Patent Grant
9335077
The present invention relates to a condenser suitable for use in, for example, a car air conditioner mounted on an automobile.
Herein and in the appended claims, the term “condenser” encompasses not only ordinary condensers but also sub-cool condensers each including a condensation section and a super-cooling section.
Further, herein and in the appended claims, the upper side, lower side, left-hand side, and right-hand side of
A condenser for a car air conditioner is known (see Patent Document 1). The known condenser includes a plurality of heat exchange tubes disposed in parallel such that they are spaced apart from one another in a vertical direction and extend in a left-right direction; left and right header tanks which are disposed such that they extend in the vertical direction and are spaced apart from each other in the left-right direction and to which opposite ends of the heat exchange tubes are connected by means of brazing; and a liquid receiver brazed to one header tank. Two heat exchange paths each formed by a plurality of heat exchange tubes successively arranged in the vertical direction are juxtaposed in the vertical direction. The interiors of the two header tanks are divided by respective partition members at a height between the two heat exchange paths, whereby two header sections; i.e., upper and lower header sections, are formed in each of the two header tanks. The heat exchange tubes which constitute the upper heat exchange path are connected to the upper header sections of the two header tanks, and the heat exchange tubes which constitute the lower heat exchange path are connected to the lower header sections of the two header tanks. The liquid receiver is brazed to the one header tank such that the liquid receiver extends across the upper and lower header sections. The liquid receiver has an inflow hole communicating with the interior of the upper header section of the one header tank, and an outflow hole communicating with the interior of the lower header section thereof. The other header tank has a refrigerant inlet communicating with a lower portion of the interior of the upper header section, and a refrigerant outlet communicating with a vertically intermediate portion of the interior of the lower header section. The upper header sections of the two header tanks and the upper heat exchange path form a condensation section which condensates refrigerant. The lower header sections of the two header tanks and the lower heat exchange path form a super-cooling section which super-cools the refrigerant. The upper heat exchange path serves as a refrigerant condensation path for condensing the refrigerant, and the lower heat exchange path serves as a refrigerant super-cooling path for super-cooling the refrigerant.
However, in the case of the condenser disclosed in Patent Document 1, in addition to brazing between the header tanks and the heat exchange tubes, brazing between one of the header tanks and the liquid receiver is required. Therefore, the number of brazing areas increases, resulting in an increased possibility of occurrence of leakage. In addition, in the case of the condenser disclosed in Patent Document 1, since the condensation section includes only one heat exchange path, the condenser has a problem of failing to satisfy the required condensation performance.
Patent Document 1: Japanese Patent Application Laid-Open (kokai) No. 2001-141332
An object of the present invention is to solve the above problem and to provide a condenser which can reduce the number of brazing areas as compared with the condenser disclosed in Patent Document 1 and can improve condensation performance.
To achieve the above object, the present invention comprises the following modes.
1) A condenser comprising a plurality of heat exchange tubes disposed in parallel such that the heat exchange tubes are spaced apart from one another in a vertical direction and extend in a left-right direction; and header tanks which extend in the vertical direction and to which left and right end portions of the heat exchange tubes are connected, in which three or more heat exchange paths each formed by a plurality of heat exchange tubes successively arranged in the vertical direction are juxtaposed in the vertical direction, refrigerant flows in the same direction within all the heat exchange tubes which constitute each heat exchange path, and the flow direction of the refrigerant within the heat exchange tubes which constitute a certain heat exchange path is opposite the flow direction of the refrigerant within the heat exchange tubes which constitute another heat exchange path adjacent to the certain heat exchange path, wherein a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute at least an uppermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute a heat exchange path(s) provided below the heat exchange path formed by the heat exchange tubes connected to the first header tank are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; an upper end of the second header tank is located above a lower end of the first header tank; and the second header tank has a gas-liquid separation function making use of gravitational force.
2) A condenser according to par. 1), wherein the heat exchange path formed by the heat exchange tubes connected to the first header tank and the uppermost heat exchange path of the heat exchange paths formed by the heat exchange tubes connected to the second header tank each serve as a refrigerant condensation path for condensing the refrigerant; and the heat exchange path(s) formed by the heat exchange tubes connected to the second header tank, excluding the uppermost heat exchange path, serves as a refrigerant super-cooling path for super-cooling the refrigerant.
3) A condenser according to par. 1) or 2), wherein at least one of a desiccant, a gas-liquid separation member, and a filter is disposed within the second header tank.
4) A condenser according to par. 1) or 2), wherein heat exchange tubes which constitute at least one heat exchange path are connected to the first header tank; and heat exchange tubes which constitute at least two heat exchange paths are connected to the second header tank.
5) A condenser comprising a plurality of heat exchange tubes disposed in parallel such that the heat exchange tubes are spaced apart from one another in a vertical direction; and header tanks which extend in the vertical direction and to which left and right end portions of the heat exchange tubes are connected, in which two or more heat exchange paths each formed by a plurality of heat exchange tubes successively arranged in the vertical direction are juxtaposed in the vertical direction, refrigerant flows in the same direction within all the heat exchange tubes which constitute each heat exchange path, and the flow direction of the refrigerant within the heat exchange tubes which constitute a certain heat exchange path is opposite the flow direction of the refrigerant within the heat exchange tubes which constitute another heat exchange path adjacent to the certain heat exchange path, wherein a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute a heat exchange path(s) excluding a lowermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute the lowermost heat exchange path are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; and an upper end of the second header tank is located above a lower end of the first header tank.
6) A condenser comprising a plurality of heat exchange tubes disposed in parallel such that the heat exchange tubes are spaced apart from one another in a vertical direction; and header tanks which extend in the vertical direction and to which left and right end portions of the heat exchange tubes are connected, in which two or more heat exchange paths each formed by a plurality of heat exchange tubes successively arranged in the vertical direction are juxtaposed in the vertical direction, refrigerant flows in the same direction within all the heat exchange tubes which constitute each heat exchange path, and the flow direction of the refrigerant within the heat exchange tubes which constitute a certain heat exchange path is opposite the flow direction of the refrigerant within the heat exchange tubes which constitute another heat exchange path adjacent to the certain heat exchange path, wherein a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute a heat exchange path(s) excluding an uppermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute the uppermost heat exchange path are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; and a lower end of the second header tank is located below an upper end of the first header tank.
7) A condenser according to par. 5) or 6), wherein each of all the heat exchange paths serves as a refrigerant condensation path for condensing the refrigerant.
8) A condenser according to par. 5) or 6), wherein at least one of a desiccant, a gas-liquid separation member, and a filter is disposed within the second header tank.
9) A condenser according to par. 1), 5), or 6), wherein the second header tank is disposed on the outer side of the first header tank with respect to the left-right direction; all the heat exchange tubes are straight; second-header-tank-side end portions of the heat exchange tubes connected to the second header tank extend outward with respect to the left-right direction beyond first-header-tank-side end portions of the heat exchange tubes connected to the first header tank.
10) A condenser according to par. 1), 5), or 6), wherein the second header tank is positionally shifted from the first header tank in an air-passing direction; second-header-tank-side end portions of the heat exchange tubes connected to the second header tank are bent; and a bent portion of each bent heat exchange tube is located in the same plane as the remaining unbent portion of the heat exchange tube.
11) A condenser according to par. 1), 5), or 6), wherein the second header tank is positionally shifted from the first header tank in an air-passing direction; second-header-tank-side end portions of the heat exchange tubes connected to the second header tank are bent in a folded back shape; and a bent portion of each bent heat exchange tube is located in a plane shifted from a plane in which the remaining unbent portion of the heat exchange tube is located.
12) A condenser according to par. 1), 5), or 6), wherein the second header tank is positionally shifted from the first header tank in an air-passing direction; first-header-tank-side end portions of the heat exchange tubes connected to the first header tank and second-header-tank-side end portions of the heat exchange tubes connected to the second header tank are bent; and a bent portion of each bent heat exchange tube is located in the same plane as the remaining unbent portion of the heat exchange tube.
According to the condensers of pars. 1) to 4), a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute at least an uppermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute a heat exchange path(s) provided below the heat exchange path formed by the heat exchange tubes connected to the first header tank are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; an upper end of the second header tank is located above a lower end of the first header tank; and the second header tank has a gas-liquid separation function making use of gravitational force. Therefore, a liquid receiver used in the condenser described in Patent Document 1 is not required, and brazing between the liquid receiver and the corresponding header tank becomes unnecessary. Accordingly, the number of brazing areas decreases as compared with the condenser described in Patent Document 1, and the possibility of occurrence of leakage decreases. Furthermore, since two or more refrigerant condensation paths for condensing refrigerant can be provided, condensing performance can be improved.
According to the condenser of par. 2), refrigerant flows from the plurality of heat exchange tubes which constitute the lowermost refrigerant condensation path into the second header tank, and the refrigerant undergoes gas-liquid separation within the second header tank. Therefore, it is possible to suppress generation of a pressure drop, to thereby prevent re-gasification of the liquid-phase refrigerant. In contrast, in the case of the condenser described in Patent Document 1, the refrigerant having flowed into an upper header section from a plurality of heat exchange tubes which constitute an upper heat exchange path serving as a refrigerant condensation path flows into the liquid receiver via an inflow hole of the liquid receiver. Therefore, a pressure drop is likely to occur when the refrigerant flows into the liquid receiver, and re-gasification of the liquid-phase refrigerant occurs.
Furthermore, according to the condenser of par. 2), refrigerant flows from the plurality of heat exchange tubes which constitute the lowermost refrigerant condensation path into the second header tank, and the refrigerant undergoes gas-liquid separation within the second header tank. Therefore, gas-liquid separation can be performed efficiently within the second header tank. That is, gas-liquid mixed phase refrigerant containing a gas-phase component in a large amount flows through an upper heat exchange tube(s) of the plurality of heat exchange tubes which constitute the refrigerant condensation path, and gas-liquid mixed phase refrigerant containing a liquid-phase component in a large amount flows through a lower heat exchange tube(s) of the plurality of heat exchange tubes. Since these gas-liquid mixed phase refrigerants flow into the second header tank without mixing, gas-liquid separation can be performed efficiently. In contrast, in the case of the condenser described in Patent Document 1, even if gas-liquid mixed phase refrigerant containing a gas-phase component in a large amount flows through an upper heat exchange tube(s) of the plurality of heat exchange tubes which constitute the upper heat exchange path serving as a refrigerant condensation path, and gas-liquid mixed phase refrigerant containing a liquid-phase component in a large amount flows through a lower heat exchange tube(s) of the plurality of heat exchange tubes, these gas-liquid mixed phase refrigerants flow into the liquid receiver after having mixed together within the upper header section. Therefore, gas-liquid separation cannot be performed efficiently.
According to the condenser of par. 5), a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute a heat exchange path(s) excluding a lowermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute the lowermost heat exchange path are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; and an upper end of the second header tank is located above a lower end of the first header tank. Therefore, a liquid receiver used in the condenser described in Patent Document 1 is not required, and brazing between the liquid receiver and the corresponding header tank becomes unnecessary. Accordingly, the number of brazing areas decreases as compared with the condenser described in Patent Document 1, and the possibility of occurrence of leakage decreases. Furthermore, since two or more refrigerant condensation paths for condensing refrigerant can be provided, condensing performance can be improved.
Furthermore, refrigerant flows from the plurality of heat exchange tubes which constitute the lowermost refrigerant condensation path into the second header tank, and the refrigerant undergoes gas-liquid separation within the second header tank. Therefore, gas-liquid separation can be performed efficiently within the second header tank. That is, gas-liquid mixed phase refrigerant containing a gas-phase component in a large amount flows through an upper heat exchange tube(s) of the plurality of heat exchange tubes which constitute the lowermost heat exchange path, and gas-liquid mixed phase refrigerant containing a liquid-phase component in a large amount flows through a lower heat exchange tube(s) of the plurality of heat exchange tubes. Since these gas-liquid mixed phase refrigerants flow into the second header tank without mixing, gas-liquid separation can be performed efficiently.
According to the condenser of par. 6), a first header tank and a second header tank are separately provided at a left end portion or right end portion of the condenser; heat exchange tubes which constitute a heat exchange path(s) excluding an uppermost heat exchange path are connected to the first header tank; heat exchange tubes which constitute the uppermost heat exchange path are connected to the second header tank; the first header tank and the second header tank are positionally shifted from each other as viewed from above; and a lower end of the second header tank is located below an upper end of the first header tank. Therefore, a liquid receiver used in the condenser described in Patent Document 1 is not required, and brazing between the liquid receiver and the corresponding header tank becomes unnecessary. Accordingly, the number of brazing areas decreases as compared with the condenser described in Patent Document 1, and the possibility of occurrence of leakage decreases. Furthermore, since two or more refrigerant condensation paths for condensing refrigerant can be provided, condensing performance can be improved.
Furthermore, refrigerant flows from the plurality of heat exchange tubes which constitute the uppermost refrigerant condensation path into the second header tank, and the refrigerant undergoes gas-liquid separation within the second header tank. Therefore, gas-liquid separation can be performed efficiently within the second header tank. That is, gas-liquid mixed phase refrigerant containing a gas-phase component in a large amount flows through an upper heat exchange tube(s) of the plurality of heat exchange tubes which constitute the uppermost heat exchange path, and gas-liquid mixed phase refrigerant containing a liquid-phase component in a large amount flows through a lower heat exchange tube(s) of the plurality of heat exchange tubes. Since these gas-liquid mixed phase refrigerants flow into the second header tank without mixing, gas-liquid separation can be performed efficiently.
According to the condensers of pars. 9) to 12), the first header tank and the second header tank can be relatively easily shifted from each other as viewed from above.
According to the condensers of pars. 10) to 12), even in the case where other equipment must be disposed on the side of the condenser opposite (with respect to the air passing direction) the side where the second header tank is disposed, the second header tank does not hinder the disposition of the equipment. For example, in general, a radiator is disposed on the downstream side (with respect to the air passing direction) of a condenser of a car air conditioner. By means of disposing the second header tank at a location shifted toward the upstream side with respect to the air passing direction, it is possible to prevent the second header tank from hindering the installation of the radiator.
Embodiments of the present invention will next be described with reference to the drawings.
In the following description, the direction toward the reverse side of a sheet on which
Furthermore, the term “aluminum” as used in the following description encompasses aluminum alloys in addition to pure aluminum.
Moreover, the same reference numerals are used throughout the drawings to refer to the same portions and members, and their repeated descriptions are omitted.
In
Left and right end portions of the heat exchange tubes (2) are connected, by means of brazing, to the header tanks (3), (4), and (5), which extend in the vertical direction. Each of the corrugate fins (6) is disposed between and brazed to adjacent heat exchange tubes (2), or is disposed on the outer side of the uppermost or lowermost heat exchange tube (2) and brazed to the corresponding heat exchange tube (2). The side plates (7) are disposed on the corresponding outer sides of the uppermost and lowermost corrugate fins (6), and are brazed to these corrugate fins (6). Three heat exchange paths (P1), (P2), and (P3) each formed by a plurality of heat exchange tubes (2) successively arranged in the vertical direction are juxtaposed in the vertical direction. The three heat exchange paths will be referred to as the first to third heat exchange paths (P1), (P2), and (P3) from the upper side. The flow direction of refrigerant is the same among all the heat exchange tubes (2) which constitute the respective heat exchange paths (P1), (P2), and (P3). The flow direction of refrigerant in the heat exchange tubes (2) which constitute a certain heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes (2) which constitute another heat exchange path adjacent to the certain heat exchange path.
As shown in
The third header tank (5) is disposed on the right end side of the condenser (1), and all the heat exchange tubes (2) which constitute the first to third heat exchange paths (P1) to (P3) are connected to the third header tank (5). The transverse cross sectional shape of the third header tank (5) is identical with that of the first header tank (3). The interior of the third header tank (5) is divided into an upper header section (11) and a lower header section (12) by means of an aluminum partition plate (8) provided at a height between the second heat exchange path (P2) and the third heat exchange path (P3).
The first header tank (3), a portion of the second header tank (4) to which the heat exchange tubes (2) of the second heat exchange path (P2) are connected, the upper header section (11) of the third header tank (5), the first heat exchange path (P1), and the second heat exchange path (P2) form a condensation section (1A), which condensates refrigerant. A portion of the second header tank (4) to which the heat exchange tubes (2) of the third heat exchange path (P3) are connected, the lower header section (12) of the third header tank (5), and the third heat exchange path (P3) form a super-cooling section (1B), which super-cools refrigerant. The first and second heat exchange paths (P1) and (P2) (a heat exchange path formed by the heat exchange tubes (2) connected to the first header tank (3) and the uppermost heat exchange path of the heat exchange paths formed by the heat exchange tubes (2) connected to the second header tank (4)) each serve as a refrigerant condensation path for condensing refrigerant. The third heat exchange path (P3) (the heat exchange path(s) formed by the heat exchange tubes (2) connected to the second header tank (4), excluding the uppermost heat exchange path) serves as a refrigerant super-cooling path for super-cooling refrigerant.
A refrigerant inlet (13) is formed in an upper end portion of the first header tank (3), which constitutes the condensation section (1A). A refrigerant outlet (15) is formed in the lower header section (12) of the third header tank (5), which constitutes the super-cooling section (1B). A refrigerant inlet member (14) communicating with the refrigerant inlet (13) is joined to the first header tank (3). A refrigerant outlet member (16) communicating with the refrigerant outlet (15) is joined to the lower header section (12) of the third header tank (5).
All the heat exchange tubes (2) are straight; and left end portions (end portions on the side toward the second header tank (4)) of the heat exchange tubes (2) connected to the second header tank (4) extend leftward beyond left end portions (end portions on the side toward the first header tank (3)) of the heat exchange tubes (2) connected to the first header tank (3).
The condenser (1) is manufactured through batch brazing of all the components.
The condenser (1) constitutes a refrigeration cycle in cooperation with a compressor, an expansion valve (pressure reducer), and an evaporator; and the refrigeration cycle is mounted on a vehicle as a car air conditioner.
In the condenser (1) having the above-described structure, gas phase refrigerant of high temperature and high pressure compressed by the compressor flows into the first header tank (3) via the refrigerant inlet member (14) and the refrigerant inlet (13). The gas phase refrigerant is condensed while flowing rightward within the heat exchange tubes (2) of the first heat exchange path (P1), and flows into the upper header section (11) of the third header tank (5). The refrigerant having flowed into the upper header section (11) of the third header tank (5) is condensed while flowing leftward within the heat exchange tubes (2) of the second heat exchange path (P2), and flows into the second header tank (4).
The refrigerant having flowed into the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the second header tank (4) because of gravitational force, and enters the heat exchange tubes (2) of the third heat exchange path (P3). The liquid-predominant mixed phase refrigerant having entered the heat exchange tubes (2) of the third heat exchange path (P3) is super-cooled while flowing rightward within the heat exchange tubes (2). After that, the super-cooled refrigerant enters the lower header section (12) of the third header tank (5), and flows out via the refrigerant outlet (15) and the refrigerant outlet member (16). The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the case of a condenser (20) shown in
Left and right end portions of the heat exchange tubes (2) which constitute the first and second heat exchange paths (P1) and (P2) are connected to the first header tank (3) and the third header tank (5), respectively, by means of brazing. Left and right end portions of the heat exchange tubes (2) which constitute the third and fourth heat exchange paths (P3) and (P4) are connected to the second header tank (4) and the third header tank (5), respectively, by means of brazing.
The interior of the third header tank (5) is divided into an upper header section (23), an intermediate header section (24), and a lower header section (25) by aluminum partition plates (21) and (22), which are provided at a height between the first heat exchange path (P1) and the second heat exchange path (P2) and a height between the third heat exchange path (P3) and the fourth heat exchange path (P4), respectively. Left end portions of the heat exchange tubes (2) of the first heat exchange path (P1) are connected to the first header tank (3), and right end portions thereof are connected to the upper header section (23) of the third header tank (5). A left end portion of the second heat exchange path (P2) is connected to the first header tank (3), and a right end portion thereof is connected to the intermediate header section (24) of the third header tank (5). Left end portions of the heat exchange tubes (2) of the third heat exchange path (P3) are connected to the second header tank (4), and right end portions thereof are connected to the intermediate header section (24) of the third header tank (5). Left end portions of the heat exchange tubes (2) of the fourth heat exchange path (P4) are connected to the second header tank (4), and right end portions thereof are connected to the lower header section (25) of the third header tank (5).
The first header tank (3), a portion of the second header tank (4) to which the heat exchange tubes (2) of the third heat exchange path (P3) are connected, the upper and intermediate header sections (23) and (24) of the third header tank (5), and the first to third heat exchange paths (P1) to (P3) form a condensation section (20A), which condenses refrigerant. A portion of the second header tank (4) to which the heat exchange tubes (2) of the fourth heat exchange path (P4) are connected, the lower header section (25) of the third header tank (5), and the fourth heat exchange path (P4) form a super-cooling section (20B), which super-cools refrigerant. The first to third heat exchange paths (P1) to (P3) each serve as a refrigerant condensation path for condensing refrigerant, and the fourth heat exchange path (P4) serves as a refrigerant super-cooling path for super-cooling refrigerant.
A refrigerant inlet (26) is formed in the upper header section (23) of the third header tank (5), which constitutes the condensation section (20A), and a refrigerant outlet (27) is formed in the third header tank (5), which constitutes the super-cooling section (20B). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (26) is joined to the upper header section (23) of the third header tank (5), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (27) is joined to the lower header section (25) of the third header tank (5).
The remaining structure is similar to that of the condenser shown in
In the condenser (20) shown in
The refrigerant having flowed into the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the second header tank (4) because of gravitational force, and enters the heat exchange tubes (2) of the fourth heat exchange path (P4). The liquid-predominant mixed phase refrigerant having entered the heat exchange tubes (2) of the fourth heat exchange path (P4) is super-cooled while flowing rightward within the heat exchange tubes (2). After that, the super-cooled refrigerant enters the lower header section (25) of the third header tank (5), and flows out via the refrigerant outlet (27) and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the case of a condenser (30) shown in
Furthermore, a gas-liquid separation member (33) formed of aluminum is disposed within the second header tank (4) at a height between the third heat exchange path (P3) and the fourth heat exchange path (P4). The gas-liquid separation member (33) assumes a plate-like shape, and has a rectifying through hole (34) formed therein. The gas-liquid separation member (33) prevents the influence of agitating swirls, generated by the flow of the refrigerant flowing from the heat exchange tubes (2) of the third heat exchange path (P3) into the second header tank (4), from propagating to a portion of the interior of the second header tank (4) located below the gas-liquid separation member (33), to thereby cause the gas phase component of the gas-liquid mixed phase refrigerant to stay in the upper portion of the interior of the second header tank (4). As a result, only the liquid-predominant mixed phase refrigerant is fed to the portion of the interior of the second header tank (4) located below the gas-liquid separation member (33) via the rectifying through hole (34), whereby the liquid-predominant mixed phase refrigerant effectively flows into the heat exchange tubes (2) of the fourth heat exchange path (P4).
Furthermore, a desiccant (35) is disposed in a portion of the interior of the second header tank (4) located above the gas-liquid separation member (33). The desiccant (35) removes moisture from the refrigerant flowing into the second header tank (4) via the heat exchange tubes (2) of the third heat exchange path (P3). The desiccant (35) is placed in the tubular main body (31) after manufacture of the condenser (30) but before attachment of the lid (32) to the tubular main body (31).
The remaining structure is similar to that of the condenser (20) shown in
In the condenser (30) shown in
In the case of a condenser (50) shown in
Left and right end portions of the heat exchange tubes (2) which constitute the first heat exchange path (P1) are connected to the first header tank (3) and the third header tank (5), respectively, by means of brazing. Left and right end portions of the heat exchange tubes (2) which constitute the second through fourth heat exchange paths (P2), (P3), and (P4) are connected to the second header tank (4) and the third header tank (5), respectively, by means of brazing.
The interior of the second header tank (4) is divided into an upper header section (52) and a lower header section (53) by an aluminum partition plate (51) provided at a height between the third heat exchange path (P3) and the fourth heat exchange path (P4). The interior of the third header tank (5) is divided into an upper header section (55) and a lower header section (56) by an aluminum partition plates (54) provided at a height between the second heat exchange path (P2) and the third heat exchange path (P3). Left end portions of the heat exchange tubes (2) of the first heat exchange path (P1) are connected to the first header tank (3), and right end portions thereof are connected to the upper header section (55) of the third header tank (5). A left end portion of the second heat exchange path (P2) is connected to the upper header section (52) of the second header tank (4), and a right end portion thereof is connected to the upper header section (55) of the third header tank (5). Left end portions of the heat exchange tubes (2) of the third heat exchange path (P3) are connected to the upper header section (52) of the second header tank (4), and right end portions thereof are connected to the lower header section (56) of the third header tank (5). Left end portions of the heat exchange tubes (2) of the fourth heat exchange path (P4) are connected to the lower header section (53) of the second header tank (4), and right end portions thereof are connected to the lower header section (56) of the third header tank (5).
The first header tank (3), a portion of the second header tank (4) to which the heat exchange tubes (2) of the second heat exchange path (P2) are connected, the upper header section (55) of the third header tank (5), and the first and second heat exchange paths (P1) and (P2) form a condensation section (50A), which condenses refrigerant. A portion of the second header tank (4) to which the heat exchange tubes (2) of the third and fourth heat exchange paths (P3) and (P4) are connected, the lower header section (56) of the third header tank (5), and the third and fourth heat exchange paths (P3) and (P4) form a super-cooling section (50B), which super-cools refrigerant. The first and second heat exchange paths (P1) and (P2) each serve as a refrigerant condensation path for condensing refrigerant, and the third and fourth heat exchange paths (P3) and (P4) each serve as a refrigerant super-cooling path for super-cooling refrigerant.
A refrigerant inlet (57) is formed in an upper end portion of the first header tank (3), which constitutes the condensation section (50A), and a refrigerant outlet (58) is formed in the lower header section (53) of the second header tank (4), which constitutes the super-cooling section (1B). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (57) is joined to the first header tank (3), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (58) is joined to the second header tank (4).
The remaining structure is similar to that of the condenser shown in
In the condenser (1) shown in
The refrigerant having flowed into the upper header section (52) of the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the upper header section (52) of the second header tank (4) because of gravitational force, and enters the heat exchange tubes (2) of the third heat exchange path (P3). The liquid-predominant mixed phase refrigerant having entered the heat exchange tubes (2) of the third heat exchange path (P3) is super-cooled while flowing rightward within the heat exchange tubes (2), and flows into the lower header section (56) of the third header tank (5). The liquid-predominant mixed phase refrigerant having flowed into the lower header section (56) of the third header tank (5) is super-cooled while flowing leftward within the heat exchange tubes (2) of the fourth heat exchange path (P4). After that, the super-cooled refrigerant enters the lower header section (53) of the second header tank (4), and flows out via the refrigerant outlet (58) and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the upper header section (52) of the second header tank (4) stays in an upper region within the upper header section (52) of the second header tank (4).
In the case of a condenser (60) shown in
Left and right end portions of the heat exchange tubes (2) which constitute the first and second heat exchange paths (P1) and (P2) are connected to the first header tank (3) and the third header tank (5), respectively, by means of brazing. Left and right end portions of the heat exchange tubes (2) which constitute the third heat exchange path (P3) are connected to the second header tank (4) and the third header tank (5), respectively, by means of brazing.
The interior of the third header tank (5) is divided into an upper header section (62) and a lower header section (63) by an aluminum partition plate (61) provided at a height between the first heat exchange path (P1) and the second heat exchange path (P2). Left end portions of the heat exchange tubes (2) of the first heat exchange path (P1) are connected to the first header tank (3), and right end portions thereof are connected to the upper header section (62) of the third header tank (5). A left end portion of the second heat exchange path (P2) is connected to the first header tank (3), and a right end portion thereof is connected to the lower header section (63) of the third header tank (5). Left end portions of the heat exchange tubes (2) of the third heat exchange path (P3) are connected to the second header tank (4), and right end portions thereof are connected to the lower header section (63) of the third header tank (5).
The first to third header tank (3) to (5) and the first to third heat exchange paths (P1) to (P3) form a condensation section (60A), which condenses refrigerant. The first to third heat exchange paths (P1) to (P3); i.e., all the heat exchange paths, serve as a refrigerant condensation path for condensing refrigerant.
A refrigerant inlet (64) is formed in an upper end portion of the upper header section (62) of the third header tank (5), which constitutes the condensation section (60A), and a refrigerant outlet (65) is formed in a lower end portion of the second header tank (4). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (64) is joined to the upper header section (62) of the third header tank (5), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (65) is joined to the second header tank (4).
The remaining structure is similar to that of the condenser shown in
In the condenser (60) shown in
The refrigerant having flowed into the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the second header tank (4) because of gravitational force, and flows out via the refrigerant outlet (65) and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the case of a condenser (70) shown in
The first to fourth header tank (3), (4), (71), and (72) and the first to third heat exchange paths (P1) to (P3) form a condensation section (70A), which condenses refrigerant. The first to third heat exchange paths (P1) to (P3); i.e., all the heat exchange paths, serve as a refrigerant condensation path for condensing refrigerant.
A refrigerant inlet (73) is formed in an upper end portion of the third header tank (71), which constitutes the condensation section (70A), and a refrigerant outlet (65) is formed in a lower end portion of the second header tank (4). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (73) is joined to the third header tank (5), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (65) is joined to the second header tank (4).
The remaining structure is similar to that of the condenser shown in
In the condenser (1) shown in
The refrigerant having flowed into the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the second header tank (4) because of gravitational force, and flows out via the refrigerant outlet (65) and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the case of a condenser (80) shown in
The two heat exchange paths will be referred to as the first and second heat exchange paths (P1) and (P2) from the upper side. The flow direction of refrigerant is the same among all the heat exchange tubes (2) which constitute the respective heat exchange paths (P1) and (P2). The flow direction of refrigerant in the heat exchange tubes (2) which constitute one heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes (2) which constitute the other adjacent heat exchange path.
Left and right end portions of the heat exchange tubes (2) which constitute the first heat exchange path (P1) are connected to the first header tank (3) and the third header tank (5), respectively, by means of brazing. Left and right end portions of the heat exchange tubes (2) which constitute the second heat exchange path (P2) are connected to the second header tank (4) and the third header tank (5), respectively, by means of brazing.
The first to third header tank (3) to (5) and the first and second heat exchange paths (P1) and (P2) form a condensation section (80A), which condenses refrigerant. The first and second heat exchange paths (P1) and (P2); i.e., all the heat exchange paths, serve as a refrigerant condensation path for condensing refrigerant.
A refrigerant inlet (81) is formed in an upper end portion of the first header tank (5), which constitutes the condensation section (80A), and a refrigerant outlet (82) is formed in a lower end portion of the second header tank (4). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (81) is joined to the first header tank (5), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (82) is joined to the second header tank (4).
The remaining structure is similar to that of the condenser shown in
In the condenser (80) shown in
The refrigerant having flowed into the second header tank (4) is gas-liquid mixed phase refrigerant. A portion of the gas-liquid mixed phase refrigerant; i.e., liquid-predominant mixed phase refrigerant, stays in a lower region within the second header tank (4) because of gravitational force, and flows out via the refrigerant outlet (82) and the refrigerant outlet member. The refrigerant is then fed to the evaporator via the expansion valve.
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the case of a condenser (90) shown in
The two heat exchange paths will be referred to as the first and second heat exchange paths (P1) and (P2) from the lower side. The flow direction of refrigerant is the same among all the heat exchange tubes (2) which constitute the respective heat exchange paths (P1) and (P2). The flow direction of refrigerant in the heat exchange tubes (2) which constitute one heat exchange path is opposite the flow direction of refrigerant in the heat exchange tubes (2) which constitute the other adjacent heat exchange path.
The lower end of the second header tank (4) is located below the upper end of the first header tank (3), and the second header tank (4) has a gas-liquid separation function.
Left and right end portions of the heat exchange tubes (2) which constitute the first heat exchange path (P1) are connected to the first header tank (3) and the third header tank (5), respectively, by means of brazing. Left and right end portions of the heat exchange tubes (2) which constitute the second heat exchange path (P2) are connected to the second header tank (4) and the third header tank (5), respectively, by means of brazing.
The first to third header tank (3) to (5) and the first and second heat exchange paths (P1) and (P2) form a condensation section (90A), which condenses refrigerant. The first and second heat exchange paths (P1) and (P2); i.e., all the heat exchange paths, serve as a refrigerant condensation path for condensing refrigerant.
A refrigerant inlet (91) is formed in a lower end portion of the first header tank (5), which constitutes the condensation section (90A), and a refrigerant outlet (92) is formed in a lower end portion of the second header tank (4). A refrigerant inlet member (not shown) communicating with the refrigerant inlet (91) is joined to the first header tank (3), and a refrigerant outlet member (not shown) communicating with the refrigerant outlet (92) is joined to the second header tank (4).
The remaining structure is similar to that of the condenser shown in
In the condenser (90) shown in
Meanwhile, the gas phase component of the gas-liquid mixed phase refrigerant having flowed into the second header tank (4) stays in an upper region within the second header tank (4).
In the condenser (90) shown in
In
In
In
The condenser according to the present invention is suitably used in a car air conditioner mounted on an automobile.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2008-269505 | Oct 2008 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2009/068050 | 10/20/2009 | WO | 00 | 11/18/2010 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2010/047320 | 4/29/2010 | WO | A |
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|---|---|---|---|
| 2004390 | Benzinger | Jun 1935 | A |
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| 4972683 | Beatenbough | Nov 1990 | A |
| 4977956 | Aoki et al. | Dec 1990 | A |
| 5033539 | Kohtaka | Jul 1991 | A |
| 5168925 | Suzumura et al. | Dec 1992 | A |
| 5546761 | Matsuo et al. | Aug 1996 | A |
| 6810949 | Staffa et al. | Nov 2004 | B1 |
| 20020124593 | Yamazaki et al. | Sep 2002 | A1 |
| 20050217831 | Manaka | Oct 2005 | A1 |
| Number | Date | Country |
|---|---|---|
| 2747768 | Oct 1997 | FR |
| 3-31266 | Mar 1991 | JP |
| 11-316065 | Nov 1999 | JP |
| 2001-141332 | May 2001 | JP |
| 2002-286393 | Oct 2002 | JP |
| 2003-106708 | Apr 2003 | JP |
| 2005-106409 | Apr 2005 | JP |
| Entry |
|---|
| Machine translation of description of FR-2747768; retreived from www.espace.net on Mar. 2015. |
| International Search Report for International Application No. PCT/JP2009/068050 dated Dec. 8, 2009. |
| Written Opinion of the International Searching Authority for International Application No. PCT/JP2009/068050 dated Dec. 8, 2009. |
| Number | Date | Country | |
|---|---|---|---|
| 20110186277 A1 | Aug 2011 | US |
