WO2020004292A1 - Structure de réservoir d'échangeur thermique - Google Patents

Structure de réservoir d'échangeur thermique Download PDF

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Publication number
WO2020004292A1
WO2020004292A1 PCT/JP2019/024854 JP2019024854W WO2020004292A1 WO 2020004292 A1 WO2020004292 A1 WO 2020004292A1 JP 2019024854 W JP2019024854 W JP 2019024854W WO 2020004292 A1 WO2020004292 A1 WO 2020004292A1
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WO
WIPO (PCT)
Prior art keywords
plate
header
flat
tank
intermediate plate
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.)
Ceased
Application number
PCT/JP2019/024854
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English (en)
Japanese (ja)
Inventor
純也 池田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
T Rad Co Ltd
Original Assignee
T Rad Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by T Rad Co Ltd filed Critical T Rad Co Ltd
Priority to JP2020527493A priority Critical patent/JPWO2020004292A1/ja
Publication of WO2020004292A1 publication Critical patent/WO2020004292A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • 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
    • 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

Definitions

  • the present invention relates to a heat exchanger tank structure suitable for cooling high-pressure oil or gas.
  • the conventional oil cooler has a header tank main body and a header plate, and a number of flat tubes are inserted through the header plate.
  • an oil cooler that guides high-pressure oil to such a header tank, supplies it to each flat tube, guides cooling air to the outer surface side of the flat tube, and exchanges heat with the oil.
  • high-pressure oil is introduced into the header tank, a bending moment is generated mainly in the width direction of the header tank at the connection between the header plate and the header tank body due to the internal pressure.
  • bending stress also occurs at the base of the flat tube at the joint between the flat tube and the header plate, and the tube may be cracked.
  • a high pressure resistant header tank described in Patent Document 1 has been proposed.
  • This has an inner plate having a tube connection hole, a middle plate having a plurality of slits, and an outer plate closing one surface of the middle plate, and these are stacked to form a header tank. More specifically, this header tank has a number of tube connection holes in the inner plate, and the middle plate has a number of slits orthogonal to the connection holes. Then, the outer plate closes one surface of the middle plate, and they are laminated, and the high-pressure refrigerant flows through the flat tube and the slit in the inner plate. According to the patent document, it is described that this header tank is low-cost and suitable for miniaturization.
  • an object of the present invention is to provide a heat exchanger tank structure having a small flow resistance and a high pressure resistance.
  • the present invention according to claim 1 includes a header plate 2 in which a large number of tube insertion holes 2a are arranged in parallel, A first intermediate plate 3 having a heat medium flow path opened in the thickness direction by the thickness thereof, An end plate 4 that covers the outside of the first intermediate plate 3, A large number of tubes 14 whose ends are inserted into the respective tube insertion holes 2a of the header plate 2, The first intermediate plate 3 and the end plate 4 are formed in a flat plate shape, The header plate 2, the first intermediate plate 3, and the end plate 4 are integrally brazed and joined in the thickness direction, and a gap between the ends of the large number of tubes 14 and the header plate 2 is formed.
  • the header plate 2, the first intermediate plate 3, and the end plate 4 are formed in a flat rectangular shape in which the outer peripheries of the header plate 2, the end plate 4 and the end plate 4 are substantially aligned.
  • the first intermediate plate 3 has a flat frame-shaped opening hole 3a, and the entire width Wa of the opening hole 3a of the first intermediate plate 3 is smaller than the total width Wh of the tube insertion hole 2a of the header plate 2.
  • the heat exchanger tank structure according to claim 1 wherein:
  • the present invention according to claim 3 has a planar intermediate second plate 6 interposed between the header plate 2 and the first intermediate plate 3, In the second intermediate plate 6, a number of slits 7 are opened in the thickness direction to form a flow path, 3.
  • a flat tube insertion hole 2a is formed in the header plate 2 at a constant pitch in a longitudinal direction of the header plate 2
  • An elongated slit 7 is formed in the second intermediate plate 6 in the longitudinal direction of the second intermediate plate 6 at the same pitch as the tube insertion hole 2a.
  • a plurality of tube insertion holes 2a are arranged apart from each other in the width direction of the header plate 2,
  • the tank structure of the heat exchanger according to claim 3 or 4 wherein the entire length Wb of the slit 7 is formed longer than the entire width Wh of the tube insertion hole 2a.
  • a heat medium entrance / exit 4 a is opened in a plane of the end plate 4, 2.
  • the invention according to claim 7 is a header plate having a large number of tube insertion holes 2a arranged in parallel, A large number of tubes 14 whose ends are inserted into the respective tube insertion holes 2a of the header plate 2, A tank body 23a made of a flat extruded material having a flat top surface 19 and a pair of side edges 20 raised from the edge and having a cross section formed in a groove shape, and a longitudinal direction of the tank body 23a.
  • This is a tank structure of the heat exchanger in which the plate thickness of the flat tank 23 is formed larger than the plate thickness of the header plate 2.
  • the header plate 2 and the flat tank 23 are formed in a flat rectangular shape in which the outer peripheries are substantially aligned,
  • an intermediate plate 25 is interposed between the flat tank 23 and the header plate 2, and the elongated slit 7 has the same pitch as the tube insertion hole 2 a in the longitudinal direction of the intermediate plate 25. Drilled in 9.
  • Tank structure
  • the thickness of the first intermediate plate 3 having the heat medium flow path opened in the thickness direction by the thickness thereof is formed to be larger than the thickness of the header plate 2.
  • the thick first intermediate plate 3 serves as a reinforcing material for the header plate 2, and deformation (bending) of the header plate 2 is suppressed. Therefore, the stress at the base of the tube 14 due to the bending of the header plate 2 is reduced.
  • the total width Wa of the planar frame-shaped opening 3a of the first intermediate plate 3 is smaller than the total width Wh of the tube insertion hole 2a of the header plate 2 (total width Wh> total width Wa).
  • a second intermediate plate 6 is interposed between the header plate 2 and the first intermediate plate 3, a number of slits 7 are opened in the thickness direction, and each plate is connected in the thickness direction. It was brazed and joined together. The flow path of the heat medium in the tank is formed by the large number of slits 7 of the second intermediate plate 6.
  • the flattened tube insertion holes 2a and the slits 7 are formed in the header plate 2 and the second intermediate plate 6 at the same pitch at regular intervals in the longitudinal direction of each plate. Are formed parallel to the width direction of each plate, so that the flow of the heat medium between the header plate 2 and the first intermediate plate 3 is further smoothed, and the flow resistance is reduced.
  • the entire length Wb of the slit 7 is formed longer than the entire width Wh of the tube insertion hole 2a.
  • the flow path between the header plate 2 and the first intermediate plate 3 becomes wider, so that the flow of the heat medium therebetween becomes smoother and the flow resistance is reduced.
  • the entrance and exit 4a of the heat medium are formed in the end plate 4, the end of the pipe 8 is inserted into the entrance and exit 4a, and the end face of the pipe 8 is in the plane of the first intermediate plate 3. It is seated and fixed. Thereby, the positioning of the pipe 8 is facilitated, and the fixing of the pipe 8 is strengthened.
  • the invention according to claim 7 has a tank main body 23a made of an extruded material having a groove-shaped cross section, and a flat tank 23 made up of a pair of end covers 22 closing both ends thereof.
  • the flat tank 23 is formed to be thicker than the header plate 2. With the flat tank 23, a sufficient flow path of the heat medium is secured, the flow resistance is reduced, and the flat tank 23 serves as a reinforcing material for the header plate 2, so that the deformation (bending) of the header plate 2 is suppressed. Thus, the stress at the base of the tube 14 due to the bending of the header plate 2 is reduced.
  • the flat tank 23 is made of a flat extruded material having a cross section formed in a groove shape, it can be manufactured with a small amount of processing of the extruded material, and is easy to manufacture and has high pressure resistance.
  • the entire width Wc between the inner walls of the pair of side edges 20 of the flat tank 23 is formed smaller (Wh> Wc) than the entire width Wh of the tube insertion hole 2a of the header plate 2. .
  • the rigidity of the flat tank 23 is improved and the reinforcing effect is enhanced, so that the deformation (bending) of the header plate 2 is further suppressed, and the stress at the root of the tube 14 due to the bending of the header plate 2 is further reduced. Is done.
  • the intermediate plate 25 is interposed between the flat tank 23 and the header plate 2, and the elongated slit 7 is formed at the same pitch as the tube insertion hole 2 a in the longitudinal direction of the intermediate plate 25.
  • the long axis of the tube insertion hole 2a and the opening of the elongated slit 7 is formed in parallel with the width direction of the intermediate plate 25. Thereby, the flow of the heat medium between the header plate 2 and the flat tank 23 is smoothed, and the flow resistance is reduced.
  • FIG. 1 is an exploded perspective view of the tank structure of the heat exchanger according to the first embodiment of the present invention.
  • FIG. 2 is a perspective view of an essential part showing the assembled state, in which one side is omitted.
  • FIG. 3 is a sectional view taken along the line III-III in FIG. 2.
  • FIG. 4 is a sectional view taken along the line IV-IV in FIG.
  • FIG. 5 is a front view (A) and a side view (B) of a heat exchanger having the tank structure of the present invention.
  • FIG. 6 is a plan view (A), a side view (B), and a schematic CC sectional view (C) of the header plate 2 used in the tank structure.
  • FIG. 7 is a plan view of the first intermediate plate 3 used in the tank structure of the present invention.
  • FIG. 8 is a plan view of a second intermediate plate 6 used in the tank structure.
  • FIG. 9 is a plan view of an end plate 4 used in the tank structure.
  • FIG. 10 is an exploded perspective view of the tank structure of the heat exchanger according to the second embodiment of the present invention.
  • FIG. 11 is a plan view (A), a front view (B), and a side view (C) of the flat tank of the embodiment.
  • FIG. 12 is a vertical sectional view of a main part of the embodiment.
  • the heat exchanger tank structure is suitable for large work machines used at mining sites and construction sites, or heat exchangers of large vehicles, and the internal pressure of the heat exchanger tank is relatively high. It is the most suitable structure.
  • the heat exchanger according to the first embodiment includes a plurality of fins 15 and tubes 14 alternately arranged in parallel to form a core 16, and a pair of tanks at upper and lower ends of the core 16. Are arranged.
  • the tank is composed of a laminate of the end plate 4, the first intermediate plate 3, and the header plate 2. It is preferable to interpose a second intermediate plate 6 between the first intermediate plate 3 and the header plate 2.
  • the end plate 4, the first intermediate plate 3, and the second intermediate plate 6 are formed of flat rectangular plates, and their outer circumferences are substantially aligned.
  • a large number of tube insertion holes 2a are formed in the header plate 2 at regular intervals in parallel in the longitudinal direction.
  • the long axis of the tube insertion hole 2 a is formed parallel to the width direction of the header plate 2.
  • four rows of tube insertion holes 2a are arranged in the header plate 2 as shown in FIGS. The number of columns can be increased or decreased as needed.
  • FIG. 6 (C) it is preferable to form a burring portion 2b at the edge of the tube insertion hole 2a.
  • the burring portion 2b is formed from the surface of the header plate 2 to the tube 14 (FIG. 1).
  • the burring portion 2b can be formed by means such as press molding. By protruding the burring portion 2b toward the tube 14 and gradually reducing the thickness of the hole edge portion from the root to the tip end as shown in FIG. 6C, a crack is not generated in the tube insertion hole 2a. , Resulting in a structure with high pressure resistance.
  • FIGS. 1 and 4 a large number of slits 7 are formed in the second intermediate plate 6 at the same pitch as the tube insertion holes 2a in parallel in the longitudinal direction. .
  • the pitch of the slits 7 matches the pitch of the tube insertion holes 2a of the header plate 2.
  • the long axis of the slit 7 is formed parallel to the width direction of the second intermediate plate 6. It is preferable that the entire length Wb of the slit 7 is formed larger than the entire width Wh of the tube insertion hole 2a (FIG. 3).
  • FIGS. 1 and 8 when the second intermediate plate 6 has end openings 6 a at both ends in the longitudinal direction, the flow of the heat medium at that position can be made smooth. .
  • only one row of the slits 7 shown in FIGS. 1, 4, and 8 is formed, two or more rows may be provided.
  • the thickness of the second intermediate plate 6 can be equal to or greater than the thickness of the header plate 2.
  • the plate thickness of the first intermediate plate 3 is formed larger than the plate thickness of the header plate 2.
  • the first intermediate plate 3 is entirely formed in a frame shape, and an opening hole 3a is opened along the longitudinal direction.
  • two opening holes 3a are arranged in parallel in the width direction, and a partition 3b extending in the longitudinal direction can be formed therebetween.
  • the partition part 3b By this partition part 3b, the brazing area between the first intermediate plate 3 and the second intermediate plate 6 is increased, and the joining strength is improved.
  • the formation of the partition 3b is optional. It is preferable that the entire width Wa of the opening 3a be smaller than the entire width Wh of the tube insertion hole 2a (FIG. 3).
  • the end plate 4 is arranged on the first intermediate plate 3.
  • An entrance 4a is formed in an intermediate portion of the end plate 4 in the longitudinal direction.
  • the outer periphery of the end plate 4, the first intermediate plate 3, the second intermediate plate 6, and the header plate 2 are aligned with each other, and holes 13 that are aligned with each other are formed in at least four corners and intermediate portions thereof.
  • the rivets 12 are inserted into the holes 13 in the stacked state of the plates, the ends thereof are caulked, and the plates are temporarily fixed.
  • a core 16 is formed by the tubes 14 and the fins 15, and both ends of each tube 14 are inserted into each tube insertion hole 2 a of the header plate 2. As shown in FIG. 3, the distal end of each tube is inserted so as not to protrude from each slit 7 of the second intermediate plate 6.
  • the end of the pipe 8 shown in FIGS. 1 to 3 is inserted into the entrance 4a of the end plate 4, and the opening end face of the pipe 8 is seated on the plane of the first intermediate plate 3 as shown in FIG. . Further, a plurality of brackets 11 are arranged on the end plate 4.
  • Each component assembled in this way has at least one outer surface of each component coated or coated with a brazing material. Then, these assemblies are inserted into a high-temperature furnace, and the whole is brazed and fixed together.
  • the burring portion 2b of each tube insertion hole 2a is formed on the tube 14 side, the distal end of the tube 14 is inserted therein, and the tube 14 and the burring portion 2b are opened with the opening edge of the tube 14 expanded. Can be brazed together.
  • FIGS. 10 to 12 show a second embodiment of the present invention.
  • This example is different from the above-described embodiment in that, instead of the first intermediate plate 3 and the end plate 4 of the above-described embodiment, a tank main body 23a made of an extruded aluminum material and a side lid 22 closing both sides thereof are provided. The flat tank 23 is used.
  • the flat tank 23 has a flat top surface 19, and a tank body 23a made of an extruded material having a groove-like cross section having a pair of side edges 20 that are lowered from the edge thereof. It comprises a pair of side lids 22 closing both ends.
  • the side edge 20 of the tank body 23a is formed in an L-shape in cross section, and has a flange portion whose tip projects outward.
  • An entrance 21 for pipe attachment can be formed on the top surface 19 of the tank body 23a.
  • An intermediate rib 24 extending in the longitudinal direction can be formed at an intermediate position in the width direction inside the top surface 19 of the tank body 23a.
  • the outer peripheries of the end surfaces of the pair of side edges 20 of the flat tank 23 are aligned with the outer perimeter of the header plate 2.
  • the entire width Wc between the inner walls of the pair of side edges 20 of the flat tank 23 (see FIG. 10) is formed so as to be smaller than the entire width Wh of the tube insertion hole 2a of the header plate 2 (Wh> Wc).
  • the end face of the side edge 20 of the flat tank 23 and the header plate 2 are integrally brazed and joined in the thickness direction. At this time, as shown in FIG. 12, it is preferable to braze and join them via an intermediate plate 25 therebetween.
  • the intermediate plate 25 is provided with elongated slits 7 arranged in parallel at the same pitch in the longitudinal direction (FIG. 10).
  • This intermediate plate 25 corresponds to the second intermediate plate 6 of the first embodiment (the formation of the end opening 6a is optional).
  • the long axis of the flat tube insertion hole 2 a and the long axis of the opening of the elongated slit 7 are formed parallel to the width direction of the intermediate plate 25.
  • the slit 7 is formed so that the entire length Wb thereof is longer than the entire width Wh of the tube insertion hole 2a (Wb> Wh).
  • Such a flat tank 23 can be manufactured with a small processing of a tank body 23a made of extruded material and a pair of end covers 22, and the flat tank 23 secures a sufficient flow path of the heat medium, and a flow resistance. Is reduced. Furthermore, since the flat tank 23 serves as a reinforcing material for the header plate 2 and the deformation (bending) of the header plate 2 is suppressed, the stress at the root of the tube 14 due to the bending of the header plate 2 is reduced.
  • the present invention can be applied to a heat exchanger such as an oil cooler or an air cooler through which a heat medium having a high internal pressure flows.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention comprend une plaque collectrice (2) dans laquelle des trous d'insertion de tube (2a) sont alignés en une rangée, une première plaque intermédiaire (3) dans laquelle un trajet d'écoulement pour un agent thermique est formé dans la direction d'épaisseur, et une plaque d'extrémité (4) qui est montée sur le côté extérieur de la première plaque intermédiaire (3). La plaque collectrice (2), la première plaque intermédiaire (3) et la plaque d'extrémité (4) sont brasées de façon monobloc dans la direction d'épaisseur, et le brasage est également effectué entre la plaque collectrice (2) et un tube (14). L'épaisseur de la première plaque intermédiaire (3) est formée pour être supérieure à l'épaisseur de la plaque collectrice (2).
PCT/JP2019/024854 2018-06-28 2019-06-17 Structure de réservoir d'échangeur thermique Ceased WO2020004292A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2020527493A JPWO2020004292A1 (ja) 2018-06-28 2019-06-17 熱交換器のタンク構造

Applications Claiming Priority (2)

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JP2018-123683 2018-06-28
JP2018123683 2018-06-28

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WO2020004292A1 true WO2020004292A1 (fr) 2020-01-02

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PCT/JP2019/024854 Ceased WO2020004292A1 (fr) 2018-06-28 2019-06-17 Structure de réservoir d'échangeur thermique

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11060794B2 (en) * 2018-02-12 2021-07-13 Shenzhen Esin Technology Inc., Ltd. Gas-liquid heat exchanger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05296606A (ja) * 1992-03-31 1993-11-09 Modine Mfg Co 高効率蒸発器
JPH08240395A (ja) * 1995-03-06 1996-09-17 Zexel Corp 熱交換器
JP2005300135A (ja) * 2004-03-17 2005-10-27 Showa Denko Kk 熱交換器用ヘッダタンクおよびこれを用いた熱交換器
JP2009257719A (ja) * 2008-04-21 2009-11-05 Showa Denko Kk 熱交換器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05296606A (ja) * 1992-03-31 1993-11-09 Modine Mfg Co 高効率蒸発器
JPH08240395A (ja) * 1995-03-06 1996-09-17 Zexel Corp 熱交換器
JP2005300135A (ja) * 2004-03-17 2005-10-27 Showa Denko Kk 熱交換器用ヘッダタンクおよびこれを用いた熱交換器
JP2009257719A (ja) * 2008-04-21 2009-11-05 Showa Denko Kk 熱交換器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11060794B2 (en) * 2018-02-12 2021-07-13 Shenzhen Esin Technology Inc., Ltd. Gas-liquid heat exchanger

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