EP3581868A1 - Water heat exchanger and gas cooler - Google Patents

Water heat exchanger and gas cooler Download PDF

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Publication number
EP3581868A1
EP3581868A1 EP19179799.2A EP19179799A EP3581868A1 EP 3581868 A1 EP3581868 A1 EP 3581868A1 EP 19179799 A EP19179799 A EP 19179799A EP 3581868 A1 EP3581868 A1 EP 3581868A1
Authority
EP
European Patent Office
Prior art keywords
axis
heat transfer
header
transfer pipe
main body
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.)
Withdrawn
Application number
EP19179799.2A
Other languages
German (de)
English (en)
French (fr)
Inventor
Kohei Matsumoto
Masatomo KOSAKA
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems 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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3581868A1 publication Critical patent/EP3581868A1/en
Withdrawn legal-status Critical Current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
    • F28F2210/00—Heat exchange conduits

Definitions

  • the present invention relates to a water heat exchanger and a gas cooler.
  • the heat exchanger described in Japanese Unexamined Patent Application, First Publication No. 2012-21682 includes a pair of first headers and a pair of second headers formed in a cylindrical shape, a plurality of first heat transfer pipes which connect the pair of first headers to each other, and a second heat transfer pipe which connects the pair of second headers to each other.
  • the plurality of first heat transfer pipes are arranged to be spaced apart from each other between the paired first headers.
  • the plurality of second heat transfer pipes are arranged to be spaced apart from each other between the paired second headers. Holes for inserting the first heat transfer pipes and the second heat transfer pipes are formed on outer peripheral surfaces of the first headers and the second headers.
  • End portions of the first heat transfer pipes and end portions of the second heat transfer pipes slightly protrude into spaces inside the first headers and the second headers.
  • a heat exchange is performed between the fluids flowing inside the first heat transfer pipes and the second heat transfer pipes.
  • the end portions (insertion portions) of the first heat transfer pipes and the second heat transfer pipes are exposed inside the first headers and the second headers. Furthermore, the first heat transfer pipes and the second heat transfer pipes are inserted in a direction orthogonal to the first headers and the second headers, respectively. Therefore, when the refrigerant flows from the headers to the heat transfer pipes, there is a possibility that a separation may occur in the flow of the refrigerant. When a separation occurs in the flow of the refrigerant, the local flow velocity increases, and there is a risk of an occurrence of erosion or pitting in that portion.
  • the present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a water heat exchanger and a gas cooler with improved durability.
  • a water heat exchanger is provided with: a header including a tubular header main body extending in a direction of a first axis and through which water flows toward a first side in the direction of the first axis; and a tubular heat transfer pipe which is installed on the header main body so as to be inserted from an outer peripheral surface of the header main body into the header, and which extends along a second axis inclined so as to approach a second side in the direction of the first axis as it goes further from the outer peripheral surface of the header main body outward.
  • the heat transfer pipe is extended along a second axis inclined so as to approach a second side in the direction of the first axis as it goes further from the outer peripheral surface of the header main body outward.
  • separation or swirling in the flow of water is reduced, and the flow velocity of water in the header main body and the heat transfer pipe can be made uniform.
  • an inclination angle which is formed by the second axis with respect to a reference axis orthogonal to the first axis may be 10 to 45°.
  • the water in the header main body can be guided more smoothly toward the heat transfer pipe.
  • separation or swirling in the flow of water is reduced, and the flow velocity of water in the header main body and the heat transfer pipe can be made uniform.
  • the header may further include an annular burring portion in contact with an outer peripheral surface of the heat transfer pipe, the burring portion is formed at a portion of the outer peripheral surface of the header main body to which the heat transfer pipe is to be inserted, and an inner peripheral surface of the burring portion may have a cylindrical surface shape extending around the second axis.
  • the burring portion is formed at the portion of the outer peripheral surface of the header main body to which the heat transfer pipe is to be inserted.
  • the heat transfer pipe can be fixed to the header main body via the burring portion.
  • a depth of a penetrating portion of the transfer pipe which is inserted from the outer peripheral surface of the header main body into the header, can be reduced. If the depth of the penetrating portion of the heat transfer pipe is too long, there is a possibility that the flow of water may be disturbed by the end portion of the heat transfer pipe protruding to the inside of the head main body. As a result, separation or swirl occurs in the flow of water.
  • the insertion margin is small, such a likelihood can be reduced.
  • a plurality of the heat transfer pipes may be installed on the header main body so as to be aligned at intervals in the direction of the first axis, and as the heat transfer pipe is located further to a second side in the direction of the first axis, the inclination angle which is formed by the second axis with respect to the reference axis orthogonal to the first axis may increase.
  • the water flows in the header main body from the second side to the first side in the direction of the first axis.
  • water sequentially flows into the plurality of heat transfer pipes. That is, when the heat transfer pipe is located on the second side in the direction of the first axis, water having a higher flow velocity flows therein.
  • the inclination angle increases as the heat transfer pipe is located on the second side in the direction of the first axis, water having a high flow velocity can be smoothly guided into the heat transfer pipe. That is, the possibility of an occurrence of disturbance in the water flow can be further reduced.
  • a gas cooler has the water heat exchanger according to any one of the above aspects, and a gas circulation pipe which is in contact with the outer peripheral surface of the heat transfer pipe and through which gas flows.
  • a gas cooler 100 according to this embodiment is disposed in a cycle of a water heater as an example. More specifically, the gas cooler 100 heats water by performing a heat exchange between the water and the gas as a heat medium.
  • the gas cooler 100 includes a water heat exchanger 90 and a plurality of gas circulation pipes 3.
  • the water heat exchanger 90 has a header 1 and a plurality of heat transfer pipes 2.
  • the header 1 has an inlet side header 1A and an outlet side header 1B.
  • the inlet side header 1A has a tubular header main body 11 extending along a first axis A1, an introduction portion 12, and a burring portion 13 (see FIG. 2 ).
  • the introduction portion 12 for guiding water from outside is provided at the other end portion of the header main body 11 in the direction of the first axis A1.
  • the water guided from the introduction portion 12 flows from the second side to the first side in the direction of the first axis A1.
  • the outlet side header 1B is a tubular member disposed in parallel to the inlet side header 1A.
  • a discharge portion 14 for guiding the heated water to outside is provided at an end portion of the outlet side header 1B.
  • the introduction portion 12 may be provided not only at the end portion of the header main body 11 but also at an intermediate portion in an extending direction of the header main body 11.
  • a plurality of heat transfer pipes 2 are disposed between the inlet side header 1A and the outlet side header 1B.
  • the plurality of heat transfer pipes 2 are arranged at intervals in the extending direction of the inlet side header 1A and the outlet side header 1B.
  • a flow path through which water circulates is formed inside each heat transfer pipe 2.
  • the water flowing into the inlet side header 1A flows to the outlet side header 1B through the heat transfer pipes 2.
  • the gas circulation pipe 3 is spirally wound around the outer peripheral surfaces of each heat transfer pipe 2 to come into contact with the outer peripheral surfaces.
  • High-temperature gas as a heat medium flows inside the gas circulation pipe 3.
  • carbon dioxide is suitably used as such a gas.
  • the plurality of gas circulation pipes 3 are connected to a header different from the inlet side header 1A and the outlet side header 1B.
  • FIG. 2 is an enlarged view of the portion connecting between the inlet side header 1A and the plurality of heat transfer pipes 2.
  • the inlet side header 1A has a cylindrical shape centered on first axis A1.
  • Each heat transfer pipe 2 extends along a second axis A2 which is a direction intersecting the direction of the first axis A1, between the inlet side header 1A and the outlet side header 1B. It is preferable that an angle (an inclination angle ⁇ ) formed by the second axis A2 with respect to a reference axis Ac orthogonal to the first axis A1 be 10° to 45°.
  • the inclination angle ⁇ is set to 20° to 35° with respect to the reference axis Ac. Most preferably, the inclination angle ⁇ is set to 30 ° with respect to the reference axis Ac. In the present embodiment, the inclination angles ⁇ of each of the heat transfer pipes 2 are identical to each other.
  • the burring portion 13 supporting the end portions of each heat transfer pipe 2 is provided on the outer peripheral surface of the inlet side header 1A (the header main body 11).
  • the burring portion 13 has an annular shape protruding outward in a radial direction with respect to the first axis A1 from the outer peripheral surface of the inlet side header 1A. More specifically, as shown in FIG. 3 , the outer peripheral surface of the burring portion 13 has a cylindrical shape centered on the reference axis Ac.
  • the inner peripheral surface (the insertion hole 15) of the burring portion 13 has a cylindrical surface shape centered on the above-mentioned second axis A2. That is, in a cross-sectional view including the first axis A1, the insertion hole 15 extends in a direction inclined by the inclination angle ⁇ with respect to the reference axis Ac.
  • each heat transfer pipe 2 is inserted into each insertion hole 15 from the outer peripheral side.
  • the end portions of each heat transfer pipe 2 is protruded in the inside of the inlet side header 1A.
  • At least one protrusion P for determining a depth of a penetrating portion of the transfer pipe 2 inserted from the outer peripheral surface of the header main body 11 into the header 2 is formed on the outer peripheral surface of the heat transfer pipe 2. That is, each heat transfer pipe 2 is inserted into the insertion hole 15 until the protrusion P is in contact with the end surface of the burring portion 13.
  • each heat transfer pipe 2 is supported in a non-displaceable manner.
  • the burring portion 13 is provided integrally with the header main body 11.
  • the burring portion 13 prepared separately from the header main body 11 is attached to the header main body 11 by brazing or the like.
  • low-temperature water (water before heating) circulates through the header 1 and each of the heat transfer pipes 2. Specifically, water is supplied from the introduction portion 12 of the inlet side header 1A and distributed to each heat transfer pipe 2.
  • relatively high-temperature gas (a heat medium) circulates through the gas circulation pipe 3. Since the gas circulation pipe 3 is in contact with the outer peripheral surface of the heat transfer pipe 2 in this way, a movement of heat occurs between the water and the gas. That is, since the heat of the relatively high-temperature gas is transmitted to the relatively low-temperature water in the heat transfer pipe 2, the water is heated. The heated water is collected from each heat transfer pipe 2 to the outlet side header 1B, and then is taken out through the discharge portion 14.
  • each heat transfer pipe 2 has an angle with respect to the inlet side header 1A. Therefore, when water flows to the heat transfer pipe 2 from the inlet side header 1A, there is a possibility of an occurrence of separation of the flow. If separation occurs in the flow of water, the local flow velocity increases, and there is a risk of an occurrence of erosion or pitting in that portion. In particular, when the inlet side header 1A and each heat transfer pipe 2 are connected to be orthogonal to each other, since the direction of the flow of water changes rapidly, the above-mentioned phenomenon easily occurs.
  • the heat transfer pipe 2 e extends along the second axis A2 inclined so as to approach the second side in the direction of the first axis A1 as it goes further from the outer peripheral surface of the header main body 11 outward.
  • the inclination angle ⁇ which is the angle formed by the second axis A2 with respect to the reference axis Ac orthogonal to the first axis A1, is set to 10° to 45°. More preferably, the inclination angle ⁇ is set to 20° to 35° with respect to the reference axis Ac. Most preferably, the inclination angle ⁇ is set to 30° with respect to the reference axis Ac. According to this configuration, the water in the header main body 11 can be guided more smoothly toward the heat transfer pipe 2. As a result, separation or swirling in the flow of water is reduced, and the flow velocity of water in the header main body 11 and the heat transfer pipe 2 can be made uniform.
  • the burring portion 13 is provided at the insertion portion of the heat transfer pipe 2 on the outer peripheral surface of the header main body 11. That is, the heat transfer pipe 2 can be fixed to the header main body 11 by the burring portion 13. As a result, compared to a case in which the burring portion 13 is not formed, the depth of the penetrating portion of the transfer pipe 2, which is inserted from the outer peripheral surface of the header main body 11 into the header 1, can be reduced. If the depth of the penetrating portion of the heat transfer pipe is too long, there is a possibility that the flow of water flowing in the header main body 11 will be disturbed by the end portion of the heat transfer pipe 2. As a result, separation or swirling occurs in the flow of water. However, according to the above configuration, such a possibility can be reduced because the insertion margin is small.
  • the first embodiment of the present invention has been described above with reference to FIGS. 1 to 3 .
  • Various changes or modifications can be made to the above-described configuration without departing from the scope of the present invention.
  • the aforementioned embodiment demonstrated an example in which the gas cooler 100 is applied to a water heater for heating water.
  • the application target of the gas cooler 100 is not limited to a water heater, and the gas cooler 100 can also be applied to any device including an air conditioner or the like as long as the device performs a heat exchange between the fluids.
  • a second embodiment of the present invention will be described with reference to FIG. 4 .
  • components similar to those of the aforementioned first embodiment are denoted by the same code reference numerals, and a detailed description thereof will be omitted.
  • the inclination angles ⁇ of the plurality of heat transfer pipes 2 that is, the angles formed by the second axis A2 of the heat transfer pipe 2 with respect to the first axis A1 are different from each other. In the following description, among the three heat transfer pipes 2 shown in FIG.
  • a heat transfer pipe 2 located furthest to the first side in the direction of the first axis A1 is referred to as a first heat transfer pipe 21, a heat transfer pipe 2 located furthest to the second side is referred to as a third heat transfer pipe 23, and a heat transfer pipe 2 located between them is referred to as a second heat transfer pipe 22.
  • the first heat transfer pipe 21 extends along a second axis A21
  • the second heat transfer pipe 22 extends along a second axis A22.
  • the third heat transfer pipe 23 extends along a second axis A23.
  • an angle (an inclination angle ⁇ ) formed by the second axis A21 with respect to the reference axis Ac is referred to as ⁇ 1
  • an angle (inclination angle) formed by the second axis A22 with respect to the reference axis Ac is referred to as ⁇ 2
  • an angle (inclination angle) formed by the third axis with respect to the reference axis Ac is referred to as ⁇ 3.
  • the inclination angles ⁇ 1, ⁇ 2 and ⁇ 3 satisfy the relationship shown in the following Equation (1).
  • Equation (1) ⁇ 1 ⁇ ⁇ 2 ⁇ ⁇ 3 That is, as the heat transfer pipe 2 is located further to the second side in the direction of the first axis A1, the inclination angle ⁇ of the heat transfer pipe 2 increases.
  • each inclination angle ⁇ is set to satisfy the relationship according to the above equation (1).
  • the water flows in the header main body 11 (in the inlet side header 1A) from the second side toward the first side in the direction of the first axis A1.
  • water flows into the plurality of heat transfer pipes 2 sequentially. That is, water having a higher flow velocity flows in, further toward the second side in the direction of the first axis A1 with respect to the heat transfer pipe 2.
  • the inclination angle ⁇ increases further toward the second side in the direction of the first axis A1 with respect to the heat transfer pipe 2
  • water having a high flow velocity can be smoothly guided into the heat transfer pipe 2. That is, the possibility of an occurrence of disturbance in the water flow can be further reduced.
  • the second embodiment of the present invention has been described above with reference to FIG. 4 .
  • Various changes and modifications can be made to the above-described configuration without departing from the scope of the present invention.
  • the aforementioned embodiment demonstrated the example in which the gas cooler 200 is applied to a water heater for heating water.
  • the application target of the gas cooler 200 is not limited to a water heater, and the gas cooler 200 can be applied to any device including an air conditioner or the like as long as the device performs a heat exchange between the fluids.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP19179799.2A 2018-06-15 2019-06-12 Water heat exchanger and gas cooler Withdrawn EP3581868A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2018114765A JP7199842B2 (ja) 2018-06-15 2018-06-15 水熱交換器、ガスクーラ

Publications (1)

Publication Number Publication Date
EP3581868A1 true EP3581868A1 (en) 2019-12-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19179799.2A Withdrawn EP3581868A1 (en) 2018-06-15 2019-06-12 Water heat exchanger and gas cooler

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EP (1) EP3581868A1 (ja)
JP (1) JP7199842B2 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114111118A (zh) * 2021-11-11 2022-03-01 江苏华洋新思路能源装备股份有限公司 一种热管换热器用空气段冷凝器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021127869A (ja) * 2020-02-14 2021-09-02 株式会社デンソー 熱交換器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB853265A (en) * 1957-02-19 1960-11-02 Egon Runte Improvements in or relating to radiators for space heating
US4815296A (en) * 1988-03-14 1989-03-28 Ormat Turbines (1965), Ltd. Heat exchanger for condensing vapor containing non-condensable gases
JP2006242458A (ja) * 2005-03-02 2006-09-14 Denso Corp 熱交換器と、熱交換器コアおよび熱交換器の製造方法
WO2008105760A2 (en) * 2007-02-27 2008-09-04 Carrier Corporation Multi-channel flat tube evaporator with improved condensate drainage
JP2012021682A (ja) 2010-07-13 2012-02-02 Mitsubishi Electric Corp 熱交換器及びこの熱交換器を搭載したヒートポンプシステム
US20160091231A1 (en) * 2014-09-29 2016-03-31 Hitachi, Ltd. Refrigerant Distributor and Refrigeration Cycle Device Equipped with the Refrigerant Distributor
EP3009767A1 (en) * 2013-06-13 2016-04-20 Mitsubishi Electric Corporation Heat pump device
WO2018025391A1 (ja) * 2016-08-05 2018-02-08 三菱電機株式会社 熱交換器及びその熱交換器を備えた冷凍サイクル装置
CN107990758A (zh) * 2017-11-23 2018-05-04 珠海格力电器股份有限公司 换热器和热泵***

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09250894A (ja) * 1996-03-14 1997-09-22 Calsonic Corp 熱交換器
JP2002181486A (ja) * 2000-12-15 2002-06-26 Denso Corp 熱交換器
JP2002243310A (ja) * 2001-02-19 2002-08-28 Sanden Corp 熱交換器及びこれを用いた冷凍装置
JP2008008584A (ja) * 2006-06-30 2008-01-17 Sharp Corp 熱交換器
JP2008190778A (ja) * 2007-02-05 2008-08-21 Corona Corp 水冷媒熱交換器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB853265A (en) * 1957-02-19 1960-11-02 Egon Runte Improvements in or relating to radiators for space heating
US4815296A (en) * 1988-03-14 1989-03-28 Ormat Turbines (1965), Ltd. Heat exchanger for condensing vapor containing non-condensable gases
JP2006242458A (ja) * 2005-03-02 2006-09-14 Denso Corp 熱交換器と、熱交換器コアおよび熱交換器の製造方法
WO2008105760A2 (en) * 2007-02-27 2008-09-04 Carrier Corporation Multi-channel flat tube evaporator with improved condensate drainage
JP2012021682A (ja) 2010-07-13 2012-02-02 Mitsubishi Electric Corp 熱交換器及びこの熱交換器を搭載したヒートポンプシステム
EP3009767A1 (en) * 2013-06-13 2016-04-20 Mitsubishi Electric Corporation Heat pump device
US20160091231A1 (en) * 2014-09-29 2016-03-31 Hitachi, Ltd. Refrigerant Distributor and Refrigeration Cycle Device Equipped with the Refrigerant Distributor
WO2018025391A1 (ja) * 2016-08-05 2018-02-08 三菱電機株式会社 熱交換器及びその熱交換器を備えた冷凍サイクル装置
CN107990758A (zh) * 2017-11-23 2018-05-04 珠海格力电器股份有限公司 换热器和热泵***

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114111118A (zh) * 2021-11-11 2022-03-01 江苏华洋新思路能源装备股份有限公司 一种热管换热器用空气段冷凝器

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JP7199842B2 (ja) 2023-01-06
JP2019219079A (ja) 2019-12-26

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