EP2937660A1 - Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur - Google Patents

Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur Download PDF

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Publication number
EP2937660A1
EP2937660A1 EP14165808.8A EP14165808A EP2937660A1 EP 2937660 A1 EP2937660 A1 EP 2937660A1 EP 14165808 A EP14165808 A EP 14165808A EP 2937660 A1 EP2937660 A1 EP 2937660A1
Authority
EP
European Patent Office
Prior art keywords
turbulator
coolant
heat
flow
heat transfer
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Withdrawn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
EP14165808.8A
Other languages
German (de)
English (en)
Inventor
Ingolf Hoffmann
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP14165808.8A priority Critical patent/EP2937660A1/fr
Publication of EP2937660A1 publication Critical patent/EP2937660A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation

Definitions

  • the present invention relates to a turbulator for use in a coolant channel of a heat transfer element with an extension along a longitudinal direction, wherein the longitudinal direction when used in the coolant channel coincides with a flow direction of a coolant in the coolant channel.
  • the present invention further relates to a heat transfer element with such a turbulator.
  • a heat transfer from an interface to be cooled to a coolant flowing past a volume flow at the interface takes place essentially only in a flow component directed orthogonally to the interface or with turbulent flow components. With a laminar flow, however, no appreciable heat transfer can take place. Although even with a laminar flow at an interface slight turbulence due to shear and shear forces in the flow, so the possible heat transfer is only small.
  • a desired for a good heat transfer turbulent flow can be achieved for example by a high flow rate of the entire coolant or by using flow barriers that generate turbulence.
  • Flow barriers which are generally called turbulators, ensure local mixing or turbulence of the coolant.
  • flow swirler or mixing tube element can also be found.
  • the power devices are mounted on a cooling plate provided with cooling channels for the coolant.
  • the cooling system connected to the cooling plate usually consists of a pump, a surge tank and a heat exchanger in order to deliver the energy absorbed by the coolant power components to the environment can.
  • the delivery of the energy of the coolant via the heat exchanger can be carried out in such systems either by coolant / water or else by coolant / air heat exchangers.
  • turbulators are introduced into the cooling channels of the cooling plate, which are dimensioned for the largest heat flow of the various bays.
  • the disadvantage here is that associated with known turbulators and available on the market, a high pressure drop, which makes a high drive power required for the coolant flow.
  • the coolant flow is guided and distributed so that areas of the cooling plate, which are acted upon by a high heat flow, a higher, not preheated coolant portion is supplied.
  • the volume flow or the flow velocity of the coolant is selected such that a turbulent flow sets in order to obtain a practical heat resistance.
  • the object of the present invention is to provide a turbulator which can be used in a coolant channel of a cooling plate, which is acted upon at a plurality of bays with different heat flows, and at a high heat transfer effect of the cooling plate on the coolant only a small pressure drop in the coolant channel causes.
  • the object of the present invention is also to provide a simply constructed cooling plate with a coolant channel, which is acted upon at several bays with different heat fluxes and causes only a small pressure drop in the coolant channel at a high heat transfer effect on the coolant.
  • the first object is achieved by a turbulator having the features of patent claim 1.
  • Advantageous embodiments of the turbulator are the subject of the dependent claims 2 to 8.
  • the second-mentioned object is solved by the subject matter of claim 9.
  • the turbulator specified at the outset is designed such that its turbulence effect changes along the longitudinal direction. Since the turbulence effect of the turbulator used or the degree of turbulence of a coolant flow determines the heat absorption of the passing coolant from the boundary surfaces of the coolant channel in a coolant channel, the turbulence effect can be adapted to the heat flow to be transferred to the coolant. It is thus generated in the flow path only as much turbulence, as is necessary for the removal of the locally occurring heat flow. This is different locally with locally Heat flows and at a given total heat flow of the pressure drop generated by the turbulator in the cooling channel minimal.
  • turbulator has a circular extension in a transverse direction oriented transversely to the longitudinal direction.
  • the turbulator is particularly suitable for use in coolant channels with a circular cross-section.
  • a further advantageous embodiment of the turbulator is characterized in that the turbulator has a plurality of turbulator elements arranged one behind the other in the longitudinal direction and that at least two of the turbulator elements have different turbulence effects.
  • the turbulator element with the higher turbulence effect is to be arranged in the region of the coolant channel, from which the higher heat flow has to be dissipated.
  • a further advantageous embodiment is characterized in that the turbulator elements are arranged in succession in at least one first and one second group and that the turbulator elements are the same in each case in the at least first and in the second group.
  • constant turbulence effects which are adapted to the dissipated heat flow, can be generated over a larger area in the flow path.
  • the number of groups of turbulator elements corresponds to the number of different high heat flows that must be dissipated by the cooling plate.
  • the turbulator elements each have the form of a spiral winding and, in particular, different turbulator elements have different slopes. About the slope of the spiral winding can be adjusted easily the required turbulence effect.
  • FIG. 1 shows the part of a liquid cooling, which relates to the heat transfer from a heat transfer element in the form of a cooling plate 2 to a coolant flow.
  • FIG. 1 is shown in a longitudinal section schematically a cooling plate 2 with a coolant channel 4.
  • the coolant channel 4 preferably has a circular cross-section extends in the longitudinal direction through the cooling plate 2.
  • more coolant channels are generally introduced over its width parallel to the illustrated coolant channel.
  • These additional coolant channels are not shown here. They are identical to the one in FIG. 1
  • the cooling plate 2 can therefore be traversed in the longitudinal direction of, for example, six to eight parallel aligned coolant channels.
  • the cooling plate 2 is made of a metal or a metal alloy having a high thermal conductivity or a low thermal resistance, for example, aluminum or copper.
  • the material of the surface of the coolant channels 4 must continue to be compatible with the coolant used.
  • a coolant channel surface made of copper is compatible with water and the most common cooling fluids.
  • Aluminum provides good heat flow performance with an ethylene glycol-water (EGW) blend, oils and other liquids, but it is not compatible with untreated water.
  • a stainless steel coolant channel surface is required when using deionized water or other corrosive liquids.
  • a total of four semiconductor modules 8.1 to 8.4 are arranged in series and attached to the cooling plate 2 with good thermal conductivity.
  • a second surface 10 of the cooling plate 2 which is opposite to the first surface 6, another two semiconductor modules 8.5 and 8.6 are arranged side by side in the longitudinal direction of the cooling plate 2 and also attached to the cooling plate 2 with good thermal conductivity.
  • each semiconductor module 8.1 to 8.6 with a power loss of, for example, up to several kW generates the same amount of heat
  • the cooling plate 2 is loaded at the bays of the semiconductor modules 8.1 to 8.6 with locally different heat fluxes.
  • four different high heat flows or heat loads are found: Starting from the heat flow in the area A occurs in the area B about twice the heat flow. In area C, the heat flow is between the heat flow of areas A and B. Likewise, the heat flow in area D is between that of areas A and B.
  • the coolant channels 4 each end at the end faces 12 and 14 of the cooling plate 2.
  • the coolant then exits at the end face 14 from the cooling plate 2, which is represented by an arrow 18.
  • cooling system such as connected to the cooling plate 2 coolant lines, coolant delivery pumps, expansion tanks and heat exchangers for delivering the heat to the environment are not shown here. These components are known to the person skilled in the art.
  • the heat transfer from the cooling plate 2 to the coolant flowing into the coolant channels 4 takes place essentially by turbulence of the coolant in the coolant channels 4, which are superimposed on the coolant flow from the end face 12 to the end face 14.
  • turbulators 20 are also used in the coolant channels 4, which, however, increase the flow resistance in the coolant channels 4 as a side effect.
  • the turbulator 20 is a component that generates a turbulent flow from a substantially laminar particle or fluid flow. By using the turbulator 20 in the coolant channel 4, the heat transfer coefficient is increased from the cooling plate 2 to the coolant.
  • Turbulators for use in coolant channels 4 are available in various embodiments. Without limitation of generality, a helical wire turbulator is used in the present case.
  • turbulators available on the market have a constant degree of turbulence along their longitudinal axis
  • another technical approach is used in the present case.
  • the starting point is the consideration that an optimum between the required degree of turbulence with a simultaneously low flow resistance results when the turbulence generated by the turbulator 20 or the degree of turbulence of the turbulator 20 is adapted to the dissipated heat flow.
  • the turbulator 20 therefore has, in the flow direction of the coolant, different turbulence levels adapted to the heat flows to be dissipated FIG. 1 merely indicated by different gradients.
  • the turbulator 20 is constructed as a helical wire turbulator with adjoining turbulator elements 21 in the form of spiral windings.
  • the turbulator elements 21 are made of a wire material which is compatible with the coolant used.
  • the wire material is wound around a central axis 22 having a constant coil diameter 24 but at a different pitch.
  • the turbulator 20 is characterized in its longitudinal direction along the central axis 22 by a plurality of, for example four, different regions A 'to D' which correspond to the regions A to D on the cooling plate 2.
  • a first group of spiral coils in the field A 'of the turbulator 20 has, for example, the pitch a.
  • a is meant here a reference pitch, which is for example 20 mm.
  • Starting from the area A ' has a second group of spiral turns in the area B' with about twice the heat load a smaller slope of, for example, 0.35a.
  • the slope is preferably slightly less than half because of the non-linear relationship between slope, degree of turbulence and heat transfer at twice the heat load.
  • the slope in a third group of spiral turns lies between these values, e.g. At 0.4a.
  • the pitch is in a fourth group of spiral windings z. At 0.6a.
  • each group includes a plurality of turbulator elements 21 or spiral windings.
  • the individual groups A 'to D' are arranged directly next to one another.
  • FIG. 3 shows by way of example the thermal resistance Rth between the cooling plate 2 and the coolant at the various mounting locations of the semiconductor modules 8.1 to 8.4.
  • a curve 30 connects the thermal resistance Rth at the individual slots with inserted into the coolant channels 4 conventional turbulators 20, over the entire length of a constant slope of z. B. about 0.23a have.
  • a curve 32 connects the thermal resistances Rth at the installation locations when using turbulators 20 adapted to the heat load according to FIG FIG. 2 , In both cases, a low thermal resistance of 12 K / kW to 14 K / kW required for cooling can be achieved at the bays.
  • this ratio is shown with a variation of the slope in the area B '.
  • area B ' the highest heat flow must be dissipated. If a slope of 0.25a is selected in the area B ', it is possible to dissipate approximately 500 watts of power loss per watt drive power, see point 36 in FIG. 4 , With a slope of the turbulator 20 in the region B of 0.3a, approximately 530 watts of power dissipation per watt drive power can be dissipated, see point 38 in FIG FIG. 4 , With a slope of 0.35a, 560 watts of power dissipation per watt drive power can be dissipated, see point 40 in FIG. 4 ,
  • a turbulator 20 for use in a coolant channel 4 of a heat transfer element has an extension along a longitudinal direction.
  • the longitudinal direction coincides with a flow direction of a coolant in the coolant channel 4.
  • the Turbulator 20 is designed such that its turbulence effect changes along the longitudinal direction.
  • a heat transfer element has a turbulator 20 arranged in a coolant channel 4.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
EP14165808.8A 2014-04-24 2014-04-24 Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur Withdrawn EP2937660A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14165808.8A EP2937660A1 (fr) 2014-04-24 2014-04-24 Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14165808.8A EP2937660A1 (fr) 2014-04-24 2014-04-24 Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur

Publications (1)

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EP2937660A1 true EP2937660A1 (fr) 2015-10-28

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EP14165808.8A Withdrawn EP2937660A1 (fr) 2014-04-24 2014-04-24 Turbulateur destiné à l'utilisation dans un canal de réfrigérant et élément de transfert thermique doté d'un tel turbulateur

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10294855B2 (en) * 2017-04-25 2019-05-21 GM Global Technology Operations LLC Transitional turbulator
US20220082298A1 (en) * 2020-09-11 2022-03-17 Kyungdong Navien Co., Ltd. Water heating device and method for manufacturing smoke tube for water heating device
EP4398270A4 (fr) * 2021-09-02 2025-01-01 Changchun Jetty Automotive Technology Co., Ltd. Système de transmission d'énergie électrique pour véhicule, et appareil de charge et véhicule électrique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6301109B1 (en) * 2000-02-11 2001-10-09 International Business Machines Corporation Isothermal heat sink with cross-flow openings between channels
US20120192812A1 (en) * 2011-01-28 2012-08-02 Rahmani Ramin K Water heater with counter-twisted baffle
DE102012208742A1 (de) * 2012-03-28 2013-10-02 Mahle International Gmbh Abgaskühler

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6301109B1 (en) * 2000-02-11 2001-10-09 International Business Machines Corporation Isothermal heat sink with cross-flow openings between channels
US20120192812A1 (en) * 2011-01-28 2012-08-02 Rahmani Ramin K Water heater with counter-twisted baffle
DE102012208742A1 (de) * 2012-03-28 2013-10-02 Mahle International Gmbh Abgaskühler

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10294855B2 (en) * 2017-04-25 2019-05-21 GM Global Technology Operations LLC Transitional turbulator
US20220082298A1 (en) * 2020-09-11 2022-03-17 Kyungdong Navien Co., Ltd. Water heating device and method for manufacturing smoke tube for water heating device
EP4398270A4 (fr) * 2021-09-02 2025-01-01 Changchun Jetty Automotive Technology Co., Ltd. Système de transmission d'énergie électrique pour véhicule, et appareil de charge et véhicule électrique

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