EP1273858A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP1273858A1 EP1273858A1 EP01901438A EP01901438A EP1273858A1 EP 1273858 A1 EP1273858 A1 EP 1273858A1 EP 01901438 A EP01901438 A EP 01901438A EP 01901438 A EP01901438 A EP 01901438A EP 1273858 A1 EP1273858 A1 EP 1273858A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- along
- ventilating direction
- upstream side
- tubes
- ventilating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/003—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing corrosion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/14—Collecting or removing condensed and defrost water; Drip trays
Definitions
- the present invention relates to a heat exchanger which may be utilized as, for instance, an evaporator in an air-conditioning system or the like for vehicles and, more specifically, it relates to a structure adopted in the fins of the heat exchanger.
- An evaporator in the refrigerating cycle of an air-conditioning system for vehicles normally adopts a structure achieved by laminating tubes each having therein a coolant passage over a plurality of stages, providing a pair of tanks on the two sides along the lengthwise direction of the tubes to communicate with the coolant passages of the tubes and providing corrugated fins between the individual tubes so as to improve the heat exchanging efficiency, as disclosed in, for instance, Japanese Unexamined Patent Publication No. H 7-190661 or Japanese Unexamined Patent Publication No. H 8-17836.
- the moisture in the air becomes condensed and condensed water is left on the surfaces of the tubes and fins while the tubes are cooled by the coolant which becomes evaporated as it flows through the tubes and the air passing between the tubes is cooled via the tubes and the fins. Then, the condensed water is spattered from the cooling heat exchanger due to the current of air from the air blower provided on the upstream side along the ventilating direction, which causes a problem of the condensed water moving into the cabin.
- a mesh filter or the like is normally provided on the upstream side of the heat exchanger along the ventilating direction to remove dirt mixed in the air taken in from the inside or the outside of the cabin, such a filter may be omitted in order to reduce production costs.
- dirt moistened by the condensed water becomes adhered to the tubes and the presence of the moist dirt causes corrosion of the tubes.
- an object of the present invention is to provide a heat exchanger that is capable of draining condensed water from the surfaces of the tubes and fins alone the downward direction with a high degree of efficiency and preventing corrosion at the tubes caused by dirt adhering to the upstream side of the tubes along the ventilating direction from advancing while achieving a lower profile along the ventilating direction and can be utilized as an evaporator.
- a heat exchanger comprises, at least, tubes each having therein a heat exchanging medium passage, fins laminated alternately between the tubes and a tank provided at the ends of the tubes on at least one side, with the upstream side ends of the fins along the ventilating direction projecting further toward the upstream side along the ventilating direction relative to the upstream side ends of the tubes along the ventilating direction within a range in which the upstream side ends of the fins do not project beyond the upstream end face of the tank along the ventilating direction and the downstream side ends of the fins along the ventilating direction recessed toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes along the ventilating direction.
- This structure achieved by projecting in the upstream side ends of the fins along the ventilating direction further toward the upstream side along the ventilating direction relative to the upstream side ends of the tubes along the ventilating direction, does not readily allow dirt to reach the tubes provided at positions that are recessed toward the downstream side along the ventilating direction relative to the fins and thus, the risk of corrosion occurring at the tubes due to adhering dirt is reduced.
- the upstream side ends of the fins along the ventilating direction do not project out further than the end face of the tank along the ventilating direction, the overall width of the heat exchanger along the ventilating direction does not increase, thereby making it possible to save space.
- downstream side ends of the fins along the ventilating direction are recessed toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes along the ventilating direction.
- the heat exchanger according to the present invention may comprise, at least, a plurality of tubes set in parallel to one another along the ventilating direction, which each include therein a heat exchanging medium passage, a plurality of fins set in parallel to one another along the ventilating direction and laminated alternately between the tubes with the quantity thereof made to correspond to the quantity of the tubes and a tank provided at the ends of the tubes on at least one side, with the upstream side end along the ventilating direction of a fin set on the side furthest upstream along the ventilating direction projecting out further toward the upstream side along the ventilating direction relative to the upstream side end along the ventilating direction of a tube set on the side furthest upstream along the ventilating direction within a range in which the upstream side end of the fin does not project beyond the upstream side end face of the tank along the ventilating direction and the downstream side end along the ventilating direction of a fin set on the side furthest downstream along the ventilating direction recessed further toward the upstream side along the ventilating direction relative to the downstream side
- the upstream side end along the ventilating direction of a fin which is not the fin set on the side furthest upstream along the ventilating direction, too, is made to project out further toward the upstream side along the ventilating direction relative to the upstream side end along the ventilating direction of the tube facing opposite the fin along the laminating direction within the range in which the upstream side end of the fin does not come in contact with the fin set further on the upstream side along the ventilating direction.
- the downstream side end along the ventilating direction of a fin which is not set on the side furthest downstream along the ventilating direction, too is recessed further toward the upstream side along the ventilating direction relative to the downstream side end along the ventilating direction of each of tubes set in parallel to one another.
- This structure achieved by projecting the upstream side end along the ventilating direction of the fin set on the side furthest upstream along the ventilating direction further toward the upstream side along the ventilating direction relative to the upstream side end along the ventilating direction of the tube set on the side furthest upstream along the ventilating direction, does not readily allow dirt to reach the tube set at a position which is moved back further toward the upstream side along the ventilating direction relative to the fin so as to prevent the tube from becoming corroded due to dirt adhering thereto.
- the upstream side end of the fin along ventilating direction does not project beyond the end face of the tank along the ventilating direction, the overall width of the heat exchanger along the ventilating direction does not increase, thereby meeting the space-saving requirement.
- the fins are provided in parallel to one another along the ventilating direction and, at the same time, the downstream side ends along the ventilating direction of the fins provided on the upstream side along the ventilating direction are recessed further toward the upstream side along the ventilating direction to form a gap from the fins on the downstream side along the ventilating direction so that condensed water manifesting along the upstream side along the ventilating direction is made to drop downward through the gap to drain the condensed water with an even higher degree of efficiency.
- the upstream side ends along the ventilating direction of the fins are made to project out toward the upstream side along the ventilating direction by an extent greater than the extent by which the downstream side ends along the ventilating direction are recessed toward the upstream side along the ventilating direction.
- This structure in which the width of the fins along the ventilating direction is set greater than the width along the ventilating direction of the tubes facing opposite the fins along the laminating direction, allows the heat exchange with the air passing through the heat exchanger to be carried out with a higher degree of efficiency so as to improve the performance of the heat exchanger.
- the tubes constituting the heat exchanger are each formed by bending a single brazing sheet with a junction formed by joining ends of the brazing sheet on the upstream side along the ventilating direction.
- the junction adopts a structure achieved by tightly winding the portion of the brazing sheet near one of the ends.
- the wall thickness of the tubes on the upstream side along the ventilating direction is increased through the tightly-wound structure.
- the resistance against such corrosion is improved at the tubes themselves to lengthen the durability of the tubes.
- An evaporator 1 shown in FIGS. 1 and 2 is a laminated heat exchanger having tanks on the two sides thereof, which may be utilized in, for instance, the refrigerating cycle of an air-conditioning system for vehicles.
- the evaporator 1 is a two-path heat exchanger comprising a tank 2 provided at one end along its lengthwise direction, a tank 3 provided at an end on the opposite side from the tank 2, tubes 14 and 15 connected with the tank 2 and the tank 3 to communicate between the tank 2 and the tank 3, fins 16 laminated alternately over a plurality of stages between the tubes 14 and between the tubes 15 and end plates 17 and 17, each provided on either side along the laminating direction.
- the tanks 2 and 3 are each constituted of an aluminum alloy cylindrical body 5 having connection holes 4 at which the tubes 14 and 15 are connected with the tank and blocking members 6 to be detailed below with the cylindrical body 5 formed as an integrated unit through extrusion molding.
- This structure prevents leakage of the heat exchanging medium through a gap at a side of the tank formed due to incomplete bonding of a deep-drawn tank member and a blocking member in a tank in the related art constituted of the deep-drawn tank member roughly formed in a bowl shape with one end thereof left open and the blocking member blocking off the opening.
- problems such as freezing rupture caused by condensed water entering an area of the junction where the members are not completely brazed and thus where pinholes and the like are formed, can be avoided as well.
- the tank 2 is a turn-around tank having the openings on the two sides thereof each blocked with a blocking plate 6, which allows the heat exchanging medium to turn around
- the tank 3 is an intake/outlet tank that includes an intake portion 8 and an outlet portion 9 completely isolated from each other by a barrier plate 7 extending at the center within the cylindrical body 5 along the direction in which the tubes 14 and 15 are laminated, with the openings at the intake portion 8 and the outlet portion 9 on each side blocked by inserting two blocking plates 6 through mounting holes 11 formed in the cylindrical body 5.
- an intake pipe 12 is connected continuous to an end of the intake portion 8 and an outlet pipe is connected continuous to an end of the outlet portion 9.
- a sacrificial layer is formed at the surfaces of the tanks 2 and 3 by thermal-spraying zinc (Zn) onto the surfaces or by forming a layer containing zinc on the surfaces which are extruded through two-layer extrusion, so as to improve anticorrosion performance.
- the tubes 14 and 15 are each formed by bending a single brazing sheet over a plurality of stages through roll-forming or press-machining, and each tube 14 or 15 includes a heat exchanging medium passage 20 enclosed by a pair of flat surfaces 18 and 18 extending along the ventilating direction and a flat surface 19 located on the downstream side along the ventilating direction and extending along the laminating direction.
- a tightly-wound structure is achieved by tightly winding the portion of the brazing sheet near one end, thereby forming a tightly-wound portion 21 and by forming a contact portion 22 at the other end of the brazing sheet to come into contact with the base end of the tightly-wound portion 21 and a blocking portion 23 continuous to the contact portion 22 to close the downstream side opening of the heat exchanging medium passage 20.
- the wall thickness of the tubes 14 and 15 on the upstream side along the ventilating direction is increased.
- the resistance against corrosion occurring as a result of particles of dirt or the like traveling from the upstream side along the ventilating direction and becoming adhered to the tubes can be improved to increase the durability of the tubes 14 and 15.
- inner fins 24 are housed inside the individual heat exchanging medium passages 20 as shown in FIG. 2 so as to improve the mixability of the heat exchanging medium in the embodiment, a plurality of beads may also be formed on the inside of the surfaces extending perpendicular to the ventilating direction (not shown) as well for the same purposes.
- the tubes 14 and 15 may instead each be formed through extrusion molding or they may each be formed by bonding face-to-face two formed plates to each other, and tubes formed through extrusion molding may each include a plurality of heat exchanging medium passages.
- the fins 16 provided between the tubes 14 and 14 and between the tubes 15 and 15, or between the tubes 14, 15 and the end plates 17 are each formed as a single-piece corrugated fin in this embodiment.
- the upstream side ends of the fins are made to project out further toward the upstream side along the ventilating direction relative to the upstream side ends of the tubes 14 along the ventilating direction by a specific extent a in alignment with the end face of the tank 3 along the ventilating direction (in alignment with the end of the tank 2 as well although not shown).
- the downstream side ends of the fins 16 along the ventilating direction are recessed further toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes 15 along the ventilating direction by a specific extent b, as shown in FIG. 2.
- the measurement of the specific extent a by which the fins 16 project out is set larger than the measurement of the specific extent b by which the fins 16 are recessed and, as a result, the dimension of the fins 16 along the ventilating direction is larger than the dimension between the downstream side end of a tube 14 along the ventilating direction and the upstream side end of the corresponding tube 15 along the ventilating direction.
- the upstream side end surfaces of the tubes 14 along the ventilating direction are set at positions recessed relative to the fins 16 along the ventilating direction and thus, even if no air filter is provided on the upstream side of the evaporator 1 along the ventilating direction, any dirt present in the air taken in from the inside and the outside of the cabin is captured at the fins 16 and is not allowed to reach the tubes 14 readily, thereby making it possible to protect the tubes 14 from corrosion caused by dirt adhered thereto.
- the width of the evaporator 1 along the ventilating direction does not increase compared to the width of evaporators in the related art, in keeping with the space-saving requirement which necessitates the size of the evaporator 1 to be kept as small as possible.
- downstream side ends of the fins 16 along the ventilating direction are recessed further toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes 15 along the ventilating direction, condensed water having been caused by the air pressure to move over the tubes 15 or the fins 16 to the downstream side along the ventilating direction is allowed to drop downward from the evaporator along the surfaces of the tubes 15.
- the dimension of the fins taken along the ventilating direction is greater than the dimension of fins 16 in the prior art, the efficiency with which heat is exchanged with the passing air improves as well.
- the present invention is not limited to the example described above in which a single fin unit 16 is provided between the tubes and instead, a plurality of fins may be provided parallel to one another along the ventilating direction between the tubes.
- a plurality of fins may be provided parallel to one another along the ventilating direction between the tubes.
- the upstream side ends along the ventilating direction of the fins 16 set on the upstream side along the ventilating direction project out further toward the upstream side along the ventilating direction relative to the upstream side ends of the tubes 14 along the ventilating direction by a predetermined extent a without projecting beyond the end face of the tank 3 along the ventilating direction at the most (also without projecting beyond the end face of the tank 2 along the ventilating direction, although not shown) in the embodiment.
- the upstream side ends along the ventilating direction of the fins 16 set on the downstream side along the ventilating direction project out further toward the upstream side along the ventilating direction relative to the upstream side ends of the tubes 15 along the ventilating direction without reaching the downstream side ends of the tubes 14 along the ventilating direction. It is to be noted that the extent by which the fins 16 on the downstream side along the ventilating direction project out relative to the tubes 15 should be set equal to the extent a by which the fins on the upstream side along the ventilating direction project out relative to the tubes 14.
- downstream side ends along the ventilating direction of the fins 16 located on the downstream side along the ventilating direction are recessed by a specific extent b toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes 15 along the ventilating direction.
- downstream side ends along the ventilating direction of the fins 16 on the upstream side along the ventilating direction are recessed further toward the upstream side along the ventilating direction relative to the downstream side ends of the fins 14 along the ventilating direction.
- the extent by which the fins 16 on the downstream side along the ventilating direction are recessed relative to the downstream side ends of the tubes 15 along the ventilating direction be equal to the extent b by which the fins on the upstream side along the ventilating direction are recessed relative to the downstream side ends of the tubes 14 along the ventilating direction.
- the upstream side end faces of the tubes 14 along the ventilating direction are set at positions recessed relative to the fins 16 on the upstream side along the ventilating direction and thus, even if no air filter is provided on the upstream side of the evaporator 1 along the ventilating direction, any dirt present in the air taken in from the inside and the outside of the cabin is captured at the fins 16 and is not allowed to reach the tubes 14 readily, thereby making it possible to protect the tubes 14 from corrosion caused by dirt adhered thereto.
- the width of the evaporator 1 along the ventilating direction does not increase compared to the width of evaporators in the related art, in keeping with the space-saving requirement which necessitates the size of the evaporator 1 to be kept as small as possible.
- the downstream side ends along the ventilating direction of the fins 16 provided on the upstream side along the ventilating direction are recessed further toward the upstream side along the ventilating direction to form a desirable gap from the fins 16 on the downstream side along the ventilating direction so that condensed water having been caused by the air pressure to move over the surfaces of the fins 16 on the upstream side along the ventilating direction is allowed to drop downward through the gap to reliably drain the condensed water.
- downstream side ends of the fins along the ventilating direction are recessed toward the upstream side along the ventilating direction relative to the downstream side ends of the tubes along the ventilating direction, condensed water having been caused by the air pressure to move over the tubes or the fins to the downstream side along the ventilating direction can be drained in a downward direction along the surfaces of the tubes located further toward the downstream side relative to the fins to minimize the occurrence of spattering of the condensed water onto the downstream side along the ventilating direction.
- the downstream side ends along the ventilating direction of the fins provided on the upstream side along the ventilating direction are recessed further toward the upstream side along the ventilating direction to form a desirable gap from the fins provided on the downstream side along the ventilating direction so that condensed water having been caused by the air pressure to move over the surfaces of the fins on the upstream side along the ventilating direction is allowed to drop downward through the gap to reliably drain the condensed water.
- the width of the fins along the ventilating direction is greater than the width along the ventilating direction of the tubes facing opposite the fins along the laminating direction.
- the wall thickness of the tubes on the upstream side along the ventilating direction is increased by adopting a tightly-wound structure and thus, even if corrosion occurs due to dirt escaping the fins projecting out along the ventilating direction and reaching the tubes to become adhered thereto, the resistance against such corrosion is improved to lengthen the durability of the tubes.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
The upstream side ends of fins (16) along the ventilating direction
project out relative to the upstream side ends along the ventilating
direction of tubes (14) without being allowed to project out beyond the
end faces of tanks (2) and (3) along the ventilating direction so as to set
the tubes (14) at positions recessed toward the downstream side along the
ventilating direction relative to the fins (16), and the downstream side
ends of the fins (16) along the ventilating direction are recessed further
toward the upstream side along the ventilating direction relative to the
downstream side ends of tubes (15) along the ventilating direction. As a
result, the evaporator achieves a lower profile along the ventilating
direction and, at the same time, condensed water manifesting at the
surfaces of the tubes and fins is drained downward with a high degree of
efficiency, thereby minimizing occurrence of spattering of the condensed
water onto the downstream side and also, it becomes possible to prevent
corrosion from advancing at the tubes due to dirt adhering onto the
upstream side of the tubes along the ventilating direction.
Description
The present invention relates to a heat exchanger which may be
utilized as, for instance, an evaporator in an air-conditioning system or
the like for vehicles and, more specifically, it relates to a structure
adopted in the fins of the heat exchanger.
An evaporator in the refrigerating cycle of an air-conditioning
system for vehicles normally adopts a structure achieved by laminating
tubes each having therein a coolant passage over a plurality of stages,
providing a pair of tanks on the two sides along the lengthwise direction
of the tubes to communicate with the coolant passages of the tubes and
providing corrugated fins between the individual tubes so as to improve
the heat exchanging efficiency, as disclosed in, for instance, Japanese
Unexamined Patent Publication No. H 7-190661 or Japanese Unexamined
Patent Publication No. H 8-17836.
In a heat exchanger adopting such a structure, the moisture in the
air becomes condensed and condensed water is left on the surfaces of the
tubes and fins while the tubes are cooled by the coolant which becomes
evaporated as it flows through the tubes and the air passing between the
tubes is cooled via the tubes and the fins. Then, the condensed water is
spattered from the cooling heat exchanger due to the current of air from
the air blower provided on the upstream side along the ventilating
direction, which causes a problem of the condensed water moving into the
cabin.
In addition, while a mesh filter or the like is normally provided on
the upstream side of the heat exchanger along the ventilating direction to
remove dirt mixed in the air taken in from the inside or the outside of the
cabin, such a filter may be omitted in order to reduce production costs. In
such a case, dirt moistened by the condensed water becomes adhered to
the tubes and the presence of the moist dirt causes corrosion of the tubes.
At the same time, it is becoming increasingly important in recent
years to improve the function of on-vehicle air-conditioning systems and
to achieve further miniaturization and a further reduction in weight in
order to effectively address issues such as environmental protection. For
this reason, the evaporator constituting part of the refrigerating cycle in
an air-conditioning system, too, must achieve a lower profile along the
ventilating direction in the vehicle layout.
Accordingly, an object of the present invention is to provide a heat
exchanger that is capable of draining condensed water from the surfaces
of the tubes and fins alone the downward direction with a high degree of
efficiency and preventing corrosion at the tubes caused by dirt adhering to
the upstream side of the tubes along the ventilating direction from
advancing while achieving a lower profile along the ventilating direction
and can be utilized as an evaporator.
In order to achieve the object described above, a heat exchanger
according to the present invention comprises, at least, tubes each having
therein a heat exchanging medium passage, fins laminated alternately
between the tubes and a tank provided at the ends of the tubes on at least
one side, with the upstream side ends of the fins along the ventilating
direction projecting further toward the upstream side along the ventilating
direction relative to the upstream side ends of the tubes along the
ventilating direction within a range in which the upstream side ends of the
fins do not project beyond the upstream end face of the tank along the
ventilating direction and the downstream side ends of the fins along the
ventilating direction recessed toward the upstream side along the
ventilating direction relative to the downstream side ends of the tubes
along the ventilating direction.
This structure, achieved by projecting in the upstream side ends of
the fins along the ventilating direction further toward the upstream side
along the ventilating direction relative to the upstream side ends of the
tubes along the ventilating direction, does not readily allow dirt to reach
the tubes provided at positions that are recessed toward the downstream
side along the ventilating direction relative to the fins and thus, the risk of
corrosion occurring at the tubes due to adhering dirt is reduced. In
addition, since the upstream side ends of the fins along the ventilating
direction do not project out further than the end face of the tank along the
ventilating direction, the overall width of the heat exchanger along the
ventilating direction does not increase, thereby making it possible to save
space. Furthermore, the downstream side ends of the fins along the
ventilating direction are recessed toward the upstream side along the
ventilating direction relative to the downstream side ends of the tubes
along the ventilating direction. Thus, the condensed water having been
caused to travel over the tubes or the fins to the downstream side along
the ventilating direction by the air pressure is allowed to drop downward
along the surfaces of the tubes located further toward the downstream
side relative to the fins and spattering of the condensed water toward the
downstream side is minimized.
Alternatively, the heat exchanger according to the present
invention may comprise, at least, a plurality of tubes set in parallel to one
another along the ventilating direction, which each include therein a heat
exchanging medium passage, a plurality of fins set in parallel to one
another along the ventilating direction and laminated alternately between
the tubes with the quantity thereof made to correspond to the quantity of
the tubes and a tank provided at the ends of the tubes on at least one side,
with the upstream side end along the ventilating direction of a fin set on
the side furthest upstream along the ventilating direction projecting out
further toward the upstream side along the ventilating direction relative to
the upstream side end along the ventilating direction of a tube set on the
side furthest upstream along the ventilating direction within a range in
which the upstream side end of the fin does not project beyond the
upstream side end face of the tank along the ventilating direction and the
downstream side end along the ventilating direction of a fin set on the
side furthest downstream along the ventilating direction recessed further
toward the upstream side along the ventilating direction relative to the
downstream side end along the ventilating direction of the tube set on the
side furthest downstream along the ventilating direction. The upstream
side end along the ventilating direction of a fin which is not the fin set on
the side furthest upstream along the ventilating direction, too, is made to
project out further toward the upstream side along the ventilating
direction relative to the upstream side end along the ventilating direction
of the tube facing opposite the fin along the laminating direction within
the range in which the upstream side end of the fin does not come in
contact with the fin set further on the upstream side along the ventilating
direction. In addition, the downstream side end along the ventilating
direction of a fin which is not set on the side furthest downstream along
the ventilating direction, too, is recessed further toward the upstream side
along the ventilating direction relative to the downstream side end along
the ventilating direction of each of tubes set in parallel to one another.
This structure, achieved by projecting the upstream side end along
the ventilating direction of the fin set on the side furthest upstream along
the ventilating direction further toward the upstream side along the
ventilating direction relative to the upstream side end along the
ventilating direction of the tube set on the side furthest upstream along
the ventilating direction, does not readily allow dirt to reach the tube set
at a position which is moved back further toward the upstream side along
the ventilating direction relative to the fin so as to prevent the tube from
becoming corroded due to dirt adhering thereto. In addition, since the
upstream side end of the fin along ventilating direction does not project
beyond the end face of the tank along the ventilating direction, the overall
width of the heat exchanger along the ventilating direction does not
increase, thereby meeting the space-saving requirement.
While condensation of water mainly occurs on the upstream side
of the heat exchanger along the ventilating direction, the fins are provided
in parallel to one another along the ventilating direction and, at the same
time, the downstream side ends along the ventilating direction of the fins
provided on the upstream side along the ventilating direction are recessed
further toward the upstream side along the ventilating direction to form a
gap from the fins on the downstream side along the ventilating direction
so that condensed water manifesting along the upstream side along the
ventilating direction is made to drop downward through the gap to drain
the condensed water with an even higher degree of efficiency. Thus, it
becomes possible to prevent the condensed water from moving onto the
fins on the downstream side along the ventilating direction and to prevent
the condensed water from becoming spattered onto the downstream side
as well.
In addition, the upstream side ends along the ventilating direction
of the fins are made to project out toward the upstream side along the
ventilating direction by an extent greater than the extent by which the
downstream side ends along the ventilating direction are recessed toward
the upstream side along the ventilating direction.
This structure, in which the width of the fins along the ventilating
direction is set greater than the width along the ventilating direction of the
tubes facing opposite the fins along the laminating direction, allows the
heat exchange with the air passing through the heat exchanger to be
carried out with a higher degree of efficiency so as to improve the
performance of the heat exchanger.
Furthermore, the tubes constituting the heat exchanger are each
formed by bending a single brazing sheet with a junction formed by
joining ends of the brazing sheet on the upstream side along the
ventilating direction. The junction adopts a structure achieved by tightly
winding the portion of the brazing sheet near one of the ends.
With the tubes taking on the structural features and the positional
arrangement described above, the wall thickness of the tubes on the
upstream side along the ventilating direction is increased through the
tightly-wound structure. As a result, even if corrosion occurs at the tubes
due to dirt escaping the fins projecting along the ventilating direction and
becoming adhered to the tubes, the resistance against such corrosion is
improved at the tubes themselves to lengthen the durability of the tubes.
The present invention is described in further detail in the following
explanation given in reference to the attached drawings.
An evaporator 1 shown in FIGS. 1 and 2 is a laminated heat
exchanger having tanks on the two sides thereof, which may be utilized
in, for instance, the refrigerating cycle of an air-conditioning system for
vehicles. The evaporator 1 is a two-path heat exchanger comprising a tank
2 provided at one end along its lengthwise direction, a tank 3 provided at
an end on the opposite side from the tank 2, tubes 14 and 15 connected
with the tank 2 and the tank 3 to communicate between the tank 2 and the
tank 3, fins 16 laminated alternately over a plurality of stages between the
tubes 14 and between the tubes 15 and end plates 17 and 17, each
provided on either side along the laminating direction.
The tanks 2 and 3 are each constituted of an aluminum alloy
cylindrical body 5 having connection holes 4 at which the tubes 14 and 15
are connected with the tank and blocking members 6 to be detailed below
with the cylindrical body 5 formed as an integrated unit through extrusion
molding.
This structure prevents leakage of the heat exchanging medium
through a gap at a side of the tank formed due to incomplete bonding of a
deep-drawn tank member and a blocking member in a tank in the related
art constituted of the deep-drawn tank member roughly formed in a bowl
shape with one end thereof left open and the blocking member blocking
off the opening. In addition, problems such as freezing rupture caused by
condensed water entering an area of the junction where the members are
not completely brazed and thus where pinholes and the like are formed,
can be avoided as well.
While the tank 2 is a turn-around tank having the openings on the
two sides thereof each blocked with a blocking plate 6, which allows the
heat exchanging medium to turn around, the tank 3 is an intake/outlet
tank that includes an intake portion 8 and an outlet portion 9 completely
isolated from each other by a barrier plate 7 extending at the center within
the cylindrical body 5 along the direction in which the tubes 14 and 15
are laminated, with the openings at the intake portion 8 and the outlet
portion 9 on each side blocked by inserting two blocking plates 6 through
mounting holes 11 formed in the cylindrical body 5.
The barrier plate 7 at the tank 3, formed as an integrated part of
the cylindrical body 5 through extrusion molding, prevents any
deterioration in the performance of the evaporator 1, which may
otherwise be caused by the heat exchanging medium allowed to directly
travel between the intake portion and the outlet portion through a gap
created due to incomplete bonding of a barrier plate constituted as a
separate member and the tank internal circumferential surface. In
addition, an intake pipe 12 is connected continuous to an end of the intake
portion 8 and an outlet pipe is connected continuous to an end of the
outlet portion 9.
It is to be noted that since the evaporator 1 is operated in an
environment in which it is in contact with water at all times, a sacrificial
layer is formed at the surfaces of the tanks 2 and 3 by thermal-spraying
zinc (Zn) onto the surfaces or by forming a layer containing zinc on the
surfaces which are extruded through two-layer extrusion, so as to improve
anticorrosion performance.
As shown in FIG. 2, the tubes 14 and 15 are each formed by
bending a single brazing sheet over a plurality of stages through roll-forming
or press-machining, and each tube 14 or 15 includes a heat
exchanging medium passage 20 enclosed by a pair of flat surfaces 18 and
18 extending along the ventilating direction and a flat surface 19 located
on the downstream side along the ventilating direction and extending
along the laminating direction. In addition, on the upstream side along the
ventilating direction of each of the tubes 14 and 15, a tightly-wound
structure is achieved by tightly winding the portion of the brazing sheet
near one end, thereby forming a tightly-wound portion 21 and by forming
a contact portion 22 at the other end of the brazing sheet to come into
contact with the base end of the tightly-wound portion 21 and a blocking
portion 23 continuous to the contact portion 22 to close the downstream
side opening of the heat exchanging medium passage 20.
By setting the tubes 14 and 15 parallel to each other so as to place
the tightly-wound portions 21, the contact portions 22 and the blocking
portions 23 each set thereof constituting the tightly-wound structure on
the upstream side along the ventilating direction, the wall thickness of the
tubes 14 and 15 on the upstream side along the ventilating direction is
increased. As a result, the resistance against corrosion occurring as a
result of particles of dirt or the like traveling from the upstream side
along the ventilating direction and becoming adhered to the tubes can be
improved to increase the durability of the tubes 14 and 15.
It is to be noted that while inner fins 24 are housed inside the
individual heat exchanging medium passages 20 as shown in FIG. 2 so as
to improve the mixability of the heat exchanging medium in the
embodiment, a plurality of beads may also be formed on the inside of the
surfaces extending perpendicular to the ventilating direction (not shown)
as well for the same purposes. Furthermore, the tubes 14 and 15 may
instead each be formed through extrusion molding or they may each be
formed by bonding face-to-face two formed plates to each other, and
tubes formed through extrusion molding may each include a plurality of
heat exchanging medium passages.
The fins 16 provided between the tubes 14 and 14 and between the
tubes 15 and 15, or between the tubes 14, 15 and the end plates 17 are
each formed as a single-piece corrugated fin in this embodiment. The
upstream side ends of the fins are made to project out further toward the
upstream side along the ventilating direction relative to the upstream side
ends of the tubes 14 along the ventilating direction by a specific extent a
in alignment with the end face of the tank 3 along the ventilating direction
(in alignment with the end of the tank 2 as well although not shown). The
downstream side ends of the fins 16 along the ventilating direction are
recessed further toward the upstream side along the ventilating direction
relative to the downstream side ends of the tubes 15 along the ventilating
direction by a specific extent b, as shown in FIG. 2.
The measurement of the specific extent a by which the fins 16
project out is set larger than the measurement of the specific extent b by
which the fins 16 are recessed and, as a result, the dimension of the fins
16 along the ventilating direction is larger than the dimension between the
downstream side end of a tube 14 along the ventilating direction and the
upstream side end of the corresponding tube 15 along the ventilating
direction.
By adopting this structure in the fins 16, the upstream side end
surfaces of the tubes 14 along the ventilating direction are set at positions
recessed relative to the fins 16 along the ventilating direction and thus,
even if no air filter is provided on the upstream side of the evaporator 1
along the ventilating direction, any dirt present in the air taken in from the
inside and the outside of the cabin is captured at the fins 16 and is not
allowed to reach the tubes 14 readily, thereby making it possible to
protect the tubes 14 from corrosion caused by dirt adhered thereto.
Furthermore, since the fins 16 are only allowed to project out on the
upstream side along the ventilating direction to the upstream side end
faces of the tanks 2 and 3 along the ventilating direction at the most, the
width of the evaporator 1 along the ventilating direction does not increase
compared to the width of evaporators in the related art, in keeping with
the space-saving requirement which necessitates the size of the
evaporator 1 to be kept as small as possible.
In addition, since the downstream side ends of the fins 16 along
the ventilating direction are recessed further toward the upstream side
along the ventilating direction relative to the downstream side ends of the
tubes 15 along the ventilating direction, condensed water having been
caused by the air pressure to move over the tubes 15 or the fins 16 to the
downstream side along the ventilating direction is allowed to drop
downward from the evaporator along the surfaces of the tubes 15.
Furthermore, since the dimension of the fins taken along the ventilating
direction is greater than the dimension of fins 16 in the prior art, the
efficiency with which heat is exchanged with the passing air improves as
well.
However, the present invention is not limited to the example
described above in which a single fin unit 16 is provided between the
tubes and instead, a plurality of fins may be provided parallel to one
another along the ventilating direction between the tubes. Now, in
reference to FIGS. 3 and 4, an embodiment achieved by providing two
fins 16 parallel to each other along the ventilating direction is explained.
The same reference numerals are assigned to structural features identical
to those in the embodiment shown in FIGS. 1 and 2 to preclude the
necessity for a repeated explanation thereof.
As in the case with the fins 16 in the previous embodiment, the
upstream side ends along the ventilating direction of the fins 16 set on the
upstream side along the ventilating direction project out further toward
the upstream side along the ventilating direction relative to the upstream
side ends of the tubes 14 along the ventilating direction by a
predetermined extent a without projecting beyond the end face of the tank
3 along the ventilating direction at the most (also without projecting
beyond the end face of the tank 2 along the ventilating direction, although
not shown) in the embodiment. Also, the upstream side ends along the
ventilating direction of the fins 16 set on the downstream side along the
ventilating direction project out further toward the upstream side along
the ventilating direction relative to the upstream side ends of the tubes 15
along the ventilating direction without reaching the downstream side ends
of the tubes 14 along the ventilating direction. It is to be noted that the
extent by which the fins 16 on the downstream side along the ventilating
direction project out relative to the tubes 15 should be set equal to the
extent a by which the fins on the upstream side along the ventilating
direction project out relative to the tubes 14.
In addition, as in the case with the fans 16 in the previous
embodiment, the downstream side ends along the ventilating direction of
the fins 16 located on the downstream side along the ventilating direction
are recessed by a specific extent b toward the upstream side along the
ventilating direction relative to the downstream side ends of the tubes 15
along the ventilating direction. Also, the downstream side ends along the
ventilating direction of the fins 16 on the upstream side along the
ventilating direction are recessed further toward the upstream side along
the ventilating direction relative to the downstream side ends of the fins
14 along the ventilating direction. It is desirable that the extent by which
the fins 16 on the downstream side along the ventilating direction are
recessed relative to the downstream side ends of the tubes 15 along the
ventilating direction be equal to the extent b by which the fins on the
upstream side along the ventilating direction are recessed relative to the
downstream side ends of the tubes 14 along the ventilating direction.
By adopting the structure described above achieved by providing a
plurality of fins 16 parallel to one another, the upstream side end faces of
the tubes 14 along the ventilating direction are set at positions recessed
relative to the fins 16 on the upstream side along the ventilating direction
and thus, even if no air filter is provided on the upstream side of the
evaporator 1 along the ventilating direction, any dirt present in the air
taken in from the inside and the outside of the cabin is captured at the fins
16 and is not allowed to reach the tubes 14 readily, thereby making it
possible to protect the tubes 14 from corrosion caused by dirt adhered
thereto. Furthermore, since the fins 16 are only allowed to project out on
the upstream side along the ventilating direction to the upstream side end
faces of the tanks 2 and 3 along the ventilating direction at the most, the
width of the evaporator 1 along the ventilating direction does not increase
compared to the width of evaporators in the related art, in keeping with
the space-saving requirement which necessitates the size of the
evaporator 1 to be kept as small as possible.
Moreover, while condensation of water occurs on the upstream
side of the evaporator 1 along the ventilating direction, the downstream
side ends along the ventilating direction of the fins 16 provided on the
upstream side along the ventilating direction are recessed further toward
the upstream side along the ventilating direction to form a desirable gap
from the fins 16 on the downstream side along the ventilating direction so
that condensed water having been caused by the air pressure to move over
the surfaces of the fins 16 on the upstream side along the ventilating
direction is allowed to drop downward through the gap to reliably drain
the condensed water. Thus, it becomes possible to prevent the condensed
water from moving onto the fins 16 on the downstream side along the
ventilating direction and to prevent the condensed water from becoming
spattered onto the downstream side as well.
As described above, according to the present invention in which
the upstream side ends along the ventilating direction of the fins project
out further toward the upstream side along the ventilating direction
relative to the upstream side ends of the tubes along the ventilating
direction, dirt is not allowed to readily reach the tubes set at positions
recessed toward the downstream side along the ventilating direction
relative to the fins and, as a result, the risk of corrosion occurring at the
tubes due to adhering dirt can be reduced. Furthermore, since the
upstream side ends of the fins along the ventilating direction do not
project out further beyond the end faces of the tanks along the ventilating
direction, the width of the heat exchanger along the ventilating direction
does not increase in keeping with the space-saving requirement.
Moreover, since the downstream side ends of the fins along the
ventilating direction are recessed toward the upstream side along the
ventilating direction relative to the downstream side ends of the tubes
along the ventilating direction, condensed water having been caused by
the air pressure to move over the tubes or the fins to the downstream side
along the ventilating direction can be drained in a downward direction
along the surfaces of the tubes located further toward the downstream
side relative to the fins to minimize the occurrence of spattering of the
condensed water onto the downstream side along the ventilating direction.
In addition, according to the present invention in which the
upstream side ends along the ventilating direction of the fins provided on
the upstream side along the ventilating direction project out further
toward the upstream side along the ventilating direction relative to the
upstream side ends of the tubes along the ventilating direction, dirt is not
allowed to readily reach the tubes set at positions recessed toward the
upstream side along the ventilating direction relative to the fins and, as a
result, the risk of corrosion occurring at the tubes due to adhering dirt can
be reduced. Furthermore, since the upstream side ends of the fins along
the ventilating direction do not project out further beyond the end faces of
the tanks along the ventilating direction, the width of the heat exchanger
along the ventilating direction does not increase in keeping with the
space-saving requirement. Moreover, while condensation of water occurs
on the upstream side of the heat exchanger 1 along the ventilating
direction, the downstream side ends along the ventilating direction of the
fins provided on the upstream side along the ventilating direction are
recessed further toward the upstream side along the ventilating direction
to form a desirable gap from the fins provided on the downstream side
along the ventilating direction so that condensed water having been
caused by the air pressure to move over the surfaces of the fins on the
upstream side along the ventilating direction is allowed to drop downward
through the gap to reliably drain the condensed water. Thus, it becomes
possible to prevent the condensed water from moving onto the fins on the
downstream side along the ventilating direction and to prevent the
condensed water from becoming spattered onto the downstream side as
well.
Furthermore, according to the present invention, the width of the
fins along the ventilating direction is greater than the width along the
ventilating direction of the tubes facing opposite the fins along the
laminating direction. Thus, the efficiency with which heat exchange is
achieved through the fins is improved to achieve higher heat exchanging
efficiency in the heat exchanger.
Moreover, according to the present invention, the wall thickness of
the tubes on the upstream side along the ventilating direction is increased
by adopting a tightly-wound structure and thus, even if corrosion occurs
due to dirt escaping the fins projecting out along the ventilating direction
and reaching the tubes to become adhered thereto, the resistance against
such corrosion is improved to lengthen the durability of the tubes.
Claims (6)
- A heat extender comprising, at least, tubes each having therein a heat exchanging medium passage, fins laminated alternately between said tubes and a tank provided at ends of said tubes on at least one side, characterized in that:upstream side ends along the ventilating direction of said fins project out further toward the upstream side along the ventilating direction relative to upstream side ends of said tubes along the ventilating direction within a range in which the upstream side ends of said fins do not further beyond an end face of said tank on the upstream side along the ventilating direction; anddownstream side ends of said fins along the ventilating direction are recessed further toward the upstream side along the ventilating direction relative to downstream side ends of said tubes along the ventilating direction.
- A heat exchanger comprising, at least, tubes each having therein a heat exchanging medium passage, with a plurality thereof set parallel to one another along the ventilating direction, fins laminated alternately between said tubes with a plurality thereof set parallel to one another along the ventilating direction in a quantity corresponding to the quantity of said tubes and a tank provided at ends of said tubes on one side, characterized in that:an upstream side end along the ventilating direction of a fin set on a side furthest upstream along the ventilating direction project out further toward the upstream side along the ventilating direction relative to an upstream side end along the ventilating direction of a tube set on the side furthest upstream along the ventilating direction within a range in which the upstream side end of said fin along the ventilating direction does not project further beyond an end face of said tank on the upstream side along the ventilating direction; anda downstream side end along the ventilating direction of a fin set on a side furthest downstream along the ventilating direction is recessed further toward the upstream side along the ventilating direction relative to a downstream side end along the ventilating direction of a tube set on the side furthest downstream along the ventilating direction.
- A heat exchanger according to claim 2, characterized in that:an upstream side end along the ventilating direction of a fin that is not the fin set on the side furthest upstream along the ventilating direction, too, projects out further toward the upstream side along the ventilating direction relative to an upstream side end along the ventilating direction of a tube facing opposite said fin along the laminating direction within a range in which the upstream side end of said fin does not come into contact with the fin set on the side furthest upstream along the ventilating direction.
- A heat exchanger according to claim 2, characterized in that:a downstream side end along the ventilating direction of a fin that is not the fin set on the side furthest downstream along the ventilating direction, too, is recessed further toward the upstream side along the ventilating direction relative to the downstream side ends along the ventilating direction of said tubes set in parallel to one another.
- A heat exchanger according to claim 1, 2, 3 or 4, characterized in that:the extent by which the upstream side ends of said fins along the ventilating direction project out further toward the upstream side along the ventilating direction is greater than the extent by which the downstream side ends along the ventilating direction of said fins are recessed further toward the upstream side along the ventilating direction.
- A heat exchanger according to claim 1, 2, 3 or 4, characterized in that:said tubes are each formed by bending a single brazing sheet; andsaid tubes each include a junction formed by bonding ends of said brazing sheet on the upstream side along the ventilating direction and said junction assumes a structure achieved by tightly winding a portion of said brazing sheet close to one of the ends.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000107441A JP2001289535A (en) | 2000-04-10 | 2000-04-10 | Heat exchanger |
JP2000107441 | 2000-04-10 | ||
PCT/JP2001/000317 WO2001077591A1 (en) | 2000-04-10 | 2001-01-19 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1273858A1 true EP1273858A1 (en) | 2003-01-08 |
Family
ID=18620435
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01901438A Withdrawn EP1273858A1 (en) | 2000-04-10 | 2001-01-19 | Heat exchanger |
Country Status (4)
Country | Link |
---|---|
US (1) | US20030106678A1 (en) |
EP (1) | EP1273858A1 (en) |
JP (1) | JP2001289535A (en) |
WO (1) | WO2001077591A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004068052A1 (en) | 2003-01-31 | 2004-08-12 | Heinz Schilling Kg | Air/water heat exchanger with partial water ways |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4082191B2 (en) * | 2002-11-28 | 2008-04-30 | 株式会社デンソー | Air conditioner |
JP2004184034A (en) * | 2002-12-05 | 2004-07-02 | Denso Corp | Cooling unit for air-conditioning system |
JP5574700B2 (en) * | 2009-12-25 | 2014-08-20 | 株式会社ケーヒン・サーマル・テクノロジー | Evaporator with cool storage function |
JP6197338B2 (en) * | 2012-04-04 | 2017-09-20 | 株式会社デンソー | Heat exchanger |
US9046287B2 (en) * | 2013-03-15 | 2015-06-02 | Whirlpool Corporation | Specialty cooling features using extruded evaporator |
WO2015038111A1 (en) * | 2013-09-11 | 2015-03-19 | International Engine Intellectual Property Company, Llc | Thermal screen for an egr cooler |
CN112378123B (en) * | 2020-11-04 | 2021-09-10 | 上海交通大学 | Efficient flow-equalizing low-resistance reducing solar photovoltaic/photothermal heat collection/evaporator |
CN112611131B (en) * | 2020-12-14 | 2022-09-27 | 安徽美乐柯制冷空调设备有限公司 | Dry evaporator of water chilling unit |
CN115371340B (en) * | 2022-08-23 | 2024-06-11 | 浙江华美冷链科技有限公司 | Firm-mounting high-intensity electric heating pipe fixing clamp |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US898238A (en) * | 1907-05-11 | 1908-09-08 | Joseph B Long | Radiator. |
US1522404A (en) * | 1921-12-14 | 1925-01-06 | Albach John | Automobile radiator |
US1805917A (en) * | 1927-08-04 | 1931-05-19 | Ljungstroms Angturbin Ab | Cooler contacting with circulating air |
US2252211A (en) * | 1939-10-18 | 1941-08-12 | Mccord Radiator & Mfg Co | Heat exchange core |
US3045979A (en) * | 1956-03-07 | 1962-07-24 | Modine Mfg Co | Staggered serpentine structure for heat exchanges and method and means for making the same |
JPS5911267U (en) * | 1982-07-12 | 1984-01-24 | 株式会社日立製作所 | Evaporator |
JPS5918179U (en) * | 1982-07-26 | 1984-02-03 | カルソニックカンセイ株式会社 | Evaporator |
JPS59129392A (en) * | 1983-01-10 | 1984-07-25 | Nippon Denso Co Ltd | Heat exchanger |
JPS59172968U (en) * | 1983-05-06 | 1984-11-19 | 東洋ラジエ−タ−株式会社 | refrigerant evaporator |
US4546824A (en) * | 1984-03-19 | 1985-10-15 | Mccord Heat Transfer Corporation | Heat exchanger |
JPS61223465A (en) * | 1985-03-27 | 1986-10-04 | 株式会社デンソー | Evaporator |
JPH02251093A (en) * | 1989-03-23 | 1990-10-08 | Matsushita Refrig Co Ltd | Finned heat exchanger |
CA2035590A1 (en) * | 1990-02-12 | 1991-08-13 | Gregory G. Hughes | Multipass evaporator |
JP4117429B2 (en) * | 1999-02-01 | 2008-07-16 | 株式会社デンソー | Heat exchanger fins |
-
2000
- 2000-04-10 JP JP2000107441A patent/JP2001289535A/en active Pending
-
2001
- 2001-01-19 WO PCT/JP2001/000317 patent/WO2001077591A1/en not_active Application Discontinuation
- 2001-01-19 EP EP01901438A patent/EP1273858A1/en not_active Withdrawn
- 2001-01-19 US US10/257,073 patent/US20030106678A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO0177591A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004068052A1 (en) | 2003-01-31 | 2004-08-12 | Heinz Schilling Kg | Air/water heat exchanger with partial water ways |
Also Published As
Publication number | Publication date |
---|---|
WO2001077591A1 (en) | 2001-10-18 |
JP2001289535A (en) | 2001-10-19 |
US20030106678A1 (en) | 2003-06-12 |
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