EP3155343B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
EP3155343B1
EP3155343B1 EP15735841.7A EP15735841A EP3155343B1 EP 3155343 B1 EP3155343 B1 EP 3155343B1 EP 15735841 A EP15735841 A EP 15735841A EP 3155343 B1 EP3155343 B1 EP 3155343B1
Authority
EP
European Patent Office
Prior art keywords
ribs
heat exchanger
tubes
winglets
rib
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.)
Active
Application number
EP15735841.7A
Other languages
German (de)
English (en)
Other versions
EP3155343A1 (fr
Inventor
Christian Wüllner
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.)
Kelvion Germany GmbH
Original Assignee
Kelvion 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 Kelvion GmbH filed Critical Kelvion GmbH
Priority to PL15735841T priority Critical patent/PL3155343T3/pl
Publication of EP3155343A1 publication Critical patent/EP3155343A1/fr
Application granted granted Critical
Publication of EP3155343B1 publication Critical patent/EP3155343B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/08—Fins with openings, e.g. louvers

Definitions

  • the invention relates to a heat exchanger with the features of claim 1.
  • Finned tube heat exchangers are generally used as air-cooled tube bundle heat exchangers, for. B. in motor vehicles ( FR 517 418 A ). In order to efficiently carry out air-cooled heat exchangers, the highest possible heat transfer coefficients are sought.
  • One measure for increasing the heat transfer properties lies in the turbulence generation of the air flow at the ribs. Turbulators redirect the flow of air in a specific way to improve fin efficiency ( DE 596 871 C . CH 385 258 A ).
  • the fin efficiency is the ratio of the heat flow that the fin actually delivers to the ideal heat flow the rib would emit if it had the tube temperature along its entire length.
  • a heat exchanger with the characteristics of the preamble shows the font DE10 2011 050 865 A1 ,
  • the k-value to be improved by this measure the heat transfer coefficient as a measure of the heat flow of a fluid through a solid body, such.
  • the heat flow Q ⁇ is calculated from the heat transfer coefficient k multiplied by the area of the heat exchanger A and the mean temperature difference ⁇ m of the two fluids, that is, between air (outside) and product (inside).
  • the applicant is known from his own practice to arrange heat exchanger tubes in several rows one behind the other.
  • the aim is to transfer a high heat output to the heat exchanger with a small construction volume.
  • the heat exchanger tubes can be arranged one behind the other so that a heat exchanger tube in the second row is effectively in the lee of the tube of the first row.
  • the tubes of the successive rows are aligned in this sense ( EP 578 568 A1 ).
  • the invention has for its object to provide a heat exchanger, which has a significantly improved k-value.
  • the heat exchanger according to the invention comprises in cross-section elliptical tubes with outer ribs, wherein a plurality of rows of the tubes are arranged one behind the other in the flow direction.
  • the ribs are interspersed by the pipes.
  • the ribs surround the tubes completely.
  • the ribs have a collar and are connected to the tubes via the collar.
  • the surface penetrated by the flow is referred to as the viewing surface of the heat exchanger.
  • the successively arranged rows of tubes run transversely to the direction of flow.
  • the tubes of successive rows are offset by a transverse offset parallel to the previous row, that is, transverse to the direction of flow.
  • the transverse offset is not equal to a transverse spacing, which is also measured transversely to the direction of flow. In other words, the tubes of the successive rows are not aligned in the direction of flow.
  • the adjacent tubes within a row are offset from each other by a longitudinal offset to be measured in the direction of flow.
  • the tubes may be offset alternately to each other, so that in a sense results in a zigzag-shaped row.
  • the longitudinal offset that is, the offset in the flow direction, is smaller than a longitudinal pitch.
  • the pitch spacing is measured between the tubes of successive rows.
  • the longitudinal offset is preferably half the size of the longitudinal pitch. This refers to the staggered arrangement of the tubes adjacent within a row.
  • the transverse offset is preferably half as large as the transverse pitch.
  • the transverse spacing is an important quantity. It will also be referred to below as the pitch.
  • the transverse spacing of the tubes of a row is greater than the average width of the ribs measured transversely to the plane of view of this row, so that a gap between the ribs of adjacent tubes is 0.1 to 0.5 times, in particular 0.1 - 0.2 times the average width is present.
  • the quadrangular ribs have winglets.
  • This constellation of quadrangular ribs in combination with the mutually staggered tubes, the intended mean width of the gap and the winglets has surprisingly enormously positive effects on the heat transfer performance Q of such a heat exchanger.
  • a possibility has been found to increase the k-value and at the same time to improve the mean temperature difference ⁇ m .
  • turbulence generation at the fins causes heat transfer improvement.
  • these changes result in the fact that the driving temperature difference ⁇ m is worsened, always under the condition of equal electrical energy that has to be introduced into the system.
  • the electrical power of the fans is proportional to the product of volume flow and pressure loss. If the pressure loss can be reduced, it is possible to increase the flow rate with constant electrical power.
  • the invention makes use of this.
  • the increased volume flow does not lead to a reduction of the average temperature difference ⁇ m between air and the product to be cooled, but - in contrast to other solutions - to an improvement. In combinations with that too the heat exchanger performance is significantly better than systems without the features according to the invention and based on the same electrical power for the fans.
  • the goal of high heat exchanger performance at low electrical power is achieved by the combination of various measures: on the one hand, the pitch between adjacent pipes must be changed in a particular way.
  • the modification of the pitch results in a reduction of the pressure loss between input and output sides and makes it possible to drive higher flow velocities at low electrical power.
  • this alone does not improve the heat transfer coefficient.
  • the invention provides at least two rows of finned tubes one behind the other.
  • the transverse offset is preferably selected so that the viewing surfaces of the tubes overlap as little as possible. As a result, the faces of the heat exchanger tubes facing the viewing surface lie directly in the air flow and experience maximum cooling.
  • the tubes in the first row ie in the first streamed row, give off heat, so that the cooling air at an assumed inlet temperature of 30 ° C over the path of the first rib z. B. heated to 45 ° C.
  • the temperature difference ⁇ 1 in the region of the first rib is in this case 15 ° C.
  • the following row of tubes is then cooled.
  • the cooling air heats up, for example, from 45 ° C to 55 ° C.
  • the temperature difference ⁇ 2 has fallen from 15 ° C to 10 ° C with respect to this fin row.
  • the cooling air then heats up again from 55 ° C to 62 ° C.
  • the temperature difference ⁇ 3 is only 7 ° C.
  • the ribs of the heat exchanger are quadrangular in their basic form. They can be square or rectangular, so that their adjacent sides are parallel to each other. The adjacent sides can also be at an angle to each other.
  • the ribs may therefore also be trapezoidal, with their width increasing in the flow direction.
  • trapezoidal ribs is spoken in the context of this invention of a mean width of the ribs or average gap width.
  • the width of the gap preferably decreases in the flow direction.
  • the gap width is also greater than zero at the narrowest point and is preferably at least 1.0 mm.
  • the elliptical tube passes through a central opening in the rib.
  • the longitudinal axis of the tube is at the center of the ribs.
  • the ribs are preferably mirror-symmetrical with respect to their longitudinal axis and / or transverse axis, which coincide with the longer major axis or shorter major axis of the elliptical tube. This minimizes production costs.
  • the winglets may be polygonal, in particular quadrangular, for example trapezoidal.
  • the winglets can also be triangular.
  • the winglets are preferably exhibitions of the rib material. These exhibitions lead to the fact that in the immediate vicinity of the winglets openings are present in the ribs, through which the cooling air can flow. These openings are preferably located on the side facing away from the tube of the winglets.
  • the winglets preferably have a height in a range of 60% to 100%, preferably 70% to 100%, of the fin pitch of a pipe.
  • the winglets are not necessarily based on the adjacent rib of a finned tube, but bridge this distance only to a large extent.
  • the height of the winglets is in a range of 60% to 90%, especially 80% to 90% of the rib distance.
  • the rib pitch is preferably in a range of 2 mm to 5 mm, preferably 3 mm to 4 mm. These values have shown the best results.
  • the invention provides both winglets, which are integrally integral part of the rib, so also winglets, which are connected as separate components with the rib.
  • the term "winglet” therefore does not mean that an opening adjacent to the winglet is necessarily present, but may preferably be arranged.
  • the winglets are preferably perpendicular or within the scope of manufacturing tolerances substantially perpendicular to the ribs. If necessary, the winglets can also include angles other than 90 ° with the rib plane.
  • the arrangement of the winglets also influences the k-value.
  • the winglets are located in the corner of a rib and at a distance from the long sides and transverse sides of the rectangular ribs.
  • Each rib has at least four winglets and especially these four winglets.
  • the winglets are preferably in the area of the diagonal of the quadrangular ribs, in particular in a range of 40% to 80%, in particular 40% to 60% of the distance from a corner of a rib to the central tube, which passes through the rib.
  • the winglets have a base through which they are connected to the ribs.
  • the orientation of the base also affects the k-value of the heat exchanger.
  • the base is at an angle of 20 ° to 50 °, in particular 20 ° to 45 °, to the adjacent longitudinal side of the rib. In particular, the angle is 30 ° to 45 °. It is assumed that the longitudinal side of the rib is parallel to the flow direction. For trapezoidal ribs, the term "longitudinal side" is to be equated with the flow direction or central longitudinal axis of the ribs. All winglets of a rib are preferably exposed to a single side, ie the same side of the rib.
  • the winglets are for example isosceles triangles. You may have a base for this case, which is preferably longer than the other two legs of the triangle. The The ratio between the length of the base and the height of the winglets is preferably in a range of 2: 1 to 5: 1.
  • the winglets can be square as well. In a trapezoidal shape, the winglet is connected to the rib via the wider base. Its narrower upper side points away from the rib.
  • the ratio between the length of the base and the height of the winglets is in a range of 2: 1 to 8: 1. It is preferably 5: 1.
  • turbulators are arranged on the ribs, for example in the form of triangular or rectangular displays.
  • the ribs are constructed mirror-symmetrically with respect to their longitudinal axis. Rectangular ribs may additionally be mirror-symmetrical with respect to their longitudinal axis. That is, in each corner of the rib is a winglet.
  • Turbulators can be arranged in the desired number parallel to the longitudinal sides. There is at least one turbulator at a distance from each longitudinal side. The number of turbulators is preferably even.
  • the turbulators are preferably mirror-symmetric with respect to the longitudinal axis of the rib, i. they face each other in pairs. In particular, there are 2 to 5 pairs, preferably 3 pairs of turbulators.
  • the turbulators are preferably exhibitions of the fin material.
  • the exhibitions lead to the fact that in the immediate vicinity of the turbulators openings are present in the ribs, through which the cooling air can flow. In this case, these openings are preferably located on the side facing away from the tube of the turbulators.
  • the turbulators preferably extend in the longitudinal direction of the rib, ie parallel to the longitudinal axis of the elliptical opening. As a result, the flow resistance is low.
  • the turbulators are arranged at diverging distances from the elliptical tube.
  • the distance of a turbulator from the elliptical tube is smallest when it is located on the central transverse axis of the rib.
  • the tube has its greatest width in the transverse direction.
  • the at least one further turbulator which is arranged between the central turbulator and the winglet, has both a greater distance from the elliptical tube and from the longitudinal side of the rib. These further turbulators follow in their intervals the contour of the elliptical tube. she are viewed in the flow direction, ie viewed in the direction of the inflow side of the rib, between two consecutive in the flow direction winglets.
  • the turbulators cause that already heated air flow from the pipe can not flow unhindered across, but is guided along the elliptical contour. Downstream, the flow directed by the turbulators meets the winglets, which also redirect the flow towards the pipe.
  • the turbulators are preferably perpendicular or within the scope of manufacturing tolerances substantially perpendicular to the ribs. If required, the turbulators can also include angles other than 90 ° with the rib plane.
  • the shape of the ribs also has an influence on the k value.
  • the rectangular ribs may have an aspect ratio of 1: 1 to 3: 1, preferably 3: 2 to 3: 1. This means that the ribs are square in the extreme case.
  • the rectangular shape is preferred because of the elliptical tubes.
  • the preferably longer longitudinal sides of such a rib point in the flow direction.
  • the transverse sides are perpendicular to the flow direction.
  • the gap width of the gap between the ribs of one row is preferably 10% to 45%, preferably 15% to 45% of the average width of the ribs.
  • the gap width is 10% to 30%, preferably 15% to 30% of the average width of the ribs. Values between 10% and 20% are considered particularly favorable. These values have shown very good k-value improvements while reducing pressure losses. Even with a slight k-value deterioration, the pressure losses are significantly lower, so that the heat exchanger performance is improved overall. The same applies to the trapezoidal ribs, in which an average gap width is assumed.
  • the average width of the ribs is about twice as large as the short main axis of the ellipse of the elliptical in cross section tubes.
  • An elliptical opening in the rib corresponds to the contour of the pipe cross-section.
  • the ellipse has a width (short major axis) of z. B. 14 mm, so that the rib has an average width of about 28 mm.
  • the gap between the ribs has a gap width in a range of 3 mm to 8 mm, preferably in a range of 4 mm up to 8 mm.
  • the deltoid winglets contribute significantly to increasing the efficiency of the ribs as a means of generating turbulence.
  • the arrangement according to the invention allows an increase in the k value calculated by CFD simulations and proven by practical tests, whereby the heat exchanger according to the invention can be produced less expensively with less use of material.
  • FIG. 1 shows a sectional view through a portion of a heat exchanger 1.
  • the heat exchanger 1 comprises a plurality of elliptical tubes 2 with outer, rectangular ribs 3.
  • the tubes 2 penetrate the rectangular ribs 3 in the middle.
  • Several of the outside ribbed tubes 2 are arranged in successive rows R1, R2.
  • the heat exchanger 1 is in this embodiment in the image plane from the bottom in the direction of the arrow p on the outside of cooling air flowing.
  • the cooling air can be sucked, for example.
  • a non-illustrated fan requires this an electric power Pel.
  • the fan generates a volume flow V ⁇ , which is conveyed through the viewing surface 4 at a flow velocity v.
  • the viewing surface 4 is the flow-facing upstream side of the heat exchanger. 1
  • the tubes 2 are flowed through by a medium to be cooled or product.
  • the medium can be liquid or gaseous.
  • the medium gives off heat to the tube 2 and thus to the ribs 3.
  • the cooling air absorbs the heat.
  • the temperature of the cooling air of row R1 increases by the temperature difference ⁇ 1 and via the downstream tube row R2 of tubes 2 by the temperature difference ⁇ 2.
  • ⁇ there is a temperature increase ⁇ of the cooling air and an average temperature difference between the cooling air and the product to be cooled of ⁇ m and a pressure drop ⁇ p between the inlet and the outlet side of the heat exchanger. 1
  • the tubes 2 are arranged one behind the other in the direction of flow.
  • This arrangement is referred to as a staggered arrangement because the tubes 2 of a row of tubes R1, R2 do not respectively a straight line, but in the flow direction of the cooling air forward and backward are.
  • the offset in the direction of the flow of cooling air between adjacent tubes is the longitudinal offset LV. It is half the size of the longitudinal pitch LT of the zigzag-shaped rows R1, R2.
  • FIG. 2 In contrast to the staggered arrangement shows FIG. 2 a pushed arrangement in which the individual tubes 2 a row of tubes R1, R2 are moved transversely to the direction of flow of the cooling air to the transverse offset VQ.
  • the transverse offset VQ is half the size of the transverse division TQ.
  • the centers of a row of tubes R1, R2 are enclosed FIG. 2 on a common axis. This arrangement is referred to as a pushed arrangement.
  • row refers to the tubes 2 of a row R1 initially flown or the tubes 2 of a subsequent row of tubes R2.
  • the term “row” may also mean, in particular in the staggered arrangement, that the tubes 2 do not lie exactly on a line, but in a sense follow one another in a zigzag shape.
  • the invention provides both in the embodiment of the FIG. 1 as well as in the embodiment of FIG. 2 in that the individual tubes 2 of a row R1, R2 are arranged at a certain transverse spacing TQ or short pitch apart.
  • the pitch TQ is greater than the measured parallel to the face 4 width B of a rib 3. This results in a gap 5 with a gap width S, which is in a range of 0.1 to 0.5 times, preferably from 0.1 to 0.2 times the width B lies.
  • the ribs 3 In addition to the displaced or staggered arrangement and the intended gap width S, the ribs 3 have in their corner region E so-called winglets 6a (FIG. FIG. 10 ).
  • winglets 6a 7 turbulators 13 may be arranged in the region of the longitudinal sides, as shown in the FIGS. 3 and 4 can be seen.
  • the embodiments of the FIGS. 3 and 4 differ from those of Figures 1 and 2 only through the additional turbulators 13 on the ribs 3. Details of the turbulators 13 and the shape of the ribs 3 are in the FIGS. 13 to 15 shown.
  • FIGS. 5 and 6 show alternative winglets 6b which, unlike the first four embodiments, are not trapezoidal but triangular.
  • the offset or pushed arrangement of the ribs 3 corresponds to the FIGS. 5, 6 that of the Figures 1 and 2 , The description there is used to avoid repetition.
  • FIGS. 7 and 8 are shown essentially the Embodiment of FIGS. 3 and 4 , with the difference that the winglets 6b in the corners E are triangular and not trapezoidal.
  • FIGS. 3 and 4 or 1 and 2, respectively.
  • S1 in FIG. 8 the width of a gap 18 between the successive rows of tubes R1, R2.
  • the embodiment of the FIG. 9 is essentially the same as that of FIG. 6 that is, there is an arrangement of ribs 3 in a pushed arrangement.
  • the only difference from the embodiment of the FIG. 6 is that the ribs 3 are trapezoidal.
  • the dimension of the rib 3 in this case refers to the average width B or the average gap width S.
  • the gap width S decreases in the flow direction, for example from 9 mm to 1 mm. Incidentally, the description of the FIG. 6 respectively.
  • FIG. 2 Referenced.
  • FIG. 10 shows in a single representation of a rib 3 with winglets 6b in their corners E. All tubes 2 and ribs 3 are designed identically. Each rib 3 has four winglets 6b. Depending on a winglet 6b is arranged in the corner E both at a distance from the longitudinal side 7 and from a transverse side 8. The aspect ratio between the long side 7 and the transverse side 8 is in a range of 1: 1 to 1: 3.
  • the long major axis is HA1 and the short major axis of the elliptical tube 2 is HA2.
  • the short major axis HA2 in this example has a length L2 of, for example, 16 mm at a width B of the rib 3 of 26 mm.
  • the length L1 of the long main axis HA1 is 55 mm.
  • the winglets 6b are formed as punched-11 from the rib 3 itself. It can be seen from the triangular cut-outs 11 that the winglets 6b are designed as isosceles triangles. The winglets 6b are each exposed perpendicular to the ribs 3. All winglets 6b point in the same direction. In this case, they point out of the picture plane.
  • the winglets 6b are located in the corner region E not only at a distance from the longitudinal side 7 and the transverse side 8, but also at a distance A from the elliptical tube 2. They are located approximately in a range of 40% to 80%, in particular 40% 60% of the distance A, which is measured from the corner 9 to the tube 2.
  • This distance A is the smallest distance to be measured between the tube 2 and the corner 9.
  • the winglets 6b are at an angle W in a range of 20 ° to 50 °, in particular 20 ° to 45 ° to the longitudinal side 7. In this example, the angle is 30 °.
  • FIG. 11 shows a single tube 2 with the ribs 3 arranged thereon and the individual winglets 6b, which are formed as isosceles triangles.
  • the winglets 6b have a height H of 70% to 95% of the rib distance A1 and in particular a height H of 80% to 90% of the rib distance A1.
  • the base of the winglets 6b that is, those areas along which the winglets 6b have been folded and issued, each has a length of 6 mm ( Figures 10 and 12 ).
  • the winglets 6b designed as an isosceles triangle may in this case have a height H of, for example, 2 mm. It is therefore a symmetrical punching structure.
  • FIG. 12 shows a perspective view of a rib 3 with the said, formed as an isosceles triangles winglets 6b and with a collar 10, via which the ribs 3 are in contact with the tube 2.
  • the collar 10 is slightly higher than the winglets 6b.
  • the collar 10 serves as a spacer between two adjacent ribs. 3
  • FIGS. 13 to 15 illustrate the FIGS. 13 to 15 an alternative embodiment in which not only additional turbulators 13 are provided, but in which also the shape of the winglets has been changed.
  • the winglets 6a are trapezoidal ( FIG. 15 ). Its base 12 is wider than its top 14. The ratio between the base and length L3 of the base 12 and the height H is in a range of about 1: 5. The ratio of the upper side 14 to the base 12 is approximately 3: 5, in particular if the angle W1 of the flanks 15 of the winglet 6a is in a range of 30 ° to 60 °, in particular 45 °.
  • FIG. 13 shows that the winglets 6a compared to the embodiment of FIG. 10 are also formed from punched-11 of the ribs 3, so that according to the size of the winglets 6a trapezoidal punched 11 in the corners E are.
  • the turbulators 13 are also formed from punch-outs 16 and in the direction of the winglets perpendicular from the plane of the ribs 3 issued items. The punched holes are almost square. Accordingly, the turbulators 13 are also square.
  • the turbulators 13 are substantially smaller than the winglets 6a. Its height is not greater than that of the winglets 6a.
  • Each three turbulators 13 are formed at a distance from the longitudinal sides 7.
  • the punched-out regions 11 are closer to the longitudinal sides 7.
  • the winglets 6a or turbulators 13 are thereby closer to the tube than to the longitudinal side 7 and the transverse side 8, respectively FIG. 13 drawn distance A2 between the transverse side 8 and the punching 11 is greater than the width of the punched-11, in particular twice as large.
  • the distance A3 is about as long as the length L3 of the base 12 of the winglets 6a.
  • FIG. 13a shows in plan view an embodiment of a rib 3, which differs from that of FIG. 13 distinguished by additional concave recesses 19 with the radius R in the corner region E.
  • the winglets 6b are triangular.
  • This rib 3 has an elliptical opening 17 with a ratio L1 / L2 of the long main axis HA1 to the short main axis HA2 of 2.5 to 2.7.
  • the long main axis HA1 in this case is 35.8 mm long.
  • the ratio B / L2 of the width B of the rib 3 to the short major axis HA1 is 2.0 to 2.2.
  • the ratio L / L1 of the length L of the rib 3 to the long main axis HA2 is 1.5 to 1.6.
  • the winglets 6b are arranged at 45 ° to the longitudinal sides 7. They start at a distance A2 from the transverse sides 8 and end at a distance A3 from the longitudinal sides 7.
  • the ratio A2 / L is 0.10 to 0.12.
  • the ratio A3 / B is 0.2 to 0.5.
  • the turbulators 13 have a width B1 and a height H1.
  • the height H1 can be seen on the size of the punched-11 and is in this case 2 mm.
  • the punched-out portions 11 of the middle of the six paired turbulators 13 have a distance A4 from the longitudinal side 7.
  • the other punch-outs 11 of the turbulators 13 are each arranged at a distance A5 from the longitudinal side 7.
  • the turbulators 13 extend parallel to the longitudinal sides 7.
  • the ratio A4 / B is 0.11 to 0.14.
  • the ratio A5 / B is 0.13 to 0.15.
  • the ratio B1 / L is 0.05 to 0.06.
  • the center distance A6 of adjacent turbulators 13 in the longitudinal direction is 0.19 to 0.21 x L.
  • FIG. 14 shows in the perspective view of the flared winglets 6a and the three turbulators 13 along each longitudinal side. 7 FIG. 14 further shows a collar 10, over which the ribs 3 are in contact with the pipe, not shown.
  • the heat exchanger 1 has outstanding k-values which are based on a synergetic effect of the particular triangular or trapezoidal winglets 6a, 6b, the gap 5 between adjacent ribs 3 and on the displacement or displacement of the rows of tubes R1, R2 or tubes 2 is due. This connection is based on the FIG. 16 be clarified.
  • FIG. 16 shows on the horizontal axis, the flow velocity v and on the vertical axis on the one hand, the heat transfer coefficient k and the pressure loss ⁇ p .
  • the lower curves K1, K2, K3 in the image plane represent three different embodiments of heat exchangers. These curves K1, K2, K3, which show the respective pressure drop ⁇ p, correspond to the three upper curves K1 ', K2', K3 'with respect to the respective heat transfer coefficient k.
  • the gap between adjacent finned tubes is 0.67 mm.
  • This standard design usually provides for the staggered arrangement of the tubes, since, viewed in terms of heat and flow, it represents the most energetically favorable variant overall.
  • the pushed arrangement should be considered, as it achieves the highest heat transfer coefficients at a constant flow velocity, but also the highest pressure losses.
  • the curve K1 shows the standard of a staggered arrangement with very small gap width.
  • the curve K2 stands for the pushed arrangement with a small gap width and finally the curve K3 for the pushed arrangement with increased transverse distribution or increased gap width.
  • the exchange surface of the heat exchanger can be reduced. This allows cheaper construction methods.
  • the cost-effective design can also be used to reduce the power required for operation electrical power, if this should be the goal of the design of the heat exchanger.

Landscapes

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

Claims (16)

  1. Echangeur de chaleur (1) comprenant des tubes (2) avec des nervures (3) extérieures et avec des caractéristiques suivantes :
    1.1. une surface visible (4) de l'échangeur de chaleur (1) est une surface traversée par un écoulement dans la direction d'afflux (p), dans lequel plusieurs rangées (R1, R2) des tubes (2) sont disposées les unes derrière les autres dans la direction d'afflux (p) ;
    1.2. les rangées (R1, R2) s'étendent de manière transversale par rapport à la direction d'afflux (p) ;
    1.3. les tubes (2) des rangées (R1, R2) se suivant les unes les autres sont disposés de manière décalée selon un décalage transversal (VQ) de manière parallèle par rapport à la rangée (R1, R2) précédente, dans lequel le décalage transversal (VQ) n'est pas égal à une distance de division transversale (TQ) de manière transversale par rapport à la direction d'afflux (p), dans lequel le décalage transversal (VQ) et la distance de division transversale (TQ) sont mesurés depuis le point central de tubes (2) adjacents de manière transversale par rapport à la direction d'afflux (p), ou
    1.4. les tubes (2) adjacents à l'intérieur d'une rangée (R1, R2) sont disposés de manière décalée les uns par rapport aux autres selon un décalage longitudinal (VL) s'étendant dans la direction d'afflux (p), dans lequel le décalage longitudinal (VL) est inférieur à une distance de division longitudinale (TL) des tubes (2) de rangées (R1, R2) se suivant les unes les autres, dans lequel le décalage longitudinal (VL) et la distance de division longitudinale (TL) sont mesurés depuis le point central de tubes (2) adjacents dans la direction d'afflux (p) ;
    1.5. les tubes (2) traversent les nervures (3) s'étendant de manière transversale par rapport aux tubes (2) et sont reliés aux nervures (3) par l'intermédiaire d'un collet (10) au niveau des nervures (3) ;
    1.6. la distance de division transversale (TQ) des tubes (2) d'une rangée (R1, R2) est plus grande que la largeur (B) moyenne, mesurée de manière transversale par rapport à la surface visible (4) de la rangée (R1, R2), des nervures (3) de sorte qu'une fente (5) est présente entre les nervures (3) de tubes (2) adjacents ;
    1.7. les nervures (3) sont quadrangulaires et possèdent des ailettes (6a, 6b), dans lequel respectivement une ailette (6a, 6b) est disposée dans la zone d'angle (E) d'une nervure (3),
    caractérisé en ce que
    1.8. les tubes (2) présentent une section transversale elliptique, que la fente (5) présente une largeur égale à 0,1 à 0,5 fois la largeur (B) moyenne des nervures (3), et que les ailettes (6a, 6b) sont disposées à une distance (A2) des côtés longitudinaux (7) et des côtés transversaux (8) des nervures (3).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les nervures (3) sont rectangulaires ou carrées.
  3. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les nervures (3) sont de forme trapézoïdale.
  4. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le rapport entre la longueur (L) et la largeur (B) moyenne d'une nervure (3) se situe dans une plage allant de 1:1 à 3:1.
  5. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le rapport entre la longueur (L) et la largeur (B) moyenne d'une nervure (3) se situe dans une plage allant de 3:2 à 3:1.
  6. Echangeur de chaleur selon la revendication 1 à 5, caractérisé en ce que les ailettes (6a) sont quadrangulaires.
  7. Echangeur de chaleur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les ailettes (6b) sont triangulaires.
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que les ailettes (6b) sont réalisées sous la forme de triangles isocèles.
  9. Echangeur de chaleur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les ailettes (6a, 6b) possèdent une hauteur (H), qui représente 60 % à 100 % de la distance entre les nervures (A1) d'un tube (2).
  10. Echangeur de chaleur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les ailettes (6a, 6b) possèdent une hauteur (H), qui représente 70 % à 100 % de la distance entre les nervures (A1) d'un tube (2).
  11. Echangeur de chaleur selon l'une quelconque des revendications 1 à 10, caractérisé en ce que les ailettes (6a, 6b) sont disposées dans une plage allant de 40 % à 80 % de la distance (A) depuis l'angle (9) d'une nervure (3) vers le tube (2).
  12. Echangeur de chaleur selon l'une quelconque des revendications 1 à 10, caractérisé en ce que les ailettes (6) sont disposées dans une plage allant de 40 % à 60 % de la distance (A) depuis l'angle (9) d'une nervure (3) vers le tube (2).
  13. Echangeur de chaleur selon l'une quelconque des revendications 1 à 12, caractérisé en ce que les ailettes (6) possèdent une base (12), par l'intermédiaire de laquelle elles sont reliées aux nervures (3) et qui s'étend selon un angle allant de 20° à 50° par rapport au côté longitudinal (7) des nervures (3).
  14. Echangeur de chaleur selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la largeur de fente (S) moyenne d'une fente (5) entre les nervures (3) d'une rangée (R1, R2) représente 10 % à 30 % de la largeur (B) moyenne des nervures (3).
  15. Echangeur de chaleur selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la largeur de fente (S) moyenne d'une fente (5) entre les nervures (3) d'une rangée (R1, R2) représente 15 % à 30 % de la largeur (B) moyenne des nervures (3).
  16. Echangeur de chaleur selon l'une quelconque des revendications 1 à 14, caractérisé en ce que la largeur (B) moyenne de la nervure (3) correspond à deux fois +/-10 % de la longueur (L2) de l'axe principal (HA2) plus court de l'ellipse des tubes (2) elliptiques dans la section transversale.
EP15735841.7A 2014-06-11 2015-06-11 Échangeur de chaleur Active EP3155343B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15735841T PL3155343T3 (pl) 2014-06-11 2015-06-11 Wymiennik ciepła

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014108209.5A DE102014108209A1 (de) 2014-06-11 2014-06-11 Wärmetauscher
PCT/DE2015/100235 WO2015188812A1 (fr) 2014-06-11 2015-06-11 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP3155343A1 EP3155343A1 (fr) 2017-04-19
EP3155343B1 true EP3155343B1 (fr) 2018-08-15

Family

ID=53539424

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15735841.7A Active EP3155343B1 (fr) 2014-06-11 2015-06-11 Échangeur de chaleur

Country Status (5)

Country Link
EP (1) EP3155343B1 (fr)
CN (1) CN106662406B (fr)
DE (1) DE102014108209A1 (fr)
PL (1) PL3155343T3 (fr)
WO (1) WO2015188812A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110462326B (zh) * 2017-04-04 2021-03-19 三菱电机株式会社 热交换器及制冷循环装置
CN106979714B (zh) * 2017-05-08 2023-12-05 中国华能集团清洁能源技术研究院有限公司 一种菱形翅片管束
CN107976101B (zh) 2017-12-22 2023-07-14 上海发电设备成套设计研究院有限责任公司 一种外翅片换热管的使用方法
CA3036460A1 (fr) 2018-03-14 2019-09-14 Rheem Manufacturing Company Ailette d'echangeur thermique
CN113674955B (zh) * 2021-08-06 2023-01-03 浙江尔格科技股份有限公司 一种带椭圆翼片管的油风冷却器

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR517418A (fr) * 1919-07-14 1921-05-06 Lecourbe Atel Perfectionnements apportés aux échangeurs de température tels, notamment, que les radiateurs pour véhicules automobiles
DE596871C (de) * 1930-10-09 1934-05-11 Otto Happel Rippenrohr fuer Waermeaustauscher mit aus der Rippenebene herausgedrueckten Flaechen
US2063736A (en) * 1935-03-08 1936-12-08 Gen Motors Corp Heat exchanger
GB906520A (en) * 1960-03-22 1962-09-19 Hagen Krankenhagen Heat exchanger
CH385258A (de) * 1960-03-31 1964-12-15 Gea Luftkuehler Ges Mbh Mit Rippen versehenes Wärmetauscherrohr
DE2442420C3 (de) * 1974-09-05 1979-10-31 Basf Ag, 6700 Ludwigshafen Desublimator für die Gewinnung von Sublimationsprodukten, insbesondere von Phthalsäureanhydrid, aus Reaktionsgasen
EP0061873A3 (fr) * 1981-03-27 1983-04-20 Imi Radiators Limited Echangeur de chaleur à l'épreuve des attaques
SE8803215D0 (sv) * 1988-09-13 1988-09-13 Gadelius Sunrod Ab Ytforstoringselement for vermevexlartub
DE3938842A1 (de) * 1989-06-06 1991-05-29 Thermal Waerme Kaelte Klima Verfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
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.
JP4376276B2 (ja) * 2007-06-06 2009-12-02 木村工機株式会社 熱交換コイル
DE102007046403A1 (de) * 2007-07-18 2009-01-22 Lesa Maschinen Gmbh Wärmetauscher und Dampferzeugungsanlage zur Energieumwandlung
FR2940422B1 (fr) 2008-12-19 2010-12-03 Gea Batignolles Technologies T Echangeur de chaleur comprenant des tubes a ailettes rainurees
CN102032819B (zh) * 2009-10-06 2013-03-06 松下电器产业株式会社 热交换器及使用该热交换器的物品贮藏装置
US20110308228A1 (en) * 2010-06-18 2011-12-22 General Electric Company Fin and Tube Heat Exchanger
CN103438746B (zh) * 2013-08-14 2015-07-01 西安交通大学 一种用于余热回收的椭圆管h型翅片换热器
CN203605777U (zh) * 2013-11-19 2014-05-21 美的集团股份有限公司 管翅式换热器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3155343A1 (fr) 2017-04-19
PL3155343T3 (pl) 2018-12-31
CN106662406A (zh) 2017-05-10
WO2015188812A1 (fr) 2015-12-17
DE102014108209A1 (de) 2015-12-17
CN106662406B (zh) 2019-03-01

Similar Documents

Publication Publication Date Title
EP3155343B1 (fr) Échangeur de chaleur
EP1654508B2 (fr) Echangeur de chaleur et procede de fabrication dudit echangeur
EP1910764B2 (fr) Element de plaque pour refroidisseur a plaques
DE102016216019A1 (de) Einsatz für einen Kühlmantel einer elektrischen Maschine
DE102012000549A1 (de) Wärmetauscherrohr und Verfahren zum Verwenden desselben
DE112014001374T5 (de) Wärmeübertragungsfläche mit vorstehenden Zungen
DE102011102048A1 (de) Wärmetauscher
DE112005000617T5 (de) Kreuzrippen-Plattenpaar für Wärmetauscher
WO2012017044A2 (fr) Echangeur de chaleur en forme de plaque pour un dispositif de refroidissement comprenant au moins un paquet d'échangeurs de chaleur
EP2394126B1 (fr) Corps chauffant pour véhicules automobiles
EP2185884B1 (fr) Ailette pour un échangeur de chaleur
DE10196335B3 (de) Vorrichtung für den Austausch von Wärme/Feuchtigkeit
DE10342241A1 (de) Wärmetauscher
DE202017102436U1 (de) Wärmetauscher mit Mikrokanal-Struktur oder Flügelrohr-Struktur
EP3491323B1 (fr) Échangeur de chaleur présentant une structure à micro-canal ou une structure à tube à ailettes
EP2678629B1 (fr) Échangeur de chaleur
DE102012007063B4 (de) Lamellen-Rohr-Wärmetauscher mit verbesserter Wärmeübertragung
DE3209760A1 (de) Waermeaustauscher
EP3669133B1 (fr) Échangeur de chaleur
WO2004079748A2 (fr) Distanceur
DE202008016603U1 (de) Wellrippe für Wärmeaustauscher
DE1601228A1 (de) Waermetauscher
DE202015103710U1 (de) Gas-Fluid-Gegenstromwärmetauscher
WO2012123105A2 (fr) Unité de transfert de chaleur
DE102012007570B4 (de) Lamellen-Rohr-Wärmetauscher mit verbesserter Wärmeübertragung

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170104

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: KELVION GMBH

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180313

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTC Intention to grant announced (deleted)
INTG Intention to grant announced

Effective date: 20180516

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: AT

Ref legal event code: REF

Ref document number: 1030275

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180815

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502015005472

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181115

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181116

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181215

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181115

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502015005472

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20190516

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190611

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181215

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20150611

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502015005472

Country of ref document: DE

Owner name: KELVION THERMAL SOLUTIONS GERMANY GMBH, DE

Free format text: FORMER OWNER: KELVION GMBH, 44807 BOCHUM, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502015005472

Country of ref document: DE

Owner name: KELVION THERMAL SOLUTIONS GERMANY GMBH, DE

Free format text: FORMER OWNER: KELVION GERMANY GMBH, 44807 BOCHUM, DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20230620

Year of fee payment: 9

Ref country code: DE

Payment date: 20230628

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PL

Payment date: 20230601

Year of fee payment: 9

Ref country code: AT

Payment date: 20230621

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20230619

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230623

Year of fee payment: 9

Ref country code: CH

Payment date: 20230702

Year of fee payment: 9

REG Reference to a national code

Ref country code: NL

Ref legal event code: PD

Owner name: KELVION THERMAL SOLUTIONS GERMANY GMBH; DE

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), ASSIGNMENT; FORMER OWNER NAME: KELVION GERMANY GMBH

Effective date: 20231122

Ref country code: NL

Ref legal event code: HC

Owner name: KELVION GERMANY GMBH; DE

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), CHANGE OF OWNER(S) NAME; FORMER OWNER NAME: KELVION GMBH

Effective date: 20231122

REG Reference to a national code

Ref country code: BE

Ref legal event code: PD

Owner name: KELVION THERMAL SOLUTIONS GERMANY GMBH; DE

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), ASSIGNMENT; FORMER OWNER NAME: KELVION GERMANY GMBH

Effective date: 20231116

Ref country code: BE

Ref legal event code: HC

Owner name: KELVION GERMANY GMBH; DE

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), CHANGE OF OWNER(S) NAME; FORMER OWNER NAME: KELVION GMBH

Effective date: 20231116