US20190376750A1 - Water heat exchanger - Google Patents
Water heat exchanger Download PDFInfo
- Publication number
- US20190376750A1 US20190376750A1 US16/477,564 US201816477564A US2019376750A1 US 20190376750 A1 US20190376750 A1 US 20190376750A1 US 201816477564 A US201816477564 A US 201816477564A US 2019376750 A1 US2019376750 A1 US 2019376750A1
- Authority
- US
- United States
- Prior art keywords
- fluid
- flow paths
- flow
- layer
- upstream
- 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
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
-
- 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
- F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
-
- 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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
-
- 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
-
- 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
- F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
-
- 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
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 air-conditioning 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.
- 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 are formed so 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.
- a water heat exchanger is the water heat exchanger according to the above-described embodiments, in which the first flow paths are merged so that the number of flow paths at the first-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- the flow-path cross-sectional area of the first-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- 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 second flow paths are formed so 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.
- a water heat exchanger is the water heat exchanger according to the above-described embodiments, in which the second flow paths are merged so that the number of flow paths at the second-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- the flow-path cross-sectional area of the second-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- a water heat exchanger is the water heat exchanger according to the above-described embodiments, in which the second flow paths are branched so that the number of flow paths at the second-fluid outlet vicinity is larger than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- the flow-path cross-sectional area of the second-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- this configuration makes the number of flow paths at the vicinity of the inlet for the second fluid smaller, it is possible to properly maintain the distribution performance in the second flow paths for the second fluid.
- a water heat exchanger is the water heat exchanger according to the above-described embodiments, in which when the first fluid is to be cooled by the second fluid, the second flow paths are formed so 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 Modification 1 of 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 Modification 1 of one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 7 is an external view of a water heat exchanger according to Modification 2 of one or more embodiments of the present invention.
- FIG. 8 shows second flow paths of the water heat exchanger according to Modification 2 of one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 9 shows second flow paths of a water heat exchanger according to Modification 3 of one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 10 shows the second flow paths of the water heat exchanger according to Modification 3 of one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 11 shows first flow paths of a water heat exchanger according to Modification 4 of one or more embodiments of the present invention (and corresponds to FIG. 2 ).
- FIG. 12 shows second flow paths of a water heat exchanger according to Modification 5 of one or more embodiments of the present invention (and corresponds to FIG. 3 ).
- FIG. 13 shows second flow paths of the water heat exchanger according to Modification 5 of 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, a heat-pump air-conditioning device and a heat-pump hot water supply device.
- a heat-pump air-conditioning device for example, a heat-pump air-conditioning device and a heat-pump hot water supply device.
- 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 an outlet and an inlet for the first fluid, respectively, 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 in FIG. 3 ).
- the first flow paths 11 and the second flow paths 20 are arranged so as to allow cross-flows.
- the heat exchanging unit 3 having 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 11 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 , it is 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.
- each first flow path 11 is formed so 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 ).
- each second flow path 21 is formed so that a flow-path cross-sectional area 521 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 521 b of an upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- each second flow path 21 by forming each second flow path 21 so that a flow-path width W 21 a of the second-fluid outlet vicinity 21 a of each second flow path 21 is larger than a flow-path width W 21 b of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, each flow-path cross-sectional area S 211 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 flow-path cross-sectional area S 11 a of the first-fluid outlet vicinity 11 a of each first flow path 11 is larger than that of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a.
- the flow-path cross-sectional area S 21 a of the second-fluid outlet vicinity 21 a of each second flow path 21 is larger than that of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- the first flow paths 11 or the second flow paths 21 may have a structure in which the flow-path cross-sectional area of each fluid outlet vicinity is larger than that of each upstream-side portion disposed upstream of the fluid outlet vicinity.
- the flow-path cross-sectional area S 21 a of the second-fluid outlet vicinity 21 a of each second flow path 21 may be made larger than that of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, and, as shown in FIG. 5 , the flow-path cross-sectional area (here, the flow-path width) of each first flow path 11 may be the same from the inlet side to the outlet side of each first flow path 11 .
- the flow-path cross-sectional area S 11 a of the first-fluid outlet vicinity 11 a of each first flow path 11 may be made larger than that of the upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, and, as shown in FIG. 6 , the flow-path cross-sectional area (here, the flow-path width) of each second flow path 21 may be the same from the inlet side to the outlet side of each second flow path 21 .
- This structure 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, it is 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. 8 ) to another end portion of the second layer 20 (an upper end portion of the second layer 20 in FIG. 8 ) in the vertical direction as shown in FIGS. 7 and 8 , 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 structure 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 structure 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 structure of the present modification can also provide operational effects similar to those of the above-described embodiments and Modification 1.
- the first flow paths 11 and the second flow paths 21 are arranged so as to allow cross-flows, it is 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 in FIG. 9 ).
- the space in the second header 9 is divided 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 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.
- the space in the second header 8 is divided 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 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 via the second headers 8 and 9 and are arranged so that the first flow paths 11 and the second flow paths 21 allow orthogonal counter-flows (or orthogonal parallel flows).
- This structure 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 in the order of the flow path group 21 A, the flow path group 21 B and the flow path group 21 C while the second fluid makes turns leftwards and rightwards, and is cooled.
- This structure 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 in the order of the flow path group 21 C, the flow path group 21 B and the flow path group 21 A while the second fluid makes turns leftwards and rightwards, and is heated.
- the flow path group 21 A positioned in the vicinity of the outlet for the second fluid is defined as second-fluid outlet vicinity 21 a and the flow path groups 21 B and 21 C are defined as upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- the flow-path width W 21 a of each second flow path 21 of the flow path group 21 A is 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. Therefore, when the first fluid is to be cooled by a refrigerant as the second fluid, the second flow paths 21 can be formed so that the flow-path cross-sectional area S 21 a of the second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S 21 b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- the space in the second header 8 is partitioned into the spaces 8 a and 8 b and the space in the second header 9 is partitioned into the spaces 9 a and 9 b so that the flow path groups 21 A, 21 B, and 21 C are connected in series
- 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 makes the left end portions of the second flow paths 21 of the flow path group 21 A and the left end portions of the second flow paths 21 of the flow path groups 21 B communicate with each other and the connecting flow path 29 b that makes the right end portions of the second flow paths 21 of the flow path group 21 B and the right end portions of the second flow paths 21 of the flow path group 21 C 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 a space only corresponding to the space 8 a as shown in FIG. 9
- the second header 9 can have a space only corresponding to the space 9 a as shown in FIG. 9 .
- This structure of the present modification can also provide operational effects similar to those of the above-described embodiments and Modification 1.
- each first flow path 11 when water as the first fluid is to be heated by the second fluid, each first flow path 11 is formed so that the flow-path width W 11 a of the first-fluid outlet vicinity 11 a, positioned in the vicinity of the outlet for the first fluid, of each first flow path 11 is larger than the flow-path width W 11 b of the upstream-side portion lib, disposed upstream of the first-fluid outlet vicinity 11 a, of each first flow path 11 .
- each first-fluid outlet vicinity 11 a is larger than the flow-path cross-sectional area S 11 b of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, to suppress clogging of outlet vicinity portions of the first flow paths 11 caused by deposition of scale.
- the structure for forming the first flow paths 11 so that, when water as the first fluid is to be heated by the second fluid, the flow-path cross-sectional area S 11 a of the first-fluid outlet vicinity 11 a is larger than the flow-path cross-sectional area S 11 b of the upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a is not limited thereto.
- the first flow paths 11 may be merged so that the number of flow paths at the first-fluid outlet vicinities 11 a of the first flow paths 11 is less than the number of flow paths at the upstream-side portions, disposed upstream of the first-fluid outlet vicinities 11 a, of the first flow paths 11 .
- the number of flow paths at the first-fluid outlet vicinities 11 a of the first flow paths 11 is less than the number of flow paths at the upstream-side portions, disposed upstream of the first-fluid outlet vicinities 11 a, of the first flow paths 11 .
- 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 vicinity 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 vicinity 11 a, before the first flow paths 11 have been merged.
- each second flow path 21 is formed so that the flow-path width W 21 a of the second-fluid outlet vicinity 21 a, positioned in the vicinity of the outlet for the second fluid, of the second flow path 21 is larger than the flow-path width W 21 b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- the flow-path cross-sectional area S 21 a of each second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S 21 b of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, to suppress an increase in pressure loss in the second flow paths 21 caused by an increase in the amount of gas component flowing in the second flow paths 21 due to evaporation of the second fluid.
- the structure for forming the second flow paths 21 so that, when the first fluid is to be cooled by a refrigerant as the second fluid, the flow-path cross-sectional area S 21 a of the second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S 21 b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a is not limited thereto.
- the second flow paths 21 may be merged so 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 in FIG.
- 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 vicinity 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 vicinity 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 so that the number of flow paths at the second-fluid outlet vicinity 21 a is larger than the number of flow paths at the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a.
- the flow path group 21 A positioned in the vicinity of the outlet for the second fluid may be defined as a second-fluid outlet vicinity 21 a
- the flow path groups 21 B and 21 C may be defined as an upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 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 structure in which the number N 21 a of flow paths at the second-fluid outlet vicinity 21 a is larger than the number N 21 a of flow paths at the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 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 near the inlet for the second fluid.
- One or more embodiments of the present invention can be widely applied to a water heat exchanger 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 that exchanges 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 air-conditioning 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 the flow-path cross-sectional area of each first flow path and the flow-path cross-sectional area of each second flow path are made too small, for example, an increase in pressure loss and clogging of the flow paths are concerns. Therefore, it is becoming necessary to, for example, appropriately form the shapes of the flow paths that can, for example, suppress an increase in pressure loss and clogging of the flow paths.
- Japanese Unexamined Patent Application Publication No. 2010-117102
- One or more embodiments of the present invention provide a water heat exchanger that suppresses an increase in pressure loss and clogging of flow paths by 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 fluid is to be heated by the second fluid, the first flow paths are formed so 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.
- A water heat exchanger according to one or more embodiments is the water heat exchanger according to the above-described embodiments, in which the first flow paths are merged so that the number of flow paths at the first-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- Here, as described above, by merging the first flow paths so that the number of flow paths at the first-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the first-fluid outlet vicinity, the flow-path cross-sectional area of the first-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the first-fluid outlet vicinity.
- 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 fluid is to be cooled by the second fluid, the second flow paths are formed so 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.
- A water heat exchanger according to one or more embodiments is the water heat exchanger according to the above-described embodiments, in which the second flow paths are merged so that the number of flow paths at the second-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- Here, as described above, by merging the second flow paths so that the number of flow paths at the second-fluid outlet vicinity is less than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity, the flow-path cross-sectional area of the second-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- A water heat exchanger according to one or more embodiments is the water heat exchanger according to the above-described embodiments, in which the second flow paths are branched so that the number of flow paths at the second-fluid outlet vicinity is larger than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity.
- Here, as described above, by branching the second flow paths so that the number of flow paths at the second-fluid outlet vicinity is larger than the number of flow paths at the upstream-side portion disposed upstream of the second-fluid outlet vicinity, the flow-path cross-sectional area of the second-fluid outlet vicinity can be made larger than the flow-path cross-sectional area of the upstream-side portion disposed upstream of the second-fluid outlet vicinity. Moreover, here, since this configuration makes the number of flow paths at the vicinity of the inlet for the second fluid smaller, it is possible to properly maintain the distribution performance in the second flow paths for the second fluid.
- A water heat exchanger according to one or more embodiments is the water heat exchanger according to the above-described embodiments, in which when the first fluid is to be cooled by the second fluid, the second flow paths are formed so 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.
-
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 toModification 1 of one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 6 shows second flow paths of the water heat exchanger according toModification 1 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 7 is an external view of a water heat exchanger according toModification 2 of one or more embodiments of the present invention. -
FIG. 8 shows second flow paths of the water heat exchanger according toModification 2 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 9 shows second flow paths of a water heat exchanger according toModification 3 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 10 shows the second flow paths of the water heat exchanger according toModification 3 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 11 shows first flow paths of a water heat exchanger according to Modification 4 of one or more embodiments of the present invention (and corresponds toFIG. 2 ). -
FIG. 12 shows second flow paths of a water heat exchanger according to Modification 5 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). -
FIG. 13 shows second flow paths of the water heat exchanger according to Modification 5 of one or more embodiments of the present invention (and corresponds toFIG. 3 ). - Embodiments and modifications thereof of a water heat exchanger according to the present invention are described below on the basis of the drawings. Specific structures of the water heat exchanger according to the present invention are not limited to those of the embodiments and the modifications thereof below and are changeable within a scope that does not depart from the spirit of the invention.
-
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, a heat-pump air-conditioning 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 an outlet and an inlet for the first fluid, respectively, 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 inFIG. 3 ). In this way, here, thefirst flow paths 11 and thesecond flow paths 20 are arranged so as to allow cross-flows. - Here, the
heat exchanging unit 3 having 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 thefirst flow paths 11 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, 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, it is 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 structure, 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. - Here, when water as the first fluid is to be heated by the second fluid, each
first flow path 11 is formed so 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 S11b of an upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a. Specifically, by forming eachfirst flow path 11 so that a flow-path width W11a of the first-fluid outlet vicinity 11 a of eachfirst flow path 11 is larger than a flow-path width W11b of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, each flow-path cross-sectional area S11a is made larger than its corresponding flow-path cross-sectional area S11b. 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). - Here, when the first fluid is to be cooled by a refrigerant as the second fluid, each
second flow path 21 is formed so that a flow-path cross-sectional area 521 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 521 b of an upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. Specifically, by forming eachsecond flow path 21 so that a flow-path width W21a of the second-fluid outlet vicinity 21 a of eachsecond flow path 21 is larger than a flow-path width W21b of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, each flow-path cross-sectional area S211a is made larger than its corresponding flow-path cross-sectional area S21b. 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). - In such a
water heat exchanger 1, as described above, when water as the first fluid is to be heated by the second fluid, since the flow-path cross-sectional area S11a of the first-fluid outlet vicinity 11 a of eachfirst flow path 11 is larger than that of the upstream-side portion 11 b, disposed upstream of the first-fluid outlet vicinity 11 a, of eachfirst flow path 11, 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, clogging of thefirst flow paths 11 of thewater heat exchanger 1 can be suppressed, while a reduction in thermal conductivity is minimized. - In such a
water heat exchanger 1, as described above, when the first fluid is to be cooled by a refrigerant as the second fluid, since the flow-path cross-sectional area S21a 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, of eachsecond flow path 21, the second fluid containing a large amount of gas component that increases due to evaporation can 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, 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. - In the
water heat exchanger 1 of the above-described embodiments, when water as the first fluid is to be heated by the second fluid, the flow-path cross-sectional area S11 a of the first-fluid outlet vicinity 11 a of eachfirst flow path 11 is larger than that of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a. Moreover, in thewater heat exchanger 1 of the above-described embodiments, when the first fluid is to be cooled by a refrigerant as the second fluid, the flow-path cross-sectional area S21a of the second-fluid outlet vicinity 21 a of eachsecond flow path 21 is larger than that of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. However, it is not limited thereto. Only thefirst flow paths 11 or thesecond flow paths 21 may have a structure in which the flow-path cross-sectional area of each fluid outlet vicinity is larger than that of each upstream-side portion disposed upstream of the fluid outlet vicinity. - For example, when the first fluid is to be cooled by a refrigerant as the second fluid, as shown in
FIG. 3 , the flow-path cross-sectional area S21a of the second-fluid outlet vicinity 21 a of eachsecond flow path 21 may be made larger than that of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, and, as shown inFIG. 5 , the flow-path cross-sectional area (here, the flow-path width) of eachfirst flow path 11 may be the same from the inlet side to the outlet side of eachfirst flow path 11. - For example, when water as the first fluid is to be heated by the second fluid, as shown in
FIG. 2 , the flow-path cross-sectional area S11a of the first-fluid outlet vicinity 11a of eachfirst flow path 11 may be made larger than that of the upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, and, as shown inFIG. 6 , the flow-path cross-sectional area (here, the flow-path width) of eachsecond flow path 21 may be the same from the inlet side to the outlet side of eachsecond flow path 21. - This structure 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 andModification 1, thefirst flow paths 11 and thesecond flow paths 21 are arranged so as to allow cross-flows, it is not limited thereto. - For example, each
second 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. 8 ) to another end portion of the second layer 20 (an upper end portion of thesecond layer 20 inFIG. 8 ) in the vertical direction as shown inFIGS. 7 and 8 , 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 structure 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 structure 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 structure of the present modification can also provide operational effects similar to those of the above-described embodiments and
Modification 1. - (4)
Modification 3 - Although, in the
water heat exchangers 1 of the above-described embodiments andModification 1, thefirst flow paths 11 and thesecond flow paths 21 are arranged so as to allow cross-flows, it is not limited thereto. For example, thesecond 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 structure shown inFIG. 9 , thesecond flow paths 21 are divided into threeflow path groups FIG. 9 ). For example, by arranging a partitioning member in thesecond header 9, the space in thesecond header 9 is divided 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 aspace 9 b that communicates with the right end portions of thesecond flow paths 21 of theflow path groups second header 8, the space in thesecond header 8 is divided 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 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 via thesecond headers first flow paths 11 and thesecond flow paths 21 allow orthogonal counter-flows (or orthogonal parallel flows). This structure 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 in the order of theflow path group 21A, theflow path group 21B and theflow path group 21C while the second fluid makes turns leftwards and rightwards, and is cooled. This structure 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 in the order of theflow path group 21C, theflow path group 21B and theflow path group 21A while the second fluid makes turns leftwards and rightwards, and is heated. In this case, theflow path group 21A positioned in the vicinity of the outlet for the second fluid is defined as second-fluid outlet vicinity 21 a and theflow path groups side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. The flow-path width W21a of eachsecond flow path 21 of theflow path group 21A is made larger than the flow-path width W21b of eachsecond flow path 21 of theflow path groups second flow paths 21 can be formed so that the flow-path cross-sectional area S21a of the second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S21b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. - Although, in the structure shown in
FIG. 9 , the space in thesecond header 8 is partitioned into thespaces second header 9 is partitioned into thespaces flow path groups FIG. 10 , 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 makes the left end portions of thesecond flow paths 21 of theflow path group 21A and the left end portions of thesecond flow paths 21 of theflow path groups 21B communicate with each other and the connectingflow path 29 b that makes the right end portions of thesecond flow paths 21 of theflow path group 21B and the right end portions of thesecond flow paths 21 of theflow path group 21C communicate with each other are formed in thesecond layer 20. Here, grooves that form the connectingflow paths second plate 22. In this case, thesecond header 8 can have a space only corresponding to thespace 8 a as shown inFIG. 9 , and thesecond header 9 can have a space only corresponding to thespace 9 a as shown inFIG. 9 . - This structure of the present modification can also provide operational effects similar to those of the above-described embodiments and
Modification 1. - In the
water heat exchangers 1 of the above-described embodiments andModifications 1 to 3, when water as the first fluid is to be heated by the second fluid, eachfirst flow path 11 is formed so that the flow-path width W11a of the first-fluid outlet vicinity 11 a, positioned in the vicinity of the outlet for the first fluid, of eachfirst flow path 11 is larger than the flow-path width W11b of the upstream-side portion lib, disposed upstream of the first-fluid outlet vicinity 11 a, of eachfirst flow path 11. Therefore, when water as the first fluid is to be heated by the second fluid, the flow-path cross-sectional area S11a of each first-fluid outlet vicinity 11a is larger than the flow-path cross-sectional area S11b of each upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a, to suppress clogging of outlet vicinity portions of thefirst flow paths 11 caused by deposition of scale. - However, the structure for forming the
first flow paths 11 so that, when water as the first fluid is to be heated by the second fluid, the flow-path cross-sectional area S11a of the first-fluid outlet vicinity 11 a is larger than the flow-path cross-sectional area S11b of the upstream-side portion 11 b disposed upstream of the first-fluid outlet vicinity 11 a is not limited thereto. - Specifically, when water as the first fluid is to be heated by the second fluid, the
first flow paths 11 may be merged so that the number of flow paths at the first-fluid outlet vicinities 11 a of thefirst flow paths 11 is less than the number of flow paths at the upstream-side portions, disposed upstream of the first-fluid outlet vicinities 11 a, of thefirst flow paths 11. For example, as shown inFIG. 11 , by merging twofirst flow paths 11 adjacent to each other in the direction of arrangement of thefirst flow paths 11 into onefirst flow path 11 at the first-fluid outlet vicinity 11 a, the flow-path width W11a 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 W11b of the upstream-side portions 11 b, disposed upstream of the first-fluid outlet vicinity 11 a, before thefirst flow paths 11 have been merged. Therefore, when water as the first fluid is to be heated by the second fluid, the flow-path cross-sectional area S11a 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 S11b of the upstream-side portions 11 b, disposed upstream of the first-fluid outlet vicinity 11 a, before thefirst flow paths 11 have been merged. - In the
water heat exchangers 1 of the above-described embodiments andModifications 1 to 4, when the first fluid is to be cooled by a refrigerant as the second fluid, eachsecond flow path 21 is formed so that the flow-path width W21a of the second-fluid outlet vicinity 21a, positioned in the vicinity of the outlet for the second fluid, of thesecond flow path 21 is larger than the flow-path width W21b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. Therefore, when the first fluid is to be cooled by a refrigerant as the second fluid, the flow-path cross-sectional area S21a of each second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S21b of each upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, to suppress an increase in pressure loss in thesecond flow paths 21 caused by an increase in the amount of gas component flowing in thesecond flow paths 21 due to evaporation of the second fluid. - However, the structure for forming the
second flow paths 21 so that, when the first fluid is to be cooled by a refrigerant as the second fluid, the flow-path cross-sectional area S21a of the second-fluid outlet vicinity 21 a is larger than the flow-path cross-sectional area S21b of the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a is not limited thereto. - Specifically, when the first fluid is to be cooled by a refrigerant as the second fluid, the
second flow paths 21 may be merged so 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. 12 , by merging twosecond flow paths 21 adjacent to each other in the direction of arrangement of thesecond flow paths 21 into onesecond flow path 21 at the second-fluid outlet vicinities 21 a, the flow-path width W21a 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 W21b of the upstream-side portions 21 b, disposed upstream of the second-fluid outlet vicinity 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 S21b of the upstream-side portions 21 b, disposed upstream of the second-fluid outlet vicinity 21 a, before thesecond flow paths 21 have been merged. - In contrast to the structure shown in
FIG. 12 in which the flow-path cross-sectional area S21a is made larger than the total of the flow-path cross-sectional areas S21b by merging thesecond flow paths 21 at the second-fluid outlet vicinities 21 a, the total of the flow-path cross-sectional areas S21a may be made larger than the total of the flow-path cross-sectional areas S21b by branching thesecond flow paths 21 so that the number of flow paths at the second-fluid outlet vicinity 21 a is larger than the number of flow paths at the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a. For example, in the structure, such as that ofModification 3 above, in which thesecond flow paths 21 are divided into the plurality offlow path groups flow path groups FIG. 13 , theflow path group 21A positioned in the vicinity of the outlet for the second fluid may be defined as a second-fluid outlet vicinity 21 a, theflow path groups side portion 21 b disposed upstream of the second-fluid outlet vicinity 21 a, and the number N21a of thesecond flow paths 21 of theflow path group 21A may be larger than the number N21b of the flow paths of theflow path groups second flow paths 21 are equal to each other, and the flow-path cross-sectional area S21a of theflow path group 21A and the total of the flow-path cross-sectional areas S21b of theflow path groups fluid outlet vicinity 21 a is larger than the number N21a of flow paths at the upstream-side portion 21 b disposed upstream of the second-fluid outlet vicinity 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 near the inlet for the second fluid. In particular, when, not only the number N21a of flow paths of theflow path group 21A is made larger than the number N21b of flow paths of theflow path groups flow path group 21A, but also the number of flow paths of each flow path group is decreased in the order of theflow path group 21A, theflow path group 21B, and theflow path group 21C, that is, the number of flow paths are decreased as a distance from the inlet for the second fluid decreases, the distribution performance of thesecond flow paths 21 for the second fluid is effectively improved. - One or more embodiments of the present invention can be widely applied to a water heat exchanger 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 that exchanges heat between the first fluid and the second fluid.
-
- 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 without departing from the scope of the present invention. Accordingly, the scope of the invention should be limited only by the attached claims.
Claims (6)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017-004639 | 2017-01-13 | ||
JP2017004639A JP6354868B1 (en) | 2017-01-13 | 2017-01-13 | Water heat exchanger |
PCT/JP2018/000318 WO2018131597A1 (en) | 2017-01-13 | 2018-01-10 | Water heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20190376750A1 true US20190376750A1 (en) | 2019-12-12 |
Family
ID=62840400
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/477,564 Abandoned US20190376750A1 (en) | 2017-01-13 | 2018-01-10 | Water heat exchanger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20190376750A1 (en) |
EP (1) | EP3569959B1 (en) |
JP (1) | JP6354868B1 (en) |
CN (1) | CN110199169B (en) |
WO (1) | WO2018131597A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2021085535A (en) * | 2019-11-25 | 2021-06-03 | ダイキン工業株式会社 | Heat exchanger |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS53129701A (en) * | 1977-04-16 | 1978-11-13 | Toshiba Corp | Steam producer |
GB9012618D0 (en) * | 1990-06-06 | 1990-07-25 | Rolls Royce Plc | Heat exchangers |
JP3858484B2 (en) * | 1998-11-24 | 2006-12-13 | 松下電器産業株式会社 | Laminate heat exchanger |
JP2007162974A (en) * | 2005-12-09 | 2007-06-28 | Xenesys Inc | Heat exchange plate |
DE202006011645U1 (en) * | 2006-06-29 | 2006-09-28 | Hans Berg Gmbh & Co. Kg | Radiator/heat sink for flow/return pipe coupling has a panel plate with upper and lower horizontal channels interlinked via vertical channels |
DE102009048060A1 (en) * | 2008-10-03 | 2010-04-08 | Modine Manufacturing Co., Racine | Heat exchanger and method |
JP2010117102A (en) | 2008-11-14 | 2010-05-27 | Fujitsu General Ltd | Heat exchanger |
JP2011196620A (en) * | 2010-03-19 | 2011-10-06 | Toyota Industries Corp | Ebullient cooling type heat exchanger |
JP5563162B2 (en) * | 2011-07-14 | 2014-07-30 | パナソニック株式会社 | Outdoor heat exchanger and vehicle air conditioner |
CN102494547B (en) * | 2011-11-30 | 2014-04-30 | 北京航空航天大学 | Miniature micro-channel plate-fin heat exchanger |
US9377250B2 (en) * | 2012-10-31 | 2016-06-28 | The Boeing Company | Cross-flow heat exchanger having graduated fin density |
JP2015001356A (en) * | 2013-06-18 | 2015-01-05 | パナソニックIpマネジメント株式会社 | Heat pump heat exchanging device |
KR101534497B1 (en) * | 2013-10-17 | 2015-07-09 | 한국원자력연구원 | Heat exchanger for steam generator and steam generator having the same |
CN203607491U (en) * | 2013-12-03 | 2014-05-21 | 航天新长征电动汽车技术有限公司 | Heat-radiating flow field plate of fuel cell |
CN104671204B (en) * | 2015-02-15 | 2016-08-24 | 浙江大学 | Cascading double-sided how snakelike microchannel reforming hydrogen-preparation reactor |
CN204730685U (en) * | 2015-03-31 | 2015-10-28 | 江苏乐科热力科技有限公司 | A kind of sectional parallel condensation plate-type heat exchanger slab |
KR20160139725A (en) * | 2015-05-28 | 2016-12-07 | 한국원자력연구원 | Heat exchanger and nuclear reactor having the same |
-
2017
- 2017-01-13 JP JP2017004639A patent/JP6354868B1/en active Active
-
2018
- 2018-01-10 US US16/477,564 patent/US20190376750A1/en not_active Abandoned
- 2018-01-10 EP EP18739379.8A patent/EP3569959B1/en active Active
- 2018-01-10 WO PCT/JP2018/000318 patent/WO2018131597A1/en unknown
- 2018-01-10 CN CN201880006422.6A patent/CN110199169B/en active Active
Also Published As
Publication number | Publication date |
---|---|
CN110199169B (en) | 2021-08-10 |
EP3569959A1 (en) | 2019-11-20 |
EP3569959B1 (en) | 2023-08-09 |
CN110199169A (en) | 2019-09-03 |
WO2018131597A1 (en) | 2018-07-19 |
JP2018112382A (en) | 2018-07-19 |
EP3569959A4 (en) | 2020-09-02 |
JP6354868B1 (en) | 2018-07-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8474516B2 (en) | Heat exchanger having winding micro-channels | |
CN109479385B (en) | Core of laminated radiator | |
US20110226448A1 (en) | Heat exchanger having winding channels | |
JP5100860B2 (en) | Plate heat exchanger | |
JP2018189352A (en) | Heat exchanger | |
US20210254907A1 (en) | Heat exchanger | |
US11828543B2 (en) | Stacked heat exchanger | |
JP5818397B2 (en) | Plate heat exchanger | |
JP5881483B2 (en) | Multi-channel equipment | |
US20190376750A1 (en) | Water heat exchanger | |
JP6160385B2 (en) | Laminate heat exchanger | |
US20210063091A1 (en) | Plate type heat exchanger | |
CN109443056B (en) | Double-sided staggered printed circuit board type heat exchange plate and heat exchanger | |
US20190360758A1 (en) | Water heat exchanger | |
JP7072790B2 (en) | Heat exchanger | |
WO2017195588A1 (en) | Stack type heat exchanger | |
JP2018132298A (en) | Water heat exchanger | |
CN114930108A (en) | Heat exchanger | |
JP6281422B2 (en) | Laminate heat exchanger | |
EP4067800A1 (en) | Heat exchanger | |
KR20200065779A (en) | Heat exchanger plate and plate heat exchanger including the same | |
JP5933605B2 (en) | Plate heat exchanger | |
KR102393899B1 (en) | Heat exchanging device comprising printed circuit heat exchanger | |
JP6911816B2 (en) | Heat exchanger | |
JP2019021872A (en) | Multilayer heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: DAIKIN INDUSTRIES, LTD., JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SHIBATA, YUTAKA;REEL/FRAME:050011/0026 Effective date: 20180626 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE AFTER FINAL ACTION FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: ADVISORY ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: ADVISORY ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |