CN113677946A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
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- CN113677946A CN113677946A CN201980095333.8A CN201980095333A CN113677946A CN 113677946 A CN113677946 A CN 113677946A CN 201980095333 A CN201980095333 A CN 201980095333A CN 113677946 A CN113677946 A CN 113677946A
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- flow path
- heat exchanger
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- resistance
- inlet
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
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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
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
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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
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The purpose of the present invention is to provide a compact heat exchanger that can suppress the occurrence of excessive pressure loss in response to a change in the volume of a fluid caused by a phase change and can ensure an appropriate flow rate. The heat exchanger (1) is provided with a flow path (8), wherein the flow path (8) is provided with an inlet (10) into which a fluid (6) flows and an outlet (11) from which the fluid (6) that has flowed in flows out, and is in a phase change from a liquid phase to a gas phase between the inlet (10) and the outlet (11), and a resistance shape (12) that causes less flow path resistance to the flow of the fluid (6) on the outlet (11) side than on the inlet (10) side is formed inside the flow path (8).
Description
Technical Field
The present invention relates to a heat exchanger constituting a condenser or an evaporator of a refrigerator such as a turbo refrigerator.
Background
Conventionally, a shell-and-tube heat exchanger, a fin-and-tube heat exchanger, a plate-fin heat exchanger, or the like has been used as a heat exchanger involving phase change of a fluid such as an evaporator or a condenser. The shell-and-tube heat exchanger is a structure in which a single-phase fluid flows inside a tube body and an external fluid is heated/cooled to evaporate/condense the external fluid. The fin-and-tube heat exchanger is a structure in which gas flows between fins outside the tube body and fluid inside the tube body is heated/cooled to evaporate/condense fluid inside the tube body. A plate heat exchanger or a plate fin heat exchanger is a structure in which a single-phase fluid flows between one side plate and the fluid between the other side plate is heated/cooled to be evaporated/condensed. Among them, as plate-fin heat exchangers, for example, heat exchangers as described in patent documents 1 to 3 are reported.
Prior art documents
Patent document
Patent document 1: japanese Kokai publication No. 2007-520682
Patent document 2: japanese patent laid-open publication Nos. 2013-113479
Patent document 3: japanese patent laid-open publication Nos. 2013-113480
Disclosure of Invention
Technical problem to be solved by the invention
When the fluid evaporates or condenses, the fluid undergoes a phase change, and thus a large change in volume of the fluid occurs during the heat exchange process. In particular, in a portion (gas side) of the fluid flow path where the fluid inside is in a gas phase state, the volume of the fluid in the fluid flow path becomes very large, and there is a possibility that an excessive pressure loss is generated. On the other hand, if the fluid flow path is defined so that excessive pressure loss does not occur in the flow on the gas side, the flow velocity on the liquid side (the portion where the fluid inside is in the liquid phase state) is significantly reduced, and the heat transfer performance is disadvantageously reduced.
In the case of a shell-and-tube heat exchanger, an unequal pitch such as a tube pitch is used so that heat transfer performance and pressure loss are appropriately changed in accordance with a volume change in a heat exchange process of a fluid. However, in this case, the volume of the shell-and-tube heat exchanger becomes large, and there is a problem that the amount of retained fluid on the side where the phase change is performed becomes large. On the other hand, the fin-and-tube heat exchanger, the plate heat exchanger, and the plate-and-fin heat exchanger can be made more compact than the shell-and-tube heat exchanger, but the shape of the heat exchanger reported so far does not become a shape corresponding to a change in the volume of the fluid due to the above-described phase change.
The present invention has been made in view of such circumstances, and an object thereof is to provide a compact heat exchanger capable of suppressing the occurrence of an excessive pressure loss in accordance with a volume change of a fluid caused by a phase change and capable of ensuring an appropriate flow rate.
Means for solving the technical problem
In order to solve the above problem, the present invention employs the following mechanism.
The present invention provides a heat exchanger including a flow path having an inlet through which a fluid flows in and an outlet through which the fluid flows out, the flow path being configured to change phase from a liquid phase to a gas phase between the inlet and the outlet, the flow path having a resistance shape in which a magnitude of flow path resistance applied to the flow of the fluid is smaller on the outlet side than on the inlet side. .
When the fluid flowing into the flow path changes its phase (evaporates) from a liquid phase to a gas phase by heat exchange in the flow path, the volume of the fluid increases. In this case, there is a possibility that an excessive pressure loss is generated on the outlet side due to an increase in the fluid volume. However, in the heat exchanger according to the 1 st aspect of the present invention, a resistance shape in which the magnitude of the flow path resistance (for example, in 5 stages) applied to the flow of the fluid is smaller on the outlet side than on the inlet side is formed inside the flow path. Therefore, on the outlet side (gas side), the magnitude of the flow path resistance applied to the flow of the fluid is small, and therefore, the occurrence of excessive pressure loss can be suppressed. On the other hand, on the inlet side (liquid side), the flow path resistance applied to the flow of the fluid is large, and therefore, the flow velocity of the fluid can be prevented from being significantly reduced (that is, an appropriate flow velocity can be secured), and turbulence can be promoted. As described above, in the heat exchanger according to claim 1 of the present invention, it is possible to suppress the occurrence of an excessive pressure loss in accordance with a volume change of the fluid caused by the phase change, and to promote turbulent flow. Therefore, if such a heat exchanger is used, the heat exchanger has high heat transfer performance (evaporation heat transfer performance). Since only a specific resistance shape may be formed inside the flow path, the heat exchanger can be made compact.
The present invention provides a heat exchanger including a flow path having an inlet through which a fluid flows in and an outlet through which the fluid flows out, the flow path being configured such that a phase change from a gas phase to a liquid phase occurs between the inlet and the outlet, wherein a resistance shape having a larger magnitude of flow path resistance applied to the flow of the fluid is formed in the flow path on the outlet side than on the inlet side.
When the fluid flowing into the flow path changes its phase (condenses) from a gas phase to a liquid phase by heat exchange in the flow path, the volume of the fluid decreases. In this case, since the fluid volume is large on the inlet side, an excessive pressure loss may occur. However, in the heat exchanger according to claim 2 of the present invention, a resistance shape in which the magnitude of the flow path resistance (for example, in 5 stages) applied to the flow of the fluid is larger on the outlet side than on the inlet side is formed inside the flow path. Therefore, on the inlet side (gas side), the magnitude of the flow path resistance applied to the flow of the fluid is small, and therefore, the occurrence of excessive pressure loss can be suppressed. On the other hand, on the outlet side (liquid side), the magnitude of the flow path resistance applied to the flow of the fluid is large, and therefore, the flow velocity of the fluid can be prevented from being significantly reduced (that is, an appropriate flow velocity can be ensured), and turbulence can be promoted. As described above, in the heat exchanger according to claim 2 of the present invention, it is possible to suppress the occurrence of an excessive pressure loss in accordance with a volume change of the fluid caused by the phase change, and to promote turbulent flow. Therefore, if such a heat exchanger is used, the heat exchanger has high heat transfer performance (condensation performance). Since only a specific resistance shape may be formed inside the flow path, the heat exchanger can be made compact.
In the heat exchanger, the resistive shape is preferably formed by a plate constituting the flow path or a plurality of fins provided on the plate.
In this way, the resistive shapes formed inside the flow path can be formed by the plates (e.g., in a plate heat exchanger) that constitute the flow path or by a plurality of fins provided on the plates (e.g., in a plate-fin heat exchanger). Specifically, in the portion where the flow path resistance is increased, the plate or the fin is disposed so as to be perpendicular to the flow direction of the fluid. On the other hand, in the portion where the flow path resistance is reduced, the plate or the fin is arranged in parallel with the flow direction of the fluid. This enables the resistance shape to be formed. Therefore, the heat exchanger of the present invention can be suitably applied to a plate heat exchanger or a plate-fin heat exchanger in particular. Since the plate heat exchanger or the plate-fin heat exchanger can be made compact, when the heat exchanger of the present invention is applied to the plate heat exchanger or the plate-fin heat exchanger, the heat transfer performance is improved, and the heat exchanger is made compact.
In the heat exchanger, it is preferable that another flow path that exchanges heat with the fluid flowing through the flow path is provided adjacent to the flow path.
In the heat exchanger of the present invention, by providing the other flow path as described above, heat exchange can be performed between the fluid flowing through the flow path and the fluid flowing through the other flow path.
In the heat exchanger, it is preferable that a resistance shape which gives the same flow path resistance between an inlet through which the fluid flowing through the other flow path flows and an outlet through which the fluid flowing in flows out is formed in the other flow path.
As described above, if the other flow path having the resistance shape in the interior is a resistance shape in which the magnitude of the flow path resistance applied to the flow of the fluid becomes constant is combined with the above-described flow path, the heat exchanger having a structure in which one of the fluids is a single phase and the other fluid undergoes a phase change can be suitably applied.
In the heat exchanger, it is preferable that an outlet through which the fluid flowing into the other channel flows out is formed in the other channel so as to have a resistance shape having a larger flow resistance or a smaller flow resistance than an inlet through which the fluid flowing through the other channel flows in.
In the heat exchanger according to the present invention, for example, the flow path in the above-described 1 st aspect and the flow path in the above-described 2 nd aspect can be combined. That is, the heat exchanger of the present invention can be suitably applied to a heat exchanger having a structure in which one fluid is evaporated in a flow path and the other fluid is condensed in the flow path.
Effects of the invention
As long as the heat exchanger of the present invention is a heat exchanger, it is possible to suppress the occurrence of excessive pressure loss in accordance with the volume change of the fluid caused by the phase change, and to ensure a suitable flow rate.
Drawings
Fig. 1 is an exploded perspective view showing the structure of a heat exchanger (plate-fin heat exchanger) according to embodiment 1 of the present invention.
Fig. 2 is a plan view showing a flow path in the heat exchanger according to embodiment 1 of the present invention.
Fig. 3 is a plan view showing a flow path in the heat exchanger according to embodiment 2 of the present invention.
Fig. 4 is a schematic view of the flow path and another flow path in the heat exchanger according to embodiment 3 of the present invention as viewed from the longitudinal side.
Fig. 5 is a schematic view of the flow path and another flow path in the heat exchanger according to embodiment 4 of the present invention as viewed from the longitudinal side.
Detailed Description
Hereinafter, an embodiment of a heat exchanger according to the present invention will be described with reference to the drawings.
In the following embodiments, a case where the heat exchanger according to the present invention is applied to a plate-fin heat exchanger will be described as an example.
[ 1 st embodiment ]
Hereinafter, embodiment 1 of the present invention will be described with reference to fig. 1 to 2.
Fig. 1 is an exploded perspective view showing the structure of a heat exchanger (plate-fin heat exchanger) according to the present embodiment. The heat exchanger 1 shown in fig. 1 is used in a condenser or an evaporator of a refrigerator such as a turbo refrigerator, for example. The heat exchanger 1 has a structure in which plates (1 st plates) 2a and plates (2 nd plates) 2b are alternately stacked and joined, bosses 3a and 3b are attached to the 1 st plate 2a at the leading end, and a cover plate 4 is attached to the 1 st plate 2a at the trailing end. Inner fins 5a and 5b are provided on the surfaces of the 1 st plate 2a and the 2 nd plate 2b on the cover plate 4 side, respectively.
In the heat exchanger 1, the fluid (1 st fluid) 6 flows in from the boss 3a, and the fluid (2 nd fluid) 7 flows in from the boss 3 b. The 1 st fluid 6 flows through the flow channels 8 formed between the 2 nd plate 2b and the inner fin 5 a. The 2 nd fluid 7 flows through another flow path 9 formed between the 1 st plate 2a and the inner fin 5b and adjacent to the flow path 8.
With such a configuration, in the heat exchanger 1, the flow path 8 of the 1 st fluid 6 and the other flow path 9 of the 2 nd fluid 7 are alternately arranged, and heat exchange is performed between the two fluids 6 and 7.
Next, the flow channel 8 of the present embodiment will be described in further detail with reference to fig. 2.
Fig. 2 is a plan view showing the flow channel 8 in the heat exchanger 1 of the present embodiment.
As shown in fig. 2, the channel 8 has an inlet 10 into which the 1 st fluid 6 flows and an outlet 11 from which the 1 st fluid 6 flows. In the flow path 8, the 1 st fluid 6 changes phase from a liquid phase to a gas phase between the inlet 10 and the outlet 11. That is, the heat exchanger 1 functions as an evaporator that evaporates the refrigerant.
A resistance shape 12 having a smaller flow path resistance to the flow of the 1 st fluid 6 on the outlet 11 side than on the inlet 10 side is formed inside the flow path 8. The resistance shape 12 is formed such that the magnitude of the flow path resistance becomes smaller in 5 stages from the inlet 10 side to the outlet 11 side. In the present embodiment, the resistive shape 12 is formed by a plurality of fins 13 provided on the 1 st plate 2 a.
Specifically, in a portion (liquid side) where the flow path resistance is increased, the fin 13 is disposed so as to be perpendicular to the flow direction of the fluid 6, and the length of the fin 13 (length in the direction perpendicular to the flow direction of the fluid 6) is shortened from the inlet 10 side toward the outlet 11 side. On the other hand, in the portion (gas side) where the flow path resistance is reduced, the fins 13 are arranged in parallel to the flow direction of the fluid 6, and the number of the fins 13 is arranged to be decreased from dense to sparse as going from the inlet 10 side to the outlet 11 side.
With the above-described configuration, the present embodiment exhibits the following operational advantages.
In the heat exchanger 1 according to the present embodiment, the resistance shapes 12, the magnitude of which decreases in 5 steps from the inlet 10 side to the outlet 11 side, are formed in the flow path 8 so as to apply flow path resistance to the flow of the fluid 6. Therefore, on the side of the outflow port 11 (gas side), the magnitude of the flow path resistance applied to the flow of the fluid 6 is small, and therefore, the occurrence of excessive pressure loss can be suppressed. On the other hand, on the side of the inlet 10 (liquid side), the magnitude of the flow path resistance applied to the flow of the fluid 6 is large, and therefore, the flow velocity of the fluid 6 can be prevented from significantly decreasing (that is, an appropriate flow velocity can be ensured), and turbulence can be promoted. As described above, in the heat exchanger 1 according to the present embodiment, it is possible to suppress the occurrence of an excessive pressure loss in accordance with the volume change of the fluid 6 caused by the phase change, and to promote turbulent flow. Therefore, if the heat exchanger 1 is of this type, the heat exchanger 1 has high heat transfer performance (evaporation heat transfer performance). Since only the specific resistance shape 12 needs to be formed inside the flow path 8, the heat exchanger 1 can be made compact.
In this way, the resistive shapes 12 formed inside the flow path 8 can be formed by the plurality of fins 13 provided on the 1 st plate 2a (in the plate-fin heat exchanger). Therefore, the heat exchanger 1 of the present embodiment can be suitably applied to a plate-fin heat exchanger in particular. Since the plate-fin heat exchanger can be made compact, when the heat exchanger 1 of the present embodiment is applied to a plate-fin heat exchanger, the heat transfer performance is improved, and the heat exchanger 1 is made compact.
The resistive shapes 12 may also be formed by the 1 st plate 2a (in a plate heat exchanger) constituting the flow path 8. Therefore, the heat exchanger 1 of the present embodiment can be suitably applied to a plate heat exchanger. Since the plate heat exchanger can be made compact, when the heat exchanger 1 of the present embodiment is applied to a plate heat exchanger, the heat transfer performance is improved and the heat exchanger 1 is made compact as described above.
In the present embodiment, as shown in fig. 2, a case where the resistance shape 12 is formed such that the magnitude of the flow path resistance applied to the flow of the fluid 6 becomes smaller in 5 stages from the inlet 10 side to the outlet 11 side has been described as an example, but the present invention is not limited thereto. The magnitude of the flow path resistance can be reduced in 3 to 10 stages from the inlet 10 side to the outlet 11 side.
[ 2 nd embodiment ]
Next, embodiment 2 of the present invention will be described with reference to fig. 3.
The basic configuration of the present embodiment is basically the same as that of embodiment 1, but is different from embodiment 1 in the configuration in which the phase of the 1 st fluid 26 changes from a gas phase to a liquid phase in the flow path 28 and the resistive shape 22. Therefore, in the present embodiment, the different portions will be described, and the description of the other overlapping portions will be omitted.
The same components as those in embodiment 1 are denoted by the same reference numerals, and redundant description thereof is omitted.
Fig. 3 is a plan view showing the flow channel 28 in the heat exchanger 21 of the present embodiment.
In the flow path 28 shown in fig. 3, the phase of the 1 st fluid 26 changes from a gas phase to a liquid phase between the inlet 10 and the outlet 11. That is, the heat exchanger 1 functions as a condenser that condenses the refrigerant. A resistance shape 22 having a larger magnitude of flow path resistance applied to the flow of the 1 st fluid 26 on the outlet 11 side than on the inlet 10 side is formed inside the flow path 28. The resistance shape 22 is formed such that the magnitude of the flow path resistance increases in 5 steps from the inlet 10 side to the outlet 11 side. The resistance shape 22 is formed by a plurality of fins 13 provided on the 1 st plate 2a, as in embodiment 1.
Specifically, in the portion (gas side) where the flow path resistance is reduced, the fins 13 are arranged in parallel to the flow direction of the fluid 26, and the number of the fins 13 is arranged from the inlet 10 side to the outlet 11 side so as to be increased from the sparse side to the dense side. On the other hand, in the portion (liquid side) where the flow path resistance is increased, the fin 13 is disposed so as to be perpendicular to the flow direction of the fluid 26, and the length of the fin 13 (the length in the direction perpendicular to the flow direction of the fluid 26) is increased from the inlet 10 side toward the outlet 11 side.
With the above-described configuration, the present embodiment exhibits the following operational advantages.
In the heat exchanger 21 according to the present embodiment, the resistance shapes 22, the magnitude of which increases in 5 stages from the inlet 10 side to the outlet 11 side, are formed in the flow path 28 so as to apply flow path resistance to the flow of the fluid 26. Therefore, on the inlet 10 side (gas side), the magnitude of the flow path resistance applied to the flow of the fluid 26 is small, and therefore, the occurrence of excessive pressure loss can be suppressed. On the other hand, on the side of the outflow port 11 (liquid side), the magnitude of the flow path resistance applied to the flow of the fluid 26 is large, so that the flow velocity of the fluid 26 can be prevented from being significantly reduced (that is, an appropriate flow velocity can be ensured), and turbulence can be promoted. As described above, in the heat exchanger 21 according to the present embodiment, it is possible to suppress the occurrence of an excessive pressure loss in accordance with the volume change of the fluid 26 caused by the phase change, and to promote turbulent flow. Therefore, if the heat exchanger 21 is of this type, the heat exchanger 21 has high heat transfer performance (condensation performance). Since only the specific resistance shape 22 needs to be formed inside the flow channel 28, the heat exchanger 21 can be made compact.
In the present embodiment, as shown in fig. 3, the case where the resistance shape 22 is formed such that the magnitude of the flow path resistance applied to the flow of the fluid 26 becomes larger in 5 stages from the inlet 10 side to the outlet 11 side has been described as an example, but the present invention is not limited to this. The flow path resistance can be increased in a range of 3 to 10 stages from the inlet 10 side to the outlet 11 side.
[ 3 rd embodiment ]
Next, embodiment 3 of the present invention will be described with reference to fig. 4.
The basic configuration of the present embodiment is basically the same as that of embodiment 2, but differs from embodiment 2 in that a resistance shape 42 that gives the same flow path resistance between the inlet 40 and the outlet 41 is formed in the other flow path 49. Therefore, in the present embodiment, the different portions will be described, and the description of the other overlapping portions will be omitted.
The same components as those in embodiment 2 are denoted by the same reference numerals, and redundant description thereof is omitted. In fig. 4, the shape of the resistance shapes 22, 42 is conceptually shown, but this is merely a schematic illustration.
Fig. 4 is a schematic diagram of the flow channel 28 and another flow channel 49 in the heat exchanger 31 according to the present embodiment as viewed from the longitudinal side. As shown in fig. 4, in the flow path 28, the phase of the 1 st fluid 26 changes from a gas phase to a liquid phase between the inflow port 10 and the outflow port 11. A resistance shape 22 having a larger magnitude of flow path resistance applied to the flow of the 1 st fluid 26 on the outlet 11 side than on the inlet 10 side is formed inside the flow path 28.
On the other hand, the other channel 49 has an inlet 40 into which the 2 nd fluid 47 flows and an outlet 41 from which the 2 nd fluid 47 flows. In the other flow path 49, the 2 nd fluid 47 flows through the other flow path 49 in a state of maintaining a liquid phase (i.e., a single phase) without undergoing a phase change between the inflow port 40 and the outflow port 41. A resistance shape 42 that provides the same flow path resistance between the inlet 40 and the outlet 41 is formed inside the other flow path 49.
With the above-described configuration, the present embodiment exhibits the following operational advantages.
As described above, the other flow path 49 in which the resistance shape 42 is provided as the resistance shape 42 in which the magnitude of the flow path resistance applied to the flow of the fluid 47 is constant can be combined with the flow path 28 according to embodiment 2. That is, the present invention can be suitably applied to the heat exchanger 31 configured such that one fluid 47 is a single phase and the other fluid 26 undergoes a phase change.
[ 4 th embodiment ]
Next, embodiment 4 of the present invention will be described with reference to fig. 5.
The basic configuration of the present embodiment is basically the same as that of embodiment 3, but differs from embodiment 3 in the configuration of the resistive shapes 52 formed inside the other flow path 59. Therefore, in the present embodiment, the different portions will be described, and the description of the other overlapping portions will be omitted.
The same components as those in embodiment 3 are denoted by the same reference numerals, and redundant description thereof will be omitted. In fig. 5, the shape of the resistance shapes 22, 52 is conceptually shown, but this is merely a schematic illustration.
Fig. 5 is a schematic diagram of the flow channel 28 and another flow channel 59 in the heat exchanger 51 according to the present embodiment as viewed from the longitudinal side. As shown in fig. 5, in another flow path 59 according to the present embodiment, the phase of the 2 nd fluid 57 changes from the liquid phase to the gas phase between the inflow port 40 and the outflow port 41. A resistance shape 52 having a smaller flow path resistance than the inlet 40 is formed in the other flow path 59. That is, the structure of the other flow path 59 is substantially the same as the structure of the flow path 8 in embodiment 1.
With the above-described configuration, the present embodiment exhibits the following operational advantages.
In the heat exchanger 51 of the present embodiment, for example, the flow path 8 (the other flow path 59) in embodiment 1 and the flow path 28 in embodiment 2 can be combined. That is, the heat exchanger 51 of the present embodiment can be suitably applied to a heat exchanger 51 configured such that one fluid 57 evaporates in the flow path 8 (the other flow path 59) and the other fluid 26 condenses in the flow path 28.
In the embodiments described above, the case where the heat exchanger of the present invention is applied to a plate-fin heat exchanger is described as an example, but the present invention is not limited to this. Specifically, the heat exchanger of the present invention can be applied to a plate heat exchanger, a fin-and-tube heat exchanger, or the like. Further, the heat exchanger of the present invention is preferably applied to a plate heat exchanger or a plate-fin heat exchanger.
Description of the symbols
1. 21, 31, 51-heat exchanger, 2 a-plate (1 st plate), 2 b-plate (2 nd plate), 3a, 3 b-boss, 4-cover plate, 5a, 5 b-inner fin, 6, 26-fluid (1 st fluid), 7, 47, 57-fluid (2 nd fluid), 8, 28-flow path, 9, 49, 59-another flow path, 10, 40-inflow port, 11, 41-outflow port, 12, 22, 42, 52-resistance shape, 13-fin.
Claims (6)
1. A heat exchanger in which, in a heat exchanger,
the heat exchanger is provided with a flow path having an inlet through which a fluid flows in and an outlet through which the fluid flows out, and changing the phase from a liquid phase to a gas phase between the inlet and the outlet,
a resistance shape in which the magnitude of flow path resistance applied to the flow of the fluid is smaller at the outlet side than at the inlet side is formed in the flow path.
2. A heat exchanger in which, in a heat exchanger,
the heat exchanger is provided with a flow path having an inlet through which a fluid flows in and an outlet through which the fluid flows out, and changing the phase from a gas phase to a liquid phase between the inlet and the outlet,
a resistance shape in which the flow path resistance applied to the flow of the fluid is larger in magnitude at the outlet side than at the inlet side is formed in the flow path.
3. The heat exchanger according to claim 1 or 2,
the resistive shape is formed by a plate constituting the flow path or a plurality of fins provided on the plate.
4. The heat exchanger according to any one of claims 1 to 3,
another flow path that exchanges heat with the fluid flowing through the flow path is provided adjacent to the flow path.
5. The heat exchanger of claim 4,
a resistance shape that provides the same flow path resistance between an inlet through which the fluid flowing through the other flow path flows and an outlet through which the fluid flowing in flows out is formed inside the other flow path.
6. The heat exchanger of claim 4,
an outlet through which the fluid flowing into the other channel flows out is formed in the other channel so as to have a resistance shape having a larger channel resistance or a resistance shape having a smaller channel resistance than an inlet through which the fluid flowing through the other channel flows in.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/022629 WO2020246003A1 (en) | 2019-06-06 | 2019-06-06 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113677946A true CN113677946A (en) | 2021-11-19 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980095333.8A Pending CN113677946A (en) | 2019-06-06 | 2019-06-06 | Heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20220221232A1 (en) |
| CN (1) | CN113677946A (en) |
| WO (1) | WO2020246003A1 (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3992168A (en) * | 1968-05-20 | 1976-11-16 | Kobe Steel Ltd. | Heat exchanger with rectification effect |
| US5538700A (en) * | 1994-12-22 | 1996-07-23 | Uop | Process and apparatus for controlling temperatures in reactant channels |
| CN1165286A (en) * | 1996-03-18 | 1997-11-19 | 波克股份有限公司 | Heat exchanger |
| US20050274501A1 (en) * | 2004-06-09 | 2005-12-15 | Agee Keith D | Decreased hot side fin density heat exchanger |
| CN102939510A (en) * | 2010-03-08 | 2013-02-20 | 阿伟德爱科赛奥有限公司 | Heat exchange element, a heat exchanger comprising the elements, and an equipment for the manufacture of the elements |
| WO2014087225A1 (en) * | 2012-12-05 | 2014-06-12 | Blue Box Group S.R.L. | Heat exchanger |
| CN105683696A (en) * | 2013-10-17 | 2016-06-15 | 韩国原子力研究院 | Heat exchanger for steam generator and steam generator comprising same |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100516758C (en) * | 2007-06-12 | 2009-07-22 | 缪志先 | Strip-free plate-fin heat exchanger |
| US10018430B2 (en) * | 2013-03-14 | 2018-07-10 | Rochester Institute Of Technology | Heat transfer system and method incorporating tapered flow field |
| DE102014004322B4 (en) * | 2014-03-25 | 2020-08-27 | Modine Manufacturing Company | Heat recovery system and plate heat exchanger |
| JP6757150B2 (en) * | 2016-03-17 | 2020-09-16 | 株式会社神戸製鋼所 | Method of heating fluid by laminated fluid warmer and laminated fluid warmer |
-
2019
- 2019-06-06 WO PCT/JP2019/022629 patent/WO2020246003A1/en active Application Filing
- 2019-06-06 CN CN201980095333.8A patent/CN113677946A/en active Pending
- 2019-06-06 US US17/612,483 patent/US20220221232A1/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3992168A (en) * | 1968-05-20 | 1976-11-16 | Kobe Steel Ltd. | Heat exchanger with rectification effect |
| US5538700A (en) * | 1994-12-22 | 1996-07-23 | Uop | Process and apparatus for controlling temperatures in reactant channels |
| CN1165286A (en) * | 1996-03-18 | 1997-11-19 | 波克股份有限公司 | Heat exchanger |
| US20050274501A1 (en) * | 2004-06-09 | 2005-12-15 | Agee Keith D | Decreased hot side fin density heat exchanger |
| CN102939510A (en) * | 2010-03-08 | 2013-02-20 | 阿伟德爱科赛奥有限公司 | Heat exchange element, a heat exchanger comprising the elements, and an equipment for the manufacture of the elements |
| WO2014087225A1 (en) * | 2012-12-05 | 2014-06-12 | Blue Box Group S.R.L. | Heat exchanger |
| CN105683696A (en) * | 2013-10-17 | 2016-06-15 | 韩国原子力研究院 | Heat exchanger for steam generator and steam generator comprising same |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2020246003A1 (en) | 2020-12-10 |
| US20220221232A1 (en) | 2022-07-14 |
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