US20110011568A1 - Oil cooler for transmission - Google Patents
Oil cooler for transmission Download PDFInfo
- Publication number
- US20110011568A1 US20110011568A1 US12/922,301 US92230109A US2011011568A1 US 20110011568 A1 US20110011568 A1 US 20110011568A1 US 92230109 A US92230109 A US 92230109A US 2011011568 A1 US2011011568 A1 US 2011011568A1
- Authority
- US
- United States
- Prior art keywords
- heat exchange
- shaped protrusions
- ridges
- oil cooler
- plate
- 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
- 230000005540 biological transmission Effects 0.000 title claims abstract description 50
- 239000002826 coolant Substances 0.000 claims description 26
- 238000009751 slip forming Methods 0.000 claims description 3
- 230000001965 increasing effect Effects 0.000 description 12
- 238000005219 brazing Methods 0.000 description 6
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 238000004049 embossing Methods 0.000 description 3
- 230000002708 enhancing effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000000465 moulding Methods 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000002542 deteriorative effect Effects 0.000 description 1
Images
Classifications
-
- 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
- F28F3/046—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 the deformations being linear, e.g. corrugations
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
- F16H57/0417—Heat exchangers adapted or integrated in the gearing
-
- 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
- F28D1/0308—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 the conduits being formed by paired plates touching each other
- F28D1/0325—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 the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—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 the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
-
- 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
- F28D2021/0049—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for lubricants, e.g. oil coolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2240/00—Spacing means
Definitions
- the present invention relates generally to transmission oil coolers and, more particularly, to a transmission oil cooler which enhances the heat exchange efficiency and has enhanced assembly performance.
- Transmissions for vehicles convert the unidirectional rotating force of engines into the drive force of the vehicles. Transmissions are indispensable to changing the driving directions of vehicles, for example, between forward movement and backward movement, or to controlling the speed of the vehicles. Transmissions are classified into a variety of types, for example, a manual transmission, an automatic transmission, a continuously variable transmission (CVT), etc.
- CVT continuously variable transmission
- Such a transmission includes therein a plurality of operating elements, such as gears, etc.
- Transmission oil circulates in the transmission to lubricate or clean these operating elements.
- the transmission oil is heated by heat transferred from the elements.
- an oil cooler is generally used to cool the transmission oil.
- the oil cooler is located in a radiator and is thus cooled by radiator coolant.
- the oil cooler included in the radiator is constructed such that heat exchange tubes are stacked one on top of another.
- the heat exchange tubes form oil paths through which oil passes.
- Each heat exchange tube comprises a pair of plates. The plates are coupled to each other by brazing the perimeters thereof, thus forming the oil path between the plates. Furthermore, the stacked heat exchange tubes are spaced apart from each other at regular intervals so that a coolant path is formed between the heat exchange tubes.
- Each heat exchange tube has an inlet port and an outlet port on the respective opposite ends thereof.
- the oil paths of the heat exchange tubes communicate with each other using the inlet ports and the outlet ports.
- an object of the present invention is to provide a transmission oil cooler which enhances the heat exchange efficiency and has enhanced assemblability.
- the present invention provides a transmission oil cooler, including a plurality of heat exchange tubes stacked one on top of another.
- a coolant path is formed between the heat exchange tubes so that a coolant passes along the coolant path.
- Each of the heat exchange tubes comprises an upper plate and a lower plate coupled to each other by bonding perimeters thereof to each other.
- the heat exchange tube has an oil path along which oil passes.
- a plurality of recesses is formed in each of facing surfaces of the upper and lower plates. The recesses of the upper plate cross over the recesses of the lower plate, thus forming a cross structure of the oil path.
- a plurality of ridges and a plurality of valleys are continuously and alternately formed on each of an upper surface of the upper plate and a lower surface of the lower plate.
- the ridges and valleys extend parallel to each other in a diagonal direction.
- Each of the heat exchange tubes has, on opposite ends thereof, an inlet port through which the oil is drawn into the heat exchange tube, and an outlet port through which the oil is discharged out of the heat exchange tube.
- the oil paths of the heat exchange tubes communicate with each other through the inlet ports and the outlet ports.
- the upper plate comprises an upper flange provided around each of the inlet port and the outlet port, the upper flange protruding upwards from the upper surface of the upper plate
- the lower plate comprises a lower flange provided around each of the inlet port and the outlet port, the lower flange protruding downwards from the lower surface of the lower plate.
- Protrusions are discontinuously or continuously formed along the ridges on the upper and lower plates.
- the upper flange and the lower flanges of the adjacent heat exchange tubes may be coupled to each other by fitting.
- At least one of the upper and lower flanges may be tapered inwards on an end thereof.
- the protrusions may comprise a plurality of upper pin-shaped protrusions provided on the corresponding ridges of the upper plates, and a plurality of lower pin-shaped protrusions provided on the corresponding ridges of the lower plates.
- the upper pin-shaped protrusions and the lower pin-shaped protrusions of the adjacent heat exchange tubes may be in contact with each other.
- the upper pin-shaped protrusions may be arranged on an upper surface of each of the corresponding ridges of the upper plate at positions spaced apart from each other at regular intervals.
- the lower pin-shaped protrusions may be arranged on a lower surface of each of the corresponding ridges of the lower plate at positions spaced apart from each other at regular intervals.
- the upper pin-shaped protrusions and the lower pin-shaped protrusions may be disposed at positions at which the recesses of the upper plate cross over the recesses of the lower plate.
- Each of the upper pin-shaped protrusions may have a contact surface on an upper surface thereof, and each of the lower pin-shaped protrusions may have a contact surface on a lower surface thereof.
- a cross-section of each of the upper and lower pin-shaped protrusions may have one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
- the protrusions may comprise a plurality of bar-shaped protrusions provided between the ridges of the upper and lower plates. Each of the bar-shaped protrusions extends in a longitudinal direction of the ridges. A height of each of the bar-shaped protrusions may be greater than a height of the ridges, and the bar-shaped protrusions of the adjacent heat exchange tubes may be in contact with each other.
- the recesses formed in the facing surfaces of the upper and lower plates may comprise a plurality of first recesses formed at sides opposite to the respective ridges, and a plurality of second recesses formed at sides opposite to the respective bar-shaped protrusions.
- Each of the bar-shaped protrusions of the upper plate may have a contact surface on an upper surface thereof, and each of the bar-shaped protrusions of the lower plate may have a contact surface on a lower surface thereof.
- a cross-section of each of the bar-shaped protrusions of the upper and lower plates may have one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
- a positioning depression and a positioning protrusion may be respectively formed at predetermined positions corresponding to each other on portions at which the upper plate is in contact with the lower plate.
- upper and lower flanges are provided around inlet and outlet ports of upper and lower plates of each heat exchange tube.
- the cross-sectional area of the coolant path is increased by widening the interval between the heat exchange tubes, thus enhancing the heat exchange efficiency.
- FIG. 1 is a perspective view showing a transmission oil cooler, according to a first embodiment of the present invention
- FIG. 2 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal direction according to the first embodiment of the present invention
- FIG. 3 is an exploded perspective view showing an upper plate and a lower plate of a heat exchange tube according to the first embodiment of the present invention
- FIG. 4 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal and transverse directions according to the first embodiment of the present invention
- FIG. 5 is a side sectional view of the transmission oil cooler according to the first embodiment of the present invention.
- FIG. 6 is a front sectional view of the transmission oil cooler according to the first embodiment of the present invention.
- FIG. 7 is a front sectional view of a modification of the transmission oil cooler of FIG. 6 ;
- FIG. 8 is an exploded front sectional view of a modification of the transmission oil cooler of FIG. 7 ;
- FIG. 9 is a partially-broken perspective view of a transmission oil cooler taken along the longitudinal direction according to the second embodiment of the present invention.
- FIG. 10 is an exploded perspective view showing an upper plate and a lower plate of a heat exchange tube according to the second embodiment of the present invention.
- FIG. 11 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal and transverse directions according to the second embodiment of the present invention.
- FIG. 12 is a side sectional view of the transmission oil cooler according to the second embodiment of the present invention.
- FIG. 13 is a front sectional view of the transmission oil cooler according to the second embodiment of the present invention.
- FIG. 14 is a front sectional view of a modification of the transmission oil cooler of FIG. 13 ;
- FIG. 15 is an exploded front sectional view of a modification of the transmission oil cooler of FIG. 14 .
- FIGS. 1 through 8 illustrate a transmission oil cooler, according to a first embodiment of the present invention.
- the transmission oil cooler of the present invention includes a plurality of heat exchange tubes 10 which are stacked one on top of another.
- each heat exchange tube 10 has an oil path 15 along which oil passes.
- the heat exchange tube 10 comprises an upper plate 11 and a lower plate 12 which are coupled to each other. It is desirable that the upper plate 11 and the lower plate 12 be coupled to each other by bonding the perimeters 11 a and 12 a thereof to each other.
- the upper plate 11 and the lower plate 12 are made of metal, such as aluminum, etc., which has superior heat conductivity.
- the perimeters lla and 12 a of the upper and lower plates 11 and 12 are bonded to each other by brazing or the like.
- ridges 16 and valleys 18 are continuously and alternately formed on the upper surface of the upper plate 11 .
- Ridges 17 and valleys 19 are continuously and alternately formed on the lower surface of the lower plate 12 .
- the ridges 16 and the valleys 18 extend parallel to each other in a diagonal direction of the upper plate 11 .
- the ridges 17 and the valleys 19 also extend parallel to each other in a diagonal direction of the lower plate 12 .
- the ridges 16 and the valleys 18 of the upper plate 11 cross over the ridges 17 and the valleys 19 of the lower plate 12 .
- a plurality of recesses 11 b and 12 b are formed in the facing surfaces of the upper and lower plates 11 and 12 by the ridges 16 and 17 and the valley 18 and 19 .
- the recesses 11 b and 12 b are respectively formed at sides opposite to the ridges 16 and 17 .
- the recesses 11 b of the upper plate 11 also cross over the recesses 12 b of the lower plate 12 .
- the recesses 11 b extend parallel to each other in the diagonal direction of the upper plate 11
- the recesses 12 b also extend parallel to each other in the diagonal direction of the lower plate 12 .
- the ridges 16 and 17 , the valleys 18 and 19 and the recesses 11 b and 12 b may be formed in the upper and lower plates 11 and 12 by a molding or embossing process.
- the oil path 15 forms a cross structure because the recesses 11 b and 12 b of the upper and lower plates 11 and 12 cross over each other.
- oil can flow in a zigzag manner along the oil path 15 .
- the capacity to treat flowing oil can be increased, and the heat exchange efficiency between oil and coolant can be enhanced by increasing the contact area of oil.
- a coolant path 28 along which radiator coolant passes is formed between the adjacent heat exchange tubes 10 which are stacked one on top of the other.
- the coolant path 28 is formed by spacing the heat exchange tubes 10 apart from each other by a predetermined distance.
- protrusions 21 and 22 are provided on opposite sides of each heat exchange tube 10 to increase and maintain the distance by which the adjacent heat exchange tubes 10 are spaced apart from each other.
- the protrusions 21 and 22 are discontinuously formed along the longitudinal directions of the ridges 16 and 17 , respectively.
- the protrusions 21 and 22 comprise upper pin-shaped protrusions 21 which protrude from the upper surface of the upper plate 11 , and lower pin-shaped protrusions 22 which protrude from the lower surface of the lower plate 12 .
- the upper pin-shaped protrusions 21 are formed on the upper surface of the ridges 16 of the upper plate 11 and are spaced apart from each other at regular intervals.
- the lower pin-shaped protrusions 22 are formed on the lower surface of the ridges 17 of the lower plate 12 and are spaced apart from each other at regular intervals.
- the upper pin-shaped protrusions 21 and the lower pin-shaped protrusions 22 are discontinuously formed on the ridges 16 and 17 , respectively.
- the lower pin-shaped protrusions 22 of the heat exchange tube 10 which is disposed at the upper position come into contact with the respective upper pin-shaped protrusions 21 of the heat exchange tube 10 which is disposed at the lower position.
- the pin-shaped protrusions 21 and 22 are brought into contact with each other and thus supported by each other, the distance by which the adjacent heat exchange tubes 10 are spaced apart from each other can be increased and maintained. Thereby, the cross-sectional area of the coolant path 28 is increased.
- the pin-shaped protrusions 21 and 22 which come into contact with each other are bonded to each other by welding or the like.
- Contact surfaces 21 a and 22 a are respectively formed on the upper surfaces of the upper pin-shaped protrusions 21 and the lower surfaces of the lower pin-shaped protrusions 22 .
- the bonding of the pin-shaped protrusions 21 and 22 can be facilitated by contact between the contact surfaces 21 a and 22 a.
- each of the upper and lower pin-shaped protrusions 21 and 22 may have a trapezoidal shape, a rectangular shape, or a round shape, such as an elliptical or circular shape. Furthermore, in the case where the pin-shaped protrusions 21 and 22 have trapezoidal or rectangular shapes, the bonding of the contact surfaces 21 a and 22 a of the pin-shaped protrusions 21 and 22 can be further facilitated.
- a height h 1 of each of the upper and lower plates 11 and 12 including the ridges 16 and 17 and the upper and lower pin-shaped protrusions 21 and 22 be less than twice a height h 2 of each ridge 16 , 17 .
- the upper pin-shaped protrusions 21 and the lower pin-shaped protrusions 22 are disposed at positions at which the recesses 11 b of the upper plate 11 cross over the recesses 12 b of the lower plate 12 , thus making the stacked structure of the heat exchange tubes 10 more stable.
- a positioning depression 11 c and a positioning protrusion 12 c are respectively formed at corresponding predetermined positions on the perimeters lla and 12 a of the upper plate 11 and the lower plate 12 . Positioning of the upper and lower plates 11 and 12 to each other can be facilitated by the positioning depression 11 c and protrusions 12 c. Therefore, operation of temporarily coupling the upper plate 11 to the lower plate 12 can be easily and rapidly conducted. Thereby, the coupling between the upper and lower plates 11 and 12 can become precise and reliable.
- each heat exchange tube 10 has an inlet port 13 formed in a first end thereof and an outlet port 14 formed in a second end thereof.
- the inlet port 13 and the outlet port 14 communicate with the oil path 15 .
- the inlet ports 13 of the heat exchange tubes 10 communicate with each other, and the outlet ports 14 of the heat exchange tubes 10 also communicate with each other.
- the upper plate 11 includes an upper flange 23 which is provided around each of the inlet port 13 and the outlet port 14 and protrudes upwards from the upper surface of the upper plate 11 .
- the lower plate 12 includes a lower flange 24 which is provided around each of the inlet port 13 and the outlet port 14 of the lower plate 12 and protrudes downwards from the lower surface of the lower plate 12 .
- the upper flange 23 and the lower flange 24 are designed such that they are coupled to each other in a fitting manner.
- the upper flanges 23 of the heat exchange tube 10 which is disposed at the lower position are fitted into the corresponding lower flanges 24 of the heat exchange tube 10 which is disposed at the upper position, thus enhancing the sealability therebetween.
- the upper flanges 23 and the lower flanges 24 that are coupled to each other can be more reliably sealed by brazing. Thereby, the inlet ports 13 and the outlet ports 14 of the heat exchange tube 10 are sealed off from the coolant path 28 .
- an inlet port cap 25 having an inlet hole 25 a is coupled to the upper flange 23 of the uppermost heat exchange tube 10 which is related to the inlet port 13 .
- An outlet port cap 26 having an outlet hole 26 a is coupled to the other upper flange 23 of the uppermost heat exchange tube 10 which is related to the outlet port 14 .
- a stopper 27 is removably or integrally coupled to each lower flange 24 of the lowermost heat exchange tube 10 .
- the circumferential outer surfaces of the upper flanges 23 may be fitted into the circumferential inner surfaces of the corresponding lower flanges 24 .
- the circumferential outer surfaces of the lower flanges 24 may be fitted into the circumferential inner surfaces of the corresponding upper flanges 23 .
- an upper end 23 a of the upper flange 23 of each heat exchange tube 10 which is fitted into the corresponding lower flange 24 of the corresponding upper heat exchange tube 10 may be tapered towards the center axis of the upper flange 23 .
- a lower end 24 a of the lower flange 24 may be tapered towards the center axis thereof.
- flanges which are fitted into corresponding flanges of a corresponding adjacent heat exchange tube are tapered on the ends 23 a, 24 a thereof towards the center axes thereof.
- This structure can further enhance the assemblability and sealability of the upper and lower flanges 23 and 24 .
- FIGS. 9 through 15 illustrate a transmission oil cooler, according to a second embodiment of the present invention.
- the transmission oil cooler according to the second embodiment of the present invention includes a plurality of heat exchange tubes 10 .
- the heat exchange tubes 10 are stacked one on top of another.
- Each heat exchange tube 10 has an oil path 15 along which oil passes.
- the heat exchange tube 10 comprises an upper plate 11 and a lower plate 12 which are coupled to each other.
- the upper plate 11 is coupled to the lower plate 12 in such a way that a perimeter 11 a of the upper plate 11 is bonded to a perimeter 12 a of the lower plate 12 by brazing or the like.
- the upper plate 11 and the lower plate 12 are made of metal, such as aluminum, etc., which has superior heat conductivity.
- the perimeters 11 a and 12 a of the upper and lower plates 11 and 12 may be bonded to each other by welding.
- ridges 16 and valleys 18 are continuously and alternately formed on the upper surface of the upper plate 11 .
- Ridges 17 and valleys 19 are continuously and alternately formed on the lower surface of the lower plate 12 .
- the ridges 16 and the valleys 18 extend parallel to each other in a diagonal direction of the upper plate 11 .
- the ridges 17 and the valleys 19 also extend parallel to each other in a diagonal direction of the lower plate 12 .
- the ridges 16 and the valleys 18 of the upper plate 11 cross over the ridges 17 and the valleys 19 of the lower plate 12 .
- a plurality of first recesses 11 b and 12 b are formed in the facing surfaces of the upper and lower plates 11 and 12 by the ridges 16 and 17 and the valley 18 and 19 .
- the first recesses 11 b and 12 b are respectively formed at sides opposite the ridges 16 and 17 .
- the first recesses 11 b of the upper plate 11 also cross over the first recesses 12 b of the lower plate 12 .
- the first recesses 11 b extend parallel to each other in the diagonal direction of the upper plate 11
- the first recesses 12 b also extend parallel to each other in the diagonal direction of the lower plate 12 .
- the ridges 16 and 17 , the valleys 18 and 19 and the first recesses 11 b and 12 b may be formed in the upper and lower plates 11 and 12 by a molding or embossing process.
- the oil path 15 forms a cross structure because the first recesses 11 b and 12 b of the upper and lower plates 11 and 12 cross over each other.
- oil can flow in a zigzag manner along the oil path 15 .
- the capacity with which flowing oil is treated can be increased, and the heat exchange efficiency between oil and coolant can be enhanced by increasing contact area of oil.
- a coolant path 28 along which radiator coolant passes is formed between the adjacent heat exchange tubes 10 which are stacked one on top of the other.
- the coolant path 28 is formed by spacing the heat exchange tubes 10 apart from each other by a predetermined distance.
- protrusions 31 and 32 are provided on the opposite sides of each heat exchange tube 10 to increase and maintain the distance by which the adjacent heat exchange tubes 10 are spaced apart from each other.
- the cross-sectional area of the coolant path 28 can be increased without reducing the cross-sectional area of the oil path 15 .
- the protrusions 31 and 32 are continuously formed along the longitudinal directions of the ridges 16 and 17 , respectively.
- the protrusions 31 and 32 of the second embodiment comprise bar-shaped protrusions 31 and 32 , each of which is provided between adjacent ridges 16 or 17 and extend along the longitudinal direction of the ridges 16 or 17 .
- the bar-shaped protrusions 31 are arranged between the ridges 16 at positions spaced apart from each other at regular intervals, and the bar-shaped protrusions 32 are arranged between the ridges 17 at positions spaced apart from each other at regular intervals.
- the bar-shaped protrusions 31 and 32 respectively extend parallel to the ridges 16 and 17 .
- each bar-shaped protrusion 31 , 32 continuously extends a predetermined length between the corresponding ridges 16 , 17 and between corresponding valleys 18 , 19 .
- each bar-shaped protrusion 31 , 32 also extends on a plane in a diagonal direction in the same manner as that of the ridges 16 , 17 .
- each bar-shaped protrusion 31 , 32 of the upper or lower plate 11 or 12 is greater than that of each ridge 16 , 17 . As shown in FIG. 9 , it is desirable that the height hl of the bar-shaped protrusion 31 , 32 be less than twice the height h 2 of each ridge 16 , 17 . Meanwhile, the ridges 16 and 17 and the bar-shaped protrusions 31 and 32 may be formed by a molding or embossing process.
- each of the bar-shaped protrusions 31 and 32 of the upper and lower plates 11 and 12 may have a trapezoidal shape, a rectangular shape, or a round shape, such as an elliptical or circular shape.
- Contact surfaces 31 a and 32 a are respectively formed on the upper surfaces of the bar-shaped protrusions 31 of the upper plate 11 and the lower surfaces of the bar-shaped protrusions 32 of the lower plate 12 .
- the bonding of the bar-shaped protrusions and 32 can be facilitated by the contact between the contact surfaces 31 a and 32 a.
- bonding of the contact surfaces 31 a and 32 a of the bar-shaped protrusions 31 and 32 can be further facilitated
- the bar-shaped protrusions 31 of each heat exchange tube 10 which is disposed at an upper position cross M over and come into contact with the bar-shaped protrusions 32 of the corresponding heat exchange tube 10 which is disposed at a lower position.
- the distance by which the adjacent heat exchange tubes 10 are spaced apart from each other can be increased and maintained.
- the cross-sectional area of the coolant path 28 is increased.
- the bar-shaped protrusions 31 and 32 which come into contact with each other are bonded to each other by brazing or the like.
- second recesses 11 d and 12 d are respectively formed in the upper and lower plates 11 and 12 at sides opposite to the bar-shaped protrusions 31 and 32 .
- each second recess 11 d, 12 d is formed between the corresponding first recesses 11 b, 12 b of the upper or lower plate 11 or 12 .
- Each second recess 11 d, 12 d also extends on the plane in the diagonal direction in the same manner as that of the first recesses 11 b and 12 b.
- the depth of each second recess 11 d, 12 d is greater than that of each first recess 11 b, 12 b.
- the second recesses 11 d of the upper plate 11 cross over the second recesses 12 d of the lower plate 12 , so that the cross-sectional area of the oil path 15 can be increased.
- a positioning depression 11 c and a positioning protrusion 12 c are respectively formed at corresponding predetermined positions on the perimeters 11 a and 12 a of the upper plate 11 and the lower plate 12 . Positioning of the upper and lower plates 11 and 12 with respect to each other can be facilitated by the positioning depression 11 c and protrusions 12 c. Therefore, operation of temporarily coupling the upper plate 11 to the lower plate 12 can be easily and rapidly conducted. Thereby, the coupling between the upper and lower plates 11 and 12 can become precise and reliable.
- Each heat exchange tube 10 has an inlet port 13 formed in a first end thereof and an outlet port 14 formed in a second end thereof.
- the inlet port 13 and the outlet port 14 communicate with the oil path 15 .
- the inlet ports 13 of the heat exchange tubes 10 communicate with each other, and the outlet ports 14 of the heat exchange tubes 10 also communicate with each other.
- the upper plate 11 includes an upper flange 23 which is provided around each of the inlet port 13 and the outlet port 14 and protrudes upwards from the upper surface of the upper plate 11 .
- the lower plate 12 includes a lower flange 24 which is provided around each of the inlet port 13 and the outlet port 14 of the lower plate 12 and protrudes downwards from the lower surface of the lower plate 12 .
- the upper flanges 23 and the lower flanges 24 of the adjacent heat exchange tubes 10 are coupled to each other in a fitting manner, thus enhancing the sealability therebetween.
- the upper flanges 23 and the lower flanges 24 that are coupled to each other can be more reliably sealed by brazing. Thereby, the inlet ports 13 and the outlet ports 14 of the heat exchange tube 10 are sealed off from the coolant path 28 .
- an inlet port cap 25 having an inlet hole 25 a is coupled to the upper flange 23 of the uppermost heat exchange tube 10 which is related to the inlet port 13 .
- An outlet port cap 26 having an outlet hole 26 a is coupled to the other upper flange 23 of the uppermost heat exchange tube 10 which is related to the outlet port 14 .
- a stopper 27 is removably or integrally coupled to each lower flange 24 of the lowermost heat exchange tube 10 .
- the circumferential outer surfaces of the upper flanges 23 may be fitted into the circumferential inner surfaces of the corresponding lower flanges 24 .
- the circumferential outer surfaces of the lower flanges 24 may be fitted into the circumferential inner surfaces of the corresponding upper flanges 23 .
- an upper end 23 a of the upper flange 23 of each heat exchange tube 10 which is fitted into the corresponding lower flange 24 of the corresponding upper heat exchange tube 10 may be tapered towards the center axis of the upper flange 23 .
- a lower end 24 a of the lower flange 24 may be tapered towards the center axis thereof.
- flanges which are fitted into corresponding flanges of a corresponding adjacent heat exchange tube are tapered on the ends 23 a, 24 a thereof towards the center axes thereof.
- This structure can further enhance the assemblability and sealability of the upper and lower flanges 23 and 24 .
Abstract
Disclosed herein is a transmission oil cooler. The cooler includes heat exchange tubes stacked one on top of another. Each heat exchange tube comprises an upper plate and a lower plate coupled to each other. Recesses are formed in each of facing surfaces of the upper and lower plates. The recesses of the upper plate cross over the recesses of the lower plate. Ridges and valleys are alternately formed on the upper and lower plates. Each heat exchange tubes has, on opposite ends thereof, an inlet port and an outlet port. An upper flange is provided around each of the inlet port and the outlet port. A lower flange is provided around each of the inlet port and the outlet port. The upper flange and the lower flanges of the adjacent heat exchange tubes are coupled to each other by fitting.
Description
- 1. Field of the Invention
- The present invention relates generally to transmission oil coolers and, more particularly, to a transmission oil cooler which enhances the heat exchange efficiency and has enhanced assembly performance.
- 2. Description of the Related Art
- Transmissions for vehicles convert the unidirectional rotating force of engines into the drive force of the vehicles. Transmissions are indispensable to changing the driving directions of vehicles, for example, between forward movement and backward movement, or to controlling the speed of the vehicles. Transmissions are classified into a variety of types, for example, a manual transmission, an automatic transmission, a continuously variable transmission (CVT), etc.
- Such a transmission includes therein a plurality of operating elements, such as gears, etc. Transmission oil circulates in the transmission to lubricate or clean these operating elements. When the transmission is operated, the transmission oil is heated by heat transferred from the elements. Thus, the viscosity of the transmission oil is markedly reduced, resulting in a loss of the inherent function. Therefore, an oil cooler is generally used to cool the transmission oil.
- Typically, the oil cooler is located in a radiator and is thus cooled by radiator coolant.
- The oil cooler included in the radiator is constructed such that heat exchange tubes are stacked one on top of another. The heat exchange tubes form oil paths through which oil passes. Each heat exchange tube comprises a pair of plates. The plates are coupled to each other by brazing the perimeters thereof, thus forming the oil path between the plates. Furthermore, the stacked heat exchange tubes are spaced apart from each other at regular intervals so that a coolant path is formed between the heat exchange tubes.
- Each heat exchange tube has an inlet port and an outlet port on the respective opposite ends thereof. The oil paths of the heat exchange tubes communicate with each other using the inlet ports and the outlet ports.
- However, in the conventional oil cooler, the cross-sectional areas of the coolant path and the oil path are comparatively small, thus deteriorating the heat exchange efficiency of the oil cooler.
- Furthermore, with regard to the assembly of the heat exchange tubes, because the assemblability and sealability between the inlet ports and the outlet ports of the heat exchange tubes are comparatively low, the leakage of oil or coolant may take place after the assembly of the heat exchange tubes has been completed.
- Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and an object of the present invention is to provide a transmission oil cooler which enhances the heat exchange efficiency and has enhanced assemblability.
- In order to accomplish the above object, the present invention provides a transmission oil cooler, including a plurality of heat exchange tubes stacked one on top of another. A coolant path is formed between the heat exchange tubes so that a coolant passes along the coolant path. Each of the heat exchange tubes comprises an upper plate and a lower plate coupled to each other by bonding perimeters thereof to each other. The heat exchange tube has an oil path along which oil passes. A plurality of recesses is formed in each of facing surfaces of the upper and lower plates. The recesses of the upper plate cross over the recesses of the lower plate, thus forming a cross structure of the oil path. A plurality of ridges and a plurality of valleys are continuously and alternately formed on each of an upper surface of the upper plate and a lower surface of the lower plate. The ridges and valleys extend parallel to each other in a diagonal direction. Each of the heat exchange tubes has, on opposite ends thereof, an inlet port through which the oil is drawn into the heat exchange tube, and an outlet port through which the oil is discharged out of the heat exchange tube. The oil paths of the heat exchange tubes communicate with each other through the inlet ports and the outlet ports. The upper plate comprises an upper flange provided around each of the inlet port and the outlet port, the upper flange protruding upwards from the upper surface of the upper plate, and the lower plate comprises a lower flange provided around each of the inlet port and the outlet port, the lower flange protruding downwards from the lower surface of the lower plate. Protrusions are discontinuously or continuously formed along the ridges on the upper and lower plates.
- The upper flange and the lower flanges of the adjacent heat exchange tubes may be coupled to each other by fitting.
- At least one of the upper and lower flanges may be tapered inwards on an end thereof.
- The protrusions may comprise a plurality of upper pin-shaped protrusions provided on the corresponding ridges of the upper plates, and a plurality of lower pin-shaped protrusions provided on the corresponding ridges of the lower plates. The upper pin-shaped protrusions and the lower pin-shaped protrusions of the adjacent heat exchange tubes may be in contact with each other.
- The upper pin-shaped protrusions may be arranged on an upper surface of each of the corresponding ridges of the upper plate at positions spaced apart from each other at regular intervals. The lower pin-shaped protrusions may be arranged on a lower surface of each of the corresponding ridges of the lower plate at positions spaced apart from each other at regular intervals.
- The upper pin-shaped protrusions and the lower pin-shaped protrusions may be disposed at positions at which the recesses of the upper plate cross over the recesses of the lower plate.
- Each of the upper pin-shaped protrusions may have a contact surface on an upper surface thereof, and each of the lower pin-shaped protrusions may have a contact surface on a lower surface thereof.
- Furthermore, a cross-section of each of the upper and lower pin-shaped protrusions may have one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
- The protrusions may comprise a plurality of bar-shaped protrusions provided between the ridges of the upper and lower plates. Each of the bar-shaped protrusions extends in a longitudinal direction of the ridges. A height of each of the bar-shaped protrusions may be greater than a height of the ridges, and the bar-shaped protrusions of the adjacent heat exchange tubes may be in contact with each other.
- The recesses formed in the facing surfaces of the upper and lower plates may comprise a plurality of first recesses formed at sides opposite to the respective ridges, and a plurality of second recesses formed at sides opposite to the respective bar-shaped protrusions.
- Each of the bar-shaped protrusions of the upper plate may have a contact surface on an upper surface thereof, and each of the bar-shaped protrusions of the lower plate may have a contact surface on a lower surface thereof.
- A cross-section of each of the bar-shaped protrusions of the upper and lower plates may have one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
- A positioning depression and a positioning protrusion may be respectively formed at predetermined positions corresponding to each other on portions at which the upper plate is in contact with the lower plate.
- In a transmission oil cooler according to the present invention, upper and lower flanges are provided around inlet and outlet ports of upper and lower plates of each heat exchange tube. Thus, the assemblability and sealability between the inlet ports and the outlet ports can be enhanced. Thereby, after the assembly of the heat exchange tubes has been completed, oil or coolant can be prevented from leaking from the heat exchange tubes.
- Furthermore, the cross-sectional area of the coolant path is increased by widening the interval between the heat exchange tubes, thus enhancing the heat exchange efficiency.
- The above and other objects, features and advantages of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:
-
FIG. 1 is a perspective view showing a transmission oil cooler, according to a first embodiment of the present invention; -
FIG. 2 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal direction according to the first embodiment of the present invention; -
FIG. 3 is an exploded perspective view showing an upper plate and a lower plate of a heat exchange tube according to the first embodiment of the present invention; -
FIG. 4 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal and transverse directions according to the first embodiment of the present invention; -
FIG. 5 is a side sectional view of the transmission oil cooler according to the first embodiment of the present invention; -
FIG. 6 is a front sectional view of the transmission oil cooler according to the first embodiment of the present invention; -
FIG. 7 is a front sectional view of a modification of the transmission oil cooler ofFIG. 6 ; -
FIG. 8 is an exploded front sectional view of a modification of the transmission oil cooler ofFIG. 7 ; -
FIG. 9 is a partially-broken perspective view of a transmission oil cooler taken along the longitudinal direction according to the second embodiment of the present invention; -
FIG. 10 is an exploded perspective view showing an upper plate and a lower plate of a heat exchange tube according to the second embodiment of the present invention; -
FIG. 11 is a partially-broken perspective view of the transmission oil cooler taken along the longitudinal and transverse directions according to the second embodiment of the present invention; -
FIG. 12 is a side sectional view of the transmission oil cooler according to the second embodiment of the present invention; -
FIG. 13 is a front sectional view of the transmission oil cooler according to the second embodiment of the present invention; -
FIG. 14 is a front sectional view of a modification of the transmission oil cooler ofFIG. 13 ; and -
FIG. 15 is an exploded front sectional view of a modification of the transmission oil cooler ofFIG. 14 . - Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the attached drawings.
-
FIGS. 1 through 8 illustrate a transmission oil cooler, according to a first embodiment of the present invention. - As shown in the drawings, the transmission oil cooler of the present invention includes a plurality of
heat exchange tubes 10 which are stacked one on top of another. - As shown in
FIG. 2 , eachheat exchange tube 10 has anoil path 15 along which oil passes. Theheat exchange tube 10 comprises anupper plate 11 and alower plate 12 which are coupled to each other. It is desirable that theupper plate 11 and thelower plate 12 be coupled to each other by bonding theperimeters - The
upper plate 11 and thelower plate 12 are made of metal, such as aluminum, etc., which has superior heat conductivity. The perimeters lla and 12 a of the upper andlower plates - As shown in
FIGS. 2 and 3 ,ridges 16 andvalleys 18 are continuously and alternately formed on the upper surface of theupper plate 11.Ridges 17 andvalleys 19 are continuously and alternately formed on the lower surface of thelower plate 12. Theridges 16 and thevalleys 18 extend parallel to each other in a diagonal direction of theupper plate 11. Theridges 17 and thevalleys 19 also extend parallel to each other in a diagonal direction of thelower plate 12. Theridges 16 and thevalleys 18 of theupper plate 11 cross over theridges 17 and thevalleys 19 of thelower plate 12. - A plurality of
recesses lower plates ridges valley recesses ridges recesses 11 b of theupper plate 11 also cross over therecesses 12 b of thelower plate 12. In addition, therecesses 11 b extend parallel to each other in the diagonal direction of theupper plate 11, and therecesses 12 b also extend parallel to each other in the diagonal direction of thelower plate 12. Theridges valleys recesses lower plates - As such, in the present invention, the
oil path 15 forms a cross structure because therecesses lower plates oil path 15. Thereby, the capacity to treat flowing oil can be increased, and the heat exchange efficiency between oil and coolant can be enhanced by increasing the contact area of oil. - Furthermore, a
coolant path 28 along which radiator coolant passes is formed between the adjacentheat exchange tubes 10 which are stacked one on top of the other. Thecoolant path 28 is formed by spacing theheat exchange tubes 10 apart from each other by a predetermined distance. - In the present invention,
protrusions heat exchange tube 10 to increase and maintain the distance by which the adjacentheat exchange tubes 10 are spaced apart from each other. - Thanks to the
protrusions coolant path 28 can be increased without reducing the cross-sectional area of theoil path 15. In the first embodiment, theprotrusions ridges - In detail, the
protrusions protrusions 21 which protrude from the upper surface of theupper plate 11, and lower pin-shapedprotrusions 22 which protrude from the lower surface of thelower plate 12. Particularly, the upper pin-shapedprotrusions 21 are formed on the upper surface of theridges 16 of theupper plate 11 and are spaced apart from each other at regular intervals. The lower pin-shapedprotrusions 22 are formed on the lower surface of theridges 17 of thelower plate 12 and are spaced apart from each other at regular intervals. In other words, the upper pin-shapedprotrusions 21 and the lower pin-shapedprotrusions 22 are discontinuously formed on theridges - The lower pin-shaped
protrusions 22 of theheat exchange tube 10 which is disposed at the upper position come into contact with the respective upper pin-shapedprotrusions 21 of theheat exchange tube 10 which is disposed at the lower position. As such, because the pin-shapedprotrusions heat exchange tubes 10 are spaced apart from each other can be increased and maintained. Thereby, the cross-sectional area of thecoolant path 28 is increased. Furthermore, the pin-shapedprotrusions protrusions 21 and the lower surfaces of the lower pin-shapedprotrusions 22. The bonding of the pin-shapedprotrusions - The cross-section of each of the upper and lower pin-shaped
protrusions protrusions protrusions - As shown in
FIG. 6 , it is desirable that a height h1 of each of the upper andlower plates ridges protrusions ridge - In addition, the upper pin-shaped
protrusions 21 and the lower pin-shapedprotrusions 22 are disposed at positions at which therecesses 11 b of theupper plate 11 cross over therecesses 12 b of thelower plate 12, thus making the stacked structure of theheat exchange tubes 10 more stable. - Furthermore, a positioning
depression 11 c and apositioning protrusion 12 c are respectively formed at corresponding predetermined positions on the perimeters lla and 12 a of theupper plate 11 and thelower plate 12. Positioning of the upper andlower plates depression 11 c andprotrusions 12 c. Therefore, operation of temporarily coupling theupper plate 11 to thelower plate 12 can be easily and rapidly conducted. Thereby, the coupling between the upper andlower plates - Relatedly, each
heat exchange tube 10 has aninlet port 13 formed in a first end thereof and anoutlet port 14 formed in a second end thereof. Theinlet port 13 and theoutlet port 14 communicate with theoil path 15. Furthermore, theinlet ports 13 of theheat exchange tubes 10 communicate with each other, and theoutlet ports 14 of theheat exchange tubes 10 also communicate with each other. - The
upper plate 11 includes anupper flange 23 which is provided around each of theinlet port 13 and theoutlet port 14 and protrudes upwards from the upper surface of theupper plate 11. Thelower plate 12 includes alower flange 24 which is provided around each of theinlet port 13 and theoutlet port 14 of thelower plate 12 and protrudes downwards from the lower surface of thelower plate 12. Theupper flange 23 and thelower flange 24 are designed such that they are coupled to each other in a fitting manner. In detail, theupper flanges 23 of theheat exchange tube 10 which is disposed at the lower position are fitted into the correspondinglower flanges 24 of theheat exchange tube 10 which is disposed at the upper position, thus enhancing the sealability therebetween. Moreover, theupper flanges 23 and thelower flanges 24 that are coupled to each other can be more reliably sealed by brazing. Thereby, theinlet ports 13 and theoutlet ports 14 of theheat exchange tube 10 are sealed off from thecoolant path 28. - Furthermore, an
inlet port cap 25 having aninlet hole 25 a is coupled to theupper flange 23 of the uppermostheat exchange tube 10 which is related to theinlet port 13. Anoutlet port cap 26 having anoutlet hole 26 a is coupled to the otherupper flange 23 of the uppermostheat exchange tube 10 which is related to theoutlet port 14. Astopper 27 is removably or integrally coupled to eachlower flange 24 of the lowermostheat exchange tube 10. - As shown in
FIGS. 2 , 4, 5, 6 and 7, the circumferential outer surfaces of theupper flanges 23 may be fitted into the circumferential inner surfaces of the correspondinglower flanges 24. Alternatively, as shown inFIG. 8 , the circumferential outer surfaces of thelower flanges 24 may be fitted into the circumferential inner surfaces of the correspondingupper flanges 23. - Meanwhile, as shown in
FIG. 7 , anupper end 23 a of theupper flange 23 of eachheat exchange tube 10 which is fitted into the correspondinglower flange 24 of the corresponding upperheat exchange tube 10 may be tapered towards the center axis of theupper flange 23. Alternatively, as shown inFIG. 8 , in the case where thelower flange 24 of eachheat exchange tube 10 is fitted into the correspondingupper flange 23 of the corresponding lowerheat exchange tube 10, alower end 24 a of thelower flange 24 may be tapered towards the center axis thereof. - In other words, among the flanges of each heat exchange tube, flanges which are fitted into corresponding flanges of a corresponding adjacent heat exchange tube are tapered on the
ends - This structure can further enhance the assemblability and sealability of the upper and
lower flanges -
FIGS. 9 through 15 illustrate a transmission oil cooler, according to a second embodiment of the present invention. - As shown in the drawings, the transmission oil cooler according to the second embodiment of the present invention includes a plurality of
heat exchange tubes 10. Theheat exchange tubes 10 are stacked one on top of another. - Each
heat exchange tube 10 has anoil path 15 along which oil passes. Theheat exchange tube 10 comprises anupper plate 11 and alower plate 12 which are coupled to each other. Theupper plate 11 is coupled to thelower plate 12 in such a way that aperimeter 11 a of theupper plate 11 is bonded to aperimeter 12 a of thelower plate 12 by brazing or the like. - The
upper plate 11 and thelower plate 12 are made of metal, such as aluminum, etc., which has superior heat conductivity. Theperimeters lower plates - As shown in
FIGS. 9 and 10 ,ridges 16 andvalleys 18 are continuously and alternately formed on the upper surface of theupper plate 11.Ridges 17 andvalleys 19 are continuously and alternately formed on the lower surface of thelower plate 12. Theridges 16 and thevalleys 18 extend parallel to each other in a diagonal direction of theupper plate 11. Theridges 17 and thevalleys 19 also extend parallel to each other in a diagonal direction of thelower plate 12. Theridges 16 and thevalleys 18 of theupper plate 11 cross over theridges 17 and thevalleys 19 of thelower plate 12. - A plurality of
first recesses lower plates ridges valley ridges first recesses 11 b of theupper plate 11 also cross over thefirst recesses 12 b of thelower plate 12. In addition, thefirst recesses 11 b extend parallel to each other in the diagonal direction of theupper plate 11, and thefirst recesses 12 b also extend parallel to each other in the diagonal direction of thelower plate 12. Theridges valleys first recesses lower plates - As such, the
oil path 15 forms a cross structure because thefirst recesses lower plates oil path 15. Thereby, the capacity with which flowing oil is treated can be increased, and the heat exchange efficiency between oil and coolant can be enhanced by increasing contact area of oil. - Furthermore, a
coolant path 28 along which radiator coolant passes is formed between the adjacentheat exchange tubes 10 which are stacked one on top of the other. Thecoolant path 28 is formed by spacing theheat exchange tubes 10 apart from each other by a predetermined distance. - In a manner similar to the first embodiment,
protrusions heat exchange tube 10 to increase and maintain the distance by which the adjacentheat exchange tubes 10 are spaced apart from each other. - Thanks to the
protrusions coolant path 28 can be increased without reducing the cross-sectional area of theoil path 15. - In the second embodiment, the
protrusions ridges protrusions protrusions adjacent ridges ridges - The bar-shaped
protrusions 31 are arranged between theridges 16 at positions spaced apart from each other at regular intervals, and the bar-shapedprotrusions 32 are arranged between theridges 17 at positions spaced apart from each other at regular intervals. The bar-shapedprotrusions ridges protrusion ridges valleys protrusion ridges protrusion lower plate ridge FIG. 9 , it is desirable that the height hl of the bar-shapedprotrusion ridge ridges protrusions - Furthermore, the cross-section of each of the bar-shaped
protrusions lower plates protrusions 31 of theupper plate 11 and the lower surfaces of the bar-shapedprotrusions 32 of thelower plate 12. The bonding of the bar-shaped protrusions and 32 can be facilitated by the contact between the contact surfaces 31 a and 32 a. Particularly, in the case where the bar-shapedprotrusions protrusions - In addition, the bar-shaped
protrusions 31 of eachheat exchange tube 10 which is disposed at an upper position cross M over and come into contact with the bar-shapedprotrusions 32 of the correspondingheat exchange tube 10 which is disposed at a lower position. Hence, the distance by which the adjacentheat exchange tubes 10 are spaced apart from each other can be increased and maintained. Thereby, the cross-sectional area of thecoolant path 28 is increased. Furthermore, the bar-shapedprotrusions - In the second embodiment, second recesses 11 d and 12 d are respectively formed in the upper and
lower plates protrusions second recess first recesses lower plate second recess first recesses second recess first recess first recesses second recesses 11 d of theupper plate 11 cross over thesecond recesses 12 d of thelower plate 12, so that the cross-sectional area of theoil path 15 can be increased. - Meanwhile, a positioning
depression 11 c and apositioning protrusion 12 c are respectively formed at corresponding predetermined positions on theperimeters upper plate 11 and thelower plate 12. Positioning of the upper andlower plates depression 11 c andprotrusions 12 c. Therefore, operation of temporarily coupling theupper plate 11 to thelower plate 12 can be easily and rapidly conducted. Thereby, the coupling between the upper andlower plates - Each
heat exchange tube 10 has aninlet port 13 formed in a first end thereof and anoutlet port 14 formed in a second end thereof. Theinlet port 13 and theoutlet port 14 communicate with theoil path 15. Furthermore, theinlet ports 13 of theheat exchange tubes 10 communicate with each other, and theoutlet ports 14 of theheat exchange tubes 10 also communicate with each other. - The
upper plate 11 includes anupper flange 23 which is provided around each of theinlet port 13 and theoutlet port 14 and protrudes upwards from the upper surface of theupper plate 11. Thelower plate 12 includes alower flange 24 which is provided around each of theinlet port 13 and theoutlet port 14 of thelower plate 12 and protrudes downwards from the lower surface of thelower plate 12. Theupper flanges 23 and thelower flanges 24 of the adjacentheat exchange tubes 10 are coupled to each other in a fitting manner, thus enhancing the sealability therebetween. Moreover, theupper flanges 23 and thelower flanges 24 that are coupled to each other can be more reliably sealed by brazing. Thereby, theinlet ports 13 and theoutlet ports 14 of theheat exchange tube 10 are sealed off from thecoolant path 28. - Furthermore, an
inlet port cap 25 having aninlet hole 25 a is coupled to theupper flange 23 of the uppermostheat exchange tube 10 which is related to theinlet port 13. Anoutlet port cap 26 having anoutlet hole 26 a is coupled to the otherupper flange 23 of the uppermostheat exchange tube 10 which is related to theoutlet port 14. Astopper 27 is removably or integrally coupled to eachlower flange 24 of the lowermostheat exchange tube 10. - As shown in
FIGS. 9 , 11, 12, 13 and 14, the circumferential outer surfaces of theupper flanges 23 may be fitted into the circumferential inner surfaces of the correspondinglower flanges 24. Alternatively, as shown inFIG. 15 , the circumferential outer surfaces of thelower flanges 24 may be fitted into the circumferential inner surfaces of the correspondingupper flanges 23. - As shown in
FIG. 14 , anupper end 23 a of theupper flange 23 of eachheat exchange tube 10 which is fitted into the correspondinglower flange 24 of the corresponding upperheat exchange tube 10 may be tapered towards the center axis of theupper flange 23. Alternatively, as shown inFIG. 15 , in the case where thelower flange 24 of eachheat exchange tube 10 is fitted into the correspondingupper flange 23 of the corresponding lowerheat exchange tube 10, alower end 24 a of thelower flange 24 may be tapered towards the center axis thereof. - In other words, among the flanges of each heat exchange tube, flanges which are fitted into corresponding flanges of a corresponding adjacent heat exchange tube are tapered on the
ends lower flanges
Claims (13)
1. A transmission oil cooler, comprising a plurality of heat exchange tubes stacked one on top of another,
wherein a coolant path is formed between the heat exchange tubes so that a coolant passes along the coolant path, and each of the heat exchange tubes comprises an upper plate and a lower plate coupled to each other by bonding perimeters thereof to each other, the heat exchange tube having an oil path along which oil passes,
a plurality of recesses is formed in each of facing surfaces of the upper and lower plates, the recesses of the upper plate crossing over the recesses of the lower plate, thus forming a cross structure of the oil path,
a plurality of ridges and a plurality of valleys are continuously and alternately formed on each of an upper surface of the upper plate and a lower surface of the lower plate, the ridges and valleys extending parallel to each other in a diagonal direction,
each of the heat exchange tubes has, on opposite ends thereof, an inlet port through which the oil is drawn into the heat exchange tube, and an outlet port through which the oil is discharged out of the heat exchange tube, and the oil paths of the heat exchange tubes communicate with each other through the inlet ports and the outlet ports,
the upper plate comprises an upper flange provided around each of the inlet port and the outlet port, the upper flange protruding upwards from the upper surface of the upper plate, and the lower plate comprises a lower flange provided around each of the inlet port and the outlet port, the lower flange protruding downwards from the lower surface of the lower plate, and
protrusions are discontinuously or continuously formed along the ridges on the upper and lower plates.
2. The transmission oil cooler as set forth in claim 1 , wherein the upper flange and the lower flanges of the adjacent heat exchange tubes are coupled to each other by fitting.
3. The transmission oil cooler as set forth in claim 2 , wherein at least one of the upper and lower flanges is tapered inwards on an end thereof.
4. The transmission oil cooler as set forth in claim 1 , wherein the protrusions comprise a plurality of upper pin-shaped protrusions provided on the corresponding ridges of the upper plates, and a plurality of lower pin-shaped protrusions provided on the corresponding ridges of the lower plates, and the upper pin-shaped protrusions and the lower pin-shaped protrusions of the adjacent heat exchange tubes are in contact with each other.
5. The transmission oil cooler as set forth in claim 4 , wherein the upper pin-shaped protrusions are arranged on an upper surface of each of the corresponding ridges of the upper plate at positions spaced apart from each other at regular intervals, and the lower pin-shaped protrusions are arranged on a lower surface of each of the corresponding ridges of the lower plate at positions spaced apart from each other at regular intervals.
6. The transmission oil cooler as set forth in claim 4 , wherein the upper pin-shaped protrusions and the lower pin-shaped protrusions are disposed at positions at which the recesses of the upper plate cross over the recesses of the lower plate.
7. The transmission oil cooler as set forth in claim 4 , wherein each of the upper pin-shaped protrusions has a contact surface on an upper surface thereof, and each of the lower pin-shaped protrusions has a contact surface on a lower surface thereof.
8. The transmission oil cooler as set forth in claim 4 , wherein a cross-section of each of the upper and lower pin-shaped protrusions has one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
9. The transmission oil cooler as set forth in claim 1 , wherein the protrusions comprise a plurality of bar-shaped protrusions provided between the ridges of the upper and lower plates, each of the bar-shaped protrusions extending in a longitudinal direction of the ridges, wherein a height of each of the bar-shaped protrusions is greater than a height of the ridges, and the bar-shaped protrusions of the adjacent heat exchange tubes are in contact with each other.
10. The transmission oil cooler as set forth in claim 9 , wherein the recesses formed in the facing surfaces of the upper and lower plates comprise a plurality of first recesses formed at sides opposite to the respective ridges, and a plurality of second recesses formed at sides opposite to the respective bar-shaped protrusions.
11. The transmission oil cooler as set forth in claim 9 , wherein each of the bar-shaped protrusions of the upper plate has a contact surface on an upper surface thereof, and each of the bar-shaped protrusions of the lower plate has a contact surface on a lower surface thereof.
12. The transmission oil cooler as set forth in claim 9 , wherein a cross-section of each of the bar-shaped protrusions of the upper and lower plates has one shape selected from a trapezoidal shape, a round shape and a rectangular shape.
13. The transmission oil cooler as set forth in claim 1 , wherein a positioning depression and a positioning protrusion are respectively formed at predetermined positions corresponding to each other on portions at which the upper plate is in contact with the lower plate.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020080067004A KR100892109B1 (en) | 2008-07-10 | 2008-07-10 | Transmission oil cooler |
KR10-2008-0067004 | 2008-07-10 | ||
KR10-2008-0067008 | 2008-07-10 | ||
KR1020080067008A KR100892111B1 (en) | 2008-07-10 | 2008-07-10 | Transmission oil cooler |
PCT/KR2009/003200 WO2010005179A2 (en) | 2008-07-10 | 2009-06-16 | Oil cooler for transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110011568A1 true US20110011568A1 (en) | 2011-01-20 |
Family
ID=41507537
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/922,301 Abandoned US20110011568A1 (en) | 2008-07-10 | 2009-06-16 | Oil cooler for transmission |
Country Status (5)
Country | Link |
---|---|
US (1) | US20110011568A1 (en) |
EP (1) | EP2295834B1 (en) |
JP (1) | JP5191066B2 (en) |
CN (1) | CN101970907B (en) |
WO (1) | WO2010005179A2 (en) |
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US20150292803A1 (en) * | 2012-11-07 | 2015-10-15 | Alfa Laval Corporate Ab | Method of making a plate package for a plate heat exchanger |
US9250019B2 (en) | 2009-07-27 | 2016-02-02 | Korea Delphi Automotive Systems Corporation | Plate heat exchanger |
EP3002536A1 (en) * | 2014-10-02 | 2016-04-06 | Valeo Systemes Thermiques | Assembly comprising at least a first and a second plate for forming an exchange core of a heat exchanger and heat exchanger including said assembly |
US9562492B2 (en) | 2013-01-31 | 2017-02-07 | Toyota Jidosha Kabushiki Kaisha | Internal combustion engine |
EP3372937A1 (en) * | 2017-03-10 | 2018-09-12 | Alfa Laval Corporate AB | Heat exchanger plate, a plate package using such heat exchanger plate and a heat exchanger using such heat exchanger plate |
US10151380B2 (en) * | 2015-09-29 | 2018-12-11 | Mazda Motor Corporation | Transmission and manufacturing method of the same |
US20190264984A1 (en) * | 2016-11-21 | 2019-08-29 | Denso Corporation | Stacked heat exchanger |
US10429132B2 (en) | 2015-02-18 | 2019-10-01 | Dana Canada Corporation | Stacked plate heat exchanger with top and bottom manifolds |
US10443955B2 (en) * | 2014-09-08 | 2019-10-15 | Valeo Systemes Thermiques | Tube with a reservoir of phase-change material for a heat exchanger |
US11118848B2 (en) * | 2016-02-04 | 2021-09-14 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat-exchanging plate, and plate heat exchanger using same |
US11280560B1 (en) * | 2020-12-08 | 2022-03-22 | Dana Canada Corporation | Heat exchanger with two-piece through fittings |
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CN103822521B (en) * | 2014-03-04 | 2017-02-08 | 丹佛斯微通道换热器(嘉兴)有限公司 | Heat exchange plate and plate type heat exchanger |
CN105526813A (en) * | 2015-12-10 | 2016-04-27 | 上海理工大学 | Microchannel heat radiator |
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US10151380B2 (en) * | 2015-09-29 | 2018-12-11 | Mazda Motor Corporation | Transmission and manufacturing method of the same |
US11118848B2 (en) * | 2016-02-04 | 2021-09-14 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat-exchanging plate, and plate heat exchanger using same |
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US11280560B1 (en) * | 2020-12-08 | 2022-03-22 | Dana Canada Corporation | Heat exchanger with two-piece through fittings |
Also Published As
Publication number | Publication date |
---|---|
JP2011517757A (en) | 2011-06-16 |
CN101970907A (en) | 2011-02-09 |
EP2295834A4 (en) | 2011-07-06 |
EP2295834B1 (en) | 2013-01-09 |
CN101970907B (en) | 2015-01-07 |
WO2010005179A3 (en) | 2010-03-11 |
WO2010005179A2 (en) | 2010-01-14 |
JP5191066B2 (en) | 2013-04-24 |
EP2295834A2 (en) | 2011-03-16 |
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Owner name: KOREA DELPHI AUTOMOTIVE SYSTEMS CORPORATION, KOREA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HAN, SANG CHUL;CHOI, SIN IL;TAE, HYUK CHAN;REEL/FRAME:024977/0084 Effective date: 20100903 |
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