JP2006207995A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger having an enhanced gas-liquid separation effect in a gas-liquid separation part. <P>SOLUTION: A heat exchanger 1 is provided with a condenser part 2, a subcooling zone 3, and a gas-liquid separation part 4 arranged between the condenser part 2 and the subcooling zone 3, and is constituted to make a refrigerant flowing out of the condenser part 2 flow into the subcooling zone 3 through the gas-liquid separation part 4. The gas-liquid separation part 4 comprises a pair of headers 21, 22 and a liquid receiving tube 23 arranged between the both headers 21, 22. A refrigerant inflow port 32 is formed in an upper wall 21a of the one header 21 of the gas-liquid separation part 4 and a refrigerant flow-out port 33 is provided in a lower wall 22b of the other header 22 of the gas-liquid separation part 4. The gas-liquid separation part is provided with a flow velocity lowering means comprising a mesh 34 provided in the refrigerant inflow port 32, and comprising a flow passage length extending member 35 provided in the other header 22 to surround the refrigerant outflow port 33 and to extend a length of the flow passage for the refrigerant flowing in from the refrigerant flow-in port 32 up to the refrigerant outflow port 33. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat exchanger used in, for example, a refrigeration cycle constituting a car air conditioner.

  In this specification and claims, the top and bottom of FIGS. 1 and 8 are the top and bottom.

  2. Description of the Related Art Recently, a heat exchanger for a refrigeration cycle constituting a car air conditioner is intended to improve the ease of assembling to a vehicle body. A pair of headers arranged at intervals from each other, both ends arranged between both headers. A plurality of heat exchange pipes connected to both headers, and a condensing part composed of corrugated fins arranged between adjacent heat exchange pipes and joined to the heat exchange pipes, spaced apart from each other From a pair of headers, a plurality of heat exchange tubes arranged between both headers and having both ends connected to both headers, and corrugated fins arranged between adjacent heat exchange tubes and joined to the heat exchange tubes And a pair of tanks arranged at a distance from each other, and a vertical liquid receiver fixed across one header of the condensing unit and one header of the subcooling unit The inside By being partitioned by the members, both headers of the condensing unit and the supercooling unit are formed, and the liquid receiver has a refrigerant inflow passage leading to one header of the condensing unit and a refrigerant outflow passage leading to one header of the supercooling unit. It has a block that is fixed to one tank across both headers, and a vertical cylindrical liquid receiver body whose lower end is detachably fixed to the block. In this heat exchanger, in order to improve the refrigeration capacity of the refrigeration cycle, the liquid refrigerant condensed in the condensing unit is further cooled in the subcooling unit to a temperature lower by about 5 to 15 ° C. than the condensation temperature. It has become.

  However, in the heat exchanger described above, the diameter of the liquid receiver body is larger than the width in the ventilation direction of the condensing unit and the supercooling unit. Therefore, when this heat exchanger is arranged in the engine room, useless space is required. There is a problem that occurs. Further, a seal member between the liquid receiver main body and the block, a fixing member for fixing the heat receiver main body to the block, and the like are required, and there is a problem that the number of parts increases.

  Therefore, as a heat exchanger that solves such a problem, a pair of headers arranged at a distance from each other, a plurality of heat exchange tubes that are arranged between both headers and both end portions are connected to both headers, and A condensing unit composed of corrugated fins arranged between adjacent heat exchanging pipes and joined to the heat exchanging pipes, and a pair of headers arranged above the condensing part and spaced apart from each other, A plurality of heat exchange pipes arranged between the headers and having both end portions connected to both headers, and a supercooling part composed of corrugated fins arranged between adjacent heat exchange pipes and joined to the heat exchange pipes; A gas-liquid separation unit disposed between the condensing unit and the supercooling unit, wherein the gas-liquid separation unit is disposed between a pair of headers spaced apart from each other and the headers. Both ends are connected to both headers and The condensing unit is formed by a pair of tanks each having a passage cross-sectional area larger than that of the heat exchange pipes of the cooling section and the supercooling section and partitioned by a partition member. There is known a heat exchanger in which both headers of a supercooling part and a gas-liquid separation part are formed, and the refrigerant flowing out from the condensation part passes through the gas-liquid separation part and flows into the supercooling part (See Patent Document 1).

However, in the heat exchanger described in Patent Document 1, the gas-liquid separation unit includes a pair of headers and a single straight pipe having a larger passage cross-sectional area than the heat exchange pipes of the condensing unit and the supercooling unit. Therefore, the refrigerant flows from the condensing part into the straight pipe of the gas-liquid separation part at a relatively high speed, passes through the straight pipe in a short time, and flows into the supercooling part. Therefore, the gas-liquid separation effect in the gas-liquid separation part is not sufficient, and as a result, a large amount of gas-phase refrigerant flows into the supercooling part, resulting in insufficient supercooling effect in the supercooling part. The cooling effect of the entire refrigeration cycle is reduced.
Japanese Patent No. 3158509

  An object of the present invention is to provide a heat exchanger that solves the above problems and has an improved gas-liquid separation effect in the gas-liquid separation unit.

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

1) A pair of headers arranged at a distance from each other, and a condensing part composed of a plurality of heat exchange tubes arranged between both headers and connected at both ends to both headers, and arranged at a distance from each other A pair of headers, and a supercooling part that is arranged between the headers and has a plurality of heat exchange pipes having both ends connected to both headers, and a gas-liquid arranged between the condensing part and the supercooling part A heat exchanger in which the refrigerant flowing out from the condensing unit passes through the gas-liquid separating unit and flows into the supercooling unit,
The gas-liquid separator is composed of a pair of headers arranged at intervals from each other, and a liquid receiving pipe arranged between both headers and having both ends connected to both headers. A heat exchanger provided with a flow rate reduction means for reducing the flow rate of the refrigerant flowing into the separation unit.

  2) The heat exchanger according to 1) above, wherein the gas-liquid separation unit includes a plurality of liquid receiving pipes arranged at intervals.

  3) The heat exchanger according to 1) or 2) above, wherein a desiccant is disposed in the liquid receiving pipe.

  4) The flow rate lowering means is provided with a porous member provided at a refrigerant inlet formed in one of the headers of the gas-liquid separation unit. Heat exchanger.

  5) The heat exchanger according to 4) above, wherein the porous member is a mesh.

  6) The heat exchanger according to any one of 1) to 5) above, wherein the flow velocity lowering means includes a throttle hole-shaped refrigerant outlet formed in one of the headers of the gas-liquid separator.

  7) The above-mentioned 1) to 6) in which a pair of tanks arranged at a distance from each other are partitioned by partition members to form both headers of a condensing unit, a supercooling unit, and a gas-liquid separating unit. ).

  8) The heat exchanger as described in 7) above, wherein the width of the gas-liquid separation part in the air receiving tube is equal to or smaller than the width of the tank in the air flowing direction.

  9) The heat exchanger according to any one of 1) to 3) above, wherein a condensing unit is disposed on the upper side of the gas-liquid separation unit and a supercooling unit is disposed on the lower side.

  10) The heat exchanger according to 9) above, wherein the flow velocity lowering means includes a porous member provided at a refrigerant inlet formed on the upper wall of one of the headers of the gas-liquid separator.

  11) The heat exchanger according to 10) above, wherein the porous member is a mesh.

  12) The heat exchange according to any one of the above 9) to 11), wherein the flow velocity reduction means includes a throttle hole-like refrigerant outlet formed in the lower wall of one of the headers of the gas-liquid separator. vessel.

  13) A refrigerant inlet is formed on the upper wall of one of the gas-liquid separators, and a refrigerant outlet is also formed on the lower wall of one of the headers. A porous member provided at the inlet, and a channel length extending member that is provided so as to surround the refrigerant outlet and extends the channel length from the refrigerant inlet to the refrigerant outlet. The heat exchanger as described in 9) above.

  14) The heat exchanger according to 13) above, wherein the refrigerant inlet is formed over the entire upper wall of the header.

  15) The heat exchanger according to 13) above, wherein the refrigerant inlet is formed in a part of the upper wall of the header.

  16) The heat exchanger according to any one of 13) to 15) above, wherein the porous member is made of a mesh.

  17) The flow path length extending member protrudes upward so as to surround the inner member on the tubular inner member provided so as to protrude upward around the refrigerant outlet and the lower wall of the header on which the refrigerant outlet is formed. The heat exchanger according to any one of the above 13) to 16), comprising a hollow outer member that is provided and has an upper end closed and a through hole formed in the lower end of the peripheral wall.

  18) The heat exchanger according to 17) above, wherein the upper end of the outer member is at a lower position than the upper wall of the header on which the refrigerant outlet is formed.

  19) The heat exchanger according to 17) above, wherein the upper end of the outer member is at the same height as the upper wall of the header on which the refrigerant outlet is formed.

  20) Any one of the above 13) to 19) in which a refrigerant inflow port is formed in the upper wall of one of the gas-liquid separators and a refrigerant outflow port is formed in the lower wall of the other header The heat exchanger according to crab.

  21) Among the above 13) to 19), a refrigerant inlet is formed on the upper wall of one of the headers of the gas-liquid separator, and a refrigerant outlet is formed on the lower wall of the same header. The heat exchanger in any one.

  22) The heat exchanger according to 21) above, wherein resistance imparting means is provided in the liquid receiving pipe of the gas-liquid separation unit.

  23) The heat exchanger according to 22) above, wherein the resistance applying means comprises a mesh and / or a filter.

  24) The heat exchange according to any one of 21) to 23) above, wherein a pressure reducing hole is formed in the lower wall of the other header of the gas-liquid separation unit and communicates with the one header of the supercooling unit. vessel.

  25) A pair of tanks arranged at a distance from each other are partitioned by partition members to form both headers of a condensing unit, a supercooling unit, and a gas-liquid separating unit. The partition member between the gas-liquid separator and the condenser is the upper wall of the gas-liquid separator, and the partition member between the gas-liquid separator and the supercooler is the lower wall of the gas-liquid separator. The heat exchanger according to any one of 9) to 24).

  26) The heat exchanger according to 25) above, wherein the width of the gas-liquid separation part in the air receiving tube is equal to or smaller than the width of the tank in the air flowing direction.

  27) A refrigeration cycle comprising a compressor, the heat exchanger according to any one of 1) to 26), a decompressor, and an evaporator.

  28) A vehicle equipped with the refrigeration cycle described in 27) above.

  According to the heat exchangers of 1) and 2) above, the gas-liquid separator is disposed between the pair of headers spaced apart from each other and between the headers, and both ends are connected to the headers. Since the gas-liquid separation unit is provided with a flow rate reduction means for reducing the flow rate of the refrigerant flowing into the gas-liquid separation unit, the flow rate of the refrigerant flowing from the condensation unit into the gas-liquid separation unit is reduced. Thus, the time for passing through the gas-liquid separation unit becomes relatively long, and the gas-liquid separation effect in the gas-liquid separation unit is improved. Therefore, the amount of the gas-phase refrigerant flowing into the supercooling portion is reduced, and as a result, the supercooling effect in the supercooling portion is sufficient and the cooling effect of the entire refrigeration cycle is improved.

  According to the heat exchanger of 3) above, moisture in the refrigerant can be removed.

  According to the heat exchangers of the above 4) to 6), the configuration of the flow velocity lowering means becomes relatively simple.

  According to the heat exchanger of the above 7), the total number of parts can be reduced.

  According to the heat exchanger of 8) above, since the liquid receiving pipe does not protrude in the ventilation direction from the tank, when this heat exchanger is arranged in the engine room, it is possible to prevent a useless space from being generated. become.

According to the heat exchanger of 9) above, the gas-liquid separator is a pair of headers spaced apart from each other, and a liquid receiving pipe in which both end portions are connected to both headers. The gas-liquid separation unit is provided with a flow rate reduction means for reducing the flow rate of the refrigerant flowing into the gas-liquid separation unit, so that the flow rate of the refrigerant flowing into the gas-liquid separation unit from the condensation unit is reduced, The time for passing through the gas-liquid separation unit becomes relatively long, and the gas-liquid separation effect in the gas-liquid separation unit is improved. Accordingly, the amount of gas-phase refrigerant flowing into the supercooling section is reduced, and as a result, the supercooling effect in the supercooling section is sufficient and the cooling effect of the entire refrigeration cycle is improved. According to the vessel, the configuration of the flow velocity lowering means becomes relatively simple.

  According to the heat exchangers of the above 13) to 15), the gas-liquid separation effect in the gas-liquid separation part is further improved.

  According to the heat exchanger of 16) above, the cost of the porous member is reduced.

  According to the heat exchangers of the above 17) to 19), the configuration of the flow path length extending member becomes relatively simple.

  According to the heat exchanger of 22) above, the amount of refrigerant enclosed in the refrigeration cycle provided with this heat exchanger can be relatively reduced.

  That is, as in 21) above, the heat exchange in which the refrigerant inlet is formed in the upper wall of one of the headers of the gas-liquid separator and the refrigerant outlet is formed in the lower wall of the same header In the case of a container, if no resistance imparting means is provided in the liquid receiving pipe of the gas-liquid separation part, the refrigerant flows into the liquid receiving pipe immediately after flowing into the one header through the refrigerant inlet, Since it flows to the other header side, it is difficult to flow into the supercooling section through the refrigerant outlet unless the refrigerant amount in the liquid receiving pipe and the other header is increased. Therefore, it is necessary to increase the amount of refrigerant enclosed in the refrigeration cycle until the steady state where the degree of supercooling is constant. On the other hand, when the resistance applying means is provided in the liquid receiving pipe of the gas-liquid separator, the refrigerant immediately after flowing into the one header through the refrigerant inlet is received by the action of the resistance applying means. Since it becomes difficult to flow into the liquid pipe and through the liquid receiving pipe into the other header, the refrigerant immediately after flowing into the one header through the refrigerant inlet passes through the refrigerant outlet. It becomes easy to flow into the supercooling part. Therefore, the amount of refrigerant enclosed in the refrigeration cycle until the steady state where the degree of supercooling is constant becomes relatively small.

  According to the heat exchanger of 23) above, the cost of the resistance applying means is reduced.

  According to the heat exchanger of the above 24), the pressure in the other header where the refrigerant inlet and the refrigerant outlet are not formed is reduced by the action of the pressure reducing hole, so that the liquid-phase refrigerant in the liquid receiving pipe The gas-liquid separation effect at the gas-liquid separation part is excellent.

  According to the heat exchanger of 25) above, the total number of parts can be reduced.

  According to the heat exchanger of the above 26), since the liquid receiving pipe does not protrude in the ventilation direction from the tank, when this heat exchanger is arranged in the engine room, it is possible to prevent generation of useless space. become.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol is attached | subjected to the same part and the same thing through all drawings, and the overlapping description is abbreviate | omitted.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum. In the following description, the left and right sides in FIGS. 1 and 8 are referred to as the left and right sides, the back side (downstream side in the ventilation direction) in FIGS. 1 and 8 is the front side, and the opposite side is the back side.

Embodiment 1
This embodiment is shown in FIGS.

  FIG. 1 shows the overall configuration of this embodiment, and FIGS. 2 and 3 show the configuration of the main part thereof.

  1 and 2, the heat exchanger (1) has a condensing part (2) and a supercooling part (3) spaced vertically in the same vertical plane so that the former is located above. The gas-liquid separation unit (4) is provided between the condensation unit (2) and the supercooling unit (3), and the refrigerant flowing out of the condensation unit (2) is removed from the gas-liquid separation unit (4 ), Passes through the gas-liquid separation part (4), and flows into the supercooling part (3).

  The condensing part (2) is arranged between the first and second aluminum headers (5) (6), which are arranged in parallel in the left-right direction and extend in the vertical direction, and between the headers (5) (6). In addition, a plurality of aluminum flat heat exchange tubes (7) with the width direction directed in the front-rear direction and spaced apart in the vertical direction and both ends connected to the headers (5) (6), respectively. And an aluminum corrugated fin (8) disposed between adjacent heat exchange tubes (7) and brazed to the heat exchange tubes (7). An aluminum side plate (9) is disposed above the heat exchange pipe (7) at the upper end with a space from the heat exchange pipe (7), and is located between the side plate (9) and the heat exchange pipe (7). Further, an aluminum corrugated fin (8) is disposed and brazed to the side plate (9) and the heat exchange pipe (7).

  The first header (5) is divided into an upper header portion (5a) and a lower header portion (5b) by a plate-like partition member (11) provided at a height slightly below the middle in the vertical direction. A refrigerant inlet (12) is provided at the upper end of the upper header (5a). The condensing unit (2) includes a plurality of heat exchange tubes (7) arranged continuously in the vertical direction in a portion above the partition member (11) and a portion below the partition member (11). A passage group (13) (14) is provided. The number of heat exchange tubes (7) constituting the upper passage group (13) is larger than the number of heat exchange tubes (7) constituting the lower passage group (14). In addition, the flow direction of the refrigerant in all the heat exchange tubes (7) constituting each passage group (13) (14) is the same, and the flow direction of the refrigerant in both passage groups (13) (14) Is different.

  The supercooling section (3) is disposed between the first and second aluminum headers (15) (16) and the headers (15) (16), which are spaced apart from each other in the left-right direction and extend vertically. Adjacent to a plurality of flat aluminum heat exchange tubes (17) made of aluminum, with the width direction facing in the front-rear direction and spaced apart in the vertical direction, and both ends connected to both headers (15) and (16), respectively And an aluminum corrugated fin (18) disposed between the heat exchange tubes (17) and brazed to the heat exchange tubes (17). A refrigerant outlet (20) is provided in the first header (15). The heat exchange pipe (17) is the same as the heat exchange pipe (7) of the condensing part (2), and below the heat exchange pipe (17) at the lower end is spaced from the heat exchange pipe (17). An aluminum side plate (19) is arranged, and an aluminum corrugated fin (18) is also arranged between the side plate (19) and the heat exchange pipe (17), and the side plate (19) and the heat exchange pipe (17 ) Is brazed.

  The gas-liquid separator (4) includes aluminum first and second headers (21) (22) arranged in parallel in the left-right direction and extending in the vertical direction, and both headers (21) (22). ) Between the two headers (21) and (22), and two aluminum receiving pipes (23) in this case are provided. The liquid receiving pipe (23) is a circular pipe having an outer diameter equal to or smaller than the width in the front-rear direction of the headers (21) and (22). Note that the liquid receiving pipe (23) is not limited to a circular pipe as long as the width in the front-rear direction is equal to or smaller than the width in the front-rear direction of the header (21) (22). The surface shape can be changed, and a square tube or the like can be used. The passage sectional area of each liquid receiving pipe (23) is larger than the passage sectional area of each heat exchange pipe (7) (17). A desiccant (24) is disposed in the lower liquid receiving pipe (23). It should be noted that heat between the upper liquid receiving pipe (23) and the heat exchange pipe (7) at the lower end of the condensing part (2) and at the upper end of the lower liquid receiving pipe (23) and the supercooling part (3). Corrugated fins (8) and (18) are respectively arranged between the exchange pipe (17) and brazed to the liquid receiving pipe (23) and the heat exchange pipes (7) and (17).

  Both headers (5) and (6) of the condenser section (2), both headers (21) and (22) of the gas-liquid separator (4), and both headers (15) and (16) of the supercooling section (3) are A pair of aluminum tanks (25), (26), which are spaced apart in the direction and extend in the vertical direction, are formed by being partitioned by partition members (27) (28) (29) (30), respectively. The partition member (27) (29) between the condensing part (2) and the gas-liquid separation part (4) is the upper wall (21a) of both headers (21) (22) of the gas-liquid separation part (4) ) (22a), and the partition members (28) and (30) between the gas-liquid separator (4) and the supercooler (3) are connected to both headers (21) and (22) of the gas-liquid separator (4). It is the lower wall (21b) (22b). The upper wall (21a) of the first header (21) of the gas-liquid separation part (4) is formed with a refrigerant inlet (32) over the whole area except for its peripheral edge, and is also below the second header (22). The wall (22b) is formed with a refrigerant outlet (33) that is considerably smaller than the refrigerant inlet (32) at a portion closer to the outer side.

  The refrigerant flowing from the refrigerant inlet (12) into the upper header (5a) of the first header (5) of the condensing unit (2) passes through the upper passage group (13) and enters the second header (6). And then flows into the lower header portion (5b) of the first header (5) through the lower passage group (14). The refrigerant flowing into the lower header portion (5b) flows into the first header (21) of the gas-liquid separator (4) through the refrigerant inlet (32), and into the gas-liquid separator (4), That is, it accumulates in both headers (21) and (22) and in the liquid receiving pipe (23), and flows into the second header (16) of the supercooling section (3) through the refrigerant outlet (33). The refrigerant flowing into the second header (16) flows into the first header (15) through the heat exchange pipe (17) and flows out from the refrigerant outlet (20).

  The gas-liquid separation unit (4) is provided with a flow rate reduction means for reducing the flow rate of the refrigerant flowing from the condensation unit (2) into the gas-liquid separation unit (4). The flow velocity reducing means includes a mesh (34) as a porous member stretched in the refrigerant inlet (32) of the upper wall (21a) of the first header (21), and a refrigerant in the second header (22). A flow path length extending member (35) provided to surround the outflow port (33) and extending a flow path length from the refrigerant inflow port (32) to the refrigerant outflow port (33). Yes.

  The flow path length extension member (35) includes an aluminum tubular inner member (36) provided on the lower wall (22b) so as to communicate with the refrigerant outlet (33), and an inner side on the lower wall (22b). An aluminum hollow outer member (37) is provided so as to project upward so as to surround the member (36), and has an upper end closed and a through hole (38) formed in the lower end portion of the peripheral wall. The inner member (36) has a lower end inserted into the refrigerant outlet (33) and fixed to the lower wall (22b). As shown in FIG. 3, the outer member (37) includes a lower wall (22 b), that is, a peripheral wall (37 a) that is formed integrally with the partition member (30) and protrudes upward, and a peripheral wall (37 a). 37a) and a top wall (37b) which is integrally formed at the upper end of the peripheral wall (37a) and closes the upper end opening of the peripheral wall (37a), and a through hole (38) is formed at the lower end of the flat wall portion of the peripheral wall (37a). Has been. The upper end of the outer member (37) is at a lower position than the upper wall (21a) of the second header (22). The channel length extending member (35) is fitted into the right tank (26) through the through hole (39) formed in the peripheral wall of the right tank (26) together with the partition member (30), and is inserted into the right tank (26). It is brazed.

  The heat exchanger (1) described above constitutes a refrigeration cycle together with a compressor, a decompressor (expansion valve) and an evaporator. Such a refrigeration cycle is used as an air conditioner for vehicles such as automobiles.

  In the heat exchanger (1) described above, during the operation of the refrigeration cycle, the refrigerant passes through the refrigerant inlet (32) from the lower header part (5b) of the first header (5) of the condensing part (2). When flowing into the first header (21) of the separation section (4), the flow velocity is reduced by the action of the mesh (34). In addition, the refrigerant flows into the second header (22) through the liquid receiving pipe (23) and then into the gas-liquid separator (4), that is, in both the headers (21) (22) and the liquid receiving pipe ( 23) When passing through the refrigerant outlet (33) and flowing out into the second header (16) of the supercooling section (3), the through-hole (38) of the channel length extension member (35) After passing through the outer member (37) and flowing upward in the outer member (37), it enters the inner member (36) from the upper end opening, and passes through the refrigerant outlet (33) to the supercooling section ( Since it flows out to the second header (16) of 3), the flow velocity is reduced again here. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. As a result, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved.

  Next, an experimental example using the heat exchanger (1) having the above-described configuration (referred to as product A of the present invention) will be described with reference examples.

The size of the condensing part (2) of the product A of the present invention is 290 mm in height, 570 mm in width in the left-right direction and 16 mm in depth in the front-rear direction. The number of heat exchange tubes (7) in the condensing part (2) is 28, The total passage cross-sectional area of the total heat exchange pipe (7) is 367 mm ² . The size of the supercooling section (3) is 60mm in height, 570mm in width in the left-right direction, and 16mm in depth in the front-rear direction. The number of heat exchange tubes (17) in the supercooling section (3) is 5, The total cross-sectional area of the heat exchange pipe (17) is 65 mm ² . Furthermore, the inner diameter of the liquid receiving pipe (23) is 13.5 mm, and the outer diameter is 15.9 mm.

  In addition, as a heat exchanger which is a reference product, a pair of headers arranged at intervals from each other, a plurality of heat exchange tubes arranged between both headers and having both end portions connected to both headers, and adjacent heat A condensing part consisting of corrugated fins arranged between the exchange pipes and joined to the heat exchange pipes, a pair of headers arranged at a distance from each other, and arranged between both headers, both end parts being both headers A plurality of connected heat exchange pipes, a supercooling part comprising corrugated fins arranged between adjacent heat exchange pipes and joined to the heat exchange pipes, one header of the condensing part and one of the supercooling parts And a vertical liquid receiver fixed across the header, and a pair of tanks arranged at a distance from each other are partitioned by a partition member, thereby condensing part and subcooling part Both headers are shaped The receiver has a refrigerant inflow passage that leads to one header of the condensing part and a refrigerant outflow passage that leads to one header of the supercooling part and is fixed across both headers, and a lower end part A heat exchanger comprising a vertical cylindrical liquid receiver main body fixed detachably to the block was prepared. Use the same heat exchange pipe as the heat exchange pipe of the product A of the present invention as the heat exchange pipe of the heat exchanger of the reference product, and the size of the condenser of the heat exchanger of the reference product. The total number of heat exchange tubes and the total cross-sectional area of the total heat exchange pipe, the size of the supercooling section, and the total number of heat exchange pipes of the supercooling section and the total cross-sectional area of the total heat exchange pipe are products of the present invention. Same as A heat exchanger.

Evaluation test 1
A refrigeration cycle was assembled using the product A of the present invention and the reference product, a compressor, an expansion valve and an evaporator, respectively. First, a predetermined amount of 850 g of refrigerant was put into the refrigeration cycle to start the operation of the refrigeration cycle, and charge graphs were created by examining the degree of subcooling at various refrigerant charging amounts while adding refrigerant. The result is shown in FIG. In the charge graph shown in FIG. 4, point A is the point where supercooling of the refrigerant flowing out from the heat exchangers of the product A and the reference product is started, and point B is the inside of the gas-liquid separation part of the product A of the invention. In addition, the liquid phase refrigerant starts to accumulate in the receiver of the reference product, and the point C is a point where the gas-liquid separation part of the product A of the present invention and the receiver of the reference product are filled with the liquid refrigerant. . In the case of the product A of the present invention, the width of the steady region where the degree of supercooling is constant is the same as that of the reference product, and it can be seen that this product has sufficient performance as this type of heat exchanger.

Embodiment 2
This embodiment is shown in FIG.

  In the case of the heat exchanger (40) of this embodiment, a flow rate reduction that reduces the flow rate of the refrigerant that is provided in the gas-liquid separation unit (4) and flows into the gas-liquid separation unit (4) from the condensation unit (2) The means includes a mesh (34) as a porous member stretched in the refrigerant inlet (32) of the upper wall (21a) of the first header (21), and the lower wall (22b) of the second header (22). ) And a throttle hole-like refrigerant outlet (41) formed in the central portion of. The size of the throttle hole-shaped refrigerant outlet (41) is smaller than the size of the refrigerant outlet (33) of the heat exchanger (1) of the first embodiment.

  Other configurations are the same as those of the heat exchanger according to the first embodiment.

In the heat exchanger (40) of the second embodiment, during the operation of the refrigeration cycle, the refrigerant passes through the refrigerant inlet (32) from the lower header part (5b) of the first header (5) of the condensing part (2). When flowing into the first header (21) of the gas-liquid separator (4), the flow velocity is reduced by the action of the mesh (34). In addition, the refrigerant flows into the second header (22) through the liquid receiving pipe (23) and then into the gas-liquid separator (4), that is, in both the headers (21) (22) and the liquid receiving pipe ( 23) When accumulated in the second header (16) of the supercooling section (3) and flowing out into the second header (16) of the supercooling section (3), the second header (16) of the supercooling section (3) passes through the throttle hole-like refrigerant outlet (41). ), The flow rate is reduced here as well. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. As a result, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved.
Embodiment 3
This embodiment is shown in FIG. 6 and FIG.

  In the case of the heat exchanger (45) of this embodiment, the refrigerant inlet (32) is formed in the inner half of the upper wall (21a) of the first header (21) of the gas-liquid separator (4). The flow rate lowering means provided in the gas / liquid separator (4) and for reducing the flow rate of the refrigerant flowing into the gas / liquid separator (4) from the condenser (2) is provided on the first header (21). A mesh (34) as a porous member stretched in the refrigerant inlet (32) of the wall (21a) and a refrigerant outlet (33) in the second header (22), A flow path length extending member (46) that extends a flow path length from the refrigerant inlet (32) to the refrigerant outlet (33) of the refrigerant flowing in.

  The channel length extending member (46) is formed of an aluminum tubular inner member (47) provided in an upward projecting manner on the lower wall (22b) so as to communicate with the refrigerant outlet (33), and an inner side on the lower wall (22b). It comprises an aluminum hollow outer member (48) provided in an upward projecting manner so as to surround the member (47) and having an upper end closed and a through hole (49) formed in the lower end portion of the peripheral wall. The inner member (47) has its lower end inserted into the refrigerant outlet (33) and fixed. As shown in FIG. 7, the outer member (48) extends upward from the outer member (37) of the heat exchanger (1) of the first embodiment, that is, the upper wall (22a) of the second header (22), that is, It is integrated with the partition member (29). The upper wall (22a) also serves as a top wall (48b) for closing the upper end opening of the peripheral wall (48a) in the outer member (48). Accordingly, the upper end of the outer member (48) is at the same height as the upper wall (22a) of the second header. The channel length extending member (46) is fitted into the right tank (26) through the through hole (39) formed in the peripheral wall of the right tank (26) together with the upper and lower partition members (29) and (30). It is brazed to the tank (26).

  Other configurations are the same as those of the heat exchanger according to the first embodiment.

  In the heat exchanger (45) of the third embodiment, during the operation of the refrigeration cycle, the refrigerant passes through the refrigerant inlet (32) from the lower header portion (5b) of the first header (5) of the condensing unit (2). When flowing into the first header (21) of the gas-liquid separator (4), the flow velocity is reduced by the action of the mesh (34). In addition, the refrigerant flows into the second header (22) through the liquid receiving pipe (23) and then into the gas-liquid separator (4), that is, in both the headers (21) (22) and the liquid receiving pipe ( 23) When passing through the refrigerant outlet (33) and outflowing into the second header (16) of the supercooling section (3), the through hole (49) of the channel length extension member (46) After passing through the outer member (48) and flowing upward in the outer member (48), it enters the inner member (47) from the upper end opening, passes through the refrigerant outlet (33), and passes through the supercooling section (3 ) Flows out to the second header (16), so that the flow velocity is also reduced here. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. As a result, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved.

Embodiment 4
This embodiment is shown in FIG. 8 and FIG.

  In the case of the heat exchanger (50) of this embodiment, the first header (15) of the supercooling section (3) is moved upward by a plate-like partition member (51) provided at a middle height position in the vertical direction. It is divided into a header part (15a) and a lower header part (15b), and a refrigerant outlet (20) is provided in the lower header part (15b). The supercooling section (3) includes a plurality of heat exchange tubes (17) arranged continuously in the vertical direction at a portion above the partition member (51) and a portion below the partition member (51). ) Group of passages (52) and (53) are provided. The flow direction of the refrigerant in all the heat exchange pipes (17) constituting each passage group (52) (53) is the same, and the flow direction of the refrigerant in both passage groups (52) (53) is different. Yes.

  A refrigerant outlet (33) is formed in an outer portion of the lower wall (21b) in the first header (21) of the gas-liquid separator (4).

  The refrigerant flowing from the refrigerant inlet (12) into the upper header (5a) of the first header (5) of the condensing unit (2) passes through the upper passage group (13) and enters the second header (6). And then flows into the lower header portion (5b) of the first header (5) through the lower passage group (14). The refrigerant flowing into the lower header portion (5b) flows into the first header (21) of the gas-liquid separator (4) through the refrigerant inlet (32), and into the gas-liquid separator (4), That is, the upper header portion (15a) of the first header (15) of the supercooling portion (3) is accumulated in both headers (21) and (22) and in the liquid receiving pipe (23), passes through the refrigerant outlet (33). Flows in. The refrigerant flowing into the upper header portion (15a) of the first header (15) flows into the second header (16) through the upper passage group (52) and further passes through the lower passage group (53). Into the lower header portion (15b) of the first header (5). The refrigerant flowing into the lower header part (15b) flows out from the refrigerant outlet (20).

  The flow rate lowering means that is provided in the gas-liquid separation unit (4) and reduces the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensation unit (2) is an upper wall of the first header (21) ( 21a) a mesh (34) as a porous member stretched in the refrigerant inlet (32) and a refrigerant outlet (33) provided in the first header (21) so as to surround the refrigerant outlet (33). Formed at the center of the lower wall (22b) of the lower wall (22b) of the second header (22), and the flow path length extending member (35) extending the flow path from the inlet (32) to the refrigerant outlet (33) And a pressure reducing hole (54) communicating with the second header (16) of the supercooling section (3).

  The channel length extending member (35) is the same as the channel length extending member (35) of the first embodiment, but reversed in the left-right direction, and the outer member (37) is used instead of the partition member (30). Further, it is formed integrally with the partition member (28). The lower end portion of the inner member (36) is inserted into the refrigerant outlet (33) to be inserted into the lower wall (21b), that is, the refrigerant outlet (33) formed in the partition member (28). It is fixed to the wall (21b). The upper end of the outer member (37) is at a height position below the upper wall (21a) of the first header (21). The flow path length extension member (35) is fitted into the left tank (25) through the through hole (55) formed in the peripheral wall of the left tank (25) together with the partition member (28), and is inserted into the left tank (25). It is attached.

  Other configurations are the same as those of the heat exchanger (1) of the first embodiment.

  In the heat exchanger (50) of the fourth embodiment, during the operation of the refrigeration cycle, the refrigerant passes from the lower header part (5b) of the first header (5) of the condensing part (2) through the refrigerant inlet (32). When flowing into the first header (21) of the gas-liquid separator (4), the flow velocity is reduced by the action of the mesh (34). Further, the refrigerant accumulates in the gas-liquid separator (4), that is, in both headers (21) and (22) and in the liquid receiving pipe (23), and passes through the refrigerant outlet (33) to the supercooling section (3). When flowing into the upper header portion (15a) of the first header (15) of the first header (15), it enters the outer member (37) through the through hole (38) of the flow path length extending member (35), and enters the outer member (37). 37) After flowing upwards, the upper member (15a) enters the inner member (36) from the upper end opening, passes through the refrigerant outlet (33), and the upper header portion (15a) of the first header (15) of the supercooling portion (3). ), The flow velocity is reduced again. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. Here, as the amount of the refrigerant flowing into the gas-liquid separator (4) increases, the pressure in the second header (22) of the gas-liquid separator (4) increases, so that the first header (21). The refrigerant flowing into the first header (15) of the supercooling section (3) from the refrigerant outlet (33) directly through the flow path extension member (35) without flowing into the second header (22). ) May flow out into the upper header portion (15a), but the refrigerant in the second header (22) passes through the pressure reducing hole (54) and the second header (16) of the supercooling portion (3). As a result, the pressure in the second header (22) is reduced, and the refrigerant surely flows into the second header (22). As a result, the residence time in the gas-liquid separation unit (4) is prevented from being shortened, and the gas-liquid separation effect in the gas-liquid separation unit (4) is improved. Therefore, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved. The refrigerant flowing from the second header (22) of the gas-liquid separator (4) through the pressure reducing hole (54) into the second header (16) of the supercooling unit (3) contains a small amount of gas phase. Although the refrigerant is mixed in, the amount thereof is small, so that it is reliably liquefied and supercooled by the supercooling section (3).

Embodiment 5
This embodiment is shown in FIG. 10 and FIG.

  In the case of the heat exchanger (60) of this embodiment, the refrigerant inlet (32) is provided in the upper wall (21a) of the first header (21) of the gas-liquid separator (4), that is, the inner half of the partition member (27). ) Is formed. The flow rate lowering means provided in the gas / liquid separator (4) and for reducing the flow rate of the refrigerant flowing into the gas / liquid separator (4) from the condenser (2) is provided on the first header (21). A mesh (34) as a porous member stretched in the refrigerant inlet (32) of the wall (21a) and a refrigerant outlet (33) in the first header (21), and A flow path length extending member (46) that extends a flow path length from the refrigerant inlet (32) to the refrigerant outlet (33) of the refrigerant flowing in.

  As shown in FIG. 11, the channel length extending member (46) is the same as the channel length extending member (46) of the third embodiment, but reversed in the left-right direction, and the outer member (48) Instead of the partition members (29) and (30), they are formed integrally with the partition members (27) and (28). Then, the lower end of the inner member (47) is inserted into the refrigerant outlet (33) to be inserted into the lower wall (21b), that is, the refrigerant outlet (33) formed in the partition member (28). It is fixed to the wall (21b). The partition member (27), that is, the outer portion of the upper wall (21a) also serves as a top wall (48b) that closes the upper end opening of the peripheral wall (48a) of the outer member (48). Furthermore, the refrigerant inlet (32) is formed in the partition member (27), that is, the portion protruding inward from the flat wall portion of the peripheral wall (48a) in the upper wall (21a). Accordingly, the upper end of the outer member (48) is at the same height as the upper wall (21a) of the first header (21). The channel length extending member (46) is fitted into the left tank (25) through the through hole (55) formed in the peripheral wall of the left tank (25) together with the upper and lower partition members (27) and (18). It is brazed to the tank (25).

  Other configurations are the same as those of the heat exchanger (50) of the fourth embodiment.

  In the heat exchanger (60) of the fifth embodiment, during the operation of the refrigeration cycle, the refrigerant passes through the refrigerant inlet (32) from the lower header portion (5b) of the first header (5) of the condensing portion (2). When flowing into the first header (21) of the gas-liquid separator (4), the flow velocity is reduced by the action of the mesh (34). Further, the refrigerant accumulates in the gas-liquid separator (4), that is, in both headers (21) and (22) and in the liquid receiving pipe (23), and passes through the refrigerant outlet (33) to the supercooling section (3). When flowing into the upper header portion (15a) of the first header (15) of the first header (15), it enters the outer member (48) through the through hole (49) of the flow path length extension member (46), and enters the outer member (48). 48) After flowing upward in the upper member, it enters the inner member (47) from the upper end opening, passes through the refrigerant outlet (33), and the upper header portion (15a) of the first header (15) of the supercooling portion (3). ), The flow velocity is reduced again. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. Here, as the amount of the refrigerant flowing into the gas-liquid separator (4) increases, the pressure in the second header (22) of the gas-liquid separator (4) increases, so that the first header (21). The refrigerant that has flowed into the first header (15) of the supercooling section (3) passes directly from the refrigerant outlet (33) through the flow path length extending member (46) without flowing into the second header (22). ) May flow out into the upper header portion (15a), but the refrigerant in the second header (22) passes through the pressure reducing hole (54) and the second header (16) of the supercooling portion (3). As a result, the pressure in the second header (22) is reduced, and the refrigerant surely flows into the second header (22). As a result, the residence time in the gas-liquid separation unit (4) is prevented from being shortened, and the gas-liquid separation effect in the gas-liquid separation unit (4) is improved. Therefore, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved. The refrigerant flowing from the second header (22) of the gas-liquid separator (4) through the pressure reducing hole (54) into the second header (16) of the supercooling unit (3) contains a small amount of gas phase. Although the refrigerant is mixed in, the amount thereof is small, so that it is reliably liquefied and supercooled by the supercooling section (3).

Embodiment 6
This embodiment is shown in FIG.

  In the case of the heat exchanger (65) of this embodiment, no pressure reducing hole is formed in the lower wall (22b) of the second header (22) of the gas-liquid separator (4).

  Other configurations are the same as those of the heat exchanger according to the fifth embodiment.

  In the heat exchanger of the sixth embodiment, during the operation of the refrigeration cycle, the refrigerant is separated from the lower header (5b) of the first header (5) of the condensing unit (2) through the refrigerant inlet (32). When flowing into the first header (21) of the section (4), the flow velocity is reduced by the action of the mesh (34). Further, the refrigerant accumulates in the gas-liquid separator (4), that is, in both headers (21) and (22) and in the liquid receiving pipe (23), and passes through the refrigerant outlet (33) to the supercooling section (3). When flowing into the upper header portion (15a) of the first header (15) of the first header (15), it enters the outer member (48) through the through hole (49) of the flow path length extension member (46), and enters the outer member (48). 48) After flowing upward in the upper member, it enters the inner member (47) from the upper end opening, passes through the refrigerant outlet (33), and the upper header portion (15a) of the first header (15) of the supercooling portion (3). ), The flow velocity is reduced again. Accordingly, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. Therefore, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved.

Embodiment 7
This embodiment is shown in FIG.

  In the case of the heat exchanger (70) of this embodiment, the desiccant (24) is disposed in the liquid receiving pipe (23) on the upper side of the gas-liquid separator (4). A first filter consisting of a filter (72) made of non-woven fabric and a mesh (73) superimposed on one side of the filter (72) on the left and right sides of the desiccant (24) in the upper liquid receiving pipe (23). Resistance applying means (71A) is arranged. In addition, a second resistance application comprising a filter (72) made of non-woven fabric, etc., and a mesh (73) superimposed on the left and right sides of the filter (72) is provided at both left and right ends of the lower liquid receiving pipe (23). Means (71B) are arranged.

  As the mesh (73) used for the resistance applying means (71A) (71B), it is preferable to use a mesh having a mesh size of 120 mesh or less.

  Here, instead of at least one of the two first resistance applying means (71A) arranged in the upper liquid receiving pipe (23), the second resistance applying means (71B) may be arranged. Good. The first resistance applying means (71A) or the second resistance applying means (71B) may be disposed only on one side of the desiccant (24) in the upper liquid receiving pipe (23).

  Further, instead of at least one of the two second resistance applying means (71B) arranged in the lower liquid receiving pipe (23), the first resistance applying means (71A) may be arranged. Good. Furthermore, the first resistance applying means (71A) or the second resistance applying means (71B) may be arranged only at one end in the lower liquid receiving pipe (23).

  In the above, as the resistance applying means (71A) (71B), a filter (72) and a mesh (73) are used in an overlapped manner, but the present invention is not limited to this. 72) and a mesh (73) may be used.

  Other configurations are the same as those of the heat exchanger according to the fifth embodiment.

  Like the heat exchanger (70) of Embodiment 7, the refrigerant inlet (32) is formed in the upper wall (21a) of the first header (21) of the gas-liquid separator (4), and the first header When the refrigerant outlet (33) is formed in the lower wall (21b) of (21), resistance applying means (71A) (71B) are provided in the liquid receiving pipe (23) of the gas-liquid separator (4). When the refrigerant is enclosed in the refrigeration cycle, the refrigerant immediately after flowing into the first header (21) through the refrigerant inlet (32) by the action of the resistance applying means (71A) (71B) It becomes difficult to flow into the liquid receiving pipe (23) and also through the liquid receiving pipe (23) and into the second header (22), and as a result, the first header ( The refrigerant immediately after flowing into 21) easily flows into the upper header part (15a) of the supercooling part (3) through the refrigerant outlet (33). Therefore, the amount of refrigerant enclosed in the refrigeration cycle until the steady state where the degree of supercooling is constant becomes relatively small.

  Moreover, in the heat exchanger (70) of the seventh embodiment, during the operation of the refrigeration cycle, the refrigerant passes through the refrigerant inlet (32) from the lower header part (5b) of the first header (5) of the condensing part (2). When flowing through and flowing into the first header (21) of the gas-liquid separator (4), the flow velocity is reduced by the action of the mesh (34). Further, the refrigerant accumulates in the gas-liquid separator (4), that is, in both headers (21) and (22) and in the liquid receiving pipe (23), and passes through the refrigerant outlet (33) to the supercooling section (3). When flowing into the upper header portion (15a) of the first header (15) of the first header (15), it enters the outer member (48) through the through hole (49) of the flow path length extension member (46), and enters the outer member (48). 48) After flowing upward in the upper member, it enters the inner member (47) from the upper end opening, passes through the refrigerant outlet (33), and the upper header portion (15a) of the first header (15) of the supercooling portion (3) ), The flow velocity is reduced again. Therefore, the flow rate of the refrigerant flowing into the gas-liquid separation unit (4) from the condensing unit (2) is reduced, and the residence time in the gas-liquid separation unit (4) becomes relatively long. The gas-liquid separation effect in the separation part (4) is improved. Here, as the amount of the refrigerant flowing into the gas-liquid separator (4) increases, the pressure in the second header (22) of the gas-liquid separator (4) increases, so that the first header (21). The refrigerant that has flowed into the first header (15) of the supercooling section (3) directly passes through the channel length extending member (46) from the refrigerant outlet (33) without flowing into the second header (22). ) May flow out into the upper header portion (15a), but the refrigerant in the second header (22) passes through the pressure reducing hole (54) and the second header (16) of the supercooling portion (3). As a result, the pressure in the second header (22) is reduced, and the refrigerant surely flows into the second header (22). As a result, the residence time in the gas-liquid separation part (4) is prevented from being shortened, and the gas-liquid separation effect in the gas-liquid separation part (4) is improved. Therefore, the amount of gas-phase refrigerant flowing into the supercooling section (3) is reduced, the supercooling effect in the supercooling section (3) is sufficient, and the cooling effect of the entire refrigeration cycle is improved. The refrigerant flowing from the second header (22) of the gas-liquid separator (4) through the pressure reducing hole (54) into the second header (16) of the supercooling unit (3) contains a small amount of gas phase. Although the refrigerant is mixed in, the amount thereof is small, so that it is surely liquefied and supercooled by the supercooling section (3).

  Next, an experimental example using the heat exchanger (70) having the above-described configuration (referred to as product B of the present invention) will be described with reference examples.

  The size of the condensing part (2) of the product B of the present invention, the total number of heat exchange pipes (7) and the cross-sectional area of the total heat exchange pipe (7), the size of the supercooling part (3), the heat exchange pipe (17 ) And the total passage cross-sectional area of the total heat exchange pipe (17), and the inner and outer diameters of the liquid receiving pipe (23) of the gas-liquid separator (4) are the same as those of the product A of the present invention described above. is there.

  The reference product is the same as the reference product used in the evaluation test 1 described above, and the heat exchange tube of the product B of the present invention is used as the heat exchange tube of the condenser and subcooling unit of the heat exchanger of the reference product. The size of the condenser of the reference heat exchanger, the number of heat exchanger tubes in the condenser and the total cross-sectional area of all the heat exchanger tubes, the size of the supercooling unit, and the supercooling The total number of heat exchange tubes and the total cross-sectional area of all the heat exchange tubes were the same as those of the heat exchanger of the product B of the present invention.

Evaluation test 2
Using the product B of the present invention and the reference product, a charge graph was prepared in the same manner as in the evaluation test 1. The result is shown in FIG. In the charge graph shown in FIG. 14, point A is the point where supercooling of the refrigerant flowing out from the heat exchangers of the product B and the reference product is started, and point B is in the gas-liquid separation part of the product B of the invention. In addition, the liquid phase refrigerant starts to accumulate in the receiver of the reference product, and the point C is a point where the gas-liquid separation part of the product B of the present invention and the receiver of the reference product are filled with the liquid refrigerant. . In the case of the product B of the present invention, the width of the steady region where the degree of supercooling is constant is equivalent to that of the reference product, and it can be seen that this product has sufficient performance as this type of heat exchanger.

It is a front view which shows the whole structure of the heat exchanger of Embodiment 1 of this invention. It is a partial expanded vertical sectional view which shows a part of heat exchanger shown in FIG. It is a disassembled perspective view which expands and shows the 2nd header part of the gas-liquid separation part of the heat exchanger shown in FIG. It is a graph which shows the experimental result conducted using the heat exchanger of this invention product A shown in FIG. 1, and a reference product. It is a partial expanded vertical sectional view which shows a part of heat exchanger of Embodiment 2 of this invention. It is a partial expanded vertical sectional view which shows a part of heat exchanger of Embodiment 3 of this invention. It is a perspective view which shows the flow-path length extension member used for the heat exchanger shown in FIG. It is a front view which shows the whole structure of the heat exchanger of Embodiment 4 of this invention. It is a partial expanded vertical sectional view which shows a part of heat exchanger shown in FIG. It is a partial expanded vertical sectional view which shows a part of heat exchanger of Embodiment 5 of this invention. It is a perspective view which shows the flow-path length extension member used for the heat exchanger shown in FIG. It is a partial expanded vertical sectional view which shows a part of heat exchanger of Embodiment 6 of this invention. It is a partial expanded vertical sectional view which shows a part of heat exchanger of Embodiment 7 of this invention. It is a graph which shows the experimental result performed using the heat exchanger of this invention B shown in FIG. 13, and a reference product.

Explanation of symbols

(1) (40) (45) (50) (60) (65) (70): Heat exchanger
(2): Condensing part
(3): Supercooling section
(4): Gas-liquid separation part
(5) (6): Header
(7): Heat exchange pipe
(15) (16): Header
(17): Heat exchange pipe
(21) (22): Header
(21a) (22a): Upper wall
(21b) (22b): Lower wall
(23): Receiver tube
(25) (26): Tank
(27) (28) (29) (30): Partition member
(32): Refrigerant inlet
(33): Refrigerant outlet
(34): Mesh
(35) (46): Channel length extension member
(36) (47): Inside member
(37) (48): Outer member
(37a) (48a): Perimeter wall
(38) (49): Through hole
(41): Restricted hole refrigerant outlet
(54): Pressure reduction hole
(71A) (71B): Resistance imparting means
(72): Filter
(73): Mesh

Claims (28)

A pair of headers arranged at a distance from each other, and a condensing part consisting of a plurality of heat exchange tubes arranged between both headers and connected at both ends to both headers, and 1 arranged at a distance from each other A pair of headers, a supercooling unit composed of a plurality of heat exchange pipes arranged between the headers and having both ends connected to both headers, and a gas-liquid separation unit arranged between the condensing unit and the supercooling unit A refrigerant that flows out of the condensing part passes through the gas-liquid separation part and flows into the supercooling part,
The gas-liquid separator is composed of a pair of headers arranged at intervals from each other, and a liquid receiving pipe arranged between both headers and having both ends connected to both headers. A heat exchanger provided with a flow rate reduction means for reducing the flow rate of the refrigerant flowing into the separation unit. The heat exchanger according to claim 1, wherein the gas-liquid separation unit includes a plurality of liquid receiving pipes arranged at intervals. The heat exchanger according to claim 1 or 2, wherein a desiccant is disposed in the liquid receiving pipe. The heat exchanger according to any one of claims 1 to 3, wherein the flow velocity lowering means includes a porous member provided at a refrigerant inlet formed in one of the headers of the gas-liquid separator. . The heat exchanger according to claim 4, wherein the porous member is made of a mesh. The heat exchanger according to any one of claims 1 to 5, wherein the flow velocity lowering means includes a throttle hole-shaped refrigerant outlet formed in one of the headers of the gas-liquid separator. The inside of a pair of tank arrange | positioned mutually spaced apart by a partition member, respectively, The header of both a condensation part, a supercooling part, and a gas-liquid separation part is formed among Claims 1-6 The heat exchanger in any one of. The heat exchanger according to claim 7, wherein a width of the liquid receiving pipe of the gas-liquid separation unit is equal to or smaller than a width of the tank in the ventilation direction. The heat exchanger according to any one of claims 1 to 3, wherein a condensing unit is disposed on the upper side of the gas-liquid separation unit and a supercooling unit is disposed on the lower side. The heat exchanger according to claim 9, wherein the flow velocity lowering means includes a porous member provided at a refrigerant inlet formed on the upper wall of one of the headers of the gas-liquid separator. The heat exchanger according to claim 10, wherein the porous member is made of a mesh. The heat exchanger according to any one of claims 9 to 11, wherein the flow velocity lowering means includes a throttle hole-like refrigerant outlet formed in the lower wall of one of the headers of the gas-liquid separator. A refrigerant inlet is formed in the upper wall of one of the headers of the gas-liquid separator, and a refrigerant outlet is also formed in the lower wall of either one of the headers. And a flow path length extending member that is provided so as to surround the refrigerant outlet and extends a flow path length from the refrigerant inlet to the refrigerant outlet. Item 11. The heat exchanger according to Item 9. The heat exchanger according to claim 13, wherein the refrigerant inlet is formed over the entire upper wall of the header. The heat exchanger according to claim 13, wherein the refrigerant inlet is formed in a part of the upper wall of the header. The heat exchanger according to any one of claims 13 to 15, wherein the porous member is made of a mesh. A flow path length extending member is provided in an upward projecting manner so as to surround the inner member on a tubular inner member provided in an upward projecting shape around the refrigerant outlet and a header lower wall in which the refrigerant outlet is formed. And the heat exchanger in any one of Claims 13-16 which consists of a hollow outer member by which the upper end was closed and the through-hole was formed in the peripheral wall lower end part. The heat exchanger according to claim 17, wherein the upper end of the outer member is at a height position below the upper wall of the header in which the refrigerant outlet is formed. The heat exchanger according to claim 17, wherein the upper end of the outer member is at the same height as the upper wall of the header in which the refrigerant outlet is formed. The refrigerant inflow port is formed in the upper wall of any one header of a gas-liquid separation part, and the refrigerant outflow port is formed in the lower wall of the other header. Heat exchanger. The refrigerant inflow port is formed in the upper wall of one of the headers of the gas-liquid separator, and the refrigerant outflow port is formed in the lower wall of the same header. The described heat exchanger. The heat exchanger according to claim 21, wherein a resistance applying means is provided in a liquid receiving pipe of the gas-liquid separation unit. The heat exchanger according to claim 22, wherein the resistance applying means comprises a mesh and / or a filter. The heat exchanger according to any one of claims 21 to 23, wherein a pressure reducing hole communicating with one header of the supercooling unit is formed in a lower wall of the other header of the gas-liquid separation unit. A pair of tanks arranged at a distance from each other is partitioned by a partition member to form both headers of a condensing unit, a supercooling unit, and a gas-liquid separating unit. The partition member between the gas-liquid separation unit and the sub-cooling unit is a partition wall between the gas-liquid separation unit and the partition wall between the gas-liquid separation unit and the supercooling unit. The heat exchanger in any one of -24. 26. The heat exchanger according to claim 25, wherein the width of the liquid receiving pipe of the gas-liquid separation unit in the ventilation direction is equal to or less than the width of the tank in the ventilation direction. A refrigeration cycle comprising a compressor, the heat exchanger according to any one of claims 1 to 26, a decompressor, and an evaporator. A vehicle comprising the refrigeration cycle according to claim 27.

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