plates 35 and 36 are arranged in a space on the downstream side in the external air flow direction from the partition wall 34 of the lower header tank 30, and are for partitioning the space into three in the left-right direction. Further, the partition plates 37 and 38 are arranged in a space on the upstream side in the external air flow direction with respect to the partition wall 34 of the lower header tank 30, and are for partitioning the space into three in the left-right direction.

(Method of forming the path of heat exchanger 1)
Next, a method of forming paths U1 to U3 and D1 to D4 in the heat exchanger 1 will be described. The path is a portion of the heat exchanger 1 in which the refrigerant flows and mainly exchanges heat, and is composed of a plurality of tubes 2, and the direction of the refrigerant flowing through the tubes 2 constituting the same path. Are all the same. As described above, the upper header tank 20 is divided into two in the external air flow direction by the partition wall 24, and the lower header tank 30 is divided into two in the external air flow direction by the partition 34. Since the tube 2 on the upstream side in the direction communicates with the space R1 on the upstream side in the external air flow direction of the upper header tank 20 and the space on the upstream side in the external air flow direction of the lower header tank 30, these tubes 2 wind up. Paths U1 to U3 are formed. Further, since the tube 2 on the downstream side in the external air flow direction communicates with the space R2 on the downstream side in the external air flow direction of the upper header tank 20 and the space on the downstream side in the external air flow direction of the lower header tank 30, these. The leeward paths D1 to D4 are formed by the tube 2.

Further, the partition plates 25 to 29 are arranged in the upper header tank 20, and the partition plates 35 to 38 are arranged in the lower header tank 30. The upper header tank 20 and the lower header tank are arranged by the arrangement of the partition plates 25 to 27 on the downstream side in the external air flow direction of the upper header tank 20 and the partition plates 35 and 36 on the downstream side in the external air flow direction of the lower header tank 30. The space on the downstream side in the external air flow direction of 30 is partitioned in the left-right direction. Four leeward paths D1 to D4 can be formed by setting the arrangement positions of the partition plates 25 to 27 and the partition plates 35 and 36. In this embodiment, the leeward paths D1 to D4 are sequentially referred to as the first to fourth leeward paths, the first leeward path D1 is located on the leftmost side, and the first leeward paths D1 are sequentially on the right side. , The arrangement positions of the partition plates 25 to 27 and the partition plates 35 and 36 are set so that the second to fourth leeward paths D2 to D4 are arranged.

Further, the number of tubes 2 constituting the leeward paths D1 to D4 can be arbitrarily set by setting the arrangement positions of the partition plates 25 to 27 and the partition plates 35 and 36. The number of tubes 2 constituting the first leeward pass D1 and the number of tubes 2 constituting the fourth leeward pass D4 are the same. The number of tubes 2 constituting the second leeward pass D2 and the number of tubes 2 constituting the third leeward pass D3 are the same. The number of tubes 2 may be the same for all of the first to fourth leeward passes D1 to D4. The number of tubes 2 represents the size of the cross-sectional area of the refrigerant flow path in the path.

Further, by arranging the partition plates 28 and 29 on the upstream side in the external air flow direction of the upper header tank 20 and the partition plates 37 and 38 on the upstream side in the external air flow direction of the lower header tank 30, the upper header tank 20 and the lower side are arranged. The space on the upstream side of the header tank 30 in the external air flow direction is partitioned in the left-right direction. By setting the arrangement positions of the partition plates 28, 29 and the partition plates 37, 38, three windward paths U1 to U3 can be formed. In this embodiment, the windward passes U1 to U3 are sequentially referred to as the first to third windward passes, the first windward pass U1 is located on the leftmost side, and the first windward pass U1 is sequentially on the right side. , The arrangement positions of the partition plates 28, 29 and the partition plates 37, 38 are set so that the second and third leeward paths U2 and U3 are arranged.

Further, the number of tubes 2 constituting each windward pass U1 to U3 can be arbitrarily set by setting the arrangement positions of the partition plates 28, 29 and the partition plates 37, 38. The number of tubes 2 constituting the first windward pass U1 and the number of tubes 2 constituting the third windward pass U3 are the same. Further, the number of tubes 2 constituting the second windward pass U2 is larger than the number of tubes 2 constituting the first windward pass U1. The number of tubes 2 may be the same for all of the first to third windward passes U1 to U3. Further, the number of tubes 2 constituting the first windward pass U1 is larger than the number of tubes 2 constituting the first leeward pass D1. The number of tubes 2 constituting the second leeward pass U2 is larger than the number of tubes 2 constituting the second leeward pass D2.

As described above, the paths U1 to U3 and D1 to D4 can be formed in the heat exchanger 1. The number of passes formed in the heat exchanger 1 is not limited to the above number, and for example, the number of windward paths may be two, three or more, and the number of leeward paths may be three or more. It may be three or two, or five or more.

(Path connection structure)
The first to fourth leeward paths D1 to D4 and the first to third windward paths U1 to U3 formed in the heat exchanger 1 are connected so as to form a predetermined refrigerant path. That is, as shown in FIGS. 2 and 3, the downstream side (lower end side) of the first leeward pass D1 in the refrigerant flow direction and the upstream side (lower end side) of the first leeward pass U1 in the refrigerant flow direction are connected. ing. This is done by the first through hole 34a provided in the portion on the left side of the partition plates 35 and 37 of the partition wall 34 provided in the lower header tank 30, and the lower header tank 30 is provided by the first through hole 34a. By communicating the upstream side and the downstream side in the external air flow direction, the downstream side of the first leeward side pass D1 and the upstream side of the first leeward side pass U1 are connected.

Further, the downstream side (upper end side) of the first windward pass U1 in the refrigerant flow direction and the upstream side (upper end side) of the second leeward pass D2 in the refrigerant flow direction are connected. This is done by the first through hole 24a provided between the partition plate 25 and the partition plate 26 of the partition wall 24 provided in the upper header tank 20, and the external air flow of the upper header tank 20 by the first through hole 24a. By communicating the upstream side and the downstream side in the direction, the downstream side of the first windward pass U1 and the upstream side of the second leeward pass D2 are connected.

Further, the downstream side (lower end side) of the second leeward pass D2 in the refrigerant flow direction and the upstream side (lower end side) of the second leeward pass U2 in the refrigerant flow direction are connected. This is done by the second through hole 34b provided between the partition plate 37 of the partition plate 34 provided in the lower header tank 30 and the partition plate 38, and the outside of the lower header tank 30 by the second through hole 34b. By communicating the upstream side and the downstream side in the air flow direction, the downstream side of the second leeward side pass D2 and the upstream side of the second leeward side pass U2 are connected.

Further, the downstream side (lower end side) of the fourth leeward pass D4 in the refrigerant flow direction and the upstream side (lower end side) of the third leeward pass U3 in the refrigerant flow direction are connected. This is done by the third through hole 34c provided in the portion on the right side of the partition plates 36 and 38 of the partition wall 34 provided in the lower header tank 30, and the lower header tank 30 is provided by the third through hole 34c. By communicating the upstream side and the downstream side in the external air flow direction, the downstream side of the fourth leeward pass D4 and the upstream side of the third leeward pass U3 are connected.

Further, the downstream side (upper end side) of the third windward pass U3 in the refrigerant flow direction and the upstream side (upper end side) of the third leeward pass D3 in the refrigerant flow direction are connected. This is done by the second through hole 24b provided between the partition plate 26 and the partition plate 27 of the partition wall 24 provided in the upper header tank 20, and the external air flow of the upper header tank 20 by the second through hole 24b. By communicating the upstream side and the downstream side in the direction, the downstream side of the third windward pass U3 and the upstream side of the third leeward pass D3 are connected.

Further, the downstream side (lower end side) of the third leeward pass D3 in the refrigerant flow direction and the upstream side (lower end side) of the second leeward pass U2 in the refrigerant flow direction are connected. This is done by the second through hole 34b provided between the partition plate 37 of the partition plate 34 provided in the lower header tank 30 and the partition plate 38, and the outside of the lower header tank 30 by the second through hole 34b. By communicating the upstream side and the downstream side in the air flow direction, the downstream side of the third leeward side pass D3 and the upstream side of the second leeward side pass U2 are connected. Since the downstream side of the second leeward pass D2 and the downstream side of the third leeward pass D3 communicate with each other, it can be connected to the second leeward pass U2 by a common second through hole 34b.

For example, the portion where the refrigerant flows into the first leeward pass D1 and the portion where the refrigerant flows out from the first leeward pass D1 are separated in the vertical direction and also in the stacking direction of the tubes 2. That is, as shown in FIG. 3, the portion where the refrigerant flows into the first leeward pass D1 is on the upper end side of the first leeward pass D1 and on the right side of the first leeward pass D1. Is set to. On the other hand, the portion where the refrigerant flows out from the first leeward pass D1 is set to be on the lower end side of the first leeward pass D1 and on the left side of the first leeward pass D1. As a result, the portion where the refrigerant flows into the first leeward pass D1 and the portion where the refrigerant flows out from the first leeward pass D1 are located on the diagonal line of the first leeward pass D1. , The refrigerant distribution of each tube 2 can be made uniform.

As for the second to fourth leeward passes D2 to D4, the portion where the refrigerant flows in and the portion where the refrigerant flows out are located on the diagonal lines of the respective passes D2 to D4. The same applies to the first windward pass U1 and the third windward pass U3.

(Structure of Refrigerant Inflow Pipe 40)
As shown in FIG. 1, the refrigerant inflow pipe 40 can be provided in the upper part of the heat exchanger 1. The refrigerant inflow pipe 40 is composed of a member separate from the upper header tank 20, and is arranged outside the upper header tank 20. As a result, the refrigerant inflow pipe 40 is eliminated inside the heat exchanger 1, so that the internal structure of the upper header tank 20 is simplified. In addition, problems such as refrigerant leakage in the upper header tank 20 can be avoided.

The refrigerant inflow pipe 40 extends in the left-right direction along the upper wall portion of the upper header tank 20, and the left side is the upstream side. A decompressed refrigerant flows into the left side of the refrigerant inflow pipe 40 through a decompression device (not shown). The refrigerant inflow pipe 40 is provided on the first pipe portion 40b connected to the upstream side of the first leeward pass D1 in the refrigerant flow direction and on the downstream side in the refrigerant flow direction from the first pipe portion 40b, and is provided on the fourth leeward side. It has a second pipe portion 40a connected to the path D4. The first pipe portion 40b branches from the middle portion of the refrigerant inflow pipe 40. Of the first to fourth leeward paths D1 to D4 and the first to third leeward paths U1 to U3, the most upstream paths in the refrigerant flow direction are the first leeward path D1 and the fourth leeward path D4.

As in the first modification shown in FIG. 5, the refrigerant inflow pipe 40 may be arranged in the space R2 (inside the header tank) on the downstream side in the external air flow direction from the partition wall 24 of the upper header tank 20. .. Further, as in the second modification shown in FIG. 6, in order to equalize the amount of the refrigerant flowing into the first leeward pass D1 and the amount of the refrigerant flowing into the fourth leeward pass D4 in the refrigerant inflow pipe 40. The refrigerant diversion control structure 41 may be provided. The refrigerant diversion control structure 41 is provided between the first pipe portion 40b and the second pipe portion 40a in the refrigerant inflow pipe 40, and is composed of a throttle portion that narrows the flow path of the refrigerant inflow pipe 40.

Further, as in the modification 3 shown in FIG. 7, the refrigerant diversion control structure may be a guide portion 42 for guiding the refrigerant in the refrigerant inflow pipe 40 to the first pipe portion 40b. The guide portion 42 may be a downwardly inclined portion formed on the peripheral wall portion of the refrigerant inflow pipe 40, or may be an inclined plate or the like provided inside the refrigerant inflow pipe 40.

(Structure of Refrigerant Outflow Pipe 50)
As shown in FIG. 1, the refrigerant outflow pipe 50 can be provided in the upper part of the heat exchanger 1. The refrigerant outflow pipe 50 is composed of a member separate from the upper header tank 20, and is arranged outside the upper header tank 20. As a result, the refrigerant outflow pipe 50 is eliminated inside the heat exchanger 1, so that the internal structure of the upper header tank 20 is simplified. In addition, problems such as refrigerant leakage in the upper header tank 20 can be avoided.

The refrigerant outflow pipe 50 extends in the left-right direction along the upper wall portion of the upper header tank 20, and the left side is the downstream side. Other elements constituting the refrigeration cycle are connected to the left side of the refrigerant outflow pipe 50. The upstream end of the refrigerant outflow pipe 50 is connected to the downstream side of the second windward pass U2 in the refrigerant flow direction. Therefore, the second windward path U2 is the most downstream path in the refrigerant flow direction.

As in the modification shown in FIG. 5, the refrigerant outflow pipe 50 may be arranged in the space R1 (inside the header tank) on the upstream side in the external air flow direction from the partition wall 24 of the upper header tank 20.

(Action and effect of the embodiment)
The refrigerant flowing from the refrigerant inflow pipe 40 flows into the upper end side of the first leeward side pass D1 and the fourth leeward side pass D4, flows to the lower end side, and exchanges heat with the outside air. The refrigerant flowing through the first windward pass D1 flows into the lower end side of the first windward pass U1 and exchanges heat with the outside air while flowing through the first windward pass U1 toward the upper end side. Further, the refrigerant flowing through the fourth leeward pass D4 flows into the lower end side of the third leeward pass U3 and exchanges heat with the outside air while flowing through the third leeward pass U3 toward the upper end side.

The refrigerant flowing through the first leeward pass U1 flows into the upper end side of the second leeward pass D2 and exchanges heat with the outside air while flowing through the second leeward pass D2 toward the lower end side. The refrigerant flowing through the third leeward pass U3 flows into the upper end side of the third leeward pass D3 and exchanges heat with the outside air while flowing through the third leeward pass D3 toward the lower end side.

The refrigerant flowing through the second leeward pass D2 and the third leeward pass D3 collects in the lower header tank 30 and then flows into the lower end side of the second leeward pass U2 to the upper end of the second leeward pass U2. It exchanges heat with the outside air while flowing to the side, and then flows through the refrigerant outflow pipe 50 and flows out to the outside of the heat exchanger 1.

For example, when the compressor is stopped and the flow of the refrigerant in the refrigeration cycle is stopped, the liquid refrigerant remaining in the first leeward pass D1 exchanges heat with the outside air and expands in volume. Due to this volume expansion, the liquid refrigerant in the first windward pass D1 moves to the first windward pass U1. In the first windward pass U1, the outside air before being cooled passes through, so that the outside air and the outside air pass through as compared with the first leeward pass D1 through which the outside air cooled on the windward side passes. The temperature difference with the refrigerant becomes large. As a result, the refrigerant evaporates quickly, and the partial temperature rise delay of the heat exchanger 1 is eliminated. Therefore, the temperature of the blown air can be made uniform, and deformation and breakage due to freezing of the heat exchanger 1 can be suppressed.

Further, since the decompressed refrigerant is allowed to flow into the first leeward pass D1 and the fourth leeward pass D4, the flow of the refrigerant can be made symmetrical with respect to the heat exchanger 1. As a result, the temperature distribution of the heat exchanger 1 becomes symmetrical, and as a result, the temperature difference of the blown air between the left side and the right side of the vehicle can be further reduced, for example, between the driver's seat side and the passenger seat side. It is possible to supply air-conditioned air with a uniform temperature.

Even if there is a difference in the amount of refrigerant between the first leeward pass D1 and the fourth leeward pass D4, the second leeward pass U2 at the most downstream in the refrigerant flow direction is the second leeward pass D2. And since the refrigerant of the third leeward pass D3 merges, the temperature distribution becomes uniform in the second leeward pass U2. In particular, in the path U2 located at the most downstream in the refrigerant flow direction, the proportion of the gas refrigerant is large, and if the flow of the refrigerant is biased, the temperature difference between the parts tends to be large. , The temperature difference between parts can be reduced in the path U2 most downstream in the refrigerant flow direction.

The above embodiments are merely exemplary in all respects and should not be construed in a limited way. Further, all modifications and modifications belonging to the equivalent scope of the claims are within the scope of the present invention.

As described above, the heat exchanger according to the present invention can be used, for example, as a heat exchanger for a vehicle air conditioner mounted on an automobile.

1 Heat exchanger (condenser)
2 Tube 20 Upper header tank 24 Partition 24a Through hole 30 Lower header tank 34 Partition 34a Through hole 40 Refrigerant inflow pipe 40a Second pipe 40b First pipe 41 Squeezing part (refrigerant diversion control structure)
42 Guide unit (refrigerant diversion control structure)
50 Refrigerant outflow pipe D1 1st leeward pass D2 2nd leeward pass D3 3rd leeward pass D4 4th leeward pass U1 1st leeward pass U2 2nd leeward pass U3 3rd leeward pass

Claims (14)

A plurality of tubes extending in the vertical direction arranged on the upstream side and the downstream side in the external air flow direction, respectively, and a header tank communicating with the upper end portion and the lower end portion of the tube are provided, and the refrigerant flowing through the tube and the outside are provided. In a heat exchanger configured to exchange heat with air,
On the upstream side in the external air flow direction in the heat exchanger, a first windward path , a second windward path, and a third windward path composed of the above tubes are formed.
The first windward pass, the second windward pass, and the third windward pass are arranged in order.
A first leeward pass, a second leeward pass , a third leeward pass, and a fourth leeward path composed of the above tubes are formed on the downstream side in the external air flow direction in the heat exchanger.
The first leeward pass, the second leeward pass, the third leeward pass, and the fourth leeward pass are arranged in order.
A refrigerant inflow pipe for flowing a refrigerant into the heat exchanger is connected to the first leeward pass and the fourth leeway pass.
The downstream side of the first leeward path and the upstream side of the first leeward path are connected.
The downstream side of the first windward path and the upstream side of the second leeward path are connected.
A heat exchanger characterized in that the downstream side of the second leeward path, the downstream side of the third leeward path, and the upstream side of the second leeward path are connected. In the heat exchanger according to claim 1,
The refrigerant inflow pipe is a heat exchanger characterized in that it is composed of a member different from the header tank. In the heat exchanger according to claim 1 or 2.
Equipped with a refrigerant outflow pipe that allows the refrigerant to flow out of the heat exchanger.
The refrigerant outflow pipe is a heat exchanger characterized in that it is composed of a member different from the header tank. In the heat exchanger according to claim 2 or 3.
The refrigerant inflow pipe is a heat exchanger characterized in that it is arranged inside the header tank. In the heat exchanger according to claim 3,
The refrigerant outflow pipe is a heat exchanger characterized in that it is arranged inside the header tank. In the heat exchanger according to claim 2 or 3.
The refrigerant inflow pipe is a heat exchanger characterized in that it is arranged outside the header tank. In the heat exchanger according to claim 3,
The refrigerant outflow pipe is a heat exchanger characterized in that it is arranged outside the header tank. In the heat exchanger according to any one of claims 1 to 7.
Inside the header tank, a partition wall is provided to partition the upstream side and the downstream side in the external air flow direction.
The windward side path and the leeward side path are heat exchangers characterized in that they are connected by a through hole provided in a part of the partition wall. In the heat exchanger according to any one of claims 1 to 8.
The tubes that make up each of the above paths are stacked in a direction that intersects the flow direction of external air.
A heat exchanger characterized in that the portion where the refrigerant flows into the path and the portion where the refrigerant flows out from the path are separated in the vertical direction and also in the stacking direction of the tubes. In the heat exchanger according to claim 9,
The most downstream path in the refrigerant flow direction is composed of the above second windward path.
A heat exchanger characterized in that the downstream side of the second leeward path and the third leeward path are connected to the upstream side of the second leeward path. In the heat exchanger according to claim 1, any one of 1 0,
The refrigerant inflow pipe is characterized by being provided with a refrigerant diversion control structure for equalizing the amount of refrigerant flowing into the first leeward path and the amount of refrigerant flowing into the fourth leeward path. Heat exchanger. In the heat exchanger according to claim 1 1,
The refrigerant inflow pipe has a first pipe portion connected to the first leeward path and a second pipe portion connected to the fourth leeward path.
The refrigerant diversion control structure is a heat exchanger characterized by being a throttle portion provided between the first pipe portion and the second pipe portion in the refrigerant inflow pipe. In the heat exchanger according to claim 1 1,
The refrigerant inflow pipe is provided in a first pipe portion connected to the first leeward side path and a second pipe portion downstream of the first pipe portion in the refrigerant flow direction and connected to the fourth leeward side path. Has a pipe and
The refrigerant diversion control structure is a heat exchanger characterized by being a guide portion for guiding the refrigerant in the refrigerant inflow pipe to the first pipe portion. In the heat exchanger according to claim 1, any one of 1 to 3,
A heat exchanger characterized in that a cold storage material is provided between the adjacent tubes.

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