EP2795638B1 - Radiateur de refroidissement à refroidissement par liquide - Google Patents

Radiateur de refroidissement à refroidissement par liquide Download PDF

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Publication number
EP2795638B1
EP2795638B1 EP12812867.5A EP12812867A EP2795638B1 EP 2795638 B1 EP2795638 B1 EP 2795638B1 EP 12812867 A EP12812867 A EP 12812867A EP 2795638 B1 EP2795638 B1 EP 2795638B1
Authority
EP
European Patent Office
Prior art keywords
cooling radiator
sub
cooling
pipes
modules
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.)
Not-in-force
Application number
EP12812867.5A
Other languages
German (de)
English (en)
Other versions
EP2795638A1 (fr
Inventor
Otto Karl GROß
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.)
Schmehmann Rohrverformungstechnik GmbH
Original Assignee
Schmehmann Rohrverformungstechnik GmbH
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 Schmehmann Rohrverformungstechnik GmbH filed Critical Schmehmann Rohrverformungstechnik GmbH
Priority to SI201230612A priority Critical patent/SI2795638T1/sl
Priority to RS20160346A priority patent/RS54767B1/sr
Publication of EP2795638A1 publication Critical patent/EP2795638A1/fr
Application granted granted Critical
Publication of EP2795638B1 publication Critical patent/EP2795638B1/fr
Priority to HRP20160564TT priority patent/HRP20160564T1/hr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F27/00—Details of transformers or inductances, in general
    • H01F27/08—Cooling; Ventilating
    • H01F27/10—Liquid cooling
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F27/00—Details of transformers or inductances, in general
    • H01F27/08—Cooling; Ventilating
    • H01F27/085—Cooling by ambient air

Definitions

  • the invention relates to aderadiator, in particular aderadiator a boiler of a transformer active part, wherein thederadiator with the heated by the active part cooling liquid by gravity from above via a collection or.
  • Distributor tube, a so-called collector, down to a sub-distributor or collector, a so-called lower collector, flowing through cooling elements is formed, wherein the cooled liquid passes through the sub-manifold back into the transformer and wherein at least onederadiator removed from or directly on Transformer or its boiler is arranged.
  • Cooling radiators of this type comprise in addition to the upper and the lower collector at least a sub-module of cooling elements, which are connected via respective individual manifolds to the upper and lower collector, wherein the sub-modules have tubes which are provided on their outer side with ribs.
  • the cooling elements of transformers or other electrical equipment consist of flat, usually traversed by oil as a cooling liquid cooling elements or a corrugated metal sheet, as by the DE 10 2009 015 377 A known become.
  • the cooling radiators consisting of a plurality of such assembled or arranged on / behind each other cooling elements are designed as a welded construction. To increase the service life, they are painted by expensive dives or hot-dip galvanized.
  • the production is to be simplified at the same time gas or oil-tight connection of the cooling elements with the collectors and in particular the heat transfer and the heat transfer can be improved.
  • the sub-modules are arranged perpendicularly and transversely to the longitudinal direction of the collectors, wherein the tubes of the sub-modules for air passage are arranged parallel to one another at a distance from one another.
  • aderadiator is created, which consists of several in a row successively and successively and with an air gap to each other, inserted into openings of the upper header and the sub collector, a particularly good air passage through thederadiator total and allowed at the respective cooling elements.
  • all of the cooling elements of the cooling radiator preferably carry the heat transfer from the cooling medium flowing through the cooling radiator, preferably oil, into the ambient air flowing through the cooling radiator.
  • a particularly high energy dissipation of up to 38.00 kW / h, preferably up to 39.80 kW / h with aderadiator having a width of up to 540 mm, preferably up to 520 mm, and a height of up to 2 m, preferably up to 1.80 m causes.
  • a doctorradiator with a height of 0.5 m up to 3.60 m.
  • a flow rate of oil through thederadiator of up to 2 700 kg / h, preferably up to 2 800 kg / h, can be achieved.
  • the liquid passing through the pipes from top to bottom with the best cooling effect, in particular oil experiences the least resistance, if an optimized cross section of the elements of the cooling radiator is maintained. Since only minimal resistance occurs, the system can operate in free convection; no pumps are required.
  • Thederadiator thus exists as a compact complete unit, which consists of many desired, spaced apart, connected via the individual distribution pipes to the collector submodules.
  • the completederadiator or its sub-modules can be completely flowed around in both the transverse and in the longitudinal direction of the ambient air, possibly supported by fans / fans. The cooling or heat removal / heat transfer is thereby kept very efficient.
  • tubes and also the collector, preferably the upper and the lower collector, as well as the individual distribution pipes consist of a processable by extrusion material or material, such as in particular aluminum or aluminum alloys, magnesium or the like for extruding suitable light metals.
  • these materials have good heat transfer properties and, on the other hand, are resistant to corrosion by forming oxide layers, so that coating or similar coating or surface treatment can be dispensed with, and moreover can be easily produced, namely preferably by extrusion with the desired, arbitrary geometry.
  • the openings required for the connection of the individual components of the cooling radiator are preferably produced precisely by milling or laser machining, so that exact joints for microfluidization can be achieved by preferably laser welding with gas or oil-tight connection.
  • each sub-module comprises up to 12, preferably up to 10 tubes.
  • a cooling radiator is provided, the effective surface of which can be adapted to the required properties of the cooling radiator by means of particularly simple means and, if appropriate, can be completely adapted to be flowed around by the ambient air.
  • the tubes of the respective sub-modules have a flattened, preferably rectangular cross-section, in particular a rectangular cross-section with rounded corners. It is particularly preferred if such tubes have at least one inner web, preferably two inner webs.
  • the width of the tubes is preferably up to 130 mm, preferably up to 120 mm.
  • the distance of the tubes from one another per sub-module is up to 30 mm, preferably up to 27 mm.
  • the ribs provided on the outside of the tubes are longitudinal ribs which preferably extend over the entire length of the tubes, thus substantially over the entire length of the cooling radiator as a whole. It is particularly preferred if up to 15, most preferably up to 12, longitudinal ribs per tube are provided. In this context, it is particularly preferred if the longitudinal ribs have a height, thus an extent from the outside of the tube to the outside, of up to 15 mm, preferably up to 12 mm.
  • the distance between the longitudinal ribs to each other should be up to 25 mm, preferably up to 20 mm, to thereby ensure not only an effective surface for thederadiator with a large heat radiation, but at the same time the transition of heat from the cooling medium in the cooling radiator around and to optimize the flow of ambient air.
  • submodules are provided inderadiator. These sub-modules, which are connected to each other via an upper and a lower single distribution pipe, thus offer a particularly large effective area with a compact design ofderadiators.
  • At least the upper collector preferably also the lower collector, has a rectangular cross-section, preferably with a dimension of 20 ⁇ 80 mm cross-sectional area.
  • at least the upper header preferably both the upper and the lower header, are arranged at one end of the individual distribution pipes and thus do not hinder the air flow flowing along, in particular, from bottom to top through the cooling modules along the submodules. Only by the arrangement of the upper collector away from the middle of the individual manifolds on the end towards could be achieved by 38% improved air access to theméradiator and air leakage from thederadiator.
  • a preferred embodiment provides a prefabricated construction of thederadiators, in which the upper and lower collectors are arranged in a longitudinal extension and seen over their length at a distance lying behind each other have any number of openings, in oval tubes as a cooling element according to form-fitting, transverse to Longitudinal slotted holes provided.
  • the cooling elements are a sub-module in openings of connected to the upper and lower collector manifolds, these have as advantageous and the collector a rectangular or square format inserted.
  • the existing from the upper and lower manifolds with the inserted cooling elements sub-modules are connected with their individual distribution pipes transversely to the collectors and connected with one of their openings in fluid communication with an opening of the collector standing oil-tight with the collectors, preferably laser welded, in such a way that the collectors bridge the sub-modules arranged transversely thereto, either centrally or preferably offset to the side and towards the ends of the individual distribution pipes.
  • FIG. 1 shows a front view of a completely prefabricated, prepared for installation or removal on a transformerderadiator 1.
  • Thederadiator 1 comprises an upper manifold 2 and a lower manifold 3, which are connected via respective flanges 2a, 3a with the transformer (not shown) can to form a closed oil circuit with the transformer can.
  • a plurality of sub-modules 4 are connected, each extending perpendicularly and transversely to the longitudinal direction of the manifolds 2, 3 in the plane of the drawing.
  • the sub-modules 4 are in turn assigned to individual distribution pipes 5, the liquid-tight with the manifolds 2, 3 and the tubes of the sub-modules 4 are connected, so as to ensure the passage of the cooling medium such as oil through the entirederadiator 1 therethrough.
  • sensors 20, 21 are connected to the upper header 2 and the lower header 3, respectively, to receive both the passage amount and the entrance and exit temperature of the cooling medium through the cooling radiator 1.
  • FIG. 2 shows thederadiator 1 from FIG. 1 seen in a side view from the right and thus gives the front or first sub-module 4 to recognize.
  • FIG. 1 From the synopsis of Figures 1 and 2 can be seen that thederadiator 1 and its sub-modules 4 and in the embodiment executed as an oval tubes 6 elements (see FIG. 6 ) can be completely surrounded by the ambient air. The towards the top arrow of the FIG. 1 The heated coolant (oil) flowing in from the consumer is thereby cooled particularly effectively on its way down.
  • Thederadiator 1 can be connected to the consumer, possibly with the interposition of pipes, via flanges 2a, 3a of the collector 2, 3.
  • FIG. 3 shows thederadiator 1 from the Figures 1 and 2 in a view from above.
  • the sub-modules 4 with the inserted into the individual manifolds 5 cooling elements are arranged transversely and perpendicular to the upper collector 2 and are bridged by the collector 2 in the middle of the sub-modules 4 lying.
  • the submodules 4 each consist of five tubes 6 with a substantially rectangular cross section connected via a common single distribution tube 5.
  • a distance 22 for the passage of cooling air through the respective sub-modules 4 is provided between the tubes 6.
  • FIG. 4 shows as a single unit a single distribution pipe 5 seen from its openings 23 having side.
  • FIG. 5 shows as a single unit a collector 2 seen from the openings 24 side having seen. About the openings 24, the connection and gas- or liquid-tight welding of the upper header 2 (not shown) with individual manifolds. 5 takes place.
  • FIG. 6 shows a cross section through a tube 6 having a substantially rectangular cross-section and rounded corners.
  • a tube 6 having a substantially rectangular cross-section and rounded corners.
  • longitudinal ribs 7 are arranged over which the effective surface of the tube 6, thus the contact surface of the tube 6 with the surrounding air around the pipe 6, is significantly increased.
  • an inner web 8 is also provided within the tube 6.
  • FIG. 7 shows a second embodiment of a pipe 6 according to the invention as part of a submodule of aderadators invention.
  • the tube 6 in turn has a substantially rectangular cross section with rounded corners, wherein on each longitudinal side of the tube 6 cooling fins 7 are arranged at the same distance from each other.
  • the height of the ribs 7, thus their extent from the outside of the tube 6 to the outside, is the same over the entire circumference of the tube 6, to thereby provide consistent heat transfer conditions over the pipe 6 away.
  • inner webs 8a, 8b are provided, which extend over the entire length of the tube 6.
  • FIG. 8 an overall perspective view of a cooling radiator 1 according to the invention in a view from top to bottom.
  • Thederadiator 1 has an upper manifold 2 and a lower manifold 3, with which eight individual manifolds 5 are connected. These individual distribution pipes 5 in turn are connected to seven pipes 6, over the entire length of which longitudinal ribs 7 extend.
  • both the upper header 2 and the lower header 3 from the central arrangement of the individual distribution pipes 5 (see. Fig. 3 ) arranged offset to the end regions of the individual distribution pipes 5.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Transformer Cooling (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Claims (17)

  1. Radiateur de refroidisseur (1), comprenant un collecteur supérieur (2) et un collecteur inférieur (3) ainsi qu'au moins un sous-module (4) composé d'éléments de refroidissement, qui sont reliés par l'intermédiaire de tuyaux de distribution individuels (5) respectifs avec le collecteur supérieur (2), respectivement inférieur (3), dans lequel les sous-modules (4) présentent des tuyaux (6), qui sont pourvus sur leur côté extérieur respectif de nervures (7),
    caractérisé en ce que
    les sous-modules (4) sont disposés perpendiculairement et transversalement à la direction longitudinale du collecteur (2, 3) et en ce que les tuyaux (6) des sous-modules (4) sont disposés pour le passage de l'air avec un espacement (22) parallèlement les uns aux autres.
  2. Radiateur de refroidissement (1) selon la revendication 1, caractérisé en ce que au moins les tuyaux (6) des sous-modules (4) sont constitués d'aluminium ou d'un alliage d'aluminium.
  3. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que chaque sous-module (4) comprend jusqu'à 12, de préférence jusqu'à 10 tuyaux (6).
  4. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que les tuyaux (6) des sous-modules (4) présentent une section transversale aplatie, de préférence rectangulaire, notamment avec des coins arrondis.
  5. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que les tuyaux (6) présentent au moins un gradin intérieur (8), de préférence deux gradins intérieurs (8).
  6. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que la largeur des tuyaux (6) s'élève à 130 mm, de préférence 120 mm.
  7. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que l'espacement des tuyaux (6) par sous-module (4) s'élève à 30 mm, de préférence jusqu'à 27 mm.
  8. Radiateur de refroidissement (1) selon une des revendications précédents, caractérisé en ce que les tuyaux (6) présentent des nervures longitudinales (7), de préférence jusqu'à 15, de manière particulièrement préférée jusqu'à 12 nervures longitudinales (7).
  9. Radiateur de refroidissement (1) selon la revendication 8, caractérisé en ce que les nervures longitudinales (7) présentent une hauteur allant jusqu'à 15 mm, de préférence jusqu'à 12 mm.
  10. Radiateur de refroidissement (1) selon une des revendications 8 ou 9, caractérisé en ce que l'espacement des nervures longitudinales (7) l'une par rapport à l'autre s'élève à 25 mm, de préférence à 20 mm.
  11. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que jusqu'à 10, de préférence jusqu'à 8 sous-modules (4), sont prévus dans le radiateur de refroidissement (1).
  12. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que la largeur du radiateur de refroidissement (1) s'élève à 540 mm, de préférence à 520 mm.
  13. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que la hauteur du radiateur de refroidissement (1) est comprise entre 0,5 m et 3,60 m, de préférence s'élève à 2,00 m.
  14. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que le débit d'huile à travers le radiateur de refroidissement s'élève à 2700 kg/h, de préférence à 2800 kg/h.
  15. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que les rejets thermiques à travers le radiateur de refroidissement (1) s'élèvent à 38,00 kW/h, de préférence à 39,8 kW/h.
  16. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que au moins le collecteur supérieur (2) présente une section transversale rectangulaire, de préférence avec une dimension de 20 x 80 mm.
  17. Radiateur de refroidissement (1) selon une des revendications précédentes, caractérisé en ce que au moins le collecteur supérieur (2), de préférence tant le collecteur supérieur que le collecteur inférieur (3), sont disposés sur une extrémité des tuyaux de distribution individuels (5).
EP12812867.5A 2011-12-23 2012-12-21 Radiateur de refroidissement à refroidissement par liquide Not-in-force EP2795638B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
SI201230612A SI2795638T1 (sl) 2011-12-23 2012-12-21 Hladilni radiator s hlajenjem tekočine
RS20160346A RS54767B1 (sr) 2011-12-23 2012-12-21 Radijator za hlađenje sa tečnim hlađenjem
HRP20160564TT HRP20160564T1 (hr) 2011-12-23 2016-05-25 Hladnjak za hlađenje koji ima hlađenje tekućinom

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011122317 2011-12-23
PCT/EP2012/005336 WO2013091890A1 (fr) 2011-12-23 2012-12-21 Radiateur de refroidissement à refroidissement par liquide

Publications (2)

Publication Number Publication Date
EP2795638A1 EP2795638A1 (fr) 2014-10-29
EP2795638B1 true EP2795638B1 (fr) 2016-03-23

Family

ID=47522464

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12812867.5A Not-in-force EP2795638B1 (fr) 2011-12-23 2012-12-21 Radiateur de refroidissement à refroidissement par liquide

Country Status (14)

Country Link
US (1) US20140318750A1 (fr)
EP (1) EP2795638B1 (fr)
CN (1) CN104145316A (fr)
ES (1) ES2569729T3 (fr)
HR (1) HRP20160564T1 (fr)
HU (1) HUE029246T2 (fr)
MX (1) MX343019B (fr)
PL (1) PL2795638T3 (fr)
PT (1) PT2795638T (fr)
RS (1) RS54767B1 (fr)
RU (1) RU2625324C2 (fr)
SI (1) SI2795638T1 (fr)
UA (1) UA110292C2 (fr)
WO (1) WO2013091890A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108447657B (zh) * 2018-03-08 2024-03-12 株洲联诚集团控股股份有限公司 顶置多路进风并联散热的动车组牵引变压器冷却装置
CN113284708B (zh) * 2021-04-09 2022-10-18 国网四川省电力公司电力科学研究院 具有三维离散扩展表面的电力变压器油散热系统
JP7501954B1 (ja) 2024-03-29 2024-06-18 株式会社シアーコーポレーション 冷暖房システム

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US3016230A (en) * 1959-03-30 1962-01-09 Gen Electric Heat exchange assembly
US5252778A (en) * 1991-02-22 1993-10-12 Kabushiki Kaisha Toshiba Gas-insulated electric apparatus
FR2693546B1 (fr) * 1992-07-09 1994-09-30 Valeo Thermique Moteur Sa Echangeur de chaleur à faisceau de tubes parallèles, en particulier pour véhicule automobile.
CA2159363A1 (fr) * 1993-03-29 1994-10-13 Milne Jurisich Echangeur de chaleur
US5490559A (en) * 1994-07-20 1996-02-13 Dinulescu; Horia A. Heat exchanger with finned partition walls
CA2260890A1 (fr) * 1999-02-05 2000-08-05 Long Manufacturing Ltd. Echangeurs de chaleur fermes
JP4300628B2 (ja) * 1999-03-30 2009-07-22 株式会社デンソー 熱交換器
US6575227B1 (en) * 1999-10-26 2003-06-10 Duramax Marine, Llc Heat exchanger
CN1416580A (zh) * 2000-02-24 2003-05-07 尤尼芬国际公司 冷却变压器的系统和方法
CN2580574Y (zh) * 2002-11-18 2003-10-15 孙艺夫 一种变压器散热器
US7032808B2 (en) * 2003-10-06 2006-04-25 Outokumu Oyj Thermal spray application of brazing material for manufacture of heat transfer devices
US7770544B2 (en) * 2004-12-01 2010-08-10 Victory Energy Operations LLC Heat recovery steam generator
KR100773027B1 (ko) * 2006-11-07 2007-11-02 권오경 변압기용 방열기
RU2332818C1 (ru) * 2007-02-01 2008-08-27 Общество с ограниченной ответственностью "Теркон КТТ" Охлаждающее устройство для элементов электроники
CN201247672Y (zh) * 2008-07-11 2009-05-27 沈阳沈变所电气科技有限公司 电力变压器用高效铝合金片式散热器

Also Published As

Publication number Publication date
ES2569729T3 (es) 2016-05-12
HUE029246T2 (en) 2017-02-28
US20140318750A1 (en) 2014-10-30
PT2795638T (pt) 2016-07-07
EP2795638A1 (fr) 2014-10-29
RU2014130286A (ru) 2016-02-20
WO2013091890A1 (fr) 2013-06-27
HRP20160564T1 (hr) 2016-06-17
CN104145316A (zh) 2014-11-12
MX2014007701A (es) 2014-08-21
PL2795638T3 (pl) 2016-09-30
SI2795638T1 (sl) 2016-07-29
RU2625324C2 (ru) 2017-07-13
RS54767B1 (sr) 2016-10-31
UA110292C2 (uk) 2015-12-10
MX343019B (es) 2016-10-21

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