US20190360758A1 - Water heat exchanger - Google Patents
Water heat exchanger Download PDFInfo
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- US20190360758A1 US20190360758A1 US16/477,705 US201816477705A US2019360758A1 US 20190360758 A1 US20190360758 A1 US 20190360758A1 US 201816477705 A US201816477705 A US 201816477705A US 2019360758 A1 US2019360758 A1 US 2019360758A1
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- flow paths
- fluid
- flow
- layer
- heat exchanger
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D9/005—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 the plates having openings therein for both heat-exchange media
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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
- 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
Definitions
- the present invention relates to a water heat exchanger, and, particularly, to a water heat exchanger including a first layer and a second layer that are stacked upon each other, and exchanging heat between a first fluid and a second fluid.
- the first layer has first flow paths formed in a plurality of rows and through which water as the first fluid flows.
- the second layer has second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows.
- water heat exchangers that exchange heat between water as the first fluid and a refrigerant (such as a chlorofluorocarbon refrigerant, a natural refrigerant, and brine) as the second fluid have been used in, for example, heat-pump cooling and heating devices and heat-pump hot water supply devices.
- a refrigerant such as a chlorofluorocarbon refrigerant, a natural refrigerant, and brine
- Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2010-117102
- there exists a type of such water heat exchangers including first layers and second layers that are stacked upon each other. Each first layer has first flow paths formed in a plurality of rows and through which the first fluid flows.
- Each second layer has second flow paths formed in a plurality of rows and through which the second fluid flows.
- the above-described water heat exchanger known in the art can realize higher performance and can be made compact as a result of reducing the flow-path cross-sectional area of each first flow path and the flow-path cross-sectional area of each second flow path.
- a water heat exchanger can realize even higher performance and can be made more compact by, for example, appropriately forming the shapes of the flow paths.
- the water heat exchanger includes a first layer and a second layer that are stacked upon each other, and exchanges heat between a first fluid and a second fluid.
- the first layer has first flow paths formed in a plurality of rows and through which water as the first fluid flows.
- the second layer has second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows.
- a water heat exchanger includes a first layer and a second layer that are stacked upon each other, and exchanges heat between a first fluid and a second fluid, the first layer having first flow paths formed in a plurality of rows and through which water as the first fluid flows, the second layer having second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows.
- each first flow path extends from one end portion to another end portion of the first layer in a direction crossing a direction of arrangement of the first flow paths.
- each second flow path extends from one end portion to another end portion of the second layer in a direction crossing a direction of arrangement of the second flow paths.
- the first flow paths have a meandering shape
- the second flow paths have a meandering shape.
- the flow path length per unit volume of the water heat exchanger can be increased.
- the thermal conductivity of the first flow paths and the thermal conductivity of the second flow paths can be increased. In this way, here, the water heat exchanger can realize higher performance and can be made compact.
- the first flow paths are formed such that a flow-path cross-sectional area of a first-fluid outlet vicinity positioned in a vicinity of an outlet for the first fluid is larger than a flow-path cross-sectional area of an upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- the flow-path cross-sectional area of the first-fluid outlet vicinity of the first flow paths is larger than the flow-path cross-sectional area of the upstream-side portion, disposed upstream of the first-fluid outlet vicinity, of the first flow paths, it is possible to make it less likely for scale deposited when the first fluid is heated to clog the first-fluid outlet vicinity, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the first fluid in the first flow paths is limited to only the first-fluid outlet vicinity. In this way, here, clogging of the first flow paths of the water heat exchanger can be suppressed, while a reduction in thermal conductivity is minimized.
- the second flow paths are formed such that a flow-path cross-sectional area of a second-fluid outlet vicinity positioned in a vicinity of an outlet for the second fluid is larger than a flow-path cross-sectional area of an upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- the second fluid containing a large amount of gas component that increases due to evaporation can smoothly flow in the second-fluid outlet vicinity, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the second fluid in the second flow paths is limited to only the second-fluid outlet vicinity.
- an increase in pressure loss in the second flow paths of the water heat exchanger can be suppressed, while a reduction in thermal conductivity is minimized.
- FIG. 1 is an external view of a water heat exchanger according to one or more embodiments of the present invention.
- FIG. 2 shows first flow paths of the water heat exchanger according to one or more embodiments of the present invention.
- FIG. 3 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention.
- FIG. 4 is a perspective view of a state in which the first flow paths and the second flow paths of the water heat exchanger according to one or more embodiments of the present invention are stacked upon each other.
- FIG. 5 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 2 ).
- FIG. 6 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 7 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 2 ).
- FIG. 8 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 9 is an external view of a water heat exchanger according to one or more embodiments of the present invention.
- FIG. 10 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 11 shows second flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 12 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 13 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 2 ).
- FIG. 14 shows the first flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 2 ).
- FIG. 15 shows second flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 16 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 17 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 18 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIGS. 1 to 4 each show a water heat exchanger 1 according to one or more embodiments of the present invention.
- the water heat exchanger 1 is a heat exchanger that exchanges heat between water as a first fluid and a refrigerant as a second fluid in, for example, an air-conditioning and heating device and a heat-pump hot water supply device.
- a near-side surface in a sheet plane of the water heat exchanger 1 shown in FIGS. 1 to 3 expressions indicating directions, such as “up”, “down”, “left”, “right”, “vertical”, and “horizontal” are used. However, these expressions are used for convenience of description, and do not indicate the actual arrangement of the water heat exchanger 1 and structural portions thereof.
- the water heat exchanger 1 primarily includes a casing 2 in which a heat exchanging unit 3 that exchanges heat between the first fluid and the second fluid is provided, a first pipe 4 a and a first pipe 4 b that are each an inlet and an outlet for the first fluid, and a second pipe 5 a and a second pipe 5 b that are each an inlet and an outlet for the second fluid.
- the heat exchanging unit 3 includes first layers 10 and second layers 20 that are stacked upon each other.
- Each first layer 10 has first flow paths 11 formed in a plurality of rows and through which the first fluid flows.
- Each second layer 20 has second flow paths 21 formed in a plurality of rows and through which the second fluid flows.
- the direction in which the first layers 10 and the second layers 20 are stacked upon each other (here, a direction from the near side in the sheet plane to a far side in the sheet plane of FIGS. 1 to 3 ) is defined as a stacking direction.
- the direction in which the plurality of first flow paths 11 are arranged side by side here, a left-right direction in the sheet plane of FIG.
- each first flow path 11 extends from one end portion of the first layer 10 (an upper end portion of the first layer 10 in FIG. 2 ) to another end portion of the first layer 10 (a lower end portion of the first layer 10 in FIG. 2 ) in a direction crossing the direction of arrangement of the first flow paths 11 (here, the up-down direction or a vertical direction in the sheet plane of FIG.
- each second flow path 21 extends from one end portion of the second layer 20 (a left end portion of the second layer 20 in FIG. 3 ) to another end portion of the second layer 20 (a right end portion of the second layer 20 in FIG. 3 ) in a direction crossing the direction of arrangement of the second flow paths 21 (here, the left-right direction or a horizontal direction in the sheet plane of FIG. 3 ).
- the first flow paths 11 and the second flow paths 21 are arranged so as to allow cross-flows.
- each first flow path 11 extends in the direction crossing the direction of arrangement of the first flow paths 11 (here, the vertical direction) while each first flow path 11 linearly (that is, angularly) meanders in the direction of arrangement of the first flow paths 11 (here, the left-right direction in the sheet plane of FIG. 2 ). It is desirable that each first flow path 11 meander three or more times from the one end portion to the other end portion of the first layer 10 .
- the second flow paths 21 have a meandering shape.
- each second flow path 21 extends in the direction crossing the direction of arrangement of the second flow paths 21 (here, the horizontal direction) while each second flow path 21 linearly (that is, angularly) meanders in the direction of arrangement of the second flow paths 21 (here, the up-down direction in the sheet plane of FIG. 3 ). It is desirable that each second flow path 21 meander three or more times from the one end portion to the other end portion of the second layer 20 .
- the heat exchanging unit 3 including the first layers 10 and the second layers 20 that are stacked upon each other includes first plates 12 and second plates 22 that are alternately stacked upon each other. Grooves that form the first flow paths are formed in one surface of each first plate 12 . Grooves that form the second flow paths 21 are formed in one surface of each second plate 22 . Each first plate 12 and each second plate 22 are made of a metallic material. The grooves that form the first flow paths 11 and the grooves that form the second flow paths 21 are formed by, for example, machining or etching the first plates 12 and the second plates 22 , respectively.
- each first plate 12 and the second plates 22 are joined to each other by a joining process, such as diffusion joining, to form the heat exchanging unit 3 including the first layers 10 and the second layers 20 that are stacked upon each other.
- a joining process such as diffusion joining
- the grooves that form the flow paths 11 are formed in one surface of each first plate 12 and the grooves that form the flow paths 21 are formed in one surface of each second plate 22 , the configurations are not limited thereto.
- Each first plate 12 may have grooves that form the flow paths 11 , 21 in both surfaces thereof, and/or each second plate 22 may have grooves that form the flow paths 11 , 21 in both surfaces thereof.
- the first pipe 4 a is disposed at an upper portion of the casing 2
- the first pipe 4 b is disposed at a lower portion of the casing 2
- the casing 2 includes a first header 6 disposed at the upper portion of the casing 2 and having a space that allows upper end portions of the first flow paths 11 to merge, and a first header 7 disposed at the lower portion of the casing 2 and having a space that allows lower end portions of the first flow paths 11 to merge.
- the first pipe 4 a communicates with the upper end portions of the first flow paths 11 via the first header 6
- the first pipe 4 b communicates with the lower end portions of the first flow paths 11 via the first header 7 .
- the second pipe 5 a is disposed on a left portion of the casing 2
- the second pipe 5 b is disposed on a right portion of the casing 2
- the casing 2 includes a second header 8 disposed at the left portion of the casing 2 and having a space that allows left end portions of the second flow paths 21 to merge, and a second header 9 disposed at the right portion of the casing 2 and having a space that allows right end portions of the second flow paths 21 to merge.
- the second pipe 5 a communicates with the left end portions of the second flow paths 21 via the second header 8
- the second pipe 5 b communicates with the right end portions of the second flow paths 21 via the second header 9 .
- the first pipe 4 b when the first fluid is to be heated by the second fluid, the first pipe 4 b can be the inlet for the first fluid, the first pipe 4 a can be the outlet for the first fluid, the second pipe 5 b can be the inlet for the second fluid, and the second pipe 5 a can be the outlet for the second fluid.
- the water heat exchanger 1 functions as a heat exchanger in which the first fluid flows through the first flow paths 11 from bottom to top and is heated and in which the second fluid flows through the second flow paths 21 from right to left and is cooled.
- the first pipe 4 b when the first fluid is to be cooled by the second fluid, the first pipe 4 b can be the inlet for the first fluid, the first pipe 4 a can be the outlet for the first fluid, the second pipe 5 a can be the inlet for the second fluid, and the second pipe 5 b can be the outlet for the second fluid.
- the water heat exchanger 1 functions as a heat exchanger in which the first fluid flows through the first flow paths 11 from the bottom to the top and is cooled and in which the second fluid flows through the second flow paths 21 from the left to the right and is heated.
- the first flow paths 11 and the second flow paths 21 have a meandering shape when the first layers 10 and the second layers 20 are viewed in the stacking direction, compared to when the first flow paths 11 and the second flow paths 21 each have a straight shape, the flow path length per unit volume of the water heat exchanger 1 can be increased. Moreover, since a heat transfer accelerating effect can be realized due to such meandering shapes of the first flow paths 11 and the second flow paths 21 , compared to when the first flow paths 11 and the second flow paths 21 each have a straight shape, the thermal conductivity of the first flow paths 11 and the thermal conductivity of the second flow paths 21 can be increased. In this way, here, the water heat exchanger 1 can realize higher performance and can be made compact.
- the first flow paths 11 and the second flow paths 21 have a linearly (that is, angularly) meandering shape, the shape is not limited thereto.
- the first flow paths 11 and the second flow paths 21 may have a curvedly (that is, roundedly instead of angularly) meandering shape.
- This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- the first flow paths 11 and the second flow paths 21 both have a meandering shape, only the first flow paths 11 or only the second flow paths 21 may have a meandering shape.
- the second flow paths 21 may have a meandering shape such as that shown in FIG. 3 or FIG. 6
- the first flow paths 11 may each have a straight shape such as that shown in FIG. 7
- the first flow paths 11 may have a meandering shape such as that shown in FIG. 2 or FIG. 5
- the second flow paths 21 may each have a straight shape such as that shown in FIG. 8 .
- This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- the first flow paths 11 and the second flow paths 21 are arranged so as to allow cross-flows, the structures are not limited thereto.
- each second flow path 21 extending from the one end portion of the second layer 20 (the left end portion of the second layer 20 in FIG. 3 ) to the other end portion of the second layer 20 (the right end portion of the second layer 20 in FIG. 3 ) in the horizontal direction may be caused to extend from one end portion of the second layer 20 (a lower end portion of the second layer 20 in FIG. 10 ) to another end portion of the second layer 20 (an upper end portion of the second layer 20 in FIG. 10 ) in the vertical direction, to arrange the first flow paths 11 and the second flow paths 21 so as to allow counter-flows (or parallel flows).
- the second pipe 5 a and the second header 8 are disposed at the lower portion of the casing 2
- the second pipe 5 b and the second header 9 are disposed at the upper portion of the casing 2 .
- This configuration functions as a heat exchanger in which, when the first fluid is to be heated by the second fluid, the first fluid flows through the first flow paths 11 from the bottom to the top and is heated, and the second fluid flows through the second flow paths 21 from the top to the bottom and is cooled.
- This configuration also functions as a heat exchanger in which, when the first fluid is to be cooled by the second fluid, the first fluid flows through the first flow paths 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow paths 21 from the bottom to the top and is heated.
- This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- the first flow paths 11 and the second flow paths 21 are arranged so as to allow cross-flows, the structures are not limited thereto.
- the second flow paths 21 may be divided into a plurality of flow path groups and these flow path groups may be connected in series, to arrange the first flow paths 11 and the second flow paths 21 so as to allow orthogonal counter-flows (or orthogonal parallel flows).
- the second flow paths 21 are divided into three flow path groups 21 A, 21 B, and 21 C in the direction of arrangement of the second flow paths 21 (here, in the up-down direction in the sheet plane of FIG. 11 ).
- a partitioning member in the second header 9 partitions the space in the second header 9 into a space 9 a that communicates with the second pipe 5 b and the right end portions of the second flow paths 21 of the flow path group 21 A and into a space 9 b that communicates with the right end portions of the second flow paths 21 of the flow path groups 21 B and 21 C.
- a partitioning member in the second header 8 partitions the space in the second header 8 into a space 8 a that communicates with the second pipe 5 a and the left end portions of the second flow paths 21 of the flow path group 21 C and into a space 8 b that communicates with the left end portions of the second flow paths 21 of the flow path groups 21 A and 21 B.
- the flow path groups 21 A, 21 B, and 21 C of the second flow paths 21 are connected in series by the second headers 8 and 9 and are arranged such that the first flow paths 11 and the second flow paths 21 allow orthogonal counter-flows (or orthogonal parallel flows).
- This configuration functions as a heat exchanger in which, when the first fluid is to be heated by the second fluid, the first fluid flows through the first flow paths 11 from the bottom to the top and is heated, and the second fluid flows through the second flow paths 21 from the flow path groups 21 A to 21 B and to 21 C in that order from the top to the bottom while the second fluid makes turns leftwards and rightwards, and is cooled.
- This configuration functions as a heat exchanger in which, when the first fluid is to be cooled by the second fluid, the first fluid flows through the first flow paths 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow paths 21 from the flow path groups 21 C to 21 B and to 21 A in that order from the bottom to the top while the second fluid makes turns leftwards and rightwards, and is heated.
- the space in the second header 8 is partitioned into the spaces 8 a and 8 b such that the flow path groups 21 A, 21 B, and 21 C are connected in series and the space in the second header 9 is partitioned into the spaces 9 a and 9 b such that the flow path groups 21 A, 21 B, and 21 C are connected in series
- the structure is not limited thereto.
- a connecting flow path 29 a having the same function as the space 8 b may be disposed on the left end portions of the second flow paths 21
- a connecting flow path 29 b having the same function as the space 9 b may be disposed on the right end portions of the second flow paths 21 .
- the connecting flow path 29 a that causes the left end portions of the second flow paths 21 of the flow path groups 21 A and 21 B to communicate with each other and the connecting flow path 29 b that causes the right end portions of the second flow paths 21 of the flow path groups 21 B and 21 C to communicate with each other are formed in the second layer 20 .
- grooves that form the connecting flow paths 29 a and 29 b can be formed in the second plate 22 .
- the second header 8 can have only a space corresponding to the space 8 a in FIG. 11
- the second header 9 can have only a space corresponding to the space 9 a in FIG. 11 .
- This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- the first flow paths 11 may become clogged by scale deposited in the first flow paths 11 .
- each first flow path 11 is formed such that a flow-path cross-sectional area S 11 a of a first-fluid outlet vicinity 11 a positioned in the vicinity of the outlet for the first fluid is larger than a flow-path cross-sectional area S 11 b of an upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a .
- each flow-path cross-sectional area S 11 a is made larger than its corresponding flow-path cross-sectional area S 11 b .
- the first-fluid outlet vicinity 11 a refers to a portion that is disposed closer to the outlet and that has a flow-path length which is 20% to 50% of the flow-path length from an inlet side of the first flow path 11 (here, an end portion on a side of the first pipe 4 b ) to an outlet side of the first flow path 11 (here, an end portion on a side of the first pipe 4 a ).
- the first flow paths 11 may be merged such that the number of flow paths at the first-fluid outlet vicinities 11 a is less than the number of flow paths at the upstream-side portions disposed upstream of the first-fluid outlet vicinities 11 a .
- the number of flow paths at the first-fluid outlet vicinities 11 a is less than the number of flow paths at the upstream-side portions disposed upstream of the first-fluid outlet vicinities 11 a .
- the flow-path width W 11 a of the first-fluid outlet vicinity 11 a after the first flow paths 11 have been merged may be made larger than the total of the flow-path widths W 11 b of the upstream-side portions 11 b disposed upstream of the first-fluid outlet vicinities 11 a before the first flow paths 11 have been merged.
- the flow-path cross-sectional area S 11 a of the first-fluid outlet vicinity 11 a after the first flow paths 11 have been merged can be made larger than the total of the flow-path cross-sectional areas S 11 b of the upstream-side portions 11 b disposed upstream of the first-fluid outlet vicinities 11 a before the first flow paths 11 have been merged.
- the amount of gas component that flows through the second flow paths 21 is increased due to evaporation of the second fluid, as a result of which pressure loss in the second flow paths 21 may increase.
- each second flow path 21 is formed such that a flow-path cross-sectional area S 21 a of a second-fluid outlet vicinity 21 a positioned in the vicinity of the outlet for the second fluid is larger than a flow-path cross-sectional area S 21 b of an upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a .
- each flow-path cross-sectional area S 21 a is made larger than its corresponding flow-path cross-sectional area S 21 b .
- the second-fluid outlet vicinity 21 a refers to a portion that is disposed closer to the outlet and that has a flow-path length which is 20% to 50% of the flow-path length from an inlet side of the second flow path 21 (here, an end portion on a side of the second pipe 5 a ) to an outlet side of the second flow path 21 (here, an end portion on a side of the second pipe 5 b ).
- the first flow paths 11 and the second flow paths 21 may be arranged so as to allow orthogonal counter-flows (or orthogonal parallel flows).
- the flow path group 21 A positioned in the vicinity of the outlet for the second fluid may be defined as second-fluid outlet vicinities 21 a
- the flow path groups 21 B and 21 C may be defined as upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a
- the flow-path width W 21 a of each second flow path 21 of the flow path group 21 A may be made larger than the flow-path width W 21 b of each second flow path 21 of the flow path groups 21 B and 21 C.
- the second flow paths 21 may be merged such that the number of flow paths at the second-fluid outlet vicinities 21 a is less than the number of flow paths at the upstream-side portions disposed upstream of the second-fluid outlet vicinities 21 a .
- the second flow paths 21 may be merged such that the number of flow paths at the second-fluid outlet vicinities 21 a is less than the number of flow paths at the upstream-side portions disposed upstream of the second-fluid outlet vicinities 21 a .
- the flow-path width W 21 a of the second-fluid outlet vicinity 21 a after the second flow paths 21 have been merged may be made larger than the total of the flow-path widths W 21 b of the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a before the second flow paths 21 have been merged.
- the flow-path cross-sectional area S 21 a of the second-fluid outlet vicinity 21 a after the second flow paths 21 have been merged can be made larger than the total of the flow-path cross-sectional areas S 21 b of the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a before the second flow paths 21 have been merged.
- the total of the flow-path cross-sectional areas S 21 a may be made larger than the total of the flow-path cross-sectional areas S 21 b by branching the second flow paths 21 such that the number of flow paths at the second-fluid outlet vicinities 21 a is larger than the number of flow paths at the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a .
- the flow path group 21 A positioned in the vicinity of the outlet for the second fluid may be defined as second-fluid outlet vicinities 21 a
- the flow path groups 21 B and 21 C may be defined as upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a
- the number N 21 a of the second flow paths 21 of the flow path group 21 A may be larger than the number N 21 b of the flow paths of the flow path groups 21 B and 21 C.
- the flow-path widths W 21 a and W 21 b (the flow-path cross-sectional areas S 21 a and S 21 b ) of the second flow paths 21 are equal to each other, and the flow-path cross-sectional area S 21 a of the flow path group 21 A and the total of the flow-path cross-sectional areas S 21 b of the flow path groups 21 B and 21 C are changed by changing the number of flow paths.
- the configuration in which the number N 21 a of flow paths at the second-fluid outlet vicinities 21 a is larger than the number of flow paths at the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a not only suppresses an increase in pressure loss in the second flow paths 21 of the water heat exchanger 1 , but also can properly maintain the distribution performance in the second flow paths 21 for the second fluid by reducing the number of flow paths at the inlet for the second fluid.
- each second flow path 21 for the second fluid effectively contributes to the distribution performance in each second flow path 21 for the second fluid because, not only is the number N 21 a of flow paths of the flow path group 21 A larger than the number N 21 b of flow paths of the flow path groups 21 B and 21 C disposed upstream of the flow path group 21 A, but also the number of flow paths from largest to smallest is the number of flow paths of the flow path group 21 A, the number of flow paths of the flow path group 21 B, and the number of flow paths of the flow path group 21 C in this order, that is, the number of flow paths decreases with decreasing distance from the inlet for the second fluid.
- the present invention provides a configuration that includes a first layer and a second layer that are stacked upon each other, with the first layer having first flow paths formed in a plurality of rows and through which water as a first fluid flows and the second layer having second flow paths formed in a plurality of rows and through which a refrigerant as a second fluid flows; and can be widely applied to water heat exchangers that exchange heat between the first fluid and the second fluid.
Abstract
Description
- The present invention relates to a water heat exchanger, and, particularly, to a water heat exchanger including a first layer and a second layer that are stacked upon each other, and exchanging heat between a first fluid and a second fluid. The first layer has first flow paths formed in a plurality of rows and through which water as the first fluid flows. The second layer has second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows.
- Hitherto, water heat exchangers that exchange heat between water as the first fluid and a refrigerant (such as a chlorofluorocarbon refrigerant, a natural refrigerant, and brine) as the second fluid have been used in, for example, heat-pump cooling and heating devices and heat-pump hot water supply devices. As described in Patent Literature 1 (Japanese Unexamined Patent Application Publication No. 2010-117102), there exists a type of such water heat exchangers including first layers and second layers that are stacked upon each other. Each first layer has first flow paths formed in a plurality of rows and through which the first fluid flows. Each second layer has second flow paths formed in a plurality of rows and through which the second fluid flows.
- The above-described water heat exchanger known in the art can realize higher performance and can be made compact as a result of reducing the flow-path cross-sectional area of each first flow path and the flow-path cross-sectional area of each second flow path.
- However, when, for example, an increase in pressure loss and clogging of the flow paths are considered, there is a limit as to how small the flow-path cross-sectional area of each first flow path and the flow-path cross-sectional area of each second flow path can be made. Therefore, in order for the water heat exchanger to realize even higher performance and to be made more compact, it is necessary to, for example, appropriately form the shapes of the flow paths.
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- Japanese Unexamined Patent Application Publication No. 2010-117102
- According to one or more embodiments of the present invention, a water heat exchanger can realize even higher performance and can be made more compact by, for example, appropriately forming the shapes of the flow paths. The water heat exchanger includes a first layer and a second layer that are stacked upon each other, and exchanges heat between a first fluid and a second fluid. The first layer has first flow paths formed in a plurality of rows and through which water as the first fluid flows. The second layer has second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows.
- A water heat exchanger according to one or more embodiments includes a first layer and a second layer that are stacked upon each other, and exchanges heat between a first fluid and a second fluid, the first layer having first flow paths formed in a plurality of rows and through which water as the first fluid flows, the second layer having second flow paths formed in a plurality of rows and through which a refrigerant as the second fluid flows. When the first layer is viewed in a stacking direction of the first layer and the second layer, each first flow path extends from one end portion to another end portion of the first layer in a direction crossing a direction of arrangement of the first flow paths. When the second layer is viewed in the stacking direction, each second flow path extends from one end portion to another end portion of the second layer in a direction crossing a direction of arrangement of the second flow paths. Here, when the first layer is viewed in the stacking direction, the first flow paths have a meandering shape, and/or when the second layer is viewed in the stacking direction, the second flow paths have a meandering shape.
- Here, as described above, since the first flow paths and the second flow paths have a meandering shape when the first layer and the second layer are viewed in the stacking direction, compared to when the first flow paths and the second flow paths have a straight shape, the flow path length per unit volume of the water heat exchanger can be increased. Moreover, since a heat transfer accelerating effect can be realized due to such meandering shapes of the first flow paths and the second flow paths, compared to when the first flow paths and the second flow paths each have a straight shape, the thermal conductivity of the first flow paths and the thermal conductivity of the second flow paths can be increased. In this way, here, the water heat exchanger can realize higher performance and can be made compact.
- In a water heat exchanger according to one or more embodiments, when the first fluid is to be heated by the second fluid, the first flow paths are formed such that a flow-path cross-sectional area of a first-fluid outlet vicinity positioned in a vicinity of an outlet for the first fluid is larger than a flow-path cross-sectional area of an upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- Here, as described above, since the flow-path cross-sectional area of the first-fluid outlet vicinity of the first flow paths is larger than the flow-path cross-sectional area of the upstream-side portion, disposed upstream of the first-fluid outlet vicinity, of the first flow paths, it is possible to make it less likely for scale deposited when the first fluid is heated to clog the first-fluid outlet vicinity, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the first fluid in the first flow paths is limited to only the first-fluid outlet vicinity. In this way, here, clogging of the first flow paths of the water heat exchanger can be suppressed, while a reduction in thermal conductivity is minimized.
- In a water heat exchanger according to one or more embodiments, when the first fluid is to be cooled by the second fluid, the second flow paths are formed such that a flow-path cross-sectional area of a second-fluid outlet vicinity positioned in a vicinity of an outlet for the second fluid is larger than a flow-path cross-sectional area of an upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- Here, as described above, since the flow-path cross-sectional area of the second-fluid outlet vicinity of the second flow paths is larger than the flow-path cross-sectional area of the upstream-side portion, disposed upstream of the second-fluid outlet vicinity, of the second flow paths, the second fluid containing a large amount of gas component that increases due to evaporation can smoothly flow in the second-fluid outlet vicinity, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the second fluid in the second flow paths is limited to only the second-fluid outlet vicinity. In this way, here, an increase in pressure loss in the second flow paths of the water heat exchanger can be suppressed, while a reduction in thermal conductivity is minimized.
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FIG. 1 is an external view of a water heat exchanger according to one or more embodiments of the present invention. -
FIG. 2 shows first flow paths of the water heat exchanger according to one or more embodiments of the present invention. -
FIG. 3 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention. -
FIG. 4 is a perspective view of a state in which the first flow paths and the second flow paths of the water heat exchanger according to one or more embodiments of the present invention are stacked upon each other. -
FIG. 5 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 6 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 7 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 8 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 9 is an external view of a water heat exchanger according to one or more embodiments of the present invention. -
FIG. 10 shows second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 11 shows second flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 12 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 13 shows first flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 14 shows the first flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 15 shows second flow paths of a water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 16 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 17 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 18 shows the second flow paths of the water heat exchanger according to one or more embodiments of the present invention (and corresponds toFIG. 3 ). - One or more embodiments of a water heat exchanger according to the present invention are described below on the basis of the drawings. Specific configurations of the water heat exchanger according to one or more embodiments of the present invention are not limited to those described below and are changeable within a scope that does not depart from the spirit of the invention.
- (1) Configurations and Characteristics
-
FIGS. 1 to 4 each show awater heat exchanger 1 according to one or more embodiments of the present invention. - The
water heat exchanger 1 is a heat exchanger that exchanges heat between water as a first fluid and a refrigerant as a second fluid in, for example, an air-conditioning and heating device and a heat-pump hot water supply device. In the description below, with reference to a near-side surface in a sheet plane of thewater heat exchanger 1 shown inFIGS. 1 to 3 , expressions indicating directions, such as “up”, “down”, “left”, “right”, “vertical”, and “horizontal” are used. However, these expressions are used for convenience of description, and do not indicate the actual arrangement of thewater heat exchanger 1 and structural portions thereof. - The
water heat exchanger 1 primarily includes acasing 2 in which aheat exchanging unit 3 that exchanges heat between the first fluid and the second fluid is provided, afirst pipe 4 a and afirst pipe 4 b that are each an inlet and an outlet for the first fluid, and asecond pipe 5 a and asecond pipe 5 b that are each an inlet and an outlet for the second fluid. - The
heat exchanging unit 3 includesfirst layers 10 andsecond layers 20 that are stacked upon each other. Eachfirst layer 10 hasfirst flow paths 11 formed in a plurality of rows and through which the first fluid flows. Eachsecond layer 20 hassecond flow paths 21 formed in a plurality of rows and through which the second fluid flows. Here, the direction in which thefirst layers 10 and thesecond layers 20 are stacked upon each other (here, a direction from the near side in the sheet plane to a far side in the sheet plane ofFIGS. 1 to 3 ) is defined as a stacking direction. The direction in which the plurality offirst flow paths 11 are arranged side by side (here, a left-right direction in the sheet plane ofFIG. 2 ) is defined as a direction of arrangement of thefirst flow paths 11, and the direction in which the plurality ofsecond flow paths 21 are arranged side by side (here, an up-down direction in the sheet plane ofFIG. 3 ) is defined as a direction of arrangement of thesecond flow paths 21. When thefirst layers 10 are viewed in the stacking direction of thefirst layers 10 and thesecond layers 20, eachfirst flow path 11 extends from one end portion of the first layer 10 (an upper end portion of thefirst layer 10 inFIG. 2 ) to another end portion of the first layer 10 (a lower end portion of thefirst layer 10 inFIG. 2 ) in a direction crossing the direction of arrangement of the first flow paths 11 (here, the up-down direction or a vertical direction in the sheet plane ofFIG. 2 ). When thesecond layers 20 are viewed in the stacking direction of thefirst layers 10 and thesecond layers 20, eachsecond flow path 21 extends from one end portion of the second layer 20 (a left end portion of thesecond layer 20 inFIG. 3 ) to another end portion of the second layer 20 (a right end portion of thesecond layer 20 inFIG. 3 ) in a direction crossing the direction of arrangement of the second flow paths 21 (here, the left-right direction or a horizontal direction in the sheet plane ofFIG. 3 ). In this way, here, thefirst flow paths 11 and thesecond flow paths 21 are arranged so as to allow cross-flows. - Here, when the
first layers 10 are viewed in the stacking direction, thefirst flow paths 11 have a meandering shape. Specifically, eachfirst flow path 11 extends in the direction crossing the direction of arrangement of the first flow paths 11 (here, the vertical direction) while eachfirst flow path 11 linearly (that is, angularly) meanders in the direction of arrangement of the first flow paths 11 (here, the left-right direction in the sheet plane ofFIG. 2 ). It is desirable that eachfirst flow path 11 meander three or more times from the one end portion to the other end portion of thefirst layer 10. When thesecond layers 20 are viewed in the stacking direction, thesecond flow paths 21 have a meandering shape. Specifically, eachsecond flow path 21 extends in the direction crossing the direction of arrangement of the second flow paths 21 (here, the horizontal direction) while eachsecond flow path 21 linearly (that is, angularly) meanders in the direction of arrangement of the second flow paths 21 (here, the up-down direction in the sheet plane ofFIG. 3 ). It is desirable that eachsecond flow path 21 meander three or more times from the one end portion to the other end portion of thesecond layer 20. - Here, the
heat exchanging unit 3 including thefirst layers 10 and thesecond layers 20 that are stacked upon each other includesfirst plates 12 andsecond plates 22 that are alternately stacked upon each other. Grooves that form the first flow paths are formed in one surface of eachfirst plate 12. Grooves that form thesecond flow paths 21 are formed in one surface of eachsecond plate 22. Eachfirst plate 12 and eachsecond plate 22 are made of a metallic material. The grooves that form thefirst flow paths 11 and the grooves that form thesecond flow paths 21 are formed by, for example, machining or etching thefirst plates 12 and thesecond plates 22, respectively. After stacking predetermined numbers of thefirst plates 12 and thesecond plates 22, each being grooved thus, for example, thefirst plates 12 and thesecond plates 22 are joined to each other by a joining process, such as diffusion joining, to form theheat exchanging unit 3 including thefirst layers 10 and thesecond layers 20 that are stacked upon each other. Here, although the grooves that form theflow paths 11 are formed in one surface of eachfirst plate 12 and the grooves that form theflow paths 21 are formed in one surface of eachsecond plate 22, the configurations are not limited thereto. Eachfirst plate 12 may have grooves that form theflow paths second plate 22 may have grooves that form theflow paths - Here, the
first pipe 4 a is disposed at an upper portion of thecasing 2, and thefirst pipe 4 b is disposed at a lower portion of thecasing 2. Thecasing 2 includes afirst header 6 disposed at the upper portion of thecasing 2 and having a space that allows upper end portions of thefirst flow paths 11 to merge, and afirst header 7 disposed at the lower portion of thecasing 2 and having a space that allows lower end portions of thefirst flow paths 11 to merge. Thefirst pipe 4 a communicates with the upper end portions of thefirst flow paths 11 via thefirst header 6, and thefirst pipe 4 b communicates with the lower end portions of thefirst flow paths 11 via thefirst header 7. Here, thesecond pipe 5 a is disposed on a left portion of thecasing 2, and thesecond pipe 5 b is disposed on a right portion of thecasing 2. Thecasing 2 includes asecond header 8 disposed at the left portion of thecasing 2 and having a space that allows left end portions of thesecond flow paths 21 to merge, and asecond header 9 disposed at the right portion of thecasing 2 and having a space that allows right end portions of thesecond flow paths 21 to merge. Thesecond pipe 5 a communicates with the left end portions of thesecond flow paths 21 via thesecond header 8, and thesecond pipe 5 b communicates with the right end portions of thesecond flow paths 21 via thesecond header 9. - In the
water heat exchanger 1 having such a configuration, for example, when the first fluid is to be heated by the second fluid, thefirst pipe 4 b can be the inlet for the first fluid, thefirst pipe 4 a can be the outlet for the first fluid, thesecond pipe 5 b can be the inlet for the second fluid, and thesecond pipe 5 a can be the outlet for the second fluid. In this case, thewater heat exchanger 1 functions as a heat exchanger in which the first fluid flows through thefirst flow paths 11 from bottom to top and is heated and in which the second fluid flows through thesecond flow paths 21 from right to left and is cooled. In thewater heat exchanger 1, for example, when the first fluid is to be cooled by the second fluid, thefirst pipe 4 b can be the inlet for the first fluid, thefirst pipe 4 a can be the outlet for the first fluid, thesecond pipe 5 a can be the inlet for the second fluid, and thesecond pipe 5 b can be the outlet for the second fluid. In this case, thewater heat exchanger 1 functions as a heat exchanger in which the first fluid flows through thefirst flow paths 11 from the bottom to the top and is cooled and in which the second fluid flows through thesecond flow paths 21 from the left to the right and is heated. - In such a
water heat exchanger 1, as described above, since thefirst flow paths 11 and thesecond flow paths 21 have a meandering shape when thefirst layers 10 and thesecond layers 20 are viewed in the stacking direction, compared to when thefirst flow paths 11 and thesecond flow paths 21 each have a straight shape, the flow path length per unit volume of thewater heat exchanger 1 can be increased. Moreover, since a heat transfer accelerating effect can be realized due to such meandering shapes of thefirst flow paths 11 and thesecond flow paths 21, compared to when thefirst flow paths 11 and thesecond flow paths 21 each have a straight shape, the thermal conductivity of thefirst flow paths 11 and the thermal conductivity of thesecond flow paths 21 can be increased. In this way, here, thewater heat exchanger 1 can realize higher performance and can be made compact. - Although, in the
water heat exchanger 1 of the above-described embodiments, as shown inFIGS. 2 and 3 , thefirst flow paths 11 and thesecond flow paths 21 have a linearly (that is, angularly) meandering shape, the shape is not limited thereto. - For example, as shown in
FIGS. 5 and 6 , thefirst flow paths 11 and thesecond flow paths 21 may have a curvedly (that is, roundedly instead of angularly) meandering shape. - This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- Although, in the
water heat exchangers 1 of the above-described embodiments, thefirst flow paths 11 and thesecond flow paths 21 both have a meandering shape, only thefirst flow paths 11 or only thesecond flow paths 21 may have a meandering shape. - For example, the
second flow paths 21 may have a meandering shape such as that shown inFIG. 3 orFIG. 6 , and thefirst flow paths 11 may each have a straight shape such as that shown inFIG. 7 . In contrast, thefirst flow paths 11 may have a meandering shape such as that shown inFIG. 2 orFIG. 5 , and thesecond flow paths 21 may each have a straight shape such as that shown inFIG. 8 . - This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- Although, in the
water heat exchangers 1 of the above-described embodiments, thefirst flow paths 11 and thesecond flow paths 21 are arranged so as to allow cross-flows, the structures are not limited thereto. - For example, as shown in
FIGS. 9 and 10 , eachsecond flow path 21 extending from the one end portion of the second layer 20 (the left end portion of thesecond layer 20 inFIG. 3 ) to the other end portion of the second layer 20 (the right end portion of thesecond layer 20 inFIG. 3 ) in the horizontal direction may be caused to extend from one end portion of the second layer 20 (a lower end portion of thesecond layer 20 inFIG. 10 ) to another end portion of the second layer 20 (an upper end portion of thesecond layer 20 inFIG. 10 ) in the vertical direction, to arrange thefirst flow paths 11 and thesecond flow paths 21 so as to allow counter-flows (or parallel flows). In this case, thesecond pipe 5 a and thesecond header 8 are disposed at the lower portion of thecasing 2, and thesecond pipe 5 b and thesecond header 9 are disposed at the upper portion of thecasing 2. This configuration functions as a heat exchanger in which, when the first fluid is to be heated by the second fluid, the first fluid flows through thefirst flow paths 11 from the bottom to the top and is heated, and the second fluid flows through thesecond flow paths 21 from the top to the bottom and is cooled. This configuration also functions as a heat exchanger in which, when the first fluid is to be cooled by the second fluid, the first fluid flows through thefirst flow paths 11 from the bottom to the top and is cooled, and the second fluid flows through thesecond flow paths 21 from the bottom to the top and is heated. - This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- Although, in the
water heat exchangers 1 of the above-described embodiments, thefirst flow paths 11 and thesecond flow paths 21 are arranged so as to allow cross-flows, the structures are not limited thereto. - For example, the
second flow paths 21 may be divided into a plurality of flow path groups and these flow path groups may be connected in series, to arrange thefirst flow paths 11 and thesecond flow paths 21 so as to allow orthogonal counter-flows (or orthogonal parallel flows). Specifically, in the configuration shown inFIG. 11 , thesecond flow paths 21 are divided into threeflow path groups FIG. 11 ). For example, a partitioning member in thesecond header 9 partitions the space in thesecond header 9 into aspace 9 a that communicates with thesecond pipe 5 b and the right end portions of thesecond flow paths 21 of theflow path group 21A and into aspace 9 b that communicates with the right end portions of thesecond flow paths 21 of theflow path groups second header 8 partitions the space in thesecond header 8 into aspace 8 a that communicates with thesecond pipe 5 a and the left end portions of thesecond flow paths 21 of theflow path group 21C and into aspace 8 b that communicates with the left end portions of thesecond flow paths 21 of theflow path groups flow path groups second flow paths 21 are connected in series by thesecond headers first flow paths 11 and thesecond flow paths 21 allow orthogonal counter-flows (or orthogonal parallel flows). This configuration functions as a heat exchanger in which, when the first fluid is to be heated by the second fluid, the first fluid flows through thefirst flow paths 11 from the bottom to the top and is heated, and the second fluid flows through thesecond flow paths 21 from theflow path groups 21A to 21B and to 21C in that order from the top to the bottom while the second fluid makes turns leftwards and rightwards, and is cooled. This configuration functions as a heat exchanger in which, when the first fluid is to be cooled by the second fluid, the first fluid flows through thefirst flow paths 11 from the bottom to the top and is cooled, and the second fluid flows through thesecond flow paths 21 from theflow path groups 21C to 21B and to 21A in that order from the bottom to the top while the second fluid makes turns leftwards and rightwards, and is heated. - Although, in the configuration shown in
FIG. 11 , the space in thesecond header 8 is partitioned into thespaces flow path groups second header 9 is partitioned into thespaces flow path groups FIG. 12 , a connectingflow path 29 a having the same function as thespace 8 b may be disposed on the left end portions of thesecond flow paths 21, and a connectingflow path 29 b having the same function as thespace 9 b may be disposed on the right end portions of thesecond flow paths 21. That is, the connectingflow path 29 a that causes the left end portions of thesecond flow paths 21 of theflow path groups flow path 29 b that causes the right end portions of thesecond flow paths 21 of theflow path groups second layer 20. Here, grooves that form the connectingflow paths second plate 22. In this case, thesecond header 8 can have only a space corresponding to thespace 8 a inFIG. 11 , and thesecond header 9 can have only a space corresponding to thespace 9 a inFIG. 11 . - This configuration of the present modification can also provide operational effects similar to those of the above-described embodiments.
- In the
water heat exchangers 1 of the above-described embodiments, when water as the first fluid is to be heated by the second fluid, thefirst flow paths 11 may become clogged by scale deposited in thefirst flow paths 11. - Therefore, here, in order to suppress such clogging of portions of the
first flow paths 11 in the vicinity of the outlet caused by the deposited scale, for example, as shown inFIG. 13 , eachfirst flow path 11 is formed such that a flow-path cross-sectional area S11 a of a first-fluid outlet vicinity 11 a positioned in the vicinity of the outlet for the first fluid is larger than a flow-path cross-sectional area S11 b of an upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a. Here, by making a flow-path width W11 a of the first-fluid outlet vicinity 11 a of eachfirst flow path 11 larger than a flow-path width W11 b of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, each flow-path cross-sectional area S11 a is made larger than its corresponding flow-path cross-sectional area S11 b. The first-fluid outlet vicinity 11 a refers to a portion that is disposed closer to the outlet and that has a flow-path length which is 20% to 50% of the flow-path length from an inlet side of the first flow path 11 (here, an end portion on a side of thefirst pipe 4 b) to an outlet side of the first flow path 11 (here, an end portion on a side of thefirst pipe 4 a). - Unlike the configuration of each
first flow path 11 shown inFIG. 13 , thefirst flow paths 11 may be merged such that the number of flow paths at the first-fluid outlet vicinities 11 a is less than the number of flow paths at the upstream-side portions disposed upstream of the first-fluid outlet vicinities 11 a. For example, as shown inFIG. 14 , by merging at the first-fluid outlet vicinities 11 a twofirst flow paths 11 adjacent to each other in the direction of arrangement of thefirst flow paths 11 and forming the twofirst flow paths 11 into onefirst flow path 11, the flow-path width W11 a of the first-fluid outlet vicinity 11 a after thefirst flow paths 11 have been merged may be made larger than the total of the flow-path widths W11 b of the upstream-side portions 11 b disposed upstream of the first-fluid outlet vicinities 11 a before thefirst flow paths 11 have been merged. Therefore, the flow-path cross-sectional area S11 a of the first-fluid outlet vicinity 11 a after thefirst flow paths 11 have been merged can be made larger than the total of the flow-path cross-sectional areas S11 b of the upstream-side portions 11 b disposed upstream of the first-fluid outlet vicinities 11 a before thefirst flow paths 11 have been merged. - In such a
water heat exchanger 1, as described above, since the flow-path cross-sectional area S11 a of the first-fluid outlet vicinity 11 a of eachfirst flow path 11 is larger than the flow-path cross-sectional area of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, it is possible to make it less likely for scale deposited when the first fluid is heated to clog the first-fluid outlet vicinities 11 a, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the first fluid in thefirst flow paths 11 is limited to only the first-fluid outlet vicinities 11 a. In this way, here, not only can operational effects similar to those of the above-described embodiments, but also clogging of thefirst flow paths 11 of thewater heat exchanger 1 can be suppressed, while a reduction in thermal conductivity is minimized. - In the
water heat exchangers 1 of the above-described embodiments, when the first fluid is to be cooled by a refrigerant as the second fluid, the amount of gas component that flows through thesecond flow paths 21 is increased due to evaporation of the second fluid, as a result of which pressure loss in thesecond flow paths 21 may increase. - Therefore, here, in order to suppress such an increase in pressure loss in the
second flow paths 21 caused by evaporation of the second fluid, for example, as shown inFIG. 15 , eachsecond flow path 21 is formed such that a flow-path cross-sectional area S21 a of a second-fluid outlet vicinity 21 a positioned in the vicinity of the outlet for the second fluid is larger than a flow-path cross-sectional area S21 b of an upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. Here, by making a flow-path width W21 a of the second-fluid outlet vicinity 21 a of eachsecond flow path 21 larger than a flow-path width W21 b of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, each flow-path cross-sectional area S21 a is made larger than its corresponding flow-path cross-sectional area S21 b. The second-fluid outlet vicinity 21 a refers to a portion that is disposed closer to the outlet and that has a flow-path length which is 20% to 50% of the flow-path length from an inlet side of the second flow path 21 (here, an end portion on a side of thesecond pipe 5 a) to an outlet side of the second flow path 21 (here, an end portion on a side of thesecond pipe 5 b). Thefirst flow paths 11 and thesecond flow paths 21 may be arranged so as to allow orthogonal counter-flows (or orthogonal parallel flows). - Even the configuration, such as that of Modification 4 above, in which the
second flow paths 21 are divided into the plurality offlow path groups flow path groups fluid outlet vicinities 21 a of thesecond flow paths 21 are made large similarly to the configuration shown inFIG. 15 . In this case, for example, as shown inFIG. 16 , theflow path group 21A positioned in the vicinity of the outlet for the second fluid may be defined as second-fluid outlet vicinities 21 a, theflow path groups side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a, and the flow-path width W21 a of eachsecond flow path 21 of theflow path group 21A may be made larger than the flow-path width W21 b of eachsecond flow path 21 of theflow path groups - Unlike the configuration of each
second flow path 21 shown inFIG. 15 , thesecond flow paths 21 may be merged such that the number of flow paths at the second-fluid outlet vicinities 21 a is less than the number of flow paths at the upstream-side portions disposed upstream of the second-fluid outlet vicinities 21 a. For example, as shown inFIG. 17 , by merging at the second-fluid outlet vicinities 21 a twosecond flow paths 21 adjacent to each other in the direction of arrangement of thesecond flow paths 21 and forming the twosecond flow paths 21 into onesecond flow path 21, the flow-path width W21 a of the second-fluid outlet vicinity 21 a after thesecond flow paths 21 have been merged may be made larger than the total of the flow-path widths W21 b of the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a before thesecond flow paths 21 have been merged. Therefore, the flow-path cross-sectional area S21 a of the second-fluid outlet vicinity 21 a after thesecond flow paths 21 have been merged can be made larger than the total of the flow-path cross-sectional areas S21 b of the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a before thesecond flow paths 21 have been merged. - In contrast to the configuration shown in
FIG. 17 in which the flow-path cross-sectional area S21 a is made larger than the total of the flow-path cross-sectional areas S21 b by merging thesecond flow paths 21 at the second-fluid outlet vicinities 21 a, the total of the flow-path cross-sectional areas S21 a may be made larger than the total of the flow-path cross-sectional areas S21 b by branching thesecond flow paths 21 such that the number of flow paths at the second-fluid outlet vicinities 21 a is larger than the number of flow paths at the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a. For example, in the configuration, such as that of Modification 4 above, in which thesecond flow paths 21 are divided into the plurality offlow path groups flow path groups FIG. 18 , theflow path group 21A positioned in the vicinity of the outlet for the second fluid may be defined as second-fluid outlet vicinities 21 a, theflow path groups side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a, and the number N21 a of thesecond flow paths 21 of theflow path group 21A may be larger than the number N21 b of the flow paths of theflow path groups second flow paths 21 are equal to each other, and the flow-path cross-sectional area S21 a of theflow path group 21A and the total of the flow-path cross-sectional areas S21 b of theflow path groups - As described above, since the flow-path cross-sectional area S21 a of the second-
fluid outlet vicinity 21 a of eachsecond flow path 21 is larger than that of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, such awater heat exchanger 1 allows the second fluid containing a large amount of gas component that increases due to evaporation to smoothly flow in each second-fluid outlet vicinity 21 a, while a reduction in thermal conductivity caused by a reduction in the flow velocity of the second fluid in thesecond flow paths 21 is limited to only the second-fluid outlet vicinities 21 a. In this way, here, not only can operational effects similar to those of the above-described embodiments be provided, but also an increase in pressure loss in thesecond flow paths 21 of thewater heat exchanger 1 can be suppressed, while a reduction in thermal conductivity is minimized. - As with the configuration shown in
FIG. 18 , the configuration in which the number N21 a of flow paths at the second-fluid outlet vicinities 21 a is larger than the number of flow paths at the upstream-side portions 21 b disposed upstream of the second-fluid outlet vicinities 21 a not only suppresses an increase in pressure loss in thesecond flow paths 21 of thewater heat exchanger 1, but also can properly maintain the distribution performance in thesecond flow paths 21 for the second fluid by reducing the number of flow paths at the inlet for the second fluid. In particular, the configuration shown inFIG. 18 effectively contributes to the distribution performance in eachsecond flow path 21 for the second fluid because, not only is the number N21 a of flow paths of theflow path group 21A larger than the number N21 b of flow paths of theflow path groups flow path group 21A, but also the number of flow paths from largest to smallest is the number of flow paths of theflow path group 21A, the number of flow paths of theflow path group 21B, and the number of flow paths of theflow path group 21C in this order, that is, the number of flow paths decreases with decreasing distance from the inlet for the second fluid. - The present invention provides a configuration that includes a first layer and a second layer that are stacked upon each other, with the first layer having first flow paths formed in a plurality of rows and through which water as a first fluid flows and the second layer having second flow paths formed in a plurality of rows and through which a refrigerant as a second fluid flows; and can be widely applied to water heat exchangers that exchange heat between the first fluid and the second fluid.
- Although the disclosure has been described with respect to only a limited number of embodiments, those skilled in the art, having benefit of this disclosure, will appreciate that various other embodiments may be devised without departing from the scope of the present invention. Accordingly, the scope of the invention should be limited only by the attached claims.
-
-
- 1 water heat exchanger
- 10 first layer
- 11 first flow path
- 11 a first-fluid outlet vicinity
- 11 b upstream-side portion disposed upstream of first-fluid outlet vicinity
- 20 second layer
- 21 second flow path
- 21 a second-fluid outlet vicinity
- 21 b upstream-side portion disposed upstream of second-fluid outlet vicinity
- Although the disclosure has been described with respect to only a limited number of embodiments, those skilled in the art, having benefit of this disclosure, will appreciate that various other embodiments may be devised departing from the scope of the present invention. Accordingly, the scope of the invention should be limited only by the attached claims.
Claims (3)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017-004638 | 2017-01-13 | ||
JP2017004638A JP6432613B2 (en) | 2017-01-13 | 2017-01-13 | Water heat exchanger |
PCT/JP2018/000309 WO2018131596A1 (en) | 2017-01-13 | 2018-01-10 | Water heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20190360758A1 true US20190360758A1 (en) | 2019-11-28 |
Family
ID=62840376
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/477,705 Abandoned US20190360758A1 (en) | 2017-01-13 | 2018-01-10 | Water heat exchanger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20190360758A1 (en) |
EP (1) | EP3569962B1 (en) |
JP (1) | JP6432613B2 (en) |
CN (1) | CN110168300B (en) |
WO (1) | WO2018131596A1 (en) |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS53129701A (en) * | 1977-04-16 | 1978-11-13 | Toshiba Corp | Steam producer |
JPS6237687A (en) * | 1985-08-08 | 1987-02-18 | ヒ−トリツク・ピ−テイ−ワイ・リミテド | Heat exchanger |
US4744414A (en) * | 1986-09-02 | 1988-05-17 | Arco Chemical Company | Plastic film plate-type heat exchanger |
JP3858484B2 (en) * | 1998-11-24 | 2006-12-13 | 松下電器産業株式会社 | Laminate heat exchanger |
JP3937990B2 (en) * | 2002-09-27 | 2007-06-27 | 松下電器産業株式会社 | Heat exchanger |
JP2008128574A (en) * | 2006-11-21 | 2008-06-05 | Toshiba Corp | Heat exchanger |
US7637112B2 (en) * | 2006-12-14 | 2009-12-29 | Uop Llc | Heat exchanger design for natural gas liquefaction |
EP2169339B1 (en) * | 2007-06-18 | 2015-07-22 | Mitsubishi Electric Corporation | Heat exchange element, method of producing the heat exchange element, heat exchanger, and heat exchange and ventilation device |
JP2010117102A (en) | 2008-11-14 | 2010-05-27 | Fujitsu General Ltd | Heat exchanger |
KR100938802B1 (en) * | 2009-06-11 | 2010-01-27 | 국방과학연구소 | Heat exchanger having micro-channels |
JP2013113493A (en) * | 2011-11-29 | 2013-06-10 | Panasonic Corp | Heat exchange element and heat exchange ventilator using the same |
CN102494547B (en) * | 2011-11-30 | 2014-04-30 | 北京航空航天大学 | Miniature micro-channel plate-fin heat exchanger |
JP6001170B2 (en) * | 2012-06-26 | 2016-10-05 | エーバーシュペッヒャー・エグゾースト・テクノロジー・ゲーエムベーハー・ウント・コンパニー・カーゲー | Evaporator, waste heat utilization device for internal combustion engine, and internal combustion engine |
CN103868380B (en) * | 2012-12-11 | 2016-08-24 | 杭州三花研究院有限公司 | A kind of heat-exchangers of the plate type |
KR101534497B1 (en) * | 2013-10-17 | 2015-07-09 | 한국원자력연구원 | Heat exchanger for steam generator and steam generator having the same |
CN106440324B (en) * | 2016-12-07 | 2022-02-08 | 陈军 | Heat exchanger and air conditioner adopting same |
-
2017
- 2017-01-13 JP JP2017004638A patent/JP6432613B2/en active Active
-
2018
- 2018-01-10 EP EP18738883.0A patent/EP3569962B1/en active Active
- 2018-01-10 WO PCT/JP2018/000309 patent/WO2018131596A1/en unknown
- 2018-01-10 US US16/477,705 patent/US20190360758A1/en not_active Abandoned
- 2018-01-10 CN CN201880006479.6A patent/CN110168300B/en active Active
Also Published As
Publication number | Publication date |
---|---|
EP3569962B1 (en) | 2021-12-01 |
JP6432613B2 (en) | 2018-12-05 |
EP3569962A4 (en) | 2020-09-02 |
WO2018131596A1 (en) | 2018-07-19 |
EP3569962A1 (en) | 2019-11-20 |
JP2018112381A (en) | 2018-07-19 |
CN110168300A (en) | 2019-08-23 |
CN110168300B (en) | 2021-08-24 |
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