EP4198431A1 - Réservoir de liquide stationnaire - Google Patents

Réservoir de liquide stationnaire Download PDF

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Publication number
EP4198431A1
EP4198431A1 EP22197974.3A EP22197974A EP4198431A1 EP 4198431 A1 EP4198431 A1 EP 4198431A1 EP 22197974 A EP22197974 A EP 22197974A EP 4198431 A1 EP4198431 A1 EP 4198431A1
Authority
EP
European Patent Office
Prior art keywords
liquid tank
flat tube
stationary liquid
distribution plate
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22197974.3A
Other languages
German (de)
English (en)
Inventor
Martin Sievers
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.)
Mahle International GmbH
Original Assignee
Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP4198431A1 publication Critical patent/EP4198431A1/fr
Pending 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
    • F28D1/06—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 the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0078—Heat exchanger arrangements
    • 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
    • F28F2013/005—Thermal joints
    • F28F2013/006—Heat conductive materials

Definitions

  • the present invention relates to a stationary liquid tank.
  • the invention also relates to a heat pump system with such a stationary liquid tank.
  • the refrigerant charge is limited by various standards.
  • the limitation of the filling quantity also poses a challenge here.
  • a heat exchanger or a temperature control device for heating the process water tank is wrapped around it.
  • assembly, integration and replacement in the event of a defect are simpler than if the heat exchanger or the temperature control device is arranged in the water tank.
  • direct contact of the (drinking) water with the heat exchanger and thus contamination of the drinking water in the water tank by substances from the heat exchanger is ruled out.
  • contamination of the drinking water is also ruled out, as this escapes into the environment.
  • the flat tubes used with internal channels and webs arranged in between are designed in such a way that you just keep to the bursting pressures P BERST,MIN required by the applicable standard, thereby enabling a material-saving flat tube design.
  • thermal resistance of enamel and thermal interface layer can be increased by increasing the Reduce thermal conductivity, reduce the layer thickness and increase the cross-sectional area.
  • the layer thickness is usually as thin as possible for the application.
  • the present invention is therefore concerned with the problem of further developing a stationary liquid tank with a temperature control device in such a way that an increased heat transfer between a flat tube of a temperature control device and the stationary liquid tank is made possible.
  • the present invention is based on the general idea of achieving heat transfer between a flat tube of a temperature control device of a stationary liquid tank and the liquid tank by enlarging a heat transfer surface without increasing the refrigerant volume. According to the invention, this is made possible by two alternative embodiments, namely on the one hand by arranging a heat distribution plate between the flat tube and the liquid tank and on the other hand by integrating such a heat distribution plate into the flat tube by means of a corresponding different geometric cross-sectional shape of the flat tube.
  • the stationary liquid tank according to the invention has a temperature control device for temperature control of the liquid in the liquid tank, which is used both for heating as well as for cooling the liquid stored in the liquid tank.
  • the temperature control device which represents a heat exchanger, has at least one flat tube externally connected to the liquid tank in a heat-transferring manner, with internal channels with a respective channel width b K and webs with a respective web width b S .
  • the flat tube is made from a material with a tensile strength R m and has a bursting pressure P BERST,IST .
  • P BERST,MIN is the bursting pressure required by the standard/specification.
  • the bursting pressure P BERST,IST of the flat tube must be higher.
  • the previously described heat distribution plate is arranged between the flat tube and the liquid tank and is connected over the entire surface to the flat tube and the liquid tank.
  • the heat distribution plate has a high thermal conductivity compared to, for example, a thermally conductive layer and is made of aluminum, for example. It distributes a heat flow from the area in contact with the flat tube to a larger area, whereby the heat flow on this larger area is conducted through the heat conducting layer, which can be arranged between the heat distribution plate and the liquid tank, an enamel coating of the liquid tank and the steel of the liquid tank becomes.
  • the thermally conductive layer has a thermal conductivity that is significantly lower than that of the flat tube material and/or the heat distribution plate. This enlarged area is also effective for the heat transfer on an inside.
  • a wall of the liquid tank usually consists of a steel core and an internal and external enamel coating.
  • the flat tube with its channels and webs is designed in such a way that it satisfies the following equation: 1.2 b K + tolerance / b S ⁇ tolerance ⁇ R m / P BURST , MIN
  • the web width bs is increased with the same channel size, which consequently also increases the external dimensions of the flat tube and thus the contact surface between the flat tube and the stationary liquid tank.
  • the flat tube design according to the invention and the resulting flat tube design differs from previous flat tube designs in that the webs between the individual channels are so solid that they can withstand a significantly higher bursting pressure P BERST,IST than is required by the applicable standard, for example.
  • the flat tube wall thickness has not changed compared to the previous design. Experiments and calculations have shown that this embodiment is particularly advantageous if the lower tolerance limit of the web width is at least 20% greater than is necessary to achieve the required bursting pressure P BERST,MIN .
  • the stationary liquid tank according to the invention offers the possibility of significantly improved heat transfer compared to previous liquid tanks due to the increased heat transfer surface area on the container circumference while at the same time the internal volume of the flat tubes remains the same.
  • the second alternative embodiment also offers the great advantage of relatively short thermal conduction paths and thus a higher heat transfer rate.
  • the overall use of materials is lower, the assembly forces with which the heat exchanger is clamped around the liquid tank are lower.
  • production is simpler since there are no material connection between the flat tube and the heat distribution plate must be made and positioning of the heat conducting plate relative to the flat tubes when joining, for example by soldering, is eliminated.
  • the heat distribution plate is connected to an outside of the liquid tank via a thermally conductive layer.
  • the heat distribution plate also has a thermal conductivity ⁇ V and a thickness dv, while the thermally conductive layer has a thermal conductivity ⁇ W and a thickness dw.
  • at least two flat tubes are wound in parallel around the stationary liquid tank, with a distance s between two flat tubes.
  • a liquid tank according to the invention expediently has a heat distribution plate which is soldered to the flat tube. Soldering between the heat distribution plate and the flat tube offers an optimized heat transfer connection with an extremely short heat conduction path at the same time. In addition, solder has a significantly improved thermal conductivity compared to a thermally conductive paste (thermally conductive layer), which enables almost unhindered heat transfer between the flat tube and the heat distribution plate.
  • the flat tube has insulation on an outside facing away from the stationary liquid tank. Heat dissipation or absorption from the environment can at least be reduced via such insulation, as a result of which the efficiency of the temperature control device can be significantly increased.
  • insulation can be provided, for example, by means of a corresponding plastic coating or a type of housing, in particular made of plastic or mineral wool.
  • the temperature control device expediently has a refrigerant circuit, with the flat tube(s) forming part of the refrigerant circuit.
  • the Refrigerant which theoretically can also be a coolant, temperature control, in particular heating of the contents of the stationary liquid tank, can take place.
  • the flat tube is designed as an extruded profile or as a welded tube.
  • the design as an extruded profile for example made of aluminum, offers the great possibility of not only producing the flat tube in a high quality, but also cost-effectively. Extruded profiles of this type can also produce almost any desired cross-sectional shape using appropriate matrices.
  • the liquid tank expediently has a steel core and an internal and an external enamel coating.
  • hygienic storage of liquid in the liquid tank for example drinking water, can be ensured via the enamel coating.
  • the present invention is also based on the general idea of operating the flat tube described as part of a heat pump circuit, via which the liquid container is heated.
  • a liquid reservoir offers the advantage that temperature-controlled liquid, for example hot water, can be stored for peak demand and the heat pump system only has to be dimensioned in such a way that it heats the storage volume to the desired temperature over a longer period of time.
  • contamination of the liquid tank with refrigerant or coolant is ruled out, since a leak would escape into the environment through the double wall in the form of the flat tube wall and the container wall.
  • a stationary liquid tank 1 has a temperature control device 2 for temperature control of a liquid 3, for example water 4, in the liquid tank 1.
  • the temperature control device 2 has at least one, preferably several, flat tubes 5 with channels 6, which are connected externally to the liquid tank 1 in a heat-transferring manner and each have a channel width b K (cf. 3 ) exhibit.
  • the channels 6 are separated by webs 7 arranged between them, each having a web width bs.
  • the flat tube 5 or the flat tubes 5 consist of a material, for example aluminum, with a tensile strength R m and a bursting pressure P BERST,IST .
  • the bursting pressure results from the tensile strength of the material and the chosen geometry of the flat tube.
  • P BERST,IST is the bursting pressure that the flat tube 5 reaches.
  • the flat tubes 5 each open at the longitudinal end into collectors 8 which are clamped against the stationary liquid tank 1 by a clamping device 9 .
  • a heat-transferring surface is provided between the temperature control device 2 and the liquid tank 1 to enlarge.
  • a heat distribution plate 10 is arranged between the flat tubes 5 and the liquid tank 1, which is flatly connected to the flat tubes 5 on the one hand and the liquid tank 1 on the other (cf. 1 and 4 ).
  • Such a heat distribution plate 10 which is in particular soldered to the flat tubes 5 and thereby ensures a high level of heat transfer from them, can create a thermal conductivity that is significantly greater than that of a thermally conductive layer 11.
  • the heat-conducting plate 10 distributes the heat flow introduced from a contact surface with the flat tubes 5 over a significantly larger area, as a result of which the heat flow is conducted through the heat-conducting layer 11 and a wall of the liquid tank 1 on this larger surface.
  • a wall of the liquid tank 1 can consist, for example, of a steel core 12 and an internal and/or external enamel coating 13 (cf. 4 ). Due to the larger heat-transferring surface of the heat distribution plate 10, an improved and increased heat transfer to the inside of the wall can also be achieved.
  • the heat distribution plate 10 is preferably connected to an outside of the liquid tank 1 via the previously described thermally conductive layer 11 and has a thermal conductivity ⁇ V and a thickness d V (cf. 4 ).
  • the thermally conductive layer 11 in turn has a thermal conductivity ⁇ W and a thickness dw.
  • the temperature control device 1 Considering the temperature control device 1 according to the 1 4 to 5, it can be seen that several flat tubes 5 are arranged parallel to one another and wind around the stationary liquid tank 1.
  • the at least two flat tubes 5 of the temperature control device 2 have a distance s between them (cf. Figures 1 and 2 ) and are preferably arranged in such a way that applies: (0.25 ⁇ V d V / s) ⁇ ( ⁇ W s / d W ) ⁇ (4 ⁇ V d V / s), particularly preferably: (0.5 ⁇ V dV /s) ⁇ ( ⁇ W s/dw) ⁇ (2 ⁇ V dV /s).
  • the flat tubes 5 with the channels 6 and the webs 7 are designed in such a way that they fulfill the following equation: 1.2 b K + tolerance / b S ⁇ tolerance ⁇ R m / P BURST , IS
  • the web width bs in the respective flat tube 5 is increased with the same channel size, which increases the external dimensions of the respective flat tube 5 and thus also a contact surface between the flat tube 5 and the liquid tank 1 available for heat transfer.
  • the resulting flat tube design deviates from previous designs in that the webs 7 between the individual channels 6 are made so solid that they can withstand a significantly higher bursting pressure P BERST,IST than the bursting pressure P BERST,MIN required by the applicable standard . This design becomes interesting if the bursting pressure P BERST,MIN required for the application can be exceeded by 20% by means of a corresponding design of the web width bs and the channel width b K .
  • the channels 6 themselves can have a square cross-section, as in accordance with the Figures 1 to 4 is shown, and theoretically they can also have a rectangular, non-square or round cross-section.
  • an additional insulation 14 for example a polystyrene shell, can be provided on the flat tubes 5 on an outside facing away from the stationary liquid tank 1 (cf. 1 ).
  • the temperature control device 2 can also have a refrigerant circuit, with the flat tubes 5 representing part of this refrigerant circuit.
  • the temperature control device 2 it is of course also conceivable for the temperature control device 2 to have a coolant circuit, with the flat tubes 5 forming part of the coolant circuit in this case.
  • the flat tubes 5 can be designed as extruded profiles, in particular as aluminum extruded profiles, or alternatively as welded tubes.
  • the design as aluminum extruded profiles allows almost any design of the channels 6 and the webs 7 arranged between them.
  • the stationary liquid tank 1 can be part of a heat pump system 15, for example. Overall, with the temperature control device 2 according to the invention and the stationary liquid tank 1 according to the invention, a significantly improved temperature control of the liquid 3 can be achieved with the (internal) volume of the flat tubes 5 remaining the same.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP22197974.3A 2021-12-15 2022-09-27 Réservoir de liquide stationnaire Pending EP4198431A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021214440.3A DE102021214440A1 (de) 2021-12-15 2021-12-15 Stationärer Flüssigkeitstank

Publications (1)

Publication Number Publication Date
EP4198431A1 true EP4198431A1 (fr) 2023-06-21

Family

ID=83506638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22197974.3A Pending EP4198431A1 (fr) 2021-12-15 2022-09-27 Réservoir de liquide stationnaire

Country Status (2)

Country Link
EP (1) EP4198431A1 (fr)
DE (1) DE102021214440A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003036178A1 (fr) * 2001-10-22 2003-05-01 Rheem Australia Pty Limited Chauffe-eau ameliore a pompe a chaleur
AU2010201827A1 (en) * 2009-05-15 2010-12-02 Peter Sachs Industries Pty Ltd An Improved Hot Water Tank
CN105783552A (zh) * 2016-05-11 2016-07-20 珠海格力电器股份有限公司 热水器及其换热器总成
FR3073274A1 (fr) * 2017-11-06 2019-05-10 Emile Ivars Paul Dispositif de production d'eau chaude sanitaire et de chauffage/rafraichissement
CN112856817A (zh) * 2021-03-23 2021-05-28 格力电器（武汉）有限公司 一种热水器
CN112902445A (zh) * 2021-01-21 2021-06-04 珠海格力电器股份有限公司 水箱及其制备方法和热水器

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN211084458U (zh) 2019-09-30 2020-07-24 春意环境科技有限公司 一种适用于热泵热水器的微通道冷凝器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003036178A1 (fr) * 2001-10-22 2003-05-01 Rheem Australia Pty Limited Chauffe-eau ameliore a pompe a chaleur
AU2010201827A1 (en) * 2009-05-15 2010-12-02 Peter Sachs Industries Pty Ltd An Improved Hot Water Tank
CN105783552A (zh) * 2016-05-11 2016-07-20 珠海格力电器股份有限公司 热水器及其换热器总成
FR3073274A1 (fr) * 2017-11-06 2019-05-10 Emile Ivars Paul Dispositif de production d'eau chaude sanitaire et de chauffage/rafraichissement
CN112902445A (zh) * 2021-01-21 2021-06-04 珠海格力电器股份有限公司 水箱及其制备方法和热水器
CN112856817A (zh) * 2021-03-23 2021-05-28 格力电器（武汉）有限公司 一种热水器

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Publication number Publication date
DE102021214440A1 (de) 2023-06-15

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