US20080000627A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- US20080000627A1 US20080000627A1 US11/824,526 US82452607A US2008000627A1 US 20080000627 A1 US20080000627 A1 US 20080000627A1 US 82452607 A US82452607 A US 82452607A US 2008000627 A1 US2008000627 A1 US 2008000627A1
- Authority
- US
- United States
- Prior art keywords
- tank
- tube
- tubular
- opening
- tubes
- 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.)
- Abandoned
Links
- 238000003780 insertion Methods 0.000 claims abstract description 66
- 230000037431 insertion Effects 0.000 claims abstract description 66
- 239000012530 fluid Substances 0.000 claims abstract description 40
- 239000003507 refrigerant Substances 0.000 description 37
- 239000000463 material Substances 0.000 description 16
- 238000005219 brazing Methods 0.000 description 8
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 6
- 229910052782 aluminium Inorganic materials 0.000 description 6
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 6
- 239000000945 filler Substances 0.000 description 4
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000001125 extrusion Methods 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
Images
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0229—Double end plates; Single end plates with hollow spaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/04—Arrangements for sealing elements into header boxes or end plates
- F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0084—Condensers
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/4935—Heat exchanger or boiler making
- Y10T29/49373—Tube joint and tube plate structure
Definitions
- the present invention relates to a heat exchanger that has tubes defining external fluid passages on outer surfaces thereof and a tank connected to ends of the tubes.
- each of the tubes is constructed of a pair of plate members.
- Each plate member has a base wall portion and projections projecting from the base wall portion. The plate members are joined such that the projections project outwardly.
- the projections extends in a serpentine or meandering manner in a direction perpendicular to a longitudinal direction of the tube.
- the grooves are provided between the adjacent projections as the external fluid passage portions through which an external fluid (e.g., air) flows. Because the external fluid flows through the grooves in the meandering manner, the flow of the air is disturbed.
- This structure suppresses a growth of a temperature boundary layer adjacent to the outer surface of the tube, and improves coefficient of heat transfer on the outer surface of the tube.
- the plate members are joined to make contact with each other at the external fluid passage portions, i.e., bottom walls of the grooves, and internal fluid passages through which an internal fluid (e.g., refrigerant) flows are formed between the plate members.
- the external fluid passage portions also serve as inner pillars for improving the resistance to pressure of the tube.
- ends of the tubes are inserted in tube insertion holes of tanks and the outer surfaces of the tubes are joined (e.g., brazed) with perimeter surfaces that define the tube insertion holes.
- the grooves are disposed over the perimeter surfaces of the tube insertion holes with respect to a longitudinal direction of the tube, an inside space of the heat exchanger will be communicated with an outside of the heat exchanger through the grooves. This results in leakage of the internal fluid through the grooves.
- the tubes such that the grooves as the external fluid passage portions are not formed at the ends of the tubes.
- the outer surface of the end of the tube will be joined with the perimeter surface of the tube insertion hole without having a large clearance.
- the external fluid passage portions which also serve as the inner pillars, are not formed at the ends of the tubes, the resistance to pressure will be reduced at the ends of the tubes.
- Japanese Unexamined Patent Publication No. 2001-133189 discloses a heat exchanger having tubes without having grooves as external fluid passage portions on outer surfaces thereof and a tank.
- plural tank members are layered such that opening thereof are aligned and thus tube insertion holes are provided by the openings. Since the tank members are thin, the openings are easily formed.
- This publication is addressed to ease forming of the tube insertion holes in the heat exchanger having the tubes that do not have the grooves on the outer surfaces thereof.
- This publication does not teach how to form the tube insertion holes for receiving the ends of the tubes having the external fluid passage portions in order to restrict leakage of the internal fluid through the internal fluid passage portions at all.
- the present invention is made in view of the foregoing matter, and it is an object of the present invention to provide a heat exchanger having a connecting structure between ends of tubes and tube insertion portions of a tank, which is capable of reducing leakage of an internal fluid through external fluid passage portions of the tubes.
- a heat exchanger has a plurality of tubes for performing heat exchange between an internal fluid flowing inside of the tubes and an external fluid flowing outside of the tubes and a tank connected to ends of the tubes.
- Each of the tubes has projections that project from an outer surface thereof. The projections are arranged in a longitudinal direction of the tube such that grooves are provided between the adjacent projections as external fluid passage portions for allowing the external fluid to flow.
- the tank has a plurality of tube insertion portions defining openings in which ends of the tubes are inserted. Each of the plurality of tube insertion portions is configured such that a perimeter surface defining the opening thereof entirely covers at least one groove of the end of the tube.
- At least one external fluid passage portion at the end of the tube is entirely covered by the perimeter surface of the tube insertion portion.
- the external fluid passage portion disposed in the opening of the tube insertion portion does not extends over the perimeter surface of the tube insertion portion.
- This structure restricts an inner space of the heat exchanger from communicating with an outside of the heat exchanger through the external fluid passage portion in the tube insertion portion. Accordingly, it is less likely that the internal fluid will leak through the external fluid passage portion in the tube insertion portion.
- FIG. 1 is a schematic plan view a heat exchanger according to a first embodiment of the present invention
- FIG. 2 is a schematic perspective view of a portion of a heat exchanging part of the heat exchanger according to the first embodiment
- FIG. 3 is a schematic perspective view of a portion of a tube of the heat exchanger according to the first embodiment
- FIG. 4 is a schematic perspective view of a portion of a tank of the heat exchanger according to the first embodiment
- FIG. 5 is an exploded perspective view of the portion of the tank according to the first embodiment
- FIG. 6 is a schematic cross-sectional view of a portion of the tank according to the first embodiment
- FIG. 7 is a schematic cross-sectional view of the portion of the tank in which the tube is inserted according to the first embodiment
- FIG. 8 is a schematic cross-sectional view of a portion of a heat exchanger according to a second embodiment of the present invention.
- FIG. 9 is a schematic cross-sectional view of a portion of a heat exchanger according to a third embodiment of the present invention.
- FIG. 10 is a schematic cross-sectional view of a portion of a heat exchanger according to a fourth embodiment of the present invention.
- FIG. 11 is a schematic cross-sectional view of a portion of a heat exchanger according to a fifth embodiment of the present invention.
- FIG. 12 is a perspective view of a tubular member of the heat exchanger according to the fifth embodiment.
- FIG. 13 is a schematic cross-sectional view of a portion of a heat exchanger according to a sixth embodiment of the present invention
- FIGS. 1 to 7 A first embodiment of the present invention will be described with reference to FIGS. 1 to 7 .
- a heat exchanger 10 is for example used as a refrigerant condenser of a refrigerating cycle for a vehicle air conditioner.
- the heat exchanger 10 is mounted in an engine compartment of a vehicle, at a position where outside air is sufficiently supplied while the vehicle is running.
- An up and down arrow in FIG. 1 denotes an exemplary arrangement direction of the heat exchanger 10 in the vehicle.
- the heat exchanger 10 performs heat exchange between a high temperature, high pressure refrigerant as an internal fluid, which has been discharged from a compressor (not shown) of the refrigerating cycle, and the air as an external fluid, thereby condensing the refrigerant.
- the heat exchanger 10 generally has a heat exchanging part 13 and tanks 14 , 15 , as shown in FIG. 1 .
- the heat exchanging part 13 includes a plurality of flat tubes 11 and a plurality of fins 12 .
- the tubes 11 define refrigerant passages (internal fluid passages) therein through which the refrigerant flows.
- the fins 12 are for example corrugated fins.
- the tanks 14 , 15 are located at longitudinal ends 11 a , 11 b of the tubes 11 .
- the longitudinal ends 11 a , 11 b of the tubes 11 are inserted in openings of tube insertion portions 14 d , 15 d of the tanks 14 , 15 .
- the tanks 14 , 15 are provided to distribute and collect the refrigerant into and from the tubes 11 .
- Each of the tanks 14 , 15 includes a first tank member 14 a , 15 a , a second tank member 14 b , 15 b and caps 14 c , 15 c .
- the first tank member 14 a , 15 a has a generally semi-tubular shape.
- the second tank member 14 b , 15 b has a generally semi-tubular shape.
- the first tank member 14 a , 15 a and the second tank member 14 b , 15 b are connected to each other such that the tank 14 , 15 has a generally tubular shape.
- the caps 14 c , 15 c cover longitudinal ends of the tanks 14 , 15 .
- each of the first tank members 14 a , 15 a , the second tank members 14 b , 15 b and the caps 14 c , 15 c is made of a metal plate (e.g., aluminum material).
- a surface of the metal plate, which corresponds to an inner surface of the tank 14 , 15 is coated with a brazing material (filler material), and the metal plate is formed into a predetermined shape by pressing.
- the tank 14 has a refrigerant inlet portion 14 e at an end (e.g., lower end in FIG. 1 ) thereof.
- an inlet pipe is coupled to the refrigerant inlet portion 14 e for introducing the high pressure, high temperature refrigerant discharged from the compressor into the heat exchanger 10 .
- the tank 15 has a refrigerant outlet portion 15 e at an end (e.g., upper end in FIG. 1 ) thereof.
- an outlet pipe is coupled to the refrigerant outlet portion 15 e for discharging a liquid-phase refrigerant from the heat exchanger 10 toward an expansion valve of the refrigerating cycle.
- side plates 16 , 17 are provided to maintain a rectangular-shaped outline of the heat exchanger 10 .
- the side plates 16 , 17 are disposed parallel to the tubes 11 and ends of the side plates 16 , 17 are connected to the ends of the tanks 14 , 15 .
- the tubes 11 , the fins 12 , and the tanks 14 , 15 are joined by integrally brazing, for example.
- each of the tubes 11 is constructed of a pair of plate members 18 , 19 .
- the plate members 18 , 19 are thin plate-like members made of an aluminum material, and both surfaces of the thin plate members are coated with a brazing material.
- Each of the plate members 18 , 19 includes a flat base wall 20 and a plurality of projections 21 projecting from the flat base wall 20 .
- the plate members 18 , 19 are paired such that the projections 21 project in opposite directions and the base walls 20 have surface contact. Also, the plate members 18 , 19 are arranged such that portions between the projections 21 overlap with each other. Thus, refrigerant passages 22 through which the refrigerant flows are formed between the paired plate members 18 , 19 .
- Each of the projections 21 projects from the base wall 20 at a substantially middle position with respect to a tube width direction D 2 , which is perpendicular to a tube longitudinal direction D 1 .
- the projection 21 has a flat wall on its top and curved side walls 23 , which face in the tube longitudinal direction D 1 .
- Each of the side walls 23 of the projection 21 extends in the tube width direction D 2 in a serpentine or meandering manner.
- the projections 21 are arranged at a regular pitch P in the tube longitudinal direction D 1 such that clearances are provided between the adjacent projections 21 , i.e., the side walls 23 of the adjacent projections 21 as grooves.
- the grooves having a serpentine shape are formed between the adjacent projections 21 on outer surfaces of the tubes 11 .
- the grooves serve as air passage portions (external fluid passage portions) 24 for allowing the air in a serpentine or meandering manner.
- a bottom wall of the air passage portion 24 includes a flat wall 24 c and first and second recessed portions 24 a , 24 b that are recessed from the flat wall 24 c toward an inside of the tube 11 through step portions 24 d , 24 e .
- the first recessed portions 24 a are formed at position corresponding to peaks or most curved portions of the serpentine shaped air passage portion 24 and the second recessed portions 24 b are formed at position corresponding to the end of the air passage portion 24 .
- the first and second recessed portions 24 a , 24 b are provided by the base wall 20 .
- the first and second recessed portions 24 a , 24 b are on the same level as the base wall 20 .
- the flat wall 24 c slightly project from the base wall 20 toward an outside of the tube 11 .
- the air passage portions 24 of the plate members 18 , 19 are staggered in the tube longitudinal direction D 1 , but the first and second recessed portions 24 a , 24 b of the plate member 18 overlap with the first and second recessed portions 24 a , 24 b of the plate member 19 .
- the plate members 18 , 19 are in contact with and joined with each other at the first and second recessed portions 24 a , 24 b .
- the step portions 24 d , 24 e have height approximately 0.65 mm, respectively.
- the refrigerant passage 23 has a complex serpentine shape as shown by arrows B in FIG. 2 . Since the air passage portions 24 of the two plate members 18 , 19 are staggered in the tube longitudinal direction D 1 , the refrigerant passage 23 extends in the tube longitudinal direction D 1 while meandering in a direction in which a height of the tube 11 is measured (i.e., in an up and down direction in FIG. 2 ).
- the refrigerant passage 23 diverges at the first recessed portions 24 a and merges downstream of the first recessed portions 24 a .
- the refrigerant passage 23 extends in the tube longitudinal direction D 1 while repetitively diverging and merging in the tube width direction D 2 .
- the refrigerant passage 23 is formed in a serpentine manner both in the tube longitudinal direction D 1 and in the tube width direction D 2 .
- the fins 12 are made of a bare plate without coated by a brazing material.
- the bare plate is for example made of an aluminum material and is formed into a corrugated shape.
- Each of the fin 12 includes joining portions 12 a , 12 b to be joined with the flat top wall of the projections 21 and connecting walls 12 c , 12 d connecting the joining portions 12 a , 12 b .
- the joining portions 12 a , 12 b are flat walls.
- the connecting walls 12 c , 12 d are flat walls and extend in a tube stack direction in which the tubes 11 are stacked (i.e., up and down direction in FIG. 2 ).
- the connecting walls 12 c , 12 d are formed with louvers that are formed by cutting portions of the connecting walls 12 c , 12 d and angling the cut portions so as to oppose the flow of air.
- the air that flows through areas separated from the tubes 11 flows along the fins 12 , as shown by an arrow C in FIG. 2 .
- This air receives heat from the fins 12 and then flows out of the fins 12 .
- the fins 12 are cooled by the air passing through the fins 12 .
- the air that flows adjacent to the tubes 11 receives heat from the tubes 11 and is discharged from the heat exchanging part 13 after cooling the tubes 11 .
- the air flows through the air passage portions 24 in the serpentine manner, as shown by an arrow D in FIG. 2 , the flow of this air is disturbed.
- the coefficient of heat transfer of the air improves. Accordingly, efficiency of heat transfer improves.
- the coefficient of heat transfer of the air improves. Further, because the surface area of heat transfer is increased by the air passage portions 24 , the amount of heat radiation from the tube 11 to the air is increased.
- FIGS. 4 to 7 connecting structure of the tanks 14 , 15 and the tubes 11 will be described with reference to FIGS. 4 to 7 .
- the connecting structure of the tank 14 and the tubes 11 are the same as the connecting structure of the tank 15 and the tubes 11 .
- component parts regarding the tank 15 are indicated by numerals in parentheses.
- the first tank member 14 a , 15 a is a member to be joined with the tubes 11 .
- the first tank member 14 a , 15 a includes a flat wall 25 , 26 that extends in a direction perpendicular to the tube longitudinal direction D 1 , i.e., in a direction parallel to a tank longitudinal direction D 3 .
- a plate 27 , 28 having a substantially rectangular shape, is brazed to the flat wall 25 , 26 .
- the plate 27 , 28 is made of an aluminum material, and a surface of the plate 27 , 28 facing the first tank member 14 a , 15 a is coated with a brazing material (filler material).
- the flat wall 25 , 26 of the first tank member 14 a , 15 a is formed with first hole portions 29 , 30 .
- the first hole portions 29 , 30 of the first tank member 14 a , 15 a define oblong or oval-shaped openings.
- the plate 27 , 28 is formed with second hole portions 31 , 32 defining oblong or oval-shaped openings.
- the plate 27 , 28 includes a main wall portion defining openings and tubular portions 31 a , 32 a on peripheries of the openings of the main wall portion, as the second hole portions 31 , 32 .
- the tubular portions 31 a , 32 a project in an outward direction of the tank 14 , 15 and in a direction parallel to the tube longitudinal direction D 1 .
- Each of the tubular portions 31 a , 32 a has an oval shape in a cross-section defined in a direction perpendicular to the tube longitudinal direction D 1 .
- the tubular portion 31 a , 32 a is formed by burring a periphery of the opening of the main wall portion.
- the plate 27 , 28 is disposed on the flat wall 25 , 26 such that the openings of the second hole portions 31 , 32 are aligned with the openings of the first hole portions 29 , 30 .
- the openings of the tube insertion portions 14 d , 15 d are provided by the openings of the first and second hole portions 29 , 30 , 31 , 32 , as shown in FIG. 6 .
- a perimeter surface (perimeter portion) defining the opening of each tube insertion portion 14 d , 15 d is provided by a surface that defines the opening of the first hole portion 29 , 30 and a surface that defines the opening of the second hole portion 31 , 32 .
- the tubular portion 31 a , 32 a has a length L 2 in the tube longitudinal direction D 1 .
- the length L is equal to or greater than the pitch P of the projections 21 of the tubes 11 .
- the longitudinal end 11 a , 11 b of the tube 11 is inserted in the opening of the tube insertion portion 14 d , 15 d such that an area shown by chain double-dashed lines in FIG. 3 overlaps with the perimeter surface of the tube insertion portion 14 , 15 .
- the perimeter surface of the tube insertion portion 14 , 15 entirely covers one air passage portion 24 on each of the plate members 18 , 19 .
- the air passage portion 24 does not extend over the perimeter surface of the tube insertion portion 14 d , 15 d . Therefore, this connecting structure restricts communication between an inside space and an outside space of the heat exchanging part 13 through the air passage portions 24 . Accordingly, it is less likely that the refrigerant will leak outside of the heat exchanging part 13 through the air passage portions 24 .
- the tubular portion 31 a , 32 a is formed by burring, the length L of the perimeter surface of the tube insertion portion 14 d , 15 d is increased. As such, the air passage portion 24 of the longitudinal end 11 a , 11 b of the tube 11 is entirely covered by the perimeter surface of the tube insertion portion 14 d , 15 d.
- the tube insertion portion 14 d , 15 d is constructed by aligning the first hole portion 29 , 30 of the first tank member 14 a , 15 a with the second hole portion 31 , 32 of the plate 27 , 28 . Therefore, a thin plate member can be used as the plate member 27 , 28 .
- the tubular portions 31 a , 32 a are easily formed, as compared with a case of forming the tubular portions on a thick plate member. Accordingly, the tube insertion portions 14 d , 15 d are easily formed. Further, the tubular portions 31 a , 32 a are easily formed on the thin plate member by burring.
- the length L of the perimeter surface of the tube insertion portion 14 d , 15 d is equal to or greater than the pitch P of the projections 21 of the tube 11 , at least one air passage portion 24 is entirely covered by the perimeter surface of the tube insertion portion 14 d , 15 d , irrespective of a positional relation between the tube 11 and the tank 14 , 15 with respect to the tube longitudinal direction D 1 .
- the leakage of the refrigerant through the air passage portion 24 is restricted without being affected by the positional relation between the tube 11 and the tank 14 , 15 with respect to the tube longitudinal direction D 1 .
- the leakage of the refrigerant through the air passage portion 24 is restricted without being affected by assembling accuracy of the tube 11 to the tank 14 , 15 with respect to a tube inserting direction.
- the length L is longer than necessary as shown by a chain double-dashed line in FIG. 7 , the plural air passage portions 24 of each plate member 18 , 19 are covered by the perimeter surface. This may results in a decrease in an effect of improving the heat transfer coefficient of the air. Therefore, it is necessary to consider this matter.
- tubular portions 29 a , 30 a are formed on the peripheries of the openings of the first hole portions 29 , 30 of the first tank member 14 a , 15 a .
- the tube insertion portion 14 d , 15 d is provided by the tubular portion 29 a , 30 a of the first tank member 14 a , 15 a and the tubular portion 31 a , 32 a of the plate 27 , 28 .
- the tubular portions 29 a , 30 a project inside of the tank 14 , 15 .
- the tubular portions 29 a , 30 a are formed by burring.
- the perimeter portion of the tube insertion portion 14 d , 15 d is provided by an inner surface of the tubular portion 31 a , 32 a of the first tank member 14 a , 15 a and the inner surface of the tubular portion 29 a , 30 a of the plate 27 , 28 .
- the length L is increased greater than the length L of the first embodiment shown in FIG. 7 . Therefore, the communication between the inside space of the heat exchanging part 13 and the outside space is more securely restricted. As such, the leakage of the refrigerant through the air passage portion 24 is further effectively restricted.
- the tubular portions 29 a , 30 a of the first tank member 14 a , 15 a project inside of the tank 14 , 15 .
- the tubular portions 29 a , 30 a does not overlap with the air passage 24 outside of the tank 14 , 15 . Therefore, it is less likely that the coefficient of heat transfer of the air will be affected by the tubular portions 29 a , 30 a of the first tank member 14 a , 15 a .
- the length L of the perimeter surface is increased without reducing the coefficient of heat transfer of the air of the air passage portions 24 .
- a third embodiment of the present invention will be described with reference to FIG. 9 .
- a second plate 33 , 34 is added to the structure shown in FIG. 6 .
- the second plate 33 , 34 has third hole portions 35 , 36 defining ova-shaped openings and is arranged along an inner surface of the flat wall 25 , 26 of the first tank member 14 a , 15 a such that the openings of the third hole portions 35 , 36 are aligned with the openings of the first hole portions 29 , 30 of the first tank member 14 a , 15 a and the openings of the second hole portion 31 , 32 of the plate (hereafter, referred to as first plate) 27 , 28 .
- the tube insertion portion 14 d , 15 d is provided by the first hole portion 29 , 30 , the second hole portion 31 , 32 and the third hole portion 35 , 36 .
- the second plate 33 , 34 for example has a rectangular shape and extends in the tank longitudinal direction D 3 .
- the second plate 33 , 34 is brazed to the inner surface of the first tank member 14 a , 15 a .
- the second plate 33 , 34 is disposed on a side opposite to the first plate 27 , 28 with respect to the flat wall 25 , 26 of the first tank member 14 a , 15 a.
- the second plate 33 , 34 is provided by a plate member made of an aluminum material and a surface of the plate member facing the first tank member 14 a , 15 a is coated with a brazing material (filler material).
- the second plate 33 , 34 is the rectangular shaped plate.
- the second plate 33 , 34 may be provided by a semi-tubular shaped plate to extend over the entire inner surface of the first tank member 14 a , 15 a.
- the length L is increased greater than the length L of the first embodiment. Therefore, the communication of the inside space of the heat exchanging part 13 with the outside space through the air passage portion 24 is further restricted. As such, the leakage of the refrigerant through the air passage portion 24 is further restricted.
- the second plate 33 , 34 is formed with a tubular portion 35 a , 36 a , and thus the third hole portion 35 , 36 is provided by an opening of the tubular portion 35 a , 36 a .
- the tubular portion 35 a , 36 a projects inside of the tank 14 , 15 .
- the tubular portion 35 a , 36 b is formed by burring.
- the tube insertion portion 14 d , 15 d is provided by the tubular portions 31 a , 32 a , 35 a , 36 a of the second and third hole portions 31 , 32 , 35 , 36 and the first hole portion 29 , 30 .
- the length L of the perimeter surface of the tube insertion portion 14 d , 15 d is increased greater than the length L of the third embodiment. Therefore, the leakage of the refrigerant through the air passage portion 24 is further effectively restricted.
- a fifth embodiment will be described with reference to FIGS. 11 and 12 .
- the opening of the tube insertion portion 14 d , 15 d is provided by an opening of a tubular member 37 , 38 .
- the tubular member 37 , 38 includes a tubular wall portion 37 a , 38 a defining an opening and an annular flange portion 37 b , 38 b radially expanding from an end of the tubular wall portion 37 a , 38 a .
- the flange portion 37 b , 38 b are integrally formed with the tubular wall portion 37 a , 38 a .
- the tubular member 37 , 38 is made of an aluminum material and is coated with a brazing material (filler material).
- the tubular member 37 , 38 is inserted into the opening of the first hole portion 29 , 30 from the outside of the tank 14 , 15 , so that the flange portion 37 b , 38 b contacts the flat wall 25 , 26 of the first tank member 14 a , 15 a .
- the flange portion 37 b , 38 b is joined to the flat wall 25 , 26 of the first tank member 14 a , 15 a.
- the perimeter surface of the tube insertion portion 14 d , 15 d is provided by the inner surface of the tubular member 37 , 38 .
- the leakage of the refrigerant through the air passage portion 24 is restricted, similar to the first embodiment.
- the opening of the tube insertion portion 14 d , 15 d is provided by the opening of the first hole portion 29 , 30 of the first tank member 14 a , 15 a and the opening of the tubular wall portion 37 a , 38 a of the tubular member 37 , 38 .
- the tubular wall portion 37 a , 38 a is not inserted in the opening of the first hole portion 29 , 30 .
- the flange portion 37 b , 38 b is disposed along the inner surface of the first tank member 14 a , 15 a such that the opening of the tubular member 37 , 38 and the opening of the first hole portion 29 , 30 are aligned.
- the flange portion 37 b , 38 b is joined with the inner surface of the first tank member 14 a , 15 a.
- the perimeter surface of the tube insertion portion 14 d , 15 d is provided by the inner surface of the tubular member 37 , 38 and the surface defining the opening of the first hole portion 29 , 30 .
- the leakage of the refrigerant through the air passage portion 24 is restricted, similar to the fifth embodiment.
- the tubular portion 31 a , 32 a is formed on the plate 27 , 28 and the perimeter surface of the tube insertion portion 14 d , 15 d is provided by the inner surface of the tubular portion 31 a , 32 a and the surface defining the opening of the first hole portion 29 , 30 .
- the plate 27 , 28 has the tubular portion 31 a , 32 a .
- the wall thickness of the plate 27 , 28 and the first tank member 14 a , 15 a may be increased and thus the perimeter surface of the tube insertion portion 14 d , 15 d may be provided by the surface defining the opening of the first hole portion 29 , and an inner surface of an opening of the plate 27 , 28 .
- at least one air passage 24 of the tube 11 is entirely covered by the perimeter surface of the tube insertion portion 14 d , 15 d.
- the opening of the tube insertion portion 14 d , 15 d is constructed by aligning the openings of the plural tank members 14 a , 15 a , 27 , 28 , 33 , 34 , 37 , 38 .
- the opening of the tube insertion portion 14 d , 15 d may be formed by an opening of a single member.
- the plate 27 , 28 can be eliminated and the opening of the tube insertion portion 14 d , 15 d is provided only by the opening of the first hole portion 29 , 30 .
- a tubular portion may be formed on a periphery of the opening of the first hole portion 29 , 30 of the first tank member 14 a , 15 a to project in the direction parallel to the tube longitudinal direction D 1 , instead of the tubular portion 31 a , 32 a of the plate 27 , 28 .
- the air passage portions 24 are grooves extending in the tube width direction D 2 in the serpentine manner.
- the shape of the air passage portions 24 is not limited to the serpentine shape.
- the air passage portions 24 may be straight grooves extending obliquely with respect to the tube width direction D 2 .
- each tube 11 is constructed of the pair of plate members 18 , 19 both having the projections 21 .
- the structure of the tube 11 is not limited to the above.
- only one of the plate members 18 , 19 may have the projections 21 .
- the tube 11 may be provided by a cylindrical tube or a flat tube formed by extrusion. When the tube 11 is formed by the extrusion, the grooves as the air passage portions 24 are formed on the outer surfaces of the tube 11 by pressing the tube 11 from the outside.
- the tube insertion portion 14 d , 15 d has the oblong or oval-shaped opening.
- the shape of the opening of the tube insertion portion 14 d , 15 d is not limited to the above.
- the opening of the tube insertion portion 14 d , 15 d may have any shape so as to correspond to an external cross-sectional shape of the tube 11 .
- the shape of the plate 27 , 28 is not limited to the generally rectangular shape.
- the plate 27 , 28 may have a semi-tubular shape to correspond to the entire inner surface of the first tank member 14 a , 15 a.
- the heat exchanger 10 is not limited to the refrigerant condenser.
- the heat exchanger 10 may be any heat exchangers used for various purposes.
Abstract
A heat exchanger has tubes for performing heat exchange between an internal fluid flowing inside of the tubes and an external fluid flowing outside of the tubes and a tank connected to the tubes. Each of the tubes has projections projecting from an outer surface thereof. The projections are arranged in a longitudinal direction of the tube such that grooves are provided between the adjacent projections as external fluid passage portions. The tank has tube insertion portions defining openings into which ends of the tubes are inserted. Each of the tube insertion portions is configured such that a perimeter surface defining the opening thereof entirely covers at least one external fluid passage portion of the tube.
Description
- This application is based on Japanese Patent Application No. 2006-181260 filed on Jun. 30, 2006, the disclosure of which is incorporated herein by reference.
- The present invention relates to a heat exchanger that has tubes defining external fluid passages on outer surfaces thereof and a tank connected to ends of the tubes.
- A heat exchanger that has tubes defining grooves on its outer surfaces as external fluid passage portions is for example disclosed in Unexamined Japanese Patent Publication No. 2004-3787 (U.S. Pat. No. 6,595,273). In the heat exchanger, each of the tubes is constructed of a pair of plate members. Each plate member has a base wall portion and projections projecting from the base wall portion. The plate members are joined such that the projections project outwardly.
- The projections extends in a serpentine or meandering manner in a direction perpendicular to a longitudinal direction of the tube. The grooves are provided between the adjacent projections as the external fluid passage portions through which an external fluid (e.g., air) flows. Because the external fluid flows through the grooves in the meandering manner, the flow of the air is disturbed. This structure suppresses a growth of a temperature boundary layer adjacent to the outer surface of the tube, and improves coefficient of heat transfer on the outer surface of the tube.
- Also, the plate members are joined to make contact with each other at the external fluid passage portions, i.e., bottom walls of the grooves, and internal fluid passages through which an internal fluid (e.g., refrigerant) flows are formed between the plate members. In this structure, the external fluid passage portions also serve as inner pillars for improving the resistance to pressure of the tube.
- Further, ends of the tubes are inserted in tube insertion holes of tanks and the outer surfaces of the tubes are joined (e.g., brazed) with perimeter surfaces that define the tube insertion holes. In this case, however, if the grooves are disposed over the perimeter surfaces of the tube insertion holes with respect to a longitudinal direction of the tube, an inside space of the heat exchanger will be communicated with an outside of the heat exchanger through the grooves. This results in leakage of the internal fluid through the grooves.
- Also, it may be considered to form the tubes such that the grooves as the external fluid passage portions are not formed at the ends of the tubes. In this case, the outer surface of the end of the tube will be joined with the perimeter surface of the tube insertion hole without having a large clearance. However, since the external fluid passage portions, which also serve as the inner pillars, are not formed at the ends of the tubes, the resistance to pressure will be reduced at the ends of the tubes.
- Japanese Unexamined Patent Publication No. 2001-133189 discloses a heat exchanger having tubes without having grooves as external fluid passage portions on outer surfaces thereof and a tank. In the tank, plural tank members are layered such that opening thereof are aligned and thus tube insertion holes are provided by the openings. Since the tank members are thin, the openings are easily formed. This publication is addressed to ease forming of the tube insertion holes in the heat exchanger having the tubes that do not have the grooves on the outer surfaces thereof. This publication does not teach how to form the tube insertion holes for receiving the ends of the tubes having the external fluid passage portions in order to restrict leakage of the internal fluid through the internal fluid passage portions at all.
- The present invention is made in view of the foregoing matter, and it is an object of the present invention to provide a heat exchanger having a connecting structure between ends of tubes and tube insertion portions of a tank, which is capable of reducing leakage of an internal fluid through external fluid passage portions of the tubes.
- According to an aspect of the present invention, a heat exchanger has a plurality of tubes for performing heat exchange between an internal fluid flowing inside of the tubes and an external fluid flowing outside of the tubes and a tank connected to ends of the tubes. Each of the tubes has projections that project from an outer surface thereof. The projections are arranged in a longitudinal direction of the tube such that grooves are provided between the adjacent projections as external fluid passage portions for allowing the external fluid to flow. The tank has a plurality of tube insertion portions defining openings in which ends of the tubes are inserted. Each of the plurality of tube insertion portions is configured such that a perimeter surface defining the opening thereof entirely covers at least one groove of the end of the tube.
- Namely, at least one external fluid passage portion at the end of the tube is entirely covered by the perimeter surface of the tube insertion portion. In other words, the external fluid passage portion disposed in the opening of the tube insertion portion does not extends over the perimeter surface of the tube insertion portion. This structure restricts an inner space of the heat exchanger from communicating with an outside of the heat exchanger through the external fluid passage portion in the tube insertion portion. Accordingly, it is less likely that the internal fluid will leak through the external fluid passage portion in the tube insertion portion.
- Other objects, features and advantages of the present invention will become more apparent from the following detailed description made with reference to the accompanying drawings, in which like parts are designated by like reference numbers and in which:
-
FIG. 1 is a schematic plan view a heat exchanger according to a first embodiment of the present invention; -
FIG. 2 is a schematic perspective view of a portion of a heat exchanging part of the heat exchanger according to the first embodiment; -
FIG. 3 is a schematic perspective view of a portion of a tube of the heat exchanger according to the first embodiment; -
FIG. 4 is a schematic perspective view of a portion of a tank of the heat exchanger according to the first embodiment; -
FIG. 5 is an exploded perspective view of the portion of the tank according to the first embodiment; -
FIG. 6 is a schematic cross-sectional view of a portion of the tank according to the first embodiment; -
FIG. 7 is a schematic cross-sectional view of the portion of the tank in which the tube is inserted according to the first embodiment; -
FIG. 8 is a schematic cross-sectional view of a portion of a heat exchanger according to a second embodiment of the present invention; -
FIG. 9 is a schematic cross-sectional view of a portion of a heat exchanger according to a third embodiment of the present invention; -
FIG. 10 is a schematic cross-sectional view of a portion of a heat exchanger according to a fourth embodiment of the present invention; -
FIG. 11 is a schematic cross-sectional view of a portion of a heat exchanger according to a fifth embodiment of the present invention; -
FIG. 12 is a perspective view of a tubular member of the heat exchanger according to the fifth embodiment; and -
FIG. 13 is a schematic cross-sectional view of a portion of a heat exchanger according to a sixth embodiment of the present invention - A first embodiment of the present invention will be described with reference to
FIGS. 1 to 7 . - Referring to
FIG. 1 , aheat exchanger 10 is for example used as a refrigerant condenser of a refrigerating cycle for a vehicle air conditioner. Theheat exchanger 10 is mounted in an engine compartment of a vehicle, at a position where outside air is sufficiently supplied while the vehicle is running. An up and down arrow inFIG. 1 denotes an exemplary arrangement direction of theheat exchanger 10 in the vehicle. - The
heat exchanger 10 performs heat exchange between a high temperature, high pressure refrigerant as an internal fluid, which has been discharged from a compressor (not shown) of the refrigerating cycle, and the air as an external fluid, thereby condensing the refrigerant. Theheat exchanger 10 generally has aheat exchanging part 13 andtanks FIG. 1 . - The
heat exchanging part 13 includes a plurality offlat tubes 11 and a plurality offins 12. Thetubes 11 define refrigerant passages (internal fluid passages) therein through which the refrigerant flows. Thefins 12 are for example corrugated fins. Thetanks longitudinal ends tubes 11. The longitudinal ends 11 a, 11 b of thetubes 11 are inserted in openings oftube insertion portions tanks - The
tanks tubes 11. Each of thetanks first tank member second tank member first tank member second tank member first tank member second tank member tank caps tanks - For example, each of the
first tank members second tank members caps tank - The
tank 14 has arefrigerant inlet portion 14 e at an end (e.g., lower end inFIG. 1 ) thereof. Although not illustrated, an inlet pipe is coupled to therefrigerant inlet portion 14 e for introducing the high pressure, high temperature refrigerant discharged from the compressor into theheat exchanger 10. - The
tank 15 has arefrigerant outlet portion 15 e at an end (e.g., upper end inFIG. 1 ) thereof. Although not illustrated, an outlet pipe is coupled to therefrigerant outlet portion 15 e for discharging a liquid-phase refrigerant from theheat exchanger 10 toward an expansion valve of the refrigerating cycle. - At the ends of the
heat exchanging part 13,side plates heat exchanger 10. Theside plates tubes 11 and ends of theside plates tanks tubes 11, thefins 12, and thetanks - Referring to
FIGS. 2 and 3 , each of thetubes 11 is constructed of a pair ofplate members plate members - Each of the
plate members flat base wall 20 and a plurality ofprojections 21 projecting from theflat base wall 20. Theplate members projections 21 project in opposite directions and thebase walls 20 have surface contact. Also, theplate members projections 21 overlap with each other. Thus,refrigerant passages 22 through which the refrigerant flows are formed between the pairedplate members - Each of the
projections 21 projects from thebase wall 20 at a substantially middle position with respect to a tube width direction D2, which is perpendicular to a tube longitudinal direction D1. Theprojection 21 has a flat wall on its top andcurved side walls 23, which face in the tube longitudinal direction D1. Each of theside walls 23 of theprojection 21 extends in the tube width direction D2 in a serpentine or meandering manner. - The
projections 21 are arranged at a regular pitch P in the tube longitudinal direction D1 such that clearances are provided between theadjacent projections 21, i.e., theside walls 23 of theadjacent projections 21 as grooves. Namely, the grooves having a serpentine shape are formed between theadjacent projections 21 on outer surfaces of thetubes 11. The grooves serve as air passage portions (external fluid passage portions) 24 for allowing the air in a serpentine or meandering manner. - A bottom wall of the
air passage portion 24 includes aflat wall 24 c and first and second recessedportions flat wall 24 c toward an inside of thetube 11 throughstep portions portions 24 a are formed at position corresponding to peaks or most curved portions of the serpentine shapedair passage portion 24 and the second recessedportions 24 b are formed at position corresponding to the end of theair passage portion 24. The first and second recessedportions base wall 20. In other word, the first and second recessedportions base wall 20. Theflat wall 24 c slightly project from thebase wall 20 toward an outside of thetube 11. - Also, the
air passage portions 24 of theplate members portions plate member 18 overlap with the first and second recessedportions plate member 19. Thus, theplate members portions step portions - In the
tube 11, therefrigerant passage 23 has a complex serpentine shape as shown by arrows B inFIG. 2 . Since theair passage portions 24 of the twoplate members refrigerant passage 23 extends in the tube longitudinal direction D1 while meandering in a direction in which a height of thetube 11 is measured (i.e., in an up and down direction inFIG. 2 ). - Further, since the first recessed
portions 24 a of the twoplate members refrigerant passage 23 diverges at the first recessedportions 24 a and merges downstream of the first recessedportions 24 a. As such, therefrigerant passage 23 extends in the tube longitudinal direction D1 while repetitively diverging and merging in the tube width direction D2. Namely, therefrigerant passage 23 is formed in a serpentine manner both in the tube longitudinal direction D1 and in the tube width direction D2. - As shown in
FIG. 2 , thefins 12 are made of a bare plate without coated by a brazing material. The bare plate is for example made of an aluminum material and is formed into a corrugated shape. - Each of the
fin 12 includes joiningportions projections 21 and connectingwalls portions portions walls tubes 11 are stacked (i.e., up and down direction inFIG. 2 ). Although not illustrated, the connectingwalls walls - Next, an effect of heat exchange between the refrigerant and the air in the
heat exchanging part 13 will be described. As shown by the arrows B inFIG. 2 , since the refrigerant flows inside of thetubes 11 while meandering complexly, the flow of the refrigerant is disturbed. As such, the coefficient of heat transfer of the refrigerant improves. Accordingly, efficiency of heat transfer improves. - On the other hand, the air that flows through areas separated from the
tubes 11 flows along thefins 12, as shown by an arrow C inFIG. 2 . This air receives heat from thefins 12 and then flows out of thefins 12. Thus, thefins 12 are cooled by the air passing through thefins 12. - Also, the air that flows adjacent to the
tubes 11 receives heat from thetubes 11 and is discharged from theheat exchanging part 13 after cooling thetubes 11. In this case, as the air flows through theair passage portions 24 in the serpentine manner, as shown by an arrow D inFIG. 2 , the flow of this air is disturbed. As such, the coefficient of heat transfer of the air improves. Accordingly, efficiency of heat transfer improves. - In addition, as the air is contracted when flowing into the
air passage portions 24, the coefficient of heat transfer of the air improves. Further, because the surface area of heat transfer is increased by theair passage portions 24, the amount of heat radiation from thetube 11 to the air is increased. - Furthermore, the flow of air is further disturbed by the
step portions air passage portions 24. With this, the coefficient of heat transfer of the air further improves. - Next, connecting structure of the
tanks tubes 11 will be described with reference toFIGS. 4 to 7 . The connecting structure of thetank 14 and thetubes 11 are the same as the connecting structure of thetank 15 and thetubes 11. InFIGS. 4 to 7 , therefore, component parts regarding thetank 15 are indicated by numerals in parentheses. - The
first tank member tubes 11. Thefirst tank member flat wall plate flat wall plate plate first tank member - As shown in
FIGS. 5 and 6 , theflat wall first tank member first hole portions first hole portions first tank member plate second hole portions - Specifically, the
plate tubular portions second hole portions tubular portions tank tubular portions tubular portion - The
plate flat wall second hole portions first hole portions tube insertion portions second hole portions FIG. 6 . In other words, a perimeter surface (perimeter portion) defining the opening of eachtube insertion portion first hole portion second hole portion - Here, the
tubular portion tube insertion portion flat wall first tank member tubular portion projections 21 of thetubes 11. - As shown in
FIG. 7 , in a condition that thelongitudinal end tube 11 is inserted in the opening of thetube insertion portion 14 d, 15 f, the outer surfaces of thetube 11 is joined to the perimeter surface of the opening of thetube insertion portion - Further, the
longitudinal end tube 11 is inserted in the opening of thetube insertion portion FIG. 3 overlaps with the perimeter surface of thetube insertion portion FIGS. 3 and 7 , the perimeter surface of thetube insertion portion air passage portion 24 on each of theplate members - As such, the
air passage portion 24 does not extend over the perimeter surface of thetube insertion portion heat exchanging part 13 through theair passage portions 24. Accordingly, it is less likely that the refrigerant will leak outside of theheat exchanging part 13 through theair passage portions 24. - Since the
tubular portion tube insertion portion air passage portion 24 of thelongitudinal end tube 11 is entirely covered by the perimeter surface of thetube insertion portion - Also, the
tube insertion portion first hole portion first tank member second hole portion plate plate member - Since the
plate member tubular portions tube insertion portions tubular portions - Since the length L of the perimeter surface of the
tube insertion portion projections 21 of thetube 11, at least oneair passage portion 24 is entirely covered by the perimeter surface of thetube insertion portion tube 11 and thetank - As a result, the leakage of the refrigerant through the
air passage portion 24 is restricted without being affected by the positional relation between thetube 11 and thetank air passage portion 24 is restricted without being affected by assembling accuracy of thetube 11 to thetank - In fact, the longer the length L of the perimeter surface is, the more securely the leakage of the refrigerant through the
air passage portion 24 is restricted. However, the length L is longer than necessary as shown by a chain double-dashed line inFIG. 7 , the pluralair passage portions 24 of eachplate member - A second embodiment of the present invention will be described with reference to
FIG. 8 . As shown inFIG. 8 ,tubular portions first hole portions first tank member tube insertion portion tubular portion first tank member tubular portion plate tubular portions tank tubular portions - The perimeter portion of the
tube insertion portion tubular portion first tank member tubular portion plate tube insertion portion tubular portion first tank member tubular portion second hole portion - In this case, the length L is increased greater than the length L of the first embodiment shown in
FIG. 7 . Therefore, the communication between the inside space of theheat exchanging part 13 and the outside space is more securely restricted. As such, the leakage of the refrigerant through theair passage portion 24 is further effectively restricted. - In this case, the
tubular portions first tank member tank tubular portions air passage 24 outside of thetank tubular portions first tank member air passage portions 24. - If the length L1 of the
tubular portion FIG. 8 , the flow of the refrigerant inside of thetank tubes 11 from thetank 14, the flow of the refrigerant collected into thetank 15 from thetubes 11 will be disturbed by such the longtubular portions heat exchanger 10. Therefore, it is necessary to consider this matter. - A third embodiment of the present invention will be described with reference to
FIG. 9 . As shown inFIG. 9 , asecond plate FIG. 6 . Thesecond plate third hole portions flat wall first tank member third hole portions first hole portions first tank member second hole portion tube insertion portion first hole portion second hole portion third hole portion - In this embodiment, the
second plate second plate first tank member second plate first plate flat wall first tank member - The
second plate first tank member second plate second plate first tank member - In this embodiment, the length L of the perimeter surface of the
tube insertion portion first tank member tubular portion second plate - Accordingly, the length L is increased greater than the length L of the first embodiment. Therefore, the communication of the inside space of the
heat exchanging part 13 with the outside space through theair passage portion 24 is further restricted. As such, the leakage of the refrigerant through theair passage portion 24 is further restricted. - A fourth embodiment will be described with reference to
FIG. 10 . In the third embodiment, thesecond plate tubular portion third hole portion tubular portion tubular portion tank tubular portion 35 a, 36 b is formed by burring. Thetube insertion portion tubular portions third hole portions first hole portion - In this embodiment, the length L of the perimeter surface of the
tube insertion portion first tank member tubular portion tubular portion - Accordingly, the length L of the perimeter surface of the
tube insertion portion air passage portion 24 is further effectively restricted. - A fifth embodiment will be described with reference to
FIGS. 11 and 12 . In the fifth embodiment, the opening of thetube insertion portion tubular member - As shown in
FIG. 12 , thetubular member tubular wall portion annular flange portion tubular wall portion flange portion tubular wall portion tubular member - The
tubular member first hole portion tank flange portion flat wall first tank member flange portion flat wall first tank member - In this case, the perimeter surface of the
tube insertion portion tubular member tube insertion portion tubular member - Also in this case, the leakage of the refrigerant through the
air passage portion 24 is restricted, similar to the first embodiment. - A sixth embodiment will be described with reference to
FIG. 13 . As shown inFIG. 13 , the opening of thetube insertion portion first hole portion first tank member tubular wall portion tubular member - In the sixth embodiment, the
tubular wall portion first hole portion flange portion first tank member tubular member first hole portion flange portion first tank member - The perimeter surface of the
tube insertion portion tubular member first hole portion first tank member tubular member - Also in this case, the leakage of the refrigerant through the
air passage portion 24 is restricted, similar to the fifth embodiment. - In the first embodiment, the
tubular portion plate tube insertion portion tubular portion first hole portion plate tubular portion plate first tank member tube insertion portion first hole portion 29, and an inner surface of an opening of theplate air passage 24 of thetube 11 is entirely covered by the perimeter surface of thetube insertion portion - In the above embodiments, the opening of the
tube insertion portion plural tank members tube insertion portion FIGS. 4 to 7 , theplate tube insertion portion first hole portion first hole portion first tank member tubular portion plate - In the above embodiments, the
air passage portions 24 are grooves extending in the tube width direction D2 in the serpentine manner. However, the shape of theair passage portions 24 is not limited to the serpentine shape. For example, theair passage portions 24 may be straight grooves extending obliquely with respect to the tube width direction D2. - In the above embodiments, each
tube 11 is constructed of the pair ofplate members projections 21. However, the structure of thetube 11 is not limited to the above. For example, only one of theplate members projections 21. Also, thetube 11 may be provided by a cylindrical tube or a flat tube formed by extrusion. When thetube 11 is formed by the extrusion, the grooves as theair passage portions 24 are formed on the outer surfaces of thetube 11 by pressing thetube 11 from the outside. - In the above embodiments, the
tube insertion portion tube insertion portion tube insertion portion tube 11. - In the above first to fourth embodiments, the shape of the
plate plate first tank member - The
heat exchanger 10 is not limited to the refrigerant condenser. Theheat exchanger 10 may be any heat exchangers used for various purposes. - The example embodiments of the present invention are described above. However, the present invention is not limited to the above embodiments, but may be implemented in other ways without departing from the spirit of the invention.
Claims (9)
1. A heat exchanger comprising:
a plurality of tubes for performing heat exchange between an internal fluid flowing inside of the tubes and an external fluid flowing outside of the tubes, each of the tubes having projections that project from an outer surface thereof, the projections arranged in a longitudinal direction of the tube such that grooves are provided between the adjacent projections as external fluid passage portions for allowing the external fluid to flow; and
a tank including a plurality of tube insertion portions defining openings in which ends of the tubes are disposed, wherein
each of the tube insertion portions is configured such that a perimeter surface defining the opening thereof entirely covers at least one external fluid passage portion of the end of the tube.
2. The heat exchanger according to claim 1 , wherein
the plurality of projections are arranged at a regular pitch in the longitudinal direction of the tube, and
the perimeter surface of the opening of the tube insertion portion has a length equal to or greater than the pitch of the projections with respect to the longitudinal direction of the tube.
3. The heat exchanger according to claim 1 , wherein
each of the tube insertion portions includes a tubular portion that projects in a direction parallel to the longitudinal direction of the tube,
the tubular portion has an inner surface and defines an opening at least as a portion of the opening of the tube insertion portion, and
the inner surface of the tubular portion is included in the perimeter surface of the opening of the tube insertion portion.
4. The heat exchanger according to claim 3 , wherein the tubular portion projects outside of the tank.
5. The heat exchanger according to claim 3 , wherein the tubular portion projects inside of the tank.
6. The heat exchanger according to claim 3 , wherein the tubular portion is formed by burring.
7. The heat exchanger according to claim 3 , wherein
the tank has a plurality of tank members each defining a plurality of openings, the plurality of tank members are disposed such that the openings thereof are aligned with each other and the openings of the tube insertion portions are provided by the openings of the tank members,
the tubular portions are provided by at least one of the tank members, and
the perimeter surface of the opening of each tube insertion portion is provided by the inner surface of the tubular portion and a surface that defines the opening of the remaining tank member.
8. The heat exchanger according to claim 3 , wherein
the tank has a tank member defining a plurality of openings and tubular members each defining an opening,
the tank member and the tubular members are joined with each other such that the openings of the tubular members correspond to the openings of the tank member, and the opening of each tube insertion portion is provided by one opening of the tank member and the opening of one tubular member, and
the tubular portions are provided by the tubular members.
9. The heat exchanger according to claim 1 , wherein
the tank has a plurality of tank members each defining a plurality of openings,
the plurality of tank members are disposed such that the openings thereof are aligned with each other and provide the openings of the tube insertion portions, and
the perimeter surface of the opening of each tube insertion portion is provided by surfaces that define the openings of the tank members.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-181260 | 2006-06-30 | ||
JP2006181260A JP2008008574A (en) | 2006-06-30 | 2006-06-30 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20080000627A1 true US20080000627A1 (en) | 2008-01-03 |
Family
ID=38875385
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/824,526 Abandoned US20080000627A1 (en) | 2006-06-30 | 2007-06-29 | Heat exchanger |
Country Status (2)
Country | Link |
---|---|
US (1) | US20080000627A1 (en) |
JP (1) | JP2008008574A (en) |
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FR2947330A1 (en) * | 2009-06-25 | 2010-12-31 | Valeo Systemes Thermiques | Heat exchanger for forming gas cooler of air-conditioning system in motor vehicle, has inactive tube identical to other tubes in bundle and whose end is arranged so as to be not in fluidic communication with fluid in collector box |
US20110108252A1 (en) * | 2008-07-01 | 2011-05-12 | Arnaud Contet | Radiator module |
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US8656988B1 (en) * | 2010-03-03 | 2014-02-25 | Adams Thermal Systems, Inc. | External reinforcement of connections between header tanks and tubes in heat exchangers |
US20150129188A1 (en) * | 2013-11-08 | 2015-05-14 | Delphi Automotive Systems Luxembourg Sa | Heat exchanger |
FR3056723A1 (en) * | 2016-09-28 | 2018-03-30 | Valeo Systemes Thermiques | THERMAL EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE |
US11073345B2 (en) | 2018-10-31 | 2021-07-27 | Hanon Systems | Heat exchanger header with stiffening element |
USD967361S1 (en) * | 2020-08-17 | 2022-10-18 | Mercracing, Llc | Heat exchanger |
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JP2018179387A (en) * | 2017-04-11 | 2018-11-15 | 三菱電機株式会社 | Heat exchanger and manufacturing method of the same |
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US9631871B2 (en) * | 2008-07-01 | 2017-04-25 | Titanx Engine Cooling Holding Ab | Radiator module |
US20110108252A1 (en) * | 2008-07-01 | 2011-05-12 | Arnaud Contet | Radiator module |
US20120037346A1 (en) * | 2009-04-20 | 2012-02-16 | Kim Young Mo | Heat exchanger |
US9250021B2 (en) * | 2009-04-20 | 2016-02-02 | Kyungdong Navien Co., Ltd. | Heat exchanger |
FR2947330A1 (en) * | 2009-06-25 | 2010-12-31 | Valeo Systemes Thermiques | Heat exchanger for forming gas cooler of air-conditioning system in motor vehicle, has inactive tube identical to other tubes in bundle and whose end is arranged so as to be not in fluidic communication with fluid in collector box |
US20110140820A1 (en) * | 2009-12-10 | 2011-06-16 | Guentert Iii Joseph J | Hyper-cooled liquid-filled transformer |
US8081054B2 (en) | 2009-12-10 | 2011-12-20 | Guentert Iii Joseph J | Hyper-cooled liquid-filled transformer |
US8656988B1 (en) * | 2010-03-03 | 2014-02-25 | Adams Thermal Systems, Inc. | External reinforcement of connections between header tanks and tubes in heat exchangers |
US20150129188A1 (en) * | 2013-11-08 | 2015-05-14 | Delphi Automotive Systems Luxembourg Sa | Heat exchanger |
US9739541B2 (en) * | 2013-11-08 | 2017-08-22 | Mahle International Gmbh | Heat exchanger |
FR3056723A1 (en) * | 2016-09-28 | 2018-03-30 | Valeo Systemes Thermiques | THERMAL EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE |
WO2018060621A1 (en) * | 2016-09-28 | 2018-04-05 | Valeo Systemes Thermiques | Heat exchanger, in particular for a motor vehicle |
US11073345B2 (en) | 2018-10-31 | 2021-07-27 | Hanon Systems | Heat exchanger header with stiffening element |
USD967361S1 (en) * | 2020-08-17 | 2022-10-18 | Mercracing, Llc | Heat exchanger |
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