JP4764738B2 - Heat exchanger - Google Patents

Description

The present invention relates to a heat exchanger, and more specifically, for example, a supercritical refrigerant such as CO ₂ (carbon dioxide) is used, and is suitably used for a gas cooler of a supercritical refrigeration cycle mounted on a vehicle as a car air conditioner. It relates to a heat exchanger.

  In this specification and claims, the term “supercritical refrigeration cycle” means a refrigeration cycle in which the refrigerant is in a supercritical state exceeding the critical pressure on the high pressure side, and “supercritical refrigerant” It shall mean a refrigerant used in a supercritical refrigeration cycle.

  For example, as a heat exchanger used in a gas cooler of a supercritical refrigeration cycle applied to a car air conditioner of a vehicle, a pair of header tanks arranged at a distance from each other and a parallel arrangement with a gap between the two header tanks Each header having a flat heat exchange pipe having both ends connected to both header tanks and fins brazed to the heat exchange pipe and disposed in a ventilation gap between adjacent heat exchange pipes. The tank is formed by laminating and brazing an outer plate, an inner plate, and an intermediate plate interposed between the two plates, and opens the outer plate of the first header tank by the intermediate plate. Are formed side by side in the length direction, and an opening is formed in the outer plate of the second header tank by an intermediate plate. One chained outward bulging portion is formed to straddle the two outward bulging portions of the first header tank, and the inside of the outward bulging portion of the outer plates of both header tanks is used as the first refrigerant circulation portion. A plurality of tube insertion holes are formed in the portion corresponding to the outward bulging portion of the inner plate so as to penetrate in the length direction, and both end portions of the heat exchange tubes are disposed on the inner plates of both header tanks. In the intermediate plate, a communication hole is formed in the intermediate plate so as to penetrate each pipe insertion hole of the inner plate to the first refrigerant circulation portion of the outer plate. The communication holes are communicated by communication portions formed between adjacent communication holes in the intermediate plate, and these communication portions and the portions corresponding to the communication portions in the communication holes communicated by the communication portions, The intermediate plate is formed with a second refrigerant circulation portion that communicates with the first refrigerant circulation portion of the outer plate and in which the refrigerant flows in the length direction of the header tank, and outwardly swells in the three plates constituting each header tank A header portion is formed by a portion corresponding to the portion, and an internal refrigerant circulation space of the header portion is formed by the first refrigerant circulation portion of the outer plate and the second refrigerant circulation portion of the intermediate plate, and one of the first header tanks There is known a heat exchanger in which the header portion is an inlet header portion having a refrigerant inlet, and the other header portion is an outlet header portion having a refrigerant outlet (see Patent Document 1).

  In the supercritical refrigeration cycle, the refrigerant compressed by the compressor has a high temperature and a high pressure. Therefore, in the heat exchanger used in the supercritical refrigeration cycle, the pressure resistance of the header tank is required.

Therefore, according to the heat exchanger described in Patent Document 1, in order to improve the pressure resistance of the header tank, the outer plate is formed by pressing a relatively thick aluminum plate. However, in this case, there is a problem that the weight of the heat exchanger increases.
JP-A-2005-300135

  An object of the present invention is to provide a heat exchanger that can solve the above problems and can reduce the weight while ensuring sufficient pressure resistance of the header tank.

  In order to achieve the above object, the present invention comprises the following aspects.

1) A pair of header tanks spaced apart from each other and having at least one header part, and a plurality of heat exchanges arranged in parallel between both header tanks and having both ends connected to both header tanks. Each header tank is configured by laminating and brazing an outer plate, an inner plate, and an intermediate plate interposed between the two plates, At least one outward bulging portion extending in the length direction of the header tank and closed by the intermediate plate is formed, and the inside of the outward bulging portion serves as a first refrigerant circulation portion, and the outer side of the inner plate A plurality of tube insertion holes are formed in the portion corresponding to the bulging portion so as to penetrate in the length direction, and both ends of the heat exchange tubes are connected to the inner plugs of both header tanks. The inner plate is brazed to the inner plate and is inserted into the inner plate, and the intermediate plate is formed with a through hole through which each tube insertion hole of the inner plate communicates with the first coolant circulation portion of the outer plate. The communication hole is communicated by a communication portion formed between adjacent communication holes in the intermediate plate, and the communication portion and a portion corresponding to the communication portion in the communication hole communicated by the communication portion; Thus, a second refrigerant circulation portion is formed in the intermediate plate so as to communicate with the first refrigerant circulation portion of the outer plate and the refrigerant flows in the length direction of the header tank. A header portion is formed by a portion corresponding to the bulging portion, and an internal refrigerant circulation space in the header portion is formed by the first refrigerant circulation portion of the outer plate and the second refrigerant circulation portion of the intermediate plate. A heat exchanger in which a gap is formed,
Heat exchange in which at least a portion of the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is shifted in the ventilation direction so as not to overlap the first refrigerant circulation portion in at least one header portion. vessel.

  2) The above 1) description, wherein in the at least one header portion, the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is displaced in the ventilation direction so as not to overlap with the first refrigerant circulation portion. Heat exchanger.

  3) In at least one header portion, at least a part of the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is shifted upstream in the ventilation direction so as not to overlap with the first refrigerant circulation portion. The heat exchanger according to 1) or 2) above.

  4) The heat exchange according to any one of 1) to 3) above, wherein the cross-sectional area of the second refrigerant circulation portion of the intermediate plate is 2 to 40 times the total passage cross-sectional area in the cross section of each heat exchange pipe. vessel.

  5) The first header tank is provided with a plurality of header portions arranged in the length direction of the header tank, and the header portion at one end of the first header tank is an inlet header portion having a refrigerant inlet, The above-described 1) to 4), wherein the second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate constituting the inlet header portion is shifted to the upstream side in the ventilation direction so as not to overlap with the first refrigerant circulation portion. The heat exchanger in any one of.

  6) The second header tank is provided with a header portion having an inflow portion through which the refrigerant flows from the inlet header portion through the heat exchange pipe, and the first of the outer plates constituting the header portion of the second header tank The heat exchanger according to 5) above, wherein a portion of the second refrigerant circulation portion of the intermediate plate that communicates with the refrigerant circulation portion is located on the upstream side in the ventilation direction so as not to overlap with the first refrigerant circulation portion.

  7) The second header tank is provided with a header portion that is one less than the number of header portions of the first header tank so as to straddle two adjacent header portions of the first header tank. The heat exchanger according to 5) or 6) above, wherein the header portion on the other end side is an outlet header portion having a refrigerant outlet.

  8) The heat exchanger according to 7) above, wherein the number of header portions of the first header tank is 2, and the number of header portions of the second header tank is 1.

  9) The heat exchanger according to 8) above, wherein the outer shape, the communication hole, and the communication portion of the intermediate plate constituting the first header tank are point-symmetric with respect to the center point of the intermediate plate.

  10) The heat exchanger according to 8) or 9) above, wherein the outer shape, the communication hole and the communication portion of the intermediate plate constituting the second header tank are point-symmetric with respect to the center point of the intermediate plate.

  11) A refrigeration cycle comprising a compressor, a gas cooler, an evaporator, a decompressor, and an intermediate heat exchanger for exchanging heat between the refrigerant coming out of the gas cooler and the refrigerant coming out of the evaporator, and using a supercritical refrigerant. A supercritical refrigeration cycle in which the gas cooler includes the heat exchanger according to any one of 1) to 10) above.

  12) The supercritical refrigeration cycle according to claim 11, wherein the supercritical refrigerant comprises carbon dioxide.

  13) A vehicle equipped with the supercritical refrigeration cycle described in 11) or 12) above as a car air conditioner.

  According to the heat exchangers of 1) and 2), at least a part of the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is at least part of the first refrigerant circulation. Since it is displaced in the ventilation direction so as not to overlap with the part, the internal refrigerant circulation space of the header part is divided into two at the part where both refrigerant circulation parts are displaced. Therefore, in a portion where the first refrigerant circulation portion of the outer plate and the second refrigerant circulation portion of the intermediate plate in the header tank are displaced, the stress concentration generated in the outer plate and the intermediate plate is alleviated and the breaking pressure is improved. . As a result, the pressure resistance and fatigue durability of the header tank are improved. Moreover, since the pressure resistance of the header tank is improved, the thickness of the outer plate can be made thinner than that of the heat exchanger described in Patent Document 1, and the weight of the entire heat exchanger can be reduced. .

  In addition, since the total passage cross-sectional area of the internal refrigerant circulation space of the header portion is the same as the case where the first refrigerant circulation portion of the outer plate and the second refrigerant circulation portion of the intermediate plate are not shifted, the pressure when the refrigerant flows An increase in loss can be suppressed.

  According to the heat exchanger of 3), the refrigerant flowing through the portion of the second refrigerant circulation portion of the intermediate plate that is displaced from the first refrigerant circulation portion of the outer plate is exposed to cooler air. , Heat exchange efficiency is improved. Therefore, the heat exchange performance of the entire heat exchanger is excellent.

  According to the heat exchanger of 4), it is possible to suppress an increase in pressure loss and suppress a decrease in performance of the heat exchanger, and it is possible to prevent an increase in weight.

  According to the heat exchangers 5) to 7), the heat exchange performance is remarkably improved. That is, for example, in the case of a gas cooler of a supercritical refrigeration cycle, the temperature of the supercritical refrigerant flowing into the inlet header is considerably high. In this case, as in the heat exchanger of 5) above, the second refrigerant circulation portion of the intermediate plate that communicates with the first refrigerant circulation portion of the outer plate that constitutes the inlet header portion does not overlap with the first refrigerant circulation portion. If it is shifted to the upstream side in the ventilation direction, the high-temperature refrigerant can be cooled by the low-temperature air immediately after flowing into the heat exchange core portion, and the cooling efficiency is improved. Therefore, the heat exchange performance of the heat exchanger is improved.

  According to the heat exchanger of the above 9), when the heat exchanger is manufactured, the intermediate plate constituting the first header tank is arranged in an inverted state rotated 180 degrees around its center point. However, the intermediate plate has the same shape as the original shape. Therefore, it is possible to prevent a decrease in performance of the manufactured heat exchanger.

According to the heat exchanger of the above 10), when the heat exchanger is manufactured, the intermediate plate constituting the second header tank is arranged in an inverted state rotated 180 degrees around its center point. However, the intermediate plate has exactly the same shape as the original shape. Therefore, it is possible to prevent a decrease in performance of the manufactured heat exchanger.

  Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the heat exchanger according to the present invention is applied to a gas cooler of a supercritical refrigeration cycle.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum. Further, in the following description, the downstream side in the ventilation direction (the direction indicated by the arrow X in FIG. 1) is referred to as the front, and the opposite side is referred to as the rear. .

  1 and 2 show the overall configuration of a gas cooler to which a heat exchanger according to the present invention is applied, FIGS. 3 to 8 show the configuration of the main part thereof, and FIG. 9 shows the flow of refrigerant in the gas cooler.

In FIG. 1, a gas cooler (1) of a supercritical refrigeration cycle using a supercritical refrigerant, for example, CO ₂ , has two header tanks (2), (3) that are spaced apart in the left-right direction and extend in the up-down direction. Between the header tanks (2) and (3), a plurality of flat heat exchange pipes (4) arranged in parallel in the vertical direction and between adjacent heat exchange pipes (4) Corrugated fin (5) placed outside the heat exchange pipe (4) at the upper and lower ends and brazed to the heat exchange pipe (4), and outside the corrugated fin (5) at the upper and lower ends, respectively. And an aluminum side plate (6) brazed to the corrugated fin (5). In this embodiment, the right header tank (2) is referred to as a first header tank, and the left header tank (3) is referred to as a second header tank.

  As shown in FIGS. 2 to 5 and 7, the first header tank (2) includes a brazing sheet having a brazing filler metal layer on both sides, here an outer plate (7) formed of an aluminum brazing sheet, and both sides. A brazing sheet having a brazing material layer, here an inner plate (8) formed from an aluminum brazing sheet, and a metal bare material, here an aluminum bear material, between the outer plate (7) and the inner plate (8) The intermediate plate (9) interposed between the two is laminated and brazed to each other, and the inlet header portion (10A) and the outlet header portion (10B) are provided vertically. .

  A plurality of dome-shaped outward bulges (11A) and (11B), which extend in the vertical direction and have the same bulge height, length and width, are spaced apart from each other in the vertical direction on the outer plate (7). Formed. The peripheral edge of the opening facing the left side of each outward bulge portion (11A) (11B) in the outer plate (7) is brazed to the intermediate plate (9), and each outward bulge portion (11A) (11B) The opening facing the left side is closed by an intermediate plate (9). As a result, each of the outwardly bulging portions (11A) and (11B) is closed at both upper and lower ends, and the refrigerant circulation portions (11a) and (11b) (first refrigerant circulation portion of the outer plate) in which the refrigerant flows in the vertical direction, It has become.

  A refrigerant inlet (12) is formed at the upper end of the top part of the upper outer bulge (11A) of the outer plate (7), and communicates with the refrigerant inlet (12) on the outer surface of the outer bulge (11A). An inlet member (13) made of metal having a refrigerant inflow passage (14), here made of aluminum bare material, is brazed using a brazing material on the outer surface of the outer plate (7). In addition, a refrigerant outlet (15) is formed at the lower end of the top of the lower outer bulging portion (11B), and a refrigerant outflow passage leading to the refrigerant outlet (15) is formed on the outer surface of the outer bulging portion (11B). An outlet member (16) made of metal, here an aluminum bear material having (17), is brazed using a brazing material on the outer surface of the outer plate (7). The outer plate (7) is formed by pressing an aluminum brazing sheet having a brazing material layer on both sides.

  A plurality of through-tube insertion holes (18) that are long in the front-rear direction are formed in the inner plate (8) at intervals in the vertical direction. The plurality of tube insertion holes (18) in the upper half are formed in the vertical range of the upper outward bulge portion (11A) of the outer plate (7), and the plurality of tube insertion holes (also in the lower half) ( 18) is formed within the vertical range of the lower outer bulging portion (11B) of the outer plate (7). The length in the front-rear direction of the tube insertion hole (18) is slightly longer than the width in the front-rear direction of each outward bulge (11A) (11B). It protrudes outward from the front and rear side edges of the side bulges (11A) and (11B). In addition, it protrudes to the right and left side edges of the inner plate (8) to the right, the tip reaches the outer surface of the outer plate (7), and the boundary between the outer plate (7) and the intermediate plate (9) A covering wall (19) is formed integrally and is brazed to both the front and rear side surfaces of the outer plate (7) and the intermediate plate (9). A plurality of engaging portions (21) that engage with the outer surface of the outer plate (7) are integrally formed at the protruding end of each covering wall (19) at intervals in the vertical direction, and are formed on the outer plate (7). It is brazed. Note that the engagement portion (21) is not bent before the three plates (7), (8), and (9) are overlapped, as shown by a chain line in FIG. It is straight. The inner plate (8) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

  The intermediate plate (9) has a through-hole communication hole (22) that allows the pipe insertion hole (18) of the inner plate (8) to communicate with the refrigerant circulation part (11a) (11b) of the outer plate (7). The same number as (18) is formed. Each communication hole (22) is formed at a position corresponding to each tube insertion hole (18) of the inner plate (8), and the communication hole (22) is slightly larger than the tube insertion hole (18). Yes. The plurality of tube insertion holes (18) in the upper half of the inner plate (8) are connected to the upper side of the outer plate (7) through the plurality of communication holes (22) in the upper half of the intermediate plate (9). A plurality of pipe insertion holes (18) in the lower half are communicated with the refrigerant circulation part (11a) in the outer bulging part (11A), and a plurality of communication holes in the lower half of the intermediate plate (9) Via (22), it is communicated with the refrigerant circulation part (11b) in the lower outward bulge part (11B) of the outer plate (7). All the communication holes (22) leading to the upper refrigerant circulation part (11a) of the outer plate (7) and all the communication holes (22) communicating to the lower refrigerant circulation part (11b) are respectively in the intermediate plate (9). The communication part (23) formed by cutting off the rear end part of the part between adjacent communication holes (22) is connected. As a result, the communication portion (23) for communicating the communication holes (22) facing the refrigerant circulation portions (11a) (11b) of the outer plate (7), and the rear end portion (communication hole (22 ) In the intermediate plate (9), the refrigerant circulation part (11a) and (11b) of the outer plate (7) through which the refrigerant flows in the vertical direction. 9a) and 9b (second refrigerant circulation part of the intermediate plate) are formed. The refrigerant circulation portions (11a) and (11b) of the outer plate (7) and the refrigerant circulation portions (9a) and (9b) of the intermediate plate (9) are communicated with each other through the communication hole (22). . In the cross section of the first header tank (2), each refrigerant circulation part (9a) (9b) of the intermediate plate (9) overlaps with each refrigerant circulation part (11a) (11b) of the outer plate (7). As a result, the whole is shifted to the upstream side (rear side) in the ventilation direction with respect to the refrigerant circulation portions (11a) and (11b) of the outer plate (7).

  The inlet header portion (10A) and the outer bulge portions (11A) (11B) of the three plates (7) (8) (9) constituting the first header tank (2) An outlet header portion (10B) is formed, and both the refrigerant circulation portions (11a) (11b) of the outer plate (7) and the refrigerant circulation portions (9a) (9b) of the intermediate plate (9) An internal refrigerant circulation space for the header part (10A) and the outlet header part (10B) is formed.

  As shown in FIGS. 2, 6, and 8, the second header tank (3) has substantially the same configuration as the first header tank (2), and the same components and the same parts are denoted by the same reference numerals. Both header tanks (2) and (3) are arranged so that the inner plates (8) face each other.

  The outer plate (7) of the second header tank (3) is one less than the number of outward bulges (11A) (11B) of the first header tank (2), here one dome-shaped outer A side bulging portion (24) is formed from the upper end to the lower end of the outer plate (7) so as to straddle both outer bulging portions (11A) and (11B) of the first header tank (2). The peripheral edge of the opening facing the right side of the outward bulge (24) in the outer plate (7) is brazed to the intermediate plate (9), and the opening facing the right side of the outward bulge (24) is intermediate. It is blocked by a plate (9). As a result, both the upper and lower ends are closed in the outward bulging portion (24), and a refrigerant circulation portion (24a) (first refrigerant circulation portion of the outer plate) through which the refrigerant flows in the vertical direction. A refrigerant inlet and a refrigerant outlet are not formed in the outward bulge portion (24).

  All the tube insertion holes (18) of the inner plate (8) of the second header tank (3) are formed within the vertical range of the outward bulge (24) of the outer plate (7), All the tube insertion holes (18) of the inner plate (8) pass through all the communication holes (22) of the intermediate plate (9), and the refrigerant in the outer bulge (24) of the outer plate (7). It is communicated to the distribution department (24a). All the communication holes (22) of the intermediate plate (9) communicate with each other through the communication part (23) formed by cutting off the rear end portion of the intermediate plate (9) between adjacent communication holes (22). It has been made. As a result, the outer plate (7) is connected to the intermediate plate (9) by the communication portion (23) and the rear end portion of the communication hole (22) (the portion corresponding to the communication portion (23) in the communication hole (22)). A refrigerant circulation part (9c) (second refrigerant circulation part of the intermediate plate) is formed which communicates with the refrigerant circulation part (24a) and flows in the vertical direction. The refrigerant circulation part (24a) of the outer plate (7) and the refrigerant circulation part (9c) of the intermediate plate (9) are communicated with each other through the communication hole (22). In the cross section of the second header tank (3), the refrigerant circulation part (9c) of the intermediate plate (9) is not entirely overlapped with the refrigerant circulation part (24a) of the outer plate (7). It is shifted to the upstream side (rear side) in the ventilation direction with respect to the refrigerant circulation part (24a) of the outer plate (7).

  The two headers of the first header tank (2) are formed by the portions corresponding to the outward bulges (24) in the three plates (7), (8), and (9) that constitute the second header tank (3). One intermediate header section (20), which is one less than the sections (10A) and (10B), is provided so as to straddle both header sections (10A) and (10B) of the first header tank (2). Thus, an internal refrigerant circulation space of the intermediate header portion (20) is formed by the refrigerant circulation portion (24a) of the outer plate (7) and the refrigerant circulation portion (9c) of the intermediate plate (9).

  The heat exchange pipe (4) is made of an extruded shape made of metal, here aluminum, and has a flat shape that is wide in the front-rear direction, and a plurality of refrigerant passages (4a) extending in the length direction are formed in parallel in the inside. ing. Here, the cross-sectional area of the refrigerant circulation portions (9a), (9b), and (9c) of the intermediate plate (9) in both header tanks (2) and (3) is the total passage section in the cross section of each heat exchange pipe (4). It is preferably 2 to 40 times the area. If the cross-sectional area of the refrigerant flow section (9a) (9b) (9c) of the intermediate plate (9) is less than twice the total passage cross-sectional area in the cross section of each heat exchange pipe (4), the pressure loss will increase. The performance of the gas cooler (1) may be reduced, and if it exceeds 40 times, the pressure in the refrigerant circulation part (9a) (9b) (9c) will increase and the thickness of the outer plate (7) will increase. Otherwise, the breaking pressure cannot be improved and the weight may increase.

Both ends of the heat exchange pipe (4) are inserted into the pipe insertion holes (18) of the header tanks (2) and (3), respectively, and the inner plate (8) is used for the inner plate using the brazing material layer. It is brazed to (8). Note that both ends of the heat exchange pipe (4) enter the communication hole (22) up to an intermediate portion in the thickness direction of the intermediate plate (9). All the heat exchange pipes (4) have a right end portion that leads to an internal refrigerant circulation space of the inlet header portion (10A) of the first header tank (2) and a left end portion that is an intermediate header portion of the second header tank (3) ( 20) The internal refrigerant circulation of the heat exchange pipe group consisting of a plurality of heat exchange pipes (4) communicating with the upper half of the internal refrigerant circulation space and the right header at the outlet header part (10B) of the first header tank (2) The left end of the second header tank (3) is divided into a heat exchange pipe group consisting of a plurality of heat exchange pipes (4) that communicate with the space and the lower half of the internal refrigerant circulation space of the second header tank (3). Thus, the first and second paths (P1) (P2) are divided, and the flow direction of the refrigerant in all the heat exchange pipes (4) constituting each path (P1) (P2) is the same. And the flow direction of the refrigerant in the heat exchange pipe (4) of the two paths (P1) and (P2) is different. Therefore, the intermediate header part (20) of the second header tank (3) has an inflow part through which the refrigerant flows from the inlet header part (10A) through the heat exchange pipe (4) of the first path (P1). The portion of the refrigerant circulation portion (9c) of the intermediate plate (9) that communicates with the refrigerant circulation portion (24a) of the outer plate (7) of the second header tank (3) is the outer plate ( The corrugated fin (5), which is displaced upstream in the ventilation direction so as not to overlap with the refrigerant flow part (24a) of 7), is formed in a wavy shape using a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet. It is a thing.

  The gas cooler (1) constitutes a supercritical refrigeration cycle together with an intermediate heat exchanger that exchanges heat between the refrigerant that has come out of the compressor and the evaporator, the decompressor and the gas cooler and the refrigerant that has come out of the evaporator. For example, it is installed in a car.

In the gas cooler (1) described above, as shown in FIG. 9, the CO ₂ that has passed through the compressor passes through the refrigerant inflow passage (14) of the inlet member (13) from the refrigerant inlet (12) to the first header tank ( 2) enters the inlet header (10A) of the outer plate (7), and flows through the refrigerant circulation part (11a) of the outer plate (7) and the refrigerant circulation part (9a) of the intermediate plate (9) while flowing downwardly to the first path ( It flows into the refrigerant passages (4a) of all the heat exchange tubes (4) of P1). The CO ₂ flowing into the refrigerant passage (4a) flows leftward in the refrigerant passage (4a) and flows into the upper half (inflow portion) of the intermediate header portion (20) of the second header tank (3). To do. The CO ₂ flowing into the upper half of the intermediate header part (20) flows downward through the refrigerant circulation part (24a) of the outer plate (7) and the refrigerant circulation part (9c) of the intermediate plate (9). The first header tank is divided and flows into the refrigerant passages (4a) of all the heat exchange pipes (4) of the second path (P2), changes the flow direction and flows rightward in the refrigerant passages (4a). Enter the exit header (10B) of (2). Thereafter, CO ₂ flows downward through the refrigerant circulation part (11b) of the outer plate (7) and the refrigerant circulation part (9b) of the intermediate plate (9), and the refrigerant flows out of the refrigerant outlet (15) and the outlet member (16). It flows out through the road (17). While the CO ₂ flows in the refrigerant passage (4a) of the heat exchange pipe (4), the ventilation gap is heat-exchanged with the air flowing in the direction indicated by the arrow X in FIGS. 1 and 9, and cooled.

  10 and 11 show a second embodiment of the gas cooler to which the heat exchanger of the present invention is applied.

  As shown in FIG. 10, in the first header tank (2), the communication hole (22) in the lower half of the intermediate plate (9) is a portion between adjacent communication holes (22) in the intermediate plate (9). The communication portion (23A) is formed by cutting the central portion in the front-rear direction. As a result, the center plate (9) is connected to the lower outwardly bulging portion of the outer plate (7) by the central portion in the front-rear direction corresponding to the communication portion (23A) in the communication portion (23A) and the communication hole (22). A refrigerant circulation part (9d) is formed which communicates with the refrigerant circulation part (11b) in 11B) and flows in the vertical direction. In this case, in the cross section of the first header tank (2), the refrigerant circulation part (9d) of the intermediate plate (9) overlaps with the refrigerant circulation part (11b) of the outer plate (7). Then, the refrigerant circulation part (11b) in the lower outer bulge part (11B) of the outer plate (7) and the refrigerant circulation part (9d) of the intermediate plate (9), the outlet header part (10B) An internal refrigerant circulation space is formed. Other configurations are the same as those of the first header tank (2) shown in FIG. 5, and the same parts and the same parts are denoted by the same reference numerals.

  As shown in FIG. 11, in the second header tank (3), the communication hole (22) in the upper half of the intermediate plate (9) is a portion between adjacent communication holes (22) in the intermediate plate (9). The communication is made by the communication part (23) formed by cutting the rear end part. In addition, the communication hole (22) in the lower half of the intermediate plate (9) is a communication part formed by cutting the central part in the front-rear direction of the portion between the adjacent communication holes (22) in the intermediate plate (9). (23A). Further, the communication hole (22) at the lower end of the plurality of communication holes (22) in the upper half and the communication hole (22) at the upper end of the plurality of communication holes (22) in the lower half are intermediate. The plate (9) is communicated by a communication portion (23A) formed by cutting out the central portion in the front-rear direction of the portion between both communication holes (22). As a result, the intermediate plate (9) is formed by the rear end portion corresponding to the communication portion (23) in the rear end portion of the upper half and the communication portion (23) in the communication hole (22), and the outer plate ( 7) The refrigerant circulation part (9e) communicating with the upper half of the refrigerant circulation part (24a) in the outward bulging part (24) and the refrigerant flowing vertically, and the communication between the center part in the front-rear direction of the lower half Formed in the front-rear direction center portion corresponding to the communication portion (23A) in the communication portion (23A) and the communication hole (22) and communicates with the lower half portion of the refrigerant circulation portion (24a) in the outward bulge portion (24) At the same time, a refrigerant circulation part (9f) in which the refrigerant flows in the vertical direction is formed. Both refrigerant circulation portions (9e) and (9f) are communicated with each other through a communication hole (22) at the lower end of the plurality of communication holes (22) in the upper half. In the cross section of the second header tank (3), the refrigerant circulation part (9e) on the upper side of the intermediate plate (9) is shifted backward so as not to overlap with the refrigerant circulation part (24a) of the outer plate (7). The lower refrigerant circulation part (9f) overlaps with the refrigerant circulation part (24a) in the outer bulging part (24) of the outer plate (7). Then, the refrigerant distribution portion (24a) in the outward bulge portion (24) and the refrigerant distribution portions (9e) (9f) of the intermediate plate (9) are used to connect the internal refrigerant distribution space of the intermediate header portion (20). Is formed. Other configurations are the same as those of the second header tank (3) shown in FIG. 6, and the same parts and the same parts are denoted by the same reference numerals.

  12 and 13 show a third embodiment of the gas cooler to which the heat exchanger of the present invention is applied.

  As shown in FIG. 12, in the first header tank (2), the plurality of communication holes (22) in the lower half of the intermediate plate (9) are located between adjacent communication holes (22) in the intermediate plate (9). It is connected by the communication part (23B) formed by excising the front-end part of a part. As a result, the refrigerant circulation part (11B) in the lower outer bulge part (11B) is connected to the intermediate plate (9) by the front end part corresponding to the communication part (23B) in the communication part (23B) and the communication hole (22). A refrigerant circulation part (9g) that leads to 11b) and flows in the vertical direction is formed. In the cross section of the first header tank (2), the lower refrigerant circulation portion (9g) of the intermediate plate (9) does not overlap with the lower refrigerant circulation portion (11b) of the outer plate (7). Thus, it has shifted | deviated to the ventilation direction downstream (front side) with respect to the refrigerant | coolant distribution part (11b). Then, an internal refrigerant circulation space of the outlet header portion (10B) is formed by the refrigerant circulation portion (11b) below the outer plate (7) and the refrigerant circulation portion (9g) of the intermediate plate (9). . Therefore, the outer shape of the intermediate plate (9), the communication hole (22), and the communication portion (23) (23B) are point-symmetric with respect to the center point (O) when viewed from the left or right direction outward or inward. When rotated 180 degrees around the point (O) and turned upside down, it overlaps the original shape. Other configurations are the same as those of the first header tank (2) shown in FIG. 5 (a), and the same portions and the same portions are denoted by the same reference numerals.

  As shown in FIG. 13, in the second header tank (3), the communication hole (22) in the upper half of the intermediate plate (9) is a portion between adjacent communication holes (22) in the intermediate plate (9). The communication is made by the communication part (23) formed by cutting the rear end part. In addition, the communication hole (22) in the lower half of the intermediate plate (9) is a communication part (23B formed by cutting away the front end of the portion between adjacent communication holes (22) in the intermediate plate (9). ). The lower end communication hole (22) of the upper half communication holes (22) and the upper communication hole (22) of the lower half communication holes (22) are intermediate. The plate (9) is communicated by a communicating portion (23C) formed by cutting out the central portion in the front-rear direction of the portion between both communicating holes (22). As a result, the intermediate plate (9) is formed by the rear end portion corresponding to the communication portion (23) in the rear end portion of the upper half and the communication portion (23) in the communication hole (22), and the outer plate ( The refrigerant circulation part (9a) that communicates with the upper half of the refrigerant circulation part (24a) of 7) and in which the refrigerant flows in the vertical direction, and the communication at the communication part (23B) and the communication hole (22) at the front end of the lower half part And a refrigerant circulation part (9i) that is formed by a rear end corresponding to the part (23B) and communicates with the lower half of the refrigerant circulation part (24a) of the outer plate (7) and in which the refrigerant flows in the vertical direction. ing. Both refrigerant flow sections (9h) and (9i) are arranged at the lower end of the plurality of communication holes (22) in the upper half and the upper end of the plurality of communication holes (22) in the lower half. It communicates with the communication hole (22) and the communication part (23C) at the center in the front-rear direction. In the cross section of the second header tank (3), the refrigerant circulation part (9h) on the upper side of the intermediate plate (9) is shifted backward so as not to overlap with the refrigerant circulation part (24a) of the outer plate (7). The lower refrigerant circulation portion (9i) is shifted forward so as not to overlap with the refrigerant circulation portion (24a) in the outer bulging portion (24) of the outer plate (7). Then, the intermediate header portion is formed by the refrigerant circulation portion (24a) of the outer plate (7), both refrigerant circulation portions (9h) and (9i) of the intermediate plate (9), and the communication portion (23C) at the central portion in the front-rear direction. The internal refrigerant circulation space of (20) is formed. Therefore, the outer shape of the intermediate plate (9), the communication holes (22), and the communication portions (23) (23B) (23C) are point-symmetric with respect to the center point (O) when viewed from the outside in the left-right direction or from the inside. Thus, when it is rotated 180 degrees around the center point (O) and turned upside down, it overlaps the original shape. Other configurations are the same as those of the second header tank shown in FIG. 6, and the same parts and the same parts are denoted by the same reference numerals.

  In the above embodiment, the number of header portions (10A) (10B) of the first header tank (2) in the gas cooler (1) to which the heat exchanger according to the present invention is applied is 2, and the second header tank (3 The number of header sections (20) of 1) is 1 and the number of paths (P1) (P2) is 2, but the number of header sections of the first header tank (2) is not limited to this. Is 3 or more, the number of header sections of the second header tank (3) is one less than the number of header sections of the first header tank (2), and the number of passes is the header of the first header tank (2). It may be the same as the number of parts. In the heat exchanger according to the present invention, the first header tank is provided with a plurality of header portions arranged in the length direction, and the second header tank has the same number of header portions as the header portions of the first header tank. Provided side by side in the length direction, a refrigerant inlet is provided at a header portion at one end in the length direction of the first header tank, and at a header portion at the end opposite to the refrigerant inlet in the second header tank. A refrigerant outlet is provided, and all heat exchange tubes are composed of a plurality of heat exchange tubes arranged continuously in the length direction of the header tanks, and are divided into a number of paths one more than the number of headers of both header tanks. It may be applied to the existing gas cooler.

In the above embodiment, CO ₂ is used as the supercritical refrigerant in the supercritical refrigeration cycle. However, the present invention is not limited to this, and ethylene, ethane, nitric oxide, and the like can be used.

  Further, in the above embodiment, the heat exchange pipe (4) is made of an extruded aluminum material, but from a bent body obtained by bending a metal plate for pipe production made of an aluminum brazing sheet having a brazing filler metal layer on both sides thereof. It may be.

It is a perspective view which shows the whole structure of the gas cooler to which the heat exchanger by this invention is applied. FIG. 2 is a partially omitted vertical sectional view of the gas cooler of FIG. It is an AA line expanded sectional view of FIG. FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. FIG. 3 is an enlarged sectional view taken along the line CC in FIG. 2. FIG. 3 is an enlarged sectional view taken along line DD in FIG. 2. It is a disassembled perspective view which shows the 1st header tank of the gas cooler of FIG. It is a disassembled perspective view which shows the 2nd header tank of the gas cooler of FIG. It is a figure which shows the flow of the refrigerant | coolant in the gas cooler of FIG. It is sectional drawing equivalent to FIG. 5 which shows 2nd Embodiment of the gas cooler to which the heat exchanger by this invention is applied. It is sectional drawing equivalent to FIG. 6 which shows 2nd Embodiment of the gas cooler to which the heat exchanger by this invention is applied. It is sectional drawing equivalent to FIG. 5 which shows 3rd Embodiment of the gas cooler to which the heat exchanger by this invention is applied. It is sectional drawing equivalent to FIG. 6 which shows 3rd Embodiment of the gas cooler to which the heat exchanger by this invention is applied.

Explanation of symbols

(1): Gas cooler (heat exchanger)
(2): First header tank
(3): Second header tank
(4): Heat exchange pipe
(7): Outer plate
(8): Inside plate
(9): Intermediate plate
(9a) to (9i): Refrigerant circulation part (second refrigerant circulation part of the intermediate plate)
(10A): Entrance header
(10B): Exit header
(11A) (11B): outward bulge
(11a) (11b): Refrigerant circulation part (first refrigerant circulation part of the outer plate)
(12): Refrigerant inlet
(18): Tube insertion hole
(20): Intermediate header
(22): Communication hole
(23) (23A) (23B): Communication part
(24): Outward bulge
(24a): Refrigerant circulation part (first refrigerant circulation part of the outer plate)

Claims (13)

A pair of header tanks spaced from each other and having at least one header portion; and a plurality of heat exchange tubes disposed in parallel between the header tanks and having both end portions respectively connected to the header tanks Each header tank is formed by stacking and brazing an outer plate, an inner plate, and an intermediate plate interposed between the two plates. And at least one outward bulging portion whose opening is closed by the intermediate plate is formed, and the inside of the outward bulging portion serves as the first refrigerant circulation portion, and the outward bulging in the inner plate A plurality of tube insertion holes are formed in the portion corresponding to the portion in a penetrating manner at intervals in the length direction, and both end portions of the heat exchange tubes are connected to the inner plates of both header tanks. The inner plate is brazed to the inner plate and brazed to the inner plate, and the intermediate plate is formed with a through hole through which each tube insertion hole of the inner plate communicates with the first coolant circulation portion of the outer plate, The communication hole is communicated by a communication portion formed between adjacent communication holes in the intermediate plate, and these communication portions and a portion corresponding to the communication portion in the communication hole communicated by the communication portion. The intermediate plate is formed with a second refrigerant circulation portion that communicates with the first refrigerant circulation portion of the outer plate and in which the refrigerant flows in the length direction of the header tank, and the outward expansion of the three plates constituting each header tank A header portion is formed by a portion corresponding to the outlet portion, and an internal refrigerant circulation space in the header portion is formed by the first refrigerant circulation portion of the outer plate and the second refrigerant circulation portion of the intermediate plate. A heat exchanger are formed over a substrate
Heat exchange in which at least a portion of the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is shifted in the ventilation direction so as not to overlap the first refrigerant circulation portion in at least one header portion. vessel. 2. The heat according to claim 1, wherein in the at least one header portion, the entire second refrigerant circulation portion of the intermediate plate communicating with the first refrigerant circulation portion of the outer plate is displaced in the ventilation direction so as not to overlap the first refrigerant circulation portion. Exchanger. In at least one header portion, at least a part of the entire second refrigerant circulation portion of the intermediate plate that communicates with the first refrigerant circulation portion of the outer plate is shifted upstream in the ventilation direction so as not to overlap with the first refrigerant circulation portion. The heat exchanger according to claim 1 or 2. The heat exchanger according to any one of claims 1 to 3, wherein a cross-sectional area of the second refrigerant circulation portion of the intermediate plate is 2 to 40 times the total passage cross-sectional area in the cross section of each heat exchange pipe. The first header tank is provided with a plurality of header portions arranged in the length direction of the header tank, and the header portion at one end of the first header tank is an inlet header portion having a refrigerant inlet, and the inlet header The second refrigerant circulation portion of the intermediate plate that communicates with the first refrigerant circulation portion of the outer plate constituting the portion is shifted to the upstream side in the ventilation direction so as not to overlap with the first refrigerant circulation portion. The heat exchanger in any one. The second header tank is provided with a header portion having an inflow portion through which the refrigerant flows from the inlet header portion through the heat exchange pipe, and the first refrigerant circulation of the outer plate constituting the header portion of the second header tank 6. The heat exchanger according to claim 5, wherein a portion of the second refrigerant circulation portion of the intermediate plate that communicates with the portion is located on the inflow portion so as not to overlap with the first refrigerant circulation portion. The second header tank is provided with a header portion that is one less than the number of header portions of the first header tank so as to straddle two adjacent header portions of the first header tank, and the inlet header portion in the first header tank The heat exchanger according to claim 5 or 6, wherein the header portion on the other end side is an outlet header portion having a refrigerant outlet. The heat exchanger according to claim 7, wherein the number of header parts of the first header tank is two, and the number of header parts of the second header tank is one. The heat exchanger according to claim 8, wherein the outer shape, the communication hole, and the communication portion of the intermediate plate constituting the first header tank are point-symmetric with respect to the center point of the intermediate plate. The heat exchanger according to claim 8 or 9, wherein the outer shape, the communication hole, and the communication portion of the intermediate plate constituting the second header tank are point-symmetric with respect to the center point of the intermediate plate. A compressor, a gas cooler, an evaporator, a decompressor, and a refrigeration cycle that includes an intermediate heat exchanger that exchanges heat between the refrigerant that has come out of the gas cooler and the refrigerant that has come out of the evaporator, and uses a supercritical refrigerant, A supercritical refrigeration cycle, wherein the gas cooler comprises the heat exchanger according to any one of claims 1 to 10. The supercritical refrigeration cycle according to claim 11, wherein the supercritical refrigerant comprises carbon dioxide. A vehicle equipped with the supercritical refrigeration cycle according to claim 11 or 12 as a car air conditioner.

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