US20190162483A1 - Cooling apparatus - Google Patents
Cooling apparatus Download PDFInfo
- Publication number
- US20190162483A1 US20190162483A1 US16/201,366 US201816201366A US2019162483A1 US 20190162483 A1 US20190162483 A1 US 20190162483A1 US 201816201366 A US201816201366 A US 201816201366A US 2019162483 A1 US2019162483 A1 US 2019162483A1
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- United States
- Prior art keywords
- fin
- flow direction
- fins
- row
- coolant
- 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
- 238000001816 cooling Methods 0.000 title claims description 24
- 239000002826 coolant Substances 0.000 claims abstract description 63
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 43
- 238000010586 diagram Methods 0.000 description 18
- 239000013598 vector Substances 0.000 description 16
- 238000000926 separation method Methods 0.000 description 14
- 230000002349 favourable effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 7
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000007747 plating Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
-
- 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
-
- 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
- F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
-
- 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
- F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
- H05K7/00—Constructional details common to different types of electric apparatus
- H05K7/20—Modifications to facilitate cooling, ventilating, or heating
- H05K7/2089—Modifications to facilitate cooling, ventilating, or heating for power electronics, e.g. for inverters for controlling motor
- H05K7/20927—Liquid coolant without phase change
-
- 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
- F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
- F28D2021/0029—Heat sinks
-
- 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
- F28D2021/0043—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for fuel cells
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/62—Heating or cooling; Temperature control specially adapted for specific applications
- H01M10/625—Vehicles
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/65—Means for temperature control structurally associated with the cells
- H01M10/655—Solid structures for heat exchange or heat conduction
- H01M10/6551—Surfaces specially adapted for heat dissipation or radiation, e.g. fins or coatings
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/10—Energy storage using batteries
Definitions
- the present invention relates to a cooling apparatus including a plurality of fins within a coolant passage that is near a heat source body.
- An electric automobile or hybrid automobile using an electric motor as a drive source includes a drive circuit that converts the power supplied from a high voltage power source into power for driving the motor, and supplies this power to the motor. Since the drive circuit generates heat along with the driving, a cooling apparatus is provided near the drive circuit. For example, a coolant passage including a heat sink therein is used as the cooling apparatus.
- Japanese Laid-Open Patent Publication No. 2016-205802 shows a cooling apparatus that includes wave-shaped fins extending in the direction of the flow of coolant within the coolant passage. By bending the top end portion of each fin in the width direction of the coolant passage, an opening portion is formed between the downstream side end portions of the upstream side fins and the upstream side end portions of the downstream fins.
- the present invention takes into consideration such a problem, and it is an object of the present invention to provide a cooling apparatus that can realize favorable heat transfer between fins and a coolant.
- the present invention is a cooling apparatus comprising a plurality of fins within a coolant passage near a heat source body, wherein the plurality of fins each have a flat shape in a height direction orthogonal to a flow direction of coolant in the coolant passage, and are provided intermittently along virtual waveforms that extend in the flow direction and that make a plurality of rows in a width direction orthogonal to the flow direction and to the height direction, and with a fin provided in a first row being a first fin and two fins lined up in the flow direction and provided in a second row adjacent to the first row being a second fin and a third fin, an upstream portion including an upstream end of the first fin overlaps with a position in the flow direction of a downstream portion including a downstream end of the second fin, and a downstream portion including a downstream end of the first fin overlaps with a position in the flow direction of an upstream portion including an upstream end of the third fin.
- the fins may be provided along portions of the waveforms including two peaks.
- the waveforms may have shapes symmetrical on an axis that is a virtual line that passes through the peaks, is orthogonal to the flow direction, and is parallel to the width direction.
- the fins may each have the same shape in cross-sectional planes parallel to the flow direction and to the width direction.
- [ ⁇ L ⁇ ( ⁇ /2) ⁇ / ⁇ /2] ⁇ 100 may be greater than or equal to 30% and less than 50%.
- FIG. 1 is a perspective view of the cooling apparatus according to the present embodiment.
- FIG. 2 is an exploded perspective view of the cooling apparatus according to the present embodiment.
- FIG. 3 is a partial plan view of an inner fin.
- FIG. 4 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 0%.
- FIG. 5 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 15%.
- FIG. 6 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 25%.
- FIG. 7 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 50%.
- FIG. 8 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 0%.
- FIG. 9 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 5%.
- FIG. 10 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 10%.
- FIG. 11 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 30%.
- FIG. 12 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 40%.
- FIG. 13 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 1 [mm].
- FIG. 14 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 3 [mm].
- FIG. 15 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 5 [mm].
- FIG. 16 is a partial plan view of an inner fin according to another embodiment.
- the cooling apparatus 10 shown in FIG. 1 has a flat shape, and is provided near a bottom surface of a PCU (power control unit) of an electric vehicle such as an electric automobile of hybrid automobile.
- the PCU is a heat source body that generates heat when supplying power from a high voltage battery to an electric motor or when supplying power from a generator to a high voltage battery.
- the cooling apparatus 10 includes a top cover 20 , a bottom cover 30 , and an inner fin 40 .
- the top cover 20 , bottom cover 30 , and inner fin 40 are formed of metal with high thermal conductivity, such as aluminum or copper that has undergone nickel plating.
- the top surface of the top cover 20 is used as a heat absorbing surface.
- a side wall 32 protruding upward is formed on the circumferential edge of the bottom cover 30 , and two holes penetrating from the bottom surface to the top surface are formed at respective ends of the bottom cover 30 in the longitudinal direction. One of these holes is used as a flow inlet 34 for the coolant, and the other hole is used as a flow outlet 36 for the coolant.
- the inner fin 40 includes a board portion 42 brazed to the bottom cover 30 and a plurality of fins 44 that protrude upward from the board portion 42 .
- the bottom surface of the board portion 42 is brazed to the top surface of the bottom cover 30 .
- the bottom surface of the top cover 20 is brazed to the top end of the side wall 32 of the bottom cover 30 , or contacts the top end of each fin 44 .
- a coolant passage 12 through which coolant flows is formed by the bottom cover 30 and the top cover 20 , and a plurality of fins 44 are provided within the coolant passage 12 .
- the flow direction f of the coolant in the coolant passage 12 is substantially parallel to the longitudinal direction.
- the shape and arrangement of the fins 44 are one characteristic.
- the shape and arrangement of the fins 44 are described using FIG. 3 .
- the left-right direction in the plane of the drawing matches the longitudinal direction of the cooling apparatus 10
- the up-down direction in the plane of the drawing matches the width direction.
- a direction perpendicular to the plane of the drawing matches the height direction.
- a plurality of waveforms 60 extending in the flow direction f are assumed.
- sinusoidal curves are shown as an example of the waveforms 60 .
- the amplitudes and periods of the waveforms 60 are substantially constant from the upstream side to the downstream side in the flow direction f.
- the phases of the plurality of waveforms 60 are the same as each other at each position in the flow direction f.
- Each waveform 60 forms a shape that has linear symmetry, with a virtual line 70 .
- the virtual line 70 passes through a peak 62 , is orthogonal to the flow direction f, and is parallel to the width direction serving as an axis.
- Each fin 44 is provided intermittently along the waveform 60 .
- a gap 46 is provided between the two fins 44 in front and behind along the flow direction f, and the fins 44 and gaps 46 are arranged in a row in an alternating manner.
- One wavelength of the waveform 60 is formed by combining one fin 44 and one gap 46 that are adjacent to each other.
- the fin 44 is formed along a portion of the waveform 60 including two peaks 62 .
- the portion of the fin 44 arranged on the peak 62 on the upstream side is referred to as an upstream side peak portion 48
- the portion of the fin 44 formed on the peak 62 on the downstream side is referred to as a downstream side peak portion 50 .
- the portion of the fin 44 arranged farthest on the upstream side in the flow direction f is referred to as the upstream end 52
- the portion of the fin 44 arranged farthest on the downstream side is referred to as the downstream end 54 .
- the upstream end 52 is at a position resulting from the fin 44 being extended to the upstream side from the upstream side peak portion 48 along the waveform 60
- the downstream end 54 is at a position resulting from the fin 44 being extended to the downstream side from the downstream side peak portion 50 along the waveform 60 . Therefore, the length L of the fin 44 in the flow direction f is greater than the length ⁇ /2 of the half wavelength of the waveform 60 . Details of the extension amount by which the fin 44 extends from the upstream side peak portion 48 to the upstream end 52 and the extension amount by which the fin 44 extends from the downstream side peak portion 50 to the downstream end 54 are provided in section [4] below.
- One of these arrangement patterns is a first pattern in which the position of the fin 44 in the width direction is displaced in one direction (e.g., to an upward direction in the plane of the drawing of FIG. 3 ) as progression occurs along the fin 44 from the upstream side peak portion 48 to the downstream side peak portion 50 .
- the other arrangement pattern is a second pattern in which the position of the fin 44 in the width direction is displaced in the other direction (e.g., a downward direction in the plane of the drawing of FIG. 3 ) as progression occurs along the fin 44 from the upstream side peak portion 48 to the downstream side peak portion 50 .
- First rows 72 of the first pattern and second rows 74 of the second pattern are lined up in an alternating manner from one side to another side in the width direction.
- the intervals P between adjacent first rows 72 are constant, and the intervals P between adjacent second rows 74 are also constant. Details about the intervals Po (Po1 and Po2) between the first rows 72 and the second rows 74 are provided in section [3] below.
- the portion from the upstream side peak portion 48 to the upstream end 52 and the portion having line symmetry with respect to this portion using the virtual line 70 as an axis are referred to collectively as the upstream portion 56 .
- the portion from the downstream side peak portion 50 to the downstream end 54 and the portion having line symmetry with respect to this portion using the virtual line 70 as an axis are referred to collectively as a downstream portion 58 .
- the upstream portion 56 of the fin 44 arranged in the first row 72 overlaps with the position of the downstream portion 58 of a fin 44 arranged in the second row 74 in the flow direction f.
- the downstream portion 58 of a fin 44 arranged in the first row 72 overlaps with the position of the upstream portion 56 of a fin 44 arranged in the second row 74 in the flow direction f.
- Each fin 44 has a constant height from the upstream end 52 to the downstream end 54 , and has a flat shape in the height direction in accordance with the cooling apparatus 10 . Furthermore, the fins 44 have the same shape in each of cross-sectional planes parallel to both the flow direction f and the width direction. In other words, the fins 44 have the same shapes as seen in the plan view of FIG. 3 . The fins 44 have the same shape in the height direction.
- the intervals Po between the first rows 72 and second rows 74 include an interval Pot between a first row 72 and a second row 74 positioned on one side (upper side in the plane of the drawing) in the width direction of this first row 72 and an interval Po2 between the first row 72 and a second row 74 positioned the other side (lower side in the plane of the drawing) of this first row 72 in the width direction.
- the interval Po2 is considered to be the offset amount of the second row 74 relative to the first row 72 , and the offset amount is shown as a percentage of the interval P of the first row 72 .
- FIG. 4 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row 74 relative to the first row 72 is 0%.
- An offset of 0% means that there is no interval Po2 between the first row 72 and the second row 74 , and that a fin 44 ′ that is continuous, instead of being intermittent, is provided.
- the offset amount is 0%
- development of a temperature boundary layer in the coolant flowing on both sides of the fin 44 ′ is observed as the location progresses toward the downstream side.
- FIG. 5 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row 74 relative to the first row 72 is 15%.
- the offset amount is 15%
- development of a temperature boundary layer in the coolant flowing on the side (interval Pot side) where the flow path on the downstream side between the fin 44 of the first row 72 and the fin 44 of the second row 74 is narrow is observed, but the development of a temperature boundary layer in the coolant flowing on the side (interval Po1 side) where the flow path is wide is not observed, even on the downstream side.
- FIG. 6 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row 74 relative to the first row 72 is 25%. In the case where the offset amount is 25%, the development of the temperature boundary layer is less than in the case where the offset amount is 15%.
- FIG. 7 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row 74 relative to the first row 72 is 50%. In the case where the offset amount is 50%, development of the temperature boundary layer is not observed, even on the downstream side.
- the offset amount is set to be even a small amount, the effect of restricting development of the temperature boundary layer is realized, and particularly if the offset amount is set to be greater than or equal to 25% and less than or equal to 50%, the effect of more effectively restricting the temperature boundary layer is realized.
- the intervals Po between the first rows 72 and the second rows 74 it is preferable for the intervals Po between the first rows 72 and the second rows 74 to be greater than or equal to 0.25 P and less than or equal to 0.50 P (or greater than or equal to 0.50 P and less and or equal to 0.75 P).
- FIG. 8 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 0%.
- a large separation 80 occurs on the other side (lower side in the plane of the drawing) in the width direction of the upstream portion 56 of each fin 44 .
- FIG. 9 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 5%. In the case where the extension percentage is 5%, the separation 80 is less than in the case where the extension percentage is 0%.
- FIG. 10 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 10%. In the case where the extension percentage is 10%, the separation 80 that occurs in the cases where the extension rate is 0% and 5% is almost nonexistent.
- FIG. 11 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 30%
- FIG. 12 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 40%. In the case where the extension percentage is greater than or equal to 30%, the separation 80 does not occur.
- FIGS. 8 to 12 it is understood that if the upstream end 52 of a fin 44 extends even a small amount from the upstream side peak portion 48 along the waveform 60 or the downstream end 54 of the fin 44 extends even a small amount from the downstream side peak portion 50 along the waveform 60 , an effect of restricting the occurrence of the separation 80 is achieved. In particular, if the extension percentage is greater than or equal to 30% and less than 50%, an effect of stopping the occurrence of the separation 80 is realized.
- FIGS. 13 to 15 are tables showing results obtained by examining the velocity vectors and temperature contours while using the fins with the respective amplitudes of 1 [mm], 3 [mm], and 5 [mm], and changing the offset amounts (25%, 37.5%, and 50%) and the extension amounts (0%, 15%, and 30%). According to FIGS. 13 to 15 , it is understood that the velocity vectors and temperature contours do not significantly change as a result of different amplitudes. In other words, it is understood that there is no correlation between the amplitude, and the velocity vector and temperature contour.
- the fins 44 are described as having waveforms 60 that are sinusoidal curves. Instead of this, the same effect as in the embodiment described above can be realized with fins 44 having other waveforms 60 .
- the fins 44 may have triangular waveforms 60 .
- the fins 44 each have a flat shape in the height direction orthogonal to the flow direction f of the coolant in the coolant passage 12 , and are provided intermittently along the virtual waveforms 60 that extend in the flow direction f and that make a plurality of rows in the width direction orthogonal to the flow direction f and to the height direction.
- the upstream portion 56 including the upstream end 52 of the first fin 44 overlaps with the position in the flow direction f of the downstream portion 58 including the downstream end 54 of the second fin 44 .
- the downstream portion 58 including the downstream end 54 of the first fin 44 overlaps with a position in the flow direction f of the upstream portion 56 including the upstream end 52 of the third fin 44 .
- the fins 44 are provided along portions of the waveforms 60 including two peaks 62 . With the configuration described above, development of the temperature boundary layer and separation of the flow of coolant are further restricted, and favorable heat transfer can be realized between the fins 44 and the coolant.
- the waveforms 60 each have shapes symmetrical on the axis that is the virtual line 70 that passes through the peaks 62 , is orthogonal to the flow direction f, and is parallel to the width direction.
- the fins 44 each have the same shape in the cross-sectional planes parallel to the flow direction f and to the width direction. With the configuration described above, favorable heat transfer can be realized over a wide range, with coolant flow that is substantially uniform in the height direction.
- [ ⁇ L ⁇ ( ⁇ /2) ⁇ / ⁇ /2] ⁇ 100 may be greater than or equal to 30% and less than 50%.
- the cooling apparatus according to the present embodiment is not limited to the embodiments described above, and it is obvious that various configurations can be adopted without deviating from the scope of the present invention.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Microelectronics & Electronic Packaging (AREA)
- Geometry (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
Abstract
Description
- This application is based upon and claims the benefit of priority from Japanese Patent Application No. 2017-228527 filed on Nov. 29, 2017, the contents of which are incorporated herein by reference.
- The present invention relates to a cooling apparatus including a plurality of fins within a coolant passage that is near a heat source body.
- An electric automobile or hybrid automobile using an electric motor as a drive source includes a drive circuit that converts the power supplied from a high voltage power source into power for driving the motor, and supplies this power to the motor. Since the drive circuit generates heat along with the driving, a cooling apparatus is provided near the drive circuit. For example, a coolant passage including a heat sink therein is used as the cooling apparatus.
- Japanese Laid-Open Patent Publication No. 2016-205802 shows a cooling apparatus that includes wave-shaped fins extending in the direction of the flow of coolant within the coolant passage. By bending the top end portion of each fin in the width direction of the coolant passage, an opening portion is formed between the downstream side end portions of the upstream side fins and the upstream side end portions of the downstream fins.
- There is a cooling apparatus in which a series of fins are provided from an upstream side to a downstream side. In this cooling apparatus, since the coolant flows while contacting the fins, it is easy for the coolant that continues flowing near the fins to accumulate heat. Therefore, a temperature boundary layer is prone to occurring near the fins on the downstream side. On the other hand, in the cooling apparatus shown in Japanese Laid-Open Patent Publication No. 2016-205802, the coolant flows while contacting the fins and becomes distanced from the fins at the opening portion. Because of this, the temperature accumulated in the coolant is cancelled for the moment. Therefore, it is difficult for the temperature boundary layer to form near the fins on the downstream side.
- However, in the cooling apparatus shown in Japanese Laid-Open Patent Publication No. 2016-205802, the flow rate of the coolant in a part of the location where the fins and coolant are in contact becomes low, and in a worst case scenario, retention of the coolant occurs. In this way, although the flow of the coolant at locations distanced from the fins is maintained, the flow of the coolant near the fins becoming extremely slow, and this is referred to as separation. The heat releasing efficiency at the separation location of the flow of the coolant is reduced.
- The present invention takes into consideration such a problem, and it is an object of the present invention to provide a cooling apparatus that can realize favorable heat transfer between fins and a coolant.
- The present invention is a cooling apparatus comprising a plurality of fins within a coolant passage near a heat source body, wherein the plurality of fins each have a flat shape in a height direction orthogonal to a flow direction of coolant in the coolant passage, and are provided intermittently along virtual waveforms that extend in the flow direction and that make a plurality of rows in a width direction orthogonal to the flow direction and to the height direction, and with a fin provided in a first row being a first fin and two fins lined up in the flow direction and provided in a second row adjacent to the first row being a second fin and a third fin, an upstream portion including an upstream end of the first fin overlaps with a position in the flow direction of a downstream portion including a downstream end of the second fin, and a downstream portion including a downstream end of the first fin overlaps with a position in the flow direction of an upstream portion including an upstream end of the third fin.
- With the above configuration, it is possible to restrict the development of the temperature boundary layer by providing the fins intermittently in the flow direction of the coolant. Furthermore, by causing the positions of the upstream portion of the first fin provided in the first row and the downstream portion of the second fin provided in the second row adjacent thereto to overlap in the flow direction and also causing the positions of the downstream portion of the first fin provided in the first row and the upstream portion of the third fin provided in the second row to overlap in the flow direction, it is possible to restrict the flow of the coolant from separating from the fins. With the structure described above, favorable heat transfer can be realized between the fins and the coolant.
- In the present invention, the fins may be provided along portions of the waveforms including two peaks.
- With the above configuration, development of the temperature boundary layer and separation of the flow of coolant are further restricted, and favorable heat transfer can be realized between the fins and the coolant.
- In the present invention, the waveforms may have shapes symmetrical on an axis that is a virtual line that passes through the peaks, is orthogonal to the flow direction, and is parallel to the width direction.
- With the above configuration, separation of the flow of coolant is further restricted, and favorable heat transfer can be realized between the fins and the coolant.
- In the present invention, the fins may each have the same shape in cross-sectional planes parallel to the flow direction and to the width direction.
- With the above configuration, favorable heat transfer can be realized over a wide range, with coolant flow that is substantially uniform in the height direction.
- In the present invention, favorable heat transfer can be realized between the fins and the coolant.
- In the present embodiment, in a case where a length of a half wavelength of the waveform in the flow direction is λ/2 and a length of the fin in the flow direction is L, [{L−(λ/2)}/λ/2]×100 may be greater than or equal to 30% and less than 50%.
- With the configuration described above, the effect of preventing the occurrence of the separation is realized.
- The above and other objects, features, and advantages of the present invention will become more apparent from the following description when taken in conjunction with the accompanying drawings in which a preferred embodiment of the present invention is shown by way of illustrative example.
-
FIG. 1 is a perspective view of the cooling apparatus according to the present embodiment. -
FIG. 2 is an exploded perspective view of the cooling apparatus according to the present embodiment. -
FIG. 3 is a partial plan view of an inner fin. -
FIG. 4 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 0%. -
FIG. 5 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 15%. -
FIG. 6 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 25%. -
FIG. 7 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of the second row relative to the first row is 50%. -
FIG. 8 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 0%. -
FIG. 9 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 5%. -
FIG. 10 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 10%. -
FIG. 11 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 30%. -
FIG. 12 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 40%. -
FIG. 13 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 1 [mm]. -
FIG. 14 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 3 [mm]. -
FIG. 15 is a table showing results obtained by examining the velocity vectors and temperature contours while changing the offset amounts and the extension amounts, while using fins with amplitudes of 5 [mm]. -
FIG. 16 is a partial plan view of an inner fin according to another embodiment. - The following describes the present invention while providing examples of preferred embodiments and referencing the accompanying drawings.
- The
cooling apparatus 10 shown inFIG. 1 has a flat shape, and is provided near a bottom surface of a PCU (power control unit) of an electric vehicle such as an electric automobile of hybrid automobile. The PCU is a heat source body that generates heat when supplying power from a high voltage battery to an electric motor or when supplying power from a generator to a high voltage battery. - As shown in
FIG. 2 , thecooling apparatus 10 includes atop cover 20, abottom cover 30, and aninner fin 40. Thetop cover 20,bottom cover 30, andinner fin 40 are formed of metal with high thermal conductivity, such as aluminum or copper that has undergone nickel plating. The top surface of thetop cover 20 is used as a heat absorbing surface. Aside wall 32 protruding upward is formed on the circumferential edge of thebottom cover 30, and two holes penetrating from the bottom surface to the top surface are formed at respective ends of thebottom cover 30 in the longitudinal direction. One of these holes is used as aflow inlet 34 for the coolant, and the other hole is used as aflow outlet 36 for the coolant. - The
inner fin 40 includes aboard portion 42 brazed to thebottom cover 30 and a plurality offins 44 that protrude upward from theboard portion 42. The bottom surface of theboard portion 42 is brazed to the top surface of thebottom cover 30. The bottom surface of thetop cover 20 is brazed to the top end of theside wall 32 of thebottom cover 30, or contacts the top end of eachfin 44. In this way, acoolant passage 12 through which coolant flows is formed by thebottom cover 30 and thetop cover 20, and a plurality offins 44 are provided within thecoolant passage 12. The flow direction f of the coolant in thecoolant passage 12 is substantially parallel to the longitudinal direction. - In the present embodiment, the shape and arrangement of the
fins 44 are one characteristic. The shape and arrangement of thefins 44 are described usingFIG. 3 . InFIG. 3 , the left-right direction in the plane of the drawing matches the longitudinal direction of thecooling apparatus 10, and the up-down direction in the plane of the drawing matches the width direction. Furthermore, although not shown in the drawing, a direction perpendicular to the plane of the drawing matches the height direction. - As shown in
FIG. 3 , in the plan view of theinner fin 40, a plurality ofwaveforms 60 extending in the flow direction f are assumed. InFIG. 3 , sinusoidal curves are shown as an example of thewaveforms 60. The amplitudes and periods of thewaveforms 60 are substantially constant from the upstream side to the downstream side in the flow direction f. Furthermore, the phases of the plurality ofwaveforms 60 are the same as each other at each position in the flow direction f. Eachwaveform 60 forms a shape that has linear symmetry, with avirtual line 70. Thevirtual line 70 passes through apeak 62, is orthogonal to the flow direction f, and is parallel to the width direction serving as an axis. - Each
fin 44 is provided intermittently along thewaveform 60. In other words, in asingle waveform 60, agap 46 is provided between the twofins 44 in front and behind along the flow direction f, and thefins 44 andgaps 46 are arranged in a row in an alternating manner. One wavelength of thewaveform 60 is formed by combining onefin 44 and onegap 46 that are adjacent to each other. - The
fin 44 is formed along a portion of thewaveform 60 including twopeaks 62. The portion of thefin 44 arranged on thepeak 62 on the upstream side is referred to as an upstreamside peak portion 48, and the portion of thefin 44 formed on thepeak 62 on the downstream side is referred to as a downstreamside peak portion 50. The portion of thefin 44 arranged farthest on the upstream side in the flow direction f is referred to as theupstream end 52, and the portion of thefin 44 arranged farthest on the downstream side is referred to as thedownstream end 54. Theupstream end 52 is at a position resulting from thefin 44 being extended to the upstream side from the upstreamside peak portion 48 along thewaveform 60, and thedownstream end 54 is at a position resulting from thefin 44 being extended to the downstream side from the downstreamside peak portion 50 along thewaveform 60. Therefore, the length L of thefin 44 in the flow direction f is greater than the length λ/2 of the half wavelength of thewaveform 60. Details of the extension amount by which thefin 44 extends from the upstreamside peak portion 48 to theupstream end 52 and the extension amount by which thefin 44 extends from the downstreamside peak portion 50 to thedownstream end 54 are provided in section [4] below. - There are two arrangement patterns for the
fins 44 and thegaps 46. One of these arrangement patterns is a first pattern in which the position of thefin 44 in the width direction is displaced in one direction (e.g., to an upward direction in the plane of the drawing ofFIG. 3 ) as progression occurs along thefin 44 from the upstreamside peak portion 48 to the downstreamside peak portion 50. The other arrangement pattern is a second pattern in which the position of thefin 44 in the width direction is displaced in the other direction (e.g., a downward direction in the plane of the drawing ofFIG. 3 ) as progression occurs along thefin 44 from the upstreamside peak portion 48 to the downstreamside peak portion 50.First rows 72 of the first pattern andsecond rows 74 of the second pattern are lined up in an alternating manner from one side to another side in the width direction. The intervals P between adjacentfirst rows 72 are constant, and the intervals P between adjacentsecond rows 74 are also constant. Details about the intervals Po (Po1 and Po2) between thefirst rows 72 and thesecond rows 74 are provided in section [3] below. InFIG. 3 , an implementation state is shown in which thefirst rows 72 andsecond rows 74 are lined up from one side to the other in the width direction at uniform intervals P/2 (=0.50 P). - In a
fin 44, the portion from the upstreamside peak portion 48 to theupstream end 52 and the portion having line symmetry with respect to this portion using thevirtual line 70 as an axis are referred to collectively as theupstream portion 56. Furthermore, in afin 44, the portion from the downstreamside peak portion 50 to thedownstream end 54 and the portion having line symmetry with respect to this portion using thevirtual line 70 as an axis are referred to collectively as adownstream portion 58. Theupstream portion 56 of thefin 44 arranged in thefirst row 72 overlaps with the position of thedownstream portion 58 of afin 44 arranged in thesecond row 74 in the flow direction f. Thedownstream portion 58 of afin 44 arranged in thefirst row 72 overlaps with the position of theupstream portion 56 of afin 44 arranged in thesecond row 74 in the flow direction f. - Each
fin 44 has a constant height from theupstream end 52 to thedownstream end 54, and has a flat shape in the height direction in accordance with thecooling apparatus 10. Furthermore, thefins 44 have the same shape in each of cross-sectional planes parallel to both the flow direction f and the width direction. In other words, thefins 44 have the same shapes as seen in the plan view ofFIG. 3 . Thefins 44 have the same shape in the height direction. - As shown in
FIG. 3 , the intervals Po between thefirst rows 72 andsecond rows 74 include an interval Pot between afirst row 72 and asecond row 74 positioned on one side (upper side in the plane of the drawing) in the width direction of thisfirst row 72 and an interval Po2 between thefirst row 72 and asecond row 74 positioned the other side (lower side in the plane of the drawing) of thisfirst row 72 in the width direction. Here, the interval Po2 is considered to be the offset amount of thesecond row 74 relative to thefirst row 72, and the offset amount is shown as a percentage of the interval P of thefirst row 72. -
FIG. 4 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of thesecond row 74 relative to thefirst row 72 is 0%. An offset of 0% means that there is no interval Po2 between thefirst row 72 and thesecond row 74, and that afin 44′ that is continuous, instead of being intermittent, is provided. In the case where the offset amount is 0%, development of a temperature boundary layer in the coolant flowing on both sides of thefin 44′ is observed as the location progresses toward the downstream side. -
FIG. 5 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of thesecond row 74 relative to thefirst row 72 is 15%. In the case where the offset amount is 15%, development of a temperature boundary layer in the coolant flowing on the side (interval Pot side) where the flow path on the downstream side between thefin 44 of thefirst row 72 and thefin 44 of thesecond row 74 is narrow is observed, but the development of a temperature boundary layer in the coolant flowing on the side (interval Po1 side) where the flow path is wide is not observed, even on the downstream side. -
FIG. 6 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of thesecond row 74 relative to thefirst row 72 is 25%. In the case where the offset amount is 25%, the development of the temperature boundary layer is less than in the case where the offset amount is 15%. -
FIG. 7 is a diagram simply showing the trend of the thermal contours in a case where the offset amount of thesecond row 74 relative to thefirst row 72 is 50%. In the case where the offset amount is 50%, development of the temperature boundary layer is not observed, even on the downstream side. - According to
FIGS. 4 to 7 , it is understood that if the offset amount is set to be even a small amount, the effect of restricting development of the temperature boundary layer is realized, and particularly if the offset amount is set to be greater than or equal to 25% and less than or equal to 50%, the effect of more effectively restricting the temperature boundary layer is realized. Based on the above, it can be said that it is preferable for the intervals Po between thefirst rows 72 and thesecond rows 74 to be greater than or equal to 0.25 P and less than or equal to 0.50 P (or greater than or equal to 0.50 P and less and or equal to 0.75 P). - As described below, the extension amount is shown as a percentage of the half wavelength (=λ/2) of a
waveform 60. -
Extension Percentage=[{L−(λ/2)}/λ/2]×100(0%<Extension Percentage<50%) -
FIG. 8 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 0%. In the case where the extension percentage is 0%, alarge separation 80 occurs on the other side (lower side in the plane of the drawing) in the width direction of theupstream portion 56 of eachfin 44. -
FIG. 9 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 5%. In the case where the extension percentage is 5%, theseparation 80 is less than in the case where the extension percentage is 0%. -
FIG. 10 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 10%. In the case where the extension percentage is 10%, theseparation 80 that occurs in the cases where the extension rate is 0% and 5% is almost nonexistent. -
FIG. 11 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 30%, andFIG. 12 is a diagram simply showing the trend of a velocity vector distribution of the coolant in a case where the extension percentage is 40%. In the case where the extension percentage is greater than or equal to 30%, theseparation 80 does not occur. - According to
FIGS. 8 to 12 , it is understood that if theupstream end 52 of afin 44 extends even a small amount from the upstreamside peak portion 48 along thewaveform 60 or thedownstream end 54 of thefin 44 extends even a small amount from the downstreamside peak portion 50 along thewaveform 60, an effect of restricting the occurrence of theseparation 80 is achieved. In particular, if the extension percentage is greater than or equal to 30% and less than 50%, an effect of stopping the occurrence of theseparation 80 is realized. - The length of a
fin 44 in the width direction, i.e., the length of thefin 44 from the upstreamside peak portion 48 to the downstreamside peak portion 50 in the width direction, is referred to as the amplitude of thefin 44.FIGS. 13 to 15 are tables showing results obtained by examining the velocity vectors and temperature contours while using the fins with the respective amplitudes of 1 [mm], 3 [mm], and 5 [mm], and changing the offset amounts (25%, 37.5%, and 50%) and the extension amounts (0%, 15%, and 30%). According toFIGS. 13 to 15 , it is understood that the velocity vectors and temperature contours do not significantly change as a result of different amplitudes. In other words, it is understood that there is no correlation between the amplitude, and the velocity vector and temperature contour. - In the embodiment described above, the
fins 44 are described as havingwaveforms 60 that are sinusoidal curves. Instead of this, the same effect as in the embodiment described above can be realized withfins 44 havingother waveforms 60. For example, as shown inFIG. 16 , thefins 44 may havetriangular waveforms 60. - The
fins 44 each have a flat shape in the height direction orthogonal to the flow direction f of the coolant in thecoolant passage 12, and are provided intermittently along thevirtual waveforms 60 that extend in the flow direction f and that make a plurality of rows in the width direction orthogonal to the flow direction f and to the height direction. With thefin 44 provided in thefirst row 72 being thefirst fin 44 and the twofins 44 lined up in the flow direction f and provided in thesecond row 74 adjacent to thefirst row 72 being thesecond fin 44 and thethird fin 44, theupstream portion 56 including theupstream end 52 of thefirst fin 44 overlaps with the position in the flow direction f of thedownstream portion 58 including thedownstream end 54 of thesecond fin 44. Furthermore, thedownstream portion 58 including thedownstream end 54 of thefirst fin 44 overlaps with a position in the flow direction f of theupstream portion 56 including theupstream end 52 of thethird fin 44. - With the configuration described above, it is possible to restrict the development of the temperature boundary layer by providing the
fins 44 intermittently in the flow direction f of the coolant. Furthermore, by causing the positions of theupstream portion 56 of thefirst fin 44 provided in thefirst row 72 and thedownstream portion 58 of thesecond fin 44 provided in thesecond row 74 adjacent thereto to overlap in the flow direction f and also causing the positions of thedownstream portion 58 of thefirst fin 44 provided in thefirst row 72 and theupstream portion 56 of thethird fin 44 provided in thesecond row 74 to overlap in the flow direction f, it is possible to restrict the flow of the coolant from separating from thefins 44. With the structure described above, favorable heat transfer can be realized between thefins 44 and the coolant. - The
fins 44 are provided along portions of thewaveforms 60 including twopeaks 62. With the configuration described above, development of the temperature boundary layer and separation of the flow of coolant are further restricted, and favorable heat transfer can be realized between thefins 44 and the coolant. - The
waveforms 60 each have shapes symmetrical on the axis that is thevirtual line 70 that passes through thepeaks 62, is orthogonal to the flow direction f, and is parallel to the width direction. With the configuration described above, the separation of the flow of coolant is further restricted, and favorable heat transfer can be realized between thefins 44 and the coolant. - The
fins 44 each have the same shape in the cross-sectional planes parallel to the flow direction f and to the width direction. With the configuration described above, favorable heat transfer can be realized over a wide range, with coolant flow that is substantially uniform in the height direction. - In a case where the length of a half wavelength of the
waveform 60 in the flow direction f is λ/2 and the length of thefin 44 in the flow direction f is L, [{L−(λ/2)}/λ/2]×100 may be greater than or equal to 30% and less than 50%. With the configuration described above, the effect of preventing the occurrence of theseparation 80 is realized. - The cooling apparatus according to the present embodiment is not limited to the embodiments described above, and it is obvious that various configurations can be adopted without deviating from the scope of the present invention.
Claims (5)
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Also Published As
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CN109990639A (en) | 2019-07-09 |
JP6663899B2 (en) | 2020-03-13 |
JP2019102505A (en) | 2019-06-24 |
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