US20230089621A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- US20230089621A1 US20230089621A1 US17/908,332 US202117908332A US2023089621A1 US 20230089621 A1 US20230089621 A1 US 20230089621A1 US 202117908332 A US202117908332 A US 202117908332A US 2023089621 A1 US2023089621 A1 US 2023089621A1
- Authority
- US
- United States
- Prior art keywords
- heat transfer
- flow path
- heat exchanger
- fluid
- transfer tube
- 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.)
- Pending
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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- 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
- F28D7/1684—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 the conduits having a non-circular cross-section
-
- 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
- F28D7/163—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1653—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
- F28D7/1661—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 with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape with particular pattern of flow of the heat exchange media, e.g. change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
- F28F2009/226—Transversal partitions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2225/00—Reinforcing means
- F28F2225/04—Reinforcing means for conduits
Definitions
- the present disclosure relates to a heat exchanger.
- heat energy is generated by burning fuels, and the heat energy is extracted as, for example, rotational energy of an output shaft.
- high-temperature exhaust gas is generated in the heat engine.
- a heat exchanger has commonly included a plurality of heat transfer tubes and a fin provided in each heat transfer tube.
- a heat medium flows inside the heat transfer tube, and the other medium flows outside the heat transfer tube. As a result, heat is exchanged between the two media via the fin.
- the present disclosure has been made to solve the above problems, and an object of the present disclosure is to provide a heat exchanger with a smaller size.
- a heat exchanger includes: a pipe forming a flow path through which a first fluid is fed; a pair of partition plates provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space at a portion of the flow path; a plurality of heat transfer tubes having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates, and arranged side by side with intervals therebetween; a feeding part configured to feed a second fluid from an outside of the pipe to the closed space; and a discharging part configured to discharge the second fluid in the closed space to the outside of the pipe.
- FIG. 1 is a cross-sectional view showing a configuration of a heat exchanger according to a first embodiment of the present disclosure.
- FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1 .
- FIG. 3 is a cross-sectional view taken along line III-III in FIG. 1 .
- FIG. 4 is a cross-sectional view showing a configuration of a heat exchanger according to a second embodiment of the present disclosure.
- FIG. 5 is a cross-sectional view taken along line V-V in FIG. 4 .
- FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 4 .
- FIG. 7 is a cross-sectional view showing a configuration of a heat transfer tube according to a third embodiment of the present disclosure.
- FIG. 8 is a cross-sectional view showing a configuration of a heat exchanger according to a fourth embodiment of the present disclosure.
- FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 8 .
- FIG. 10 is an enlarged cross-sectional view of a heat transfer tube according to a fifth embodiment of the present disclosure.
- FIG. 11 is an enlarged cross-sectional view showing a modified example of the heat transfer tube according to the fifth embodiment of the present disclosure.
- FIG. 12 is a perspective view showing the modified example of the heat transfer tube according to the fifth embodiment of the present disclosure.
- the heat exchanger 100 is positioned in the midway of a pipe 1 .
- the pipe 1 forms a flow path through which exhaust gas (first fluid) discharged from a heat engine such as an engine flows.
- the pipe 1 includes a straight tubular pipe body 11 and elbow parts 10 each provided at both end portions of the pipe body 11 .
- the elbow part 10 forms a curved portion, and an inside of the elbow part 10 is provided with a plurality of vanes 4 for guiding a flowing direction of the exhaust gas to the curved portion.
- Each vane 4 is curved along a curve of the elbow part 10 .
- the plurality of vanes 4 are provided at an interval in a direction intersecting an extending direction of the elbow part 10 .
- a plurality of heat transfer tubes 3 are arranged side by side with intervals therebetween.
- the exhaust gas flows inside the heat transfer tube 3 .
- the heat transfer tube 3 is a tube having a cross section of hexagonal shape, and both ends of the heat transfer tube 3 are open.
- the inside of the heat transfer tube 3 is a first flow path F 1 .
- the plurality of the heat transfer tubes 3 are adjacent to each other so that outer surfaces thereof are in parallel to each other, and arranged so as to have a hexagonal shape as a whole.
- a space formed between the heat transfer tubes 3 is a second flow path F 2 through which water flows as a second fluid.
- a feeding part 21 as an inlet side header and a discharging part 22 as an outlet side header are provided on both end portions of the pipe body 11 .
- the feeding part 21 is provided for feeding water introduced from the outside into the pipe 1
- the discharging part 22 is provided for discharging the water that has passed through the pipe 1 to the outside. More specifically, the discharging part 22 is provided on an end portion at an upstream side (a side where the first fluid flows) of the pipe 1
- the feeding part 21 is provided on an end portion at a downstream side of the pipe 1 .
- the feeding part 21 and the discharging part 22 have the same configuration as each other except for a flowing direction of the fluid. Thus, a configuration of the discharging part 22 will be typically described herein with reference to FIG. 3 .
- the discharging part 22 includes a cylindrical discharging part body 22 H that covers the end portions of the plurality of heat transfer tubes 3 from the outside, and a partition plate 20 that blocks an opening of the discharging part body 22 H.
- An opening H for discharging water to the outside is formed in a portion of the discharging part body 22 H in a circumferential direction.
- the flow path formed by the pipe body 11 is blocked from both sides by the partition plate 20 of the discharging part 22 and the partition plate 20 of the feeding part 21 .
- a space partitioned by a pair of partition plates 20 is a closed space V.
- the heat transfer tube 3 extends so as to penetrate the partition plate 20 . That is, in the closed space V, the first flow path F 1 formed by the heat transfer tube 3 and the second flow path F 2 formed by a gap between the heat transfer tubes 3 extend in parallel.
- Each component of the heat exchanger 100 with the configuration described above is formed by a 3D printer technique represented by additive modeling (AM), which is desirable. Further, as a material for forming the heat exchanger 100 , titanium or SUS is preferably used.
- AM additive modeling
- the closed space V is formed by the partition plate 20 in the middle of extension of the pipe 1 .
- Heat exchange is performed between the first fluid flowing through the heat transfer tube 3 and the second fluid flowing outside the heat transfer tube 3 in the closed space V.
- the heat exchanger 100 can be provided in the middle of extension of the pipe 1 without changing an extending direction of the pipe 1 and without greatly enlarging an outer diameter of the pipe 1 . Accordingly, it is possible to save a space for disposing the heat exchanger 100 . As a result, the heat exchanger 100 can be easily provided even in a narrow region in which the heat exchanger 100 is difficult to be provided in the related art.
- the heat transfer tube 3 has a cross section of a polygonal (hexagonal) shape. Therefore, it is possible to further improve the efficiency of heat exchange because a wetted area of an inner surface of the heat transfer tube 3 is expanded, as compared with a case where the heat transfer tube 3 has a cross section of a quadrangular shape.
- the cross section of the heat transfer tube 3 has a circular shape, it is possible to further enlarge the wetted area.
- the shape of the cross section is a circular shape, there is a disadvantage of decreased filling density of the fluid, and thus it is desirable to determine the shape of the heat transfer tube according to the overall balance.
- FIG. 4 in the present embodiment, there is further provided a blocking part 5 blocking only a portion of the interval between the heat transfer tubes 3 .
- a plurality of the blocking parts 5 are provided at an interval in an extending direction of the pipe body 11 .
- the blocking parts 5 adjacent to each other have different regions to be blocked. More specifically, one blocking part 5 of the adjacent blocking parts 5 blocks only an upper portion in the pipe body 11 as shown in FIG. 5 .
- the other blocking part 5 blocks only a lower portion in the pipe body 11 .
- the second flow path F 2 in the pipe body 11 extends in a meandering manner. That is, the blocking part 5 functions as a baffle plate.
- the blocking part 5 changes a flowing direction of the water in the closed space V. Since the regions blocked by the adjacent blocking parts 5 are different, the water flows in a meandering manner while passing through the plurality of blocking parts 5 . As a result, because the water is uniformly distributed in the closed space V, the contact area between the water and the heat transfer tube 3 is expanded, such that it is possible to further improve the efficiency of heat exchange between the water and the exhaust gas.
- the second embodiment of the present disclosure has been described above.
- Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.
- the mode of the blocking part 5 is not limited thereto, and it is possible to adopt a configuration in which the blocking part 5 blocks left and right sides of the pipe 1 in the extending direction of the pipe 1 .
- the water can flow smoothly while meandering in a horizontal direction without against gravity, such that the efficiency of heat exchange can be further improved.
- this configuration is suitable when it is assumed that the fluid contains a component having a low density and stays in the middle of the flow path.
- a supporting part 6 is provided between the heat transfer tubes 3 adjacent to each other.
- the supporting part 6 connects outer surfaces of the heat transfer tubes 3 to each other. Further, although not shown in detail, the supporting part 6 is provided on a portion of the heat transfer tube 3 in the extending direction.
- the supporting part 6 can suppress displacement and deformation of the heat transfer tube 3 .
- the heat exchanger 100 can be stably operated for a longer period of time.
- the third embodiment of the present disclosure has been described above.
- Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.
- a configuration can be adopted in which a through-hole is formed in the supporting part 6 and the fluid flows through the through-hole.
- the supporting part 6 can suppress hindrance of fluid flow.
- the plurality of heat transfer tubes 3 are configured such that the heat transfer tube 3 disposed in a region having a smaller flow rate has a larger cross-sectional area of the flow path.
- a heat transfer tube 3 A has a larger cross-sectional area of the flow path as it is positioned upward and a heat transfer tube 3 B has a smaller cross-sectional area of the flow path as it is positioned downward.
- the flow rate of the exhaust gas tends to be larger as the heat transfer tube 3 is directed toward an outer peripheral side of the curved portion due to inertial force, and the flow rate tends to be smaller as the heat transfer tube 3 is directed toward an inner peripheral side of the curved portion.
- the heat transfer tube 3 has a larger cross-sectional area of the flow path as it is disposed in the region having a smaller flow rate.
- a fifth embodiment of the present disclosure will be described with reference to FIG. 10 .
- Components similar to those of the above-described embodiments are denoted by the same reference signs, and repeated description will not be provided.
- a plurality of fins 3 F are further provided on the inner surface of the heat transfer tube 3 .
- the fins 3 F protrude from the inner surface toward the inner peripheral side of the heat transfer tube 3 , and extend over the entire region of the heat transfer tube 3 in the extending direction.
- the plurality of such fins 3 F are arranged at an interval along the inner surface.
- the fin 3 F extends linearly in the extending direction of the heat transfer tube 3 .
- the protruding height of the fin 3 F is about 2 mm, and the width of the fin 3 F is about 1 mm.
- the efficiency of heat exchange can be further improved. Further, since the fin 3 F has a minute dimension as described above, it is difficult for dust or soot contained in the exhaust gas flowing in the heat transfer tube 3 to accumulate. As a result, the heat exchanger 100 can be stably operated for a longer period of time.
- a fin 3 F′ may extend so as to turn along the inner surface from the upstream side to the downstream side of the heat transfer tube 3 in the extending direction.
- a tip A 1 and a base end A 2 of the fin 3 F′ extend so as to turn about the central axis of the heat transfer tube 3 from one side of the heat transfer tube 3 in the circumferential direction toward the other side.
- a configuration can be adopted in which a plurality of such fins 3 F′ are arranged at an interval along the inner surface.
- the fin 3 F′ extends so as to turn along the inner surface, a turning flow component is added to the flow of the exhaust gas inside the heat transfer tube 3 .
- a staying time of the exhaust gas inside the heat transfer tube 3 becomes long, such that the efficiency of heat exchange can be further improved.
- the exhaust gas accompanies the turning flow component, it is possible to suppress generation of deposits such as dust and soot on the fin 3 F. As a result, the heat exchanger 100 can be stably operated for a longer period of time.
- the heat exchanger 100 described in each embodiment is grasped as follows, for example.
- a heat exchanger 100 includes: a pipe 1 forming a flow path through which a first fluid is fed; a pair of partition plates 20 provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space V at a portion of the flow path; a plurality of heat transfer tubes 3 having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates 20 , and arranged side by side with intervals therebetween; a feeding part 21 configured to feed a second fluid from an outside of the pipe 1 to the closed space V; and a discharging part 22 configured to discharge the second fluid in the closed space V to the outside of the pipe 1 .
- the closed space V is formed by the partition plate 20 in the middle of extension of the pipe 1 .
- Heat exchange is performed between the first fluid flowing through the heat transfer tube 3 and the second fluid flowing outside the heat transfer tube 3 in the closed space V.
- the heat exchanger 100 can be provided in the middle of extension of the pipe 1 without changing the extending direction of the pipe 1 and without greatly enlarging an outer diameter of the pipe 1 . Accordingly, it is possible to save space for disposing the heat exchanger 100 .
- the heat transfer tube 3 may have a cross section of a polygonal shape when viewed in the extending direction.
- the second fluid may be configured to flow through the interval between the plurality of heat transfer tubes 3 in the closed space V.
- the second fluid flows into the interval between the heat transfer tubes 3 , it is possible to secure a large contact area with the heat transfer tube 3 . As a result, it is possible to further improve the efficiency of heat exchange while reducing the size of the heat exchanger 100 .
- the heat exchanger 100 may further include a blocking part 5 blocking only a portion of the interval between the heat transfer tubes 3 , in which a plurality of the blocking parts 5 may be provided at an interval in the extending direction, and the blocking parts 5 adjacent to each other may have the blocking regions different from each other.
- the blocking part 5 changes a flowing direction of the second fluid in the closed space V. Since the regions blocked by the adjacent blocking parts 5 are different, the second fluid flows in a meandering manner while passing through the plurality of blocking parts 5 . As a result, since the second fluid is uniformly distributed in the closed space V, it is possible to further improve the efficiency of heat exchange.
- the heat exchanger 100 may further include a supporting part 6 provided between the heat transfer tubes 3 .
- the supporting part 6 can suppress displacement and deformation of the heat transfer tube.
- the plurality of heat transfer tubes 3 may be configured such that the heat transfer tube 3 disposed in a region having a smaller flow rate has a larger cross-sectional area of the flow path.
- the flow rate of the first fluid tends to be larger as the heat transfer tube 3 is directed toward an outer peripheral side of the curved portion due to inertial force, and the flow rate tends to be smaller as the heat transfer tube 3 is directed toward an inner peripheral side of the curved portion.
- the heat transfer tube 3 has a larger cross-sectional area of the flow path as it is disposed in the region having a smaller flow rate.
- the heat exchanger 100 according to a seventh aspect may further include a plurality of fins 3 F protruding from an inner surface of the heat transfer tube 3 , extending in the extending direction, and provided at an interval along the inner surface.
- the fin 3 F′ may extend so as to turn along the inner surface from an upstream side to a downstream side in the extending direction.
- the fin 3 F′ extends so as to turn along the inner surface, a turning flow component is added to the first fluid inside the heat transfer tube 3 .
- a staying time of the first fluid inside the heat transfer tube 3 becomes long, such that the efficiency of heat exchange can be further improved.
- the exhaust gas accompanies the turning flow component, it is possible to suppress generation of deposits such as dust on the fin 3 F′.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanger includes: a pipe forming a flow path through which a first fluid is fed; a pair of partition plates provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space at a portion of the flow path; a plurality of heat transfer tubes having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates, and arranged side by side with intervals therebetween; a feeding part configured to feed a second fluid from an outside of the pipe to the closed space; and a discharging part configured to discharge the second fluid in the closed space to the outside of the pipe.
Description
- The present disclosure relates to a heat exchanger.
- Priority is claimed on Japanese Patent Application No. 2020-214438, filed Dec. 24, 2020, the content of which is incorporated herein by reference.
- In a heat engine including an internal combustion engine and an external combustion engine, heat energy is generated by burning fuels, and the heat energy is extracted as, for example, rotational energy of an output shaft. At this time, high-temperature exhaust gas is generated in the heat engine. As a measure for effectively utilizing the heat energy of the exhaust gas, it is conceivable to install a heat exchanger in an exhaust gas flow path.
- Conventionally, a heat exchanger has commonly included a plurality of heat transfer tubes and a fin provided in each heat transfer tube. In this type of heat exchanger, a heat medium flows inside the heat transfer tube, and the other medium flows outside the heat transfer tube. As a result, heat is exchanged between the two media via the fin.
-
- [Patent Document 1]
- Japanese Unexamined Patent Application, First Publication No. 2010-223520
- Meanwhile, in recent years, there has been a demand for reduction in size of various devices including the heat engine described above. Therefore, it is necessary to significantly reduce the size of the heat exchanger.
- The present disclosure has been made to solve the above problems, and an object of the present disclosure is to provide a heat exchanger with a smaller size.
- In order to solve the problems, a heat exchanger according to the present disclosure includes: a pipe forming a flow path through which a first fluid is fed; a pair of partition plates provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space at a portion of the flow path; a plurality of heat transfer tubes having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates, and arranged side by side with intervals therebetween; a feeding part configured to feed a second fluid from an outside of the pipe to the closed space; and a discharging part configured to discharge the second fluid in the closed space to the outside of the pipe.
- According to the present disclosure, it is possible to provide a heat exchanger with a smaller size.
-
FIG. 1 is a cross-sectional view showing a configuration of a heat exchanger according to a first embodiment of the present disclosure. -
FIG. 2 is a cross-sectional view taken along line II-II inFIG. 1 . -
FIG. 3 is a cross-sectional view taken along line III-III inFIG. 1 . -
FIG. 4 is a cross-sectional view showing a configuration of a heat exchanger according to a second embodiment of the present disclosure. -
FIG. 5 is a cross-sectional view taken along line V-V inFIG. 4 . -
FIG. 6 is a cross-sectional view taken along line VI-VI inFIG. 4 . -
FIG. 7 is a cross-sectional view showing a configuration of a heat transfer tube according to a third embodiment of the present disclosure. -
FIG. 8 is a cross-sectional view showing a configuration of a heat exchanger according to a fourth embodiment of the present disclosure. -
FIG. 9 is a cross-sectional view taken along line IX-IX inFIG. 8 . -
FIG. 10 is an enlarged cross-sectional view of a heat transfer tube according to a fifth embodiment of the present disclosure. -
FIG. 11 is an enlarged cross-sectional view showing a modified example of the heat transfer tube according to the fifth embodiment of the present disclosure. -
FIG. 12 is a perspective view showing the modified example of the heat transfer tube according to the fifth embodiment of the present disclosure. - (Configuration of Heat Exchanger)
- Hereinafter, a
heat exchanger 100 according to a first embodiment of the present disclosure will be described with reference toFIGS. 1 to 3 . As shown inFIG. 1 , theheat exchanger 100 is positioned in the midway of apipe 1. Thepipe 1 forms a flow path through which exhaust gas (first fluid) discharged from a heat engine such as an engine flows. In an example ofFIG. 1 , thepipe 1 includes a straighttubular pipe body 11 andelbow parts 10 each provided at both end portions of thepipe body 11. Theelbow part 10 forms a curved portion, and an inside of theelbow part 10 is provided with a plurality of vanes 4 for guiding a flowing direction of the exhaust gas to the curved portion. Each vane 4 is curved along a curve of theelbow part 10. The plurality of vanes 4 are provided at an interval in a direction intersecting an extending direction of theelbow part 10. - Inside of the
pipe body 11, a plurality ofheat transfer tubes 3 are arranged side by side with intervals therebetween. The exhaust gas flows inside theheat transfer tube 3. As shown inFIG. 2 , theheat transfer tube 3 is a tube having a cross section of hexagonal shape, and both ends of theheat transfer tube 3 are open. The inside of theheat transfer tube 3 is a first flow path F1. In addition, the plurality of theheat transfer tubes 3 are adjacent to each other so that outer surfaces thereof are in parallel to each other, and arranged so as to have a hexagonal shape as a whole. A space formed between theheat transfer tubes 3 is a second flow path F2 through which water flows as a second fluid. - A
feeding part 21 as an inlet side header and adischarging part 22 as an outlet side header are provided on both end portions of thepipe body 11. Thefeeding part 21 is provided for feeding water introduced from the outside into thepipe 1, and thedischarging part 22 is provided for discharging the water that has passed through thepipe 1 to the outside. More specifically, thedischarging part 22 is provided on an end portion at an upstream side (a side where the first fluid flows) of thepipe 1, and thefeeding part 21 is provided on an end portion at a downstream side of thepipe 1. Thefeeding part 21 and thedischarging part 22 have the same configuration as each other except for a flowing direction of the fluid. Thus, a configuration of thedischarging part 22 will be typically described herein with reference toFIG. 3 . - As shown in
FIG. 3 , thedischarging part 22 includes a cylindricaldischarging part body 22H that covers the end portions of the plurality ofheat transfer tubes 3 from the outside, and apartition plate 20 that blocks an opening of thedischarging part body 22H. An opening H for discharging water to the outside is formed in a portion of thedischarging part body 22H in a circumferential direction. The flow path formed by thepipe body 11 is blocked from both sides by thepartition plate 20 of thedischarging part 22 and thepartition plate 20 of thefeeding part 21. A space partitioned by a pair ofpartition plates 20 is a closed space V. Further, theheat transfer tube 3 extends so as to penetrate thepartition plate 20. That is, in the closed space V, the first flow path F1 formed by theheat transfer tube 3 and the second flow path F2 formed by a gap between theheat transfer tubes 3 extend in parallel. - Each component of the
heat exchanger 100 with the configuration described above is formed by a 3D printer technique represented by additive modeling (AM), which is desirable. Further, as a material for forming theheat exchanger 100, titanium or SUS is preferably used. - Next, an operation of the
heat exchanger 100 will be described. In operating theheat exchanger 100, first, water as a second fluid is fed into the closed space V through thefeeding part 21. At this time, the heat engine is operated, high-temperature exhaust gas thus flows in theheat transfer tube 3 as a first fluid. Further, inside thepipe body 11, the water flows toward a direction opposite to the flowing direction of the exhaust gas through the gap (second flow path F2) between theheat transfer tubes 3. While the water is flowing through the second flow path F2, heat exchange occurs with the exhaust gas through a wall surface of theheat transfer tube 3. As a result, the temperature of the water becomes high, and the water is fed into an external device via the dischargingpart 22. On the other hand, the temperature of the exhaust gas becomes low, and the exhaust gas flows away toward the downstream side in thepipe 1. As such a phenomenon continuously occurs, the heat exchange between water and exhaust gas is performed. - According to the above configuration, the closed space V is formed by the
partition plate 20 in the middle of extension of thepipe 1. Heat exchange is performed between the first fluid flowing through theheat transfer tube 3 and the second fluid flowing outside theheat transfer tube 3 in the closed space V. As described above, according to the above configuration, theheat exchanger 100 can be provided in the middle of extension of thepipe 1 without changing an extending direction of thepipe 1 and without greatly enlarging an outer diameter of thepipe 1. Accordingly, it is possible to save a space for disposing theheat exchanger 100. As a result, theheat exchanger 100 can be easily provided even in a narrow region in which theheat exchanger 100 is difficult to be provided in the related art. - Moreover, according to the above configuration, the
heat transfer tube 3 has a cross section of a polygonal (hexagonal) shape. Therefore, it is possible to further improve the efficiency of heat exchange because a wetted area of an inner surface of theheat transfer tube 3 is expanded, as compared with a case where theheat transfer tube 3 has a cross section of a quadrangular shape. In addition, more preferably, when the cross section of theheat transfer tube 3 has a circular shape, it is possible to further enlarge the wetted area. When the shape of the cross section is a circular shape, there is a disadvantage of decreased filling density of the fluid, and thus it is desirable to determine the shape of the heat transfer tube according to the overall balance. - Moreover, according to the above configuration, since the water as the second fluid flows into the interval between the
heat transfer tubes 3, it is possible to secure a large contact area with theheat transfer tube 3. As a result, it is possible to further improve the efficiency of heat exchange while reducing the size of theheat exchanger 100. - The first embodiment of the present disclosure has been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.
- Next, a second embodiment of the present disclosure will be described with reference to
FIGS. 4 to 6 . Components similar to those of the first embodiment are denoted by the same reference signs, and repeated description will not be provided. As shown inFIG. 4 , in the present embodiment, there is further provided ablocking part 5 blocking only a portion of the interval between theheat transfer tubes 3. A plurality of the blockingparts 5 are provided at an interval in an extending direction of thepipe body 11. In addition, the blockingparts 5 adjacent to each other have different regions to be blocked. More specifically, one blockingpart 5 of theadjacent blocking parts 5 blocks only an upper portion in thepipe body 11 as shown inFIG. 5 . As shown inFIG. 6 , the other blockingpart 5 blocks only a lower portion in thepipe body 11. By alternately arrangingsuch blocking parts 5, the second flow path F2 in thepipe body 11 extends in a meandering manner. That is, the blockingpart 5 functions as a baffle plate. - According to the above configuration, the blocking
part 5 changes a flowing direction of the water in the closed space V. Since the regions blocked by theadjacent blocking parts 5 are different, the water flows in a meandering manner while passing through the plurality of blockingparts 5. As a result, because the water is uniformly distributed in the closed space V, the contact area between the water and theheat transfer tube 3 is expanded, such that it is possible to further improve the efficiency of heat exchange between the water and the exhaust gas. - The second embodiment of the present disclosure has been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure. For example, in the second embodiment, an example in which the blocking
part 5 blocks the upper portion or lower portion in the closed space V has been described. However, the mode of the blockingpart 5 is not limited thereto, and it is possible to adopt a configuration in which the blockingpart 5 blocks left and right sides of thepipe 1 in the extending direction of thepipe 1. In this case, the water can flow smoothly while meandering in a horizontal direction without against gravity, such that the efficiency of heat exchange can be further improved. Particularly, this configuration is suitable when it is assumed that the fluid contains a component having a low density and stays in the middle of the flow path. - Subsequently, a third embodiment of the present disclosure will be described with reference to
FIG. 7 . Components similar to those of the above-described embodiments are denoted by the same reference signs, and a repeated description will not be provided. As shown inFIG. 7 , in the present embodiment, a supportingpart 6 is provided between theheat transfer tubes 3 adjacent to each other. The supportingpart 6 connects outer surfaces of theheat transfer tubes 3 to each other. Further, although not shown in detail, the supportingpart 6 is provided on a portion of theheat transfer tube 3 in the extending direction. - According to the above configuration, the supporting
part 6 can suppress displacement and deformation of theheat transfer tube 3. As a result, theheat exchanger 100 can be stably operated for a longer period of time. - The third embodiment of the present disclosure has been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure. For example, a configuration can be adopted in which a through-hole is formed in the supporting
part 6 and the fluid flows through the through-hole. In this case, the supportingpart 6 can suppress hindrance of fluid flow. - Next, a fourth embodiment of the present disclosure will be described with reference to
FIGS. 8 and 9 . Components similar to those of the above-described embodiments are denoted by the same reference signs, and repeated description will not be provided. As shown inFIG. 9 , in the present embodiment, the plurality ofheat transfer tubes 3 are configured such that theheat transfer tube 3 disposed in a region having a smaller flow rate has a larger cross-sectional area of the flow path. Specifically, in a case where theelbow part 10 of thepipe 1 is vertically curved, aheat transfer tube 3A has a larger cross-sectional area of the flow path as it is positioned upward and aheat transfer tube 3B has a smaller cross-sectional area of the flow path as it is positioned downward. - For example, in a case where the
pipe 1 has a curved portion such as theelbow part 10 on the upstream side of thepipe 1, the flow rate of the exhaust gas tends to be larger as theheat transfer tube 3 is directed toward an outer peripheral side of the curved portion due to inertial force, and the flow rate tends to be smaller as theheat transfer tube 3 is directed toward an inner peripheral side of the curved portion. According to the above configuration, theheat transfer tube 3 has a larger cross-sectional area of the flow path as it is disposed in the region having a smaller flow rate. As a result, even when flow rate distribution is non-uniform as described above, it is possible to correct the configuration and allow the exhaust gas to flow uniformly over the entire plurality ofheat transfer tubes 3. As a result, the efficiency of theheat exchanger 100 can be further improved. - The fourth embodiment of the present disclosure has been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.
- Subsequently, a fifth embodiment of the present disclosure will be described with reference to
FIG. 10 . Components similar to those of the above-described embodiments are denoted by the same reference signs, and repeated description will not be provided. As shown inFIG. 10 , in the present embodiment, a plurality offins 3F are further provided on the inner surface of theheat transfer tube 3. Thefins 3F protrude from the inner surface toward the inner peripheral side of theheat transfer tube 3, and extend over the entire region of theheat transfer tube 3 in the extending direction. The plurality ofsuch fins 3F are arranged at an interval along the inner surface. In addition, in the present embodiment, thefin 3F extends linearly in the extending direction of theheat transfer tube 3. When the length of one side of a hexagon forming the cross section of theheat transfer tube 3 is 6 mm, for example, it is desirable for the protruding height of thefin 3F to be about 2 mm, and the width of thefin 3F is about 1 mm. - According to the above configuration, since the contact area between the exhaust gas and the
heat transfer tube 3 is expanded by including thefins 3F, the efficiency of heat exchange can be further improved. Further, since thefin 3F has a minute dimension as described above, it is difficult for dust or soot contained in the exhaust gas flowing in theheat transfer tube 3 to accumulate. As a result, theheat exchanger 100 can be stably operated for a longer period of time. - The fifth embodiment of the present disclosure has been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.
- For example, an example of the
fin 3F extending linearly in the fifth embodiment has been described. However, as shown inFIGS. 11 and 12 , afin 3F′ may extend so as to turn along the inner surface from the upstream side to the downstream side of theheat transfer tube 3 in the extending direction. InFIGS. 11 and 12 , a tip A1 and a base end A2 of thefin 3F′ extend so as to turn about the central axis of theheat transfer tube 3 from one side of theheat transfer tube 3 in the circumferential direction toward the other side. Similar to the fifth embodiment, a configuration can be adopted in which a plurality ofsuch fins 3F′ are arranged at an interval along the inner surface. - According to the above configuration, since the
fin 3F′ extends so as to turn along the inner surface, a turning flow component is added to the flow of the exhaust gas inside theheat transfer tube 3. As a result, a staying time of the exhaust gas inside theheat transfer tube 3 becomes long, such that the efficiency of heat exchange can be further improved. Further, since the exhaust gas accompanies the turning flow component, it is possible to suppress generation of deposits such as dust and soot on thefin 3F. As a result, theheat exchanger 100 can be stably operated for a longer period of time. - The
heat exchanger 100 described in each embodiment is grasped as follows, for example. - (1) A
heat exchanger 100 according to a first aspect includes: apipe 1 forming a flow path through which a first fluid is fed; a pair ofpartition plates 20 provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space V at a portion of the flow path; a plurality ofheat transfer tubes 3 having a tubular shape with both ends being open, extending so as to penetrate the pair ofpartition plates 20, and arranged side by side with intervals therebetween; a feedingpart 21 configured to feed a second fluid from an outside of thepipe 1 to the closed space V; and a dischargingpart 22 configured to discharge the second fluid in the closed space V to the outside of thepipe 1. - According to the above configuration, the closed space V is formed by the
partition plate 20 in the middle of extension of thepipe 1. Heat exchange is performed between the first fluid flowing through theheat transfer tube 3 and the second fluid flowing outside theheat transfer tube 3 in the closed space V. As described above, according to the above configuration, theheat exchanger 100 can be provided in the middle of extension of thepipe 1 without changing the extending direction of thepipe 1 and without greatly enlarging an outer diameter of thepipe 1. Accordingly, it is possible to save space for disposing theheat exchanger 100. - (2) In the
heat exchanger 100 according to a second aspect, theheat transfer tube 3 may have a cross section of a polygonal shape when viewed in the extending direction. - According to the above configuration, since a wetted area in an inner surface of the
heat transfer tube 3 is expanded, it is possible to further improve the efficiency of heat exchange. - (3) In the
heat exchanger 100 according to a third aspect, the second fluid may be configured to flow through the interval between the plurality ofheat transfer tubes 3 in the closed space V. - According to the above configuration, since the second fluid flows into the interval between the
heat transfer tubes 3, it is possible to secure a large contact area with theheat transfer tube 3. As a result, it is possible to further improve the efficiency of heat exchange while reducing the size of theheat exchanger 100. - (4) The
heat exchanger 100 according to a fourth aspect may further include a blockingpart 5 blocking only a portion of the interval between theheat transfer tubes 3, in which a plurality of the blockingparts 5 may be provided at an interval in the extending direction, and the blockingparts 5 adjacent to each other may have the blocking regions different from each other. - According to the above configuration, the blocking
part 5 changes a flowing direction of the second fluid in the closed space V. Since the regions blocked by theadjacent blocking parts 5 are different, the second fluid flows in a meandering manner while passing through the plurality of blockingparts 5. As a result, since the second fluid is uniformly distributed in the closed space V, it is possible to further improve the efficiency of heat exchange. - (5) The
heat exchanger 100 according to a fifth aspect may further include a supportingpart 6 provided between theheat transfer tubes 3. - According to the above configuration, the supporting
part 6 can suppress displacement and deformation of the heat transfer tube. - (6) In the
heat exchanger 100 according to a sixth aspect, the plurality ofheat transfer tubes 3 may be configured such that theheat transfer tube 3 disposed in a region having a smaller flow rate has a larger cross-sectional area of the flow path. - For example, in a case where the
pipe 1 has a curved portion on the upstream side of thepipe 1, the flow rate of the first fluid tends to be larger as theheat transfer tube 3 is directed toward an outer peripheral side of the curved portion due to inertial force, and the flow rate tends to be smaller as theheat transfer tube 3 is directed toward an inner peripheral side of the curved portion. According to the above configuration, theheat transfer tube 3 has a larger cross-sectional area of the flow path as it is disposed in the region having a smaller flow rate. As a result, even when flow rate distribution is non-uniform as described above, it is possible to correct the configuration and allow the first fluid to flow uniformly over the entire plurality ofheat transfer tubes 3. - (7) The
heat exchanger 100 according to a seventh aspect may further include a plurality offins 3F protruding from an inner surface of theheat transfer tube 3, extending in the extending direction, and provided at an interval along the inner surface. - According to the above configuration, since a contact area with the first fluid is expanded by the
fin 3F, it is possible to further improve the efficiency of heat exchange. - (8) In the
heat exchanger 100 according to an eighth aspect, thefin 3F′ may extend so as to turn along the inner surface from an upstream side to a downstream side in the extending direction. - According to the above configuration, since the
fin 3F′ extends so as to turn along the inner surface, a turning flow component is added to the first fluid inside theheat transfer tube 3. As a result, a staying time of the first fluid inside theheat transfer tube 3 becomes long, such that the efficiency of heat exchange can be further improved. Further, since the exhaust gas accompanies the turning flow component, it is possible to suppress generation of deposits such as dust on thefin 3F′. - According to the present disclosure, it is possible to provide a heat exchanger with a smaller size.
-
-
- 100: Heat exchanger
- 1: Pipe
- 3, 3A, 3B: Heat transfer tube
- 3F, 3F′: Fin
- 4: Vane
- 5: Blocking part
- 6: Supporting part
- 10: Elbow part
- 11: Pipe body
- 20: Partition plate
- 21: Feeding part
- 22: Discharging part
- 22H: Discharging part body
- F1: First flow path
- F2: Second flow path
- H: Opening
- V: Closed space
Claims (8)
1-8. (canceled)
9. A heat exchanger comprising:
a pipe forming a flow path through which a first fluid is fed;
a pair of partition plates provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space at a portion of the flow path;
a plurality of heat transfer tubes having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates, and arranged side by side with intervals therebetween;
a feeding part configured to feed a second fluid from an outside of the pipe to the closed space; and
a discharging part provided on an upstream side of a flow of the first fluid with respect to the feeding part, and configured to discharge the second fluid in the closed space to the outside of the pipe,
wherein the heat transfer tube has a cross section of a hexagonal shape between the pair of partition plates in the closed space, when viewed in the extending direction, and
the heat exchanger further includes a plurality of fins protruding from an inner surface of the heat transfer tube, extending in the extending direction, and provided at an interval along the inner surface.
10. The heat exchanger according to claim 9 ,
wherein the heat transfer tube among the plurality of heat transfer tubes is configured to have a larger cross-sectional area of the flow path as the heat transfer tube is disposed in a region having a smaller flow rate.
11. A heat exchanger comprising:
a pipe forming a flow path through which a first fluid is fed;
a pair of partition plates provided at an interval in an extending direction of the flow path to block the flow path, to partition a closed space at a portion of the flow path;
a plurality of heat transfer tubes having a tubular shape with both ends being open, extending so as to penetrate the pair of partition plates, and arranged side by side with intervals therebetween;
a feeding part configured to feed a second fluid from an outside of the pipe to the closed space; and
a discharging part configured to discharge the second fluid in the closed space to the outside of the pipe,
wherein the heat transfer tube has a cross section of a polygonal shape, when viewed in the extending direction,
the heat exchanger further includes a plurality of fins protruding from an inner surface of the heat transfer tube, extending in the extending direction, and provided at intervals along the inner surface, and
the plurality of heat transfer tubes are configured such that the heat transfer tube disposed in a region having a smaller flow rate has a larger cross-sectional area of the flow path.
12. The heat exchanger according to claim 9 ,
wherein the fin extends so as to turn along the inner surface from an upstream side to a downstream side in the extending direction.
13. The heat exchanger according to claim 9 ,
wherein the second fluid is configured to flow through the interval between the plurality of heat transfer tubes in the closed space.
14. The heat exchanger according to claim 9 , further comprising:
a blocking part blocking only a portion of the interval between the heat transfer tubes,
wherein a plurality of the blocking parts are provided at an interval in the extending direction, and the blocking parts adjacent to each other have the blocking regions different from each other.
15. The heat exchanger according to claim 9 , further comprising:
a supporting part provided between the heat transfer tubes.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020-214438 | 2020-12-24 | ||
JP2020214438A JP7025521B1 (en) | 2020-12-24 | 2020-12-24 | Heat exchanger |
PCT/JP2021/038174 WO2022137755A1 (en) | 2020-12-24 | 2021-10-15 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20230089621A1 true US20230089621A1 (en) | 2023-03-23 |
Family
ID=81124388
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US17/908,332 Pending US20230089621A1 (en) | 2020-12-24 | 2021-10-15 | Heat exchanger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20230089621A1 (en) |
JP (1) | JP7025521B1 (en) |
CN (1) | CN115190960B (en) |
DE (1) | DE112021003218T5 (en) |
WO (1) | WO2022137755A1 (en) |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3297081A (en) * | 1965-09-02 | 1967-01-10 | American Radiator & Standard | Tube-shell heat exchanger |
JPS56138695A (en) * | 1980-03-31 | 1981-10-29 | Nippon Sanso Kk | Heat exchanger for high-pressure fluid |
JPS58213193A (en) * | 1982-06-03 | 1983-12-12 | Toshiba Corp | Heat exchanger |
JP2652416B2 (en) * | 1988-06-29 | 1997-09-10 | 川崎重工業株式会社 | Latent heat recovery unit |
KR20040030954A (en) * | 2001-08-10 | 2004-04-09 | 쉘 인터내셔날 리써취 마트샤피지 비.브이. | Process to recover energy from hot gas |
CA2443496C (en) * | 2003-09-30 | 2011-10-11 | Dana Canada Corporation | Tube bundle heat exchanger comprising tubes with expanded sections |
CN101196381B (en) * | 2008-01-08 | 2010-06-16 | 哈尔滨工程大学 | Pipe shell type heat exchanger with dedusting function |
CN102410527A (en) * | 2011-11-10 | 2012-04-11 | 王海波 | Composite phase change heat exchanger for flue gas heat recovery of boiler |
CN103673688B (en) * | 2013-12-06 | 2015-10-28 | 河南工业大学 | A kind of grain dry miniature boiler flue gas-air heat exchanger |
JP6666703B2 (en) * | 2015-12-08 | 2020-03-18 | 株式会社Ihiプラント | Heat exchanger |
-
2020
- 2020-12-24 JP JP2020214438A patent/JP7025521B1/en active Active
-
2021
- 2021-10-15 US US17/908,332 patent/US20230089621A1/en active Pending
- 2021-10-15 WO PCT/JP2021/038174 patent/WO2022137755A1/en active Application Filing
- 2021-10-15 CN CN202180016640.XA patent/CN115190960B/en active Active
- 2021-10-15 DE DE112021003218.6T patent/DE112021003218T5/en active Pending
Also Published As
Publication number | Publication date |
---|---|
CN115190960B (en) | 2023-10-20 |
JP7025521B1 (en) | 2022-02-24 |
WO2022137755A1 (en) | 2022-06-30 |
DE112021003218T5 (en) | 2023-04-27 |
JP2022100459A (en) | 2022-07-06 |
CN115190960A (en) | 2022-10-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8069905B2 (en) | EGR gas cooling device | |
JP2011506896A (en) | Recirculation exhaust gas cooler for internal combustion engines | |
CN109959169B (en) | Heat exchange device and heat source machine | |
US8511074B2 (en) | Heat transfer unit for an internal combustion engine | |
BRPI0709556A2 (en) | heat exchanger for a motor vehicle | |
CN108463682B (en) | U-shaped tube heat exchanger | |
JP5579428B2 (en) | Exhaust gas cooler | |
EP2944911B1 (en) | Heat exchanger | |
US10202880B2 (en) | Exhaust heat exchanger | |
KR101685795B1 (en) | Heat exchanger unit | |
JP2005283095A (en) | Efficient heat exchanger, and engine using the same | |
WO2015071872A1 (en) | Heat exchanger, in particular for a condensation boiler | |
WO2020017176A1 (en) | Heat exchanger | |
US20230089621A1 (en) | Heat exchanger | |
US20230251041A1 (en) | Heat exchanger | |
JP7311655B2 (en) | Heat exchanger | |
JP2007064606A (en) | Heat exchanger tube for egr cooler | |
JP4823043B2 (en) | Heat exchanger | |
US20200224978A1 (en) | Duct heat exchanger | |
CN216205601U (en) | Heat exchange fin and heat exchange device | |
KR102513327B1 (en) | Gas-gas tube heat exchanger including insert with irregular pitch | |
CN215523226U (en) | Waste heat boiler using hot water for energy supply | |
JP2005147426A (en) | Heat exchanger | |
JP2010127171A (en) | U-turn egr cooler | |
CN115516271A (en) | Heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: MITSUBISHI HEAVY INDUSTRIES, LTD., JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HARA, NOBUHIDE;TANIMOTO, KOICHI;SENOO, SHIGEKI;AND OTHERS;REEL/FRAME:060954/0600 Effective date: 20220815 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |