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
  • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
  • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
  • F28F21/065—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing plate-like or laminated conduits
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
  • B29C49/02—Combined blow-moulding and manufacture of the preform or the parison
  • B29C49/04—Extrusion blow-moulding
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
  • F28F21/006—Constructions of heat-exchange apparatus characterised by the selection of particular materials of glass
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
  • B29C49/42—Component parts, details or accessories; Auxiliary operations
  • B29C49/64—Heating or cooling preforms, parisons or blown articles
  • B29C49/6604—Thermal conditioning of the blown article
  • B29C2049/6606—Cooling the article
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C51/00—Shaping by thermoforming, i.e. shaping sheets or sheet like preforms after heating, e.g. shaping sheets in matched moulds or by deep-drawing; Apparatus therefor
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29K—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES B29B, B29C OR B29D, RELATING TO MOULDING MATERIALS OR TO MATERIALS FOR MOULDS, REINFORCEMENTS, FILLERS OR PREFORMED PARTS, e.g. INSERTS
  • B29K2105/00—Condition, form or state of moulded material or of the material to be shaped
  • B29K2105/06—Condition, form or state of moulded material or of the material to be shaped containing reinforcements, fillers or inserts
  • B29K2105/12—Condition, form or state of moulded material or of the material to be shaped containing reinforcements, fillers or inserts of short lengths, e.g. chopped filaments, staple fibres or bristles
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29K—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES B29B, B29C OR B29D, RELATING TO MOULDING MATERIALS OR TO MATERIALS FOR MOULDS, REINFORCEMENTS, FILLERS OR PREFORMED PARTS, e.g. INSERTS
  • B29K2307/00—Use of elements other than metals as reinforcement
  • B29K2307/04—Carbon
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29K—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES B29B, B29C OR B29D, RELATING TO MOULDING MATERIALS OR TO MATERIALS FOR MOULDS, REINFORCEMENTS, FILLERS OR PREFORMED PARTS, e.g. INSERTS
  • B29K2309/00—Use of inorganic materials not provided for in groups B29K2303/00 - B29K2307/00, as reinforcement
  • B29K2309/08—Glass
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29L—INDEXING SCHEME ASSOCIATED WITH SUBCLASS B29C, RELATING TO PARTICULAR ARTICLES
  • B29L2031/00—Other particular articles
  • B29L2031/18—Heat-exchangers or parts thereof

Definitions

• the invention relates to hollow heat exchange plates, manufactured according to an industrial process, commonly used in a particular technical field, but totally ignored in the field of heat exchange between a fluid, liquid or gas, and certain hot sources, such as those formed by another fluid, radiation or a surface in contact.
• the invention relates to a hollow plate intended to constitute an elementary heat exchanger between a fluid and a hot source; the hollow plate having been obtained by extrusion blow molding of a glassy or polymeric parison and comprising:
• the connecting heads comprise plugs, which can be removed to be replaced by means for incorporating or reattaching to the connection heads, collectors associated with this plate.
• the plate comprises:
• transition zones between the connection heads and the central part comprising partitions, formed by welded pinches of the parison, adapted to provide the fluid with substantially uniform local flow rates in the channels of the central portion; and to give adequate rigidity to the walls of these areas.
• the plate has been made of a polymer loaded with suitable fibers, in particular glass or carbon.
• the walls of the plate comprise stiffening reliefs giving these walls an embossed appearance
• each of these embossed walls constitutes an alignment of alternating bosses, with facets with steep slopes and contours having ridges oriented in oblique or perpendicular directions to this alignment;
• the thickness and width of the walls of the plate are coordinated to give these walls overall rigidity, adapted to the particular use of the hollow plate.
• the facets of the alternative bosses are in the form of trapezoids and isosceles triangles, assembled to form alignments of alternating reliefs and valleys, in the form of roofs with four slopes, with slightly leveled edges;
• each of these facets comprises at least one welded elongated pinch, arranged in the direction of flow of the fluids, for dividing the surfaces of these facets into at least two parts thus subjected to reduced flexural stresses.
• the connecting heads are sections of ducts, each consisting of a pair of polymer inserts welded to the ends of the hollow plate during blowing; these inserts are provided with a central opening, with a circular or oblong periphery, provided with a contour in relief and with several grooves of the same section, arranged in the part of this periphery directed towards the inside of the hollow plate;
• the thickness and the width of the walls of these channels are coordinated to give these walls a rigidity adapted to the particular use of the plate;
• the connecting heads are necks adapted to be sealingly connected to external conduits.
• the front face of the central portion of the hollow plate is a smooth surface continuous, flat or arched;
• the partitions separating the channels are segmented and welded to the wall of this front face by unilateral pinching of the parison;
• the openings between channels, formed between two segments of partitions, are arranged staggered to give a certain transverse rigidity to the hollow plate.
• the two walls of the hollow plate have facets comprising in their centers elongated external reliefs, of determined height, having a length which is small compared to the dimensions of these facets; the external reliefs having oblique orientations with respect to the alignment of the bosses of the walls and the reliefs of the facets of a wall having an orientation opposite to that of the reliefs of the corresponding facets of the other wall;
• the plate has undergone crosslinking, in particular by ionizing radiation.
• the invention also relates to a heat exchanger, such as:
• the raised contours of the edges of these sections of stacked ducts have successively been welded together to constitute the two external collectors of this heat exchanger; two connections being welded to the contours in relief of the edges of the duct sections of the last plate of this stack;
• the invention also relates to:
• a solar water heater comprising a solar radiation sensor consisting of a previous extruded-blown plate, with embossed walls or flat walls, dark polymer, including black.
• a photovoltaic module mounting and cooling panel being an extruded-blown, glass or polymer flat-bottomed hollow plate, the hollow plate being adapted to receive a suitable flow rate of ambient air, circulating in an open circuit, either water at a temperature close to ambient, circulating in open or closed circuit.
• a mounting and cooling panel for electronic circuits being a hollow, extruded-blown, front plate with polymer flat walls, this hollow plate being adapted to receive a suitable flow rate of ambient air, circulating in an open circuit, or water at a temperature close to ambient, circulating in open or closed circuit.
• a hollow plate intended to constitute an elementary heat exchanger between a fluid and a hot source
• each channel of such a hollow plate comprise or not stiffening reliefs
• these walls have a thickness and a co-ordinate width, to ensure them a sufficient rigidity leu r allowing to maintain a substantially uniform and constant internal separation, in two inverse ranges of differential pressures and temperatures , depending on the material used.
• This hollow plate is: either globally flat or more or less arched, longitudinally and / or transversely.
• the channels are bordered by partitions formed by welded pinches of the parison.
• connection heads are adapted to be incorporated or attached to two outer conduits, associated with the hollow plate to enter and exit a fluid;
• the transition zones comprise partitions formed by welded nips of the parison, these partitions being adapted to ensure substantially uniform local flow rates to the fluid circulating in the channel or channels and to give an appropriate rigidity to the walls of these zones.
• inverted ranges it means that the maximum value of the differential pressure, authorized for a given hollow plate, decreases when the temperature of the authorized temperature for this plate increases.
• the choice of the differential pressure and the temperature of use is a compromise made in the context of these inverted ranges.
• the extent of each of the ranges of the differential pressures and maximum permissible temperatures for these plates is particularly great.
• these plates are made of a polymer loaded with suitable fibers, in particular glass or carbon.
• this device has undergone a complementary crosslinking operation, in particular by exposure to ionizing radiation.
• a first type of hollow heat exchange plate manufactured by blow molding a parison, made of polymer or glass, between the jaws of a suitable mold, is characterized in that:
• each channel of these hollow plates comprise stiffening reliefs giving them a waffled appearance
• each of these embossed walls is an alignment of alternating bosses with facets with steep slopes and contours comprising ridges oriented in oblique directions and / or perpendicular to this alignment;
• each channel The thickness and the width of the walls of each channel are coordinated to give these walls overall rigidity adapted to the particular use of the plate.
• the connecting heads of these hollow plates are sections of ducts
• these sections consist of two pairs of inserts welded to the ends of the hollow plate during its blowing;
• These inserts have a central opening, an outer face with a contour in relief and an inner face having a plurality of grooves, arranged in the portion directed towards the inside of the plate;
• a new heat exchanger between fluids is characterized in that:
• the heat exchanger consists of hollow plates, polymer or glass, with mouths welded to two external collectors;
• these walls are provided with an embossed central part, lateral flanges comprising a step determining the half internal thickness of the hollow plate, and zones of transition between this central part and the two mouths;
• the embossed central portion comprises one or more alignments of alternating bosses, with facets with steep slopes, creating a large number of sharp edges, oriented in oblique directions and / or perpendicular to these alignments;
• the internal and external gaps between the facets facing the stacked hollow plates are uniform and substantially constant in the range of the differential pressures and the permitted temperatures.
• the channels of the hollow plates, with embossed walls and welded edges, of such a heat exchanger between fluids have relatively thin and wide walls (typically 1 mm and 10 cm), to which their reliefs and their alternating stiffening recesses provide remarkable rigidity , allowing relatively high differential pressures (a few bars). This allows these channels to be relatively wide (10 cm) and to have, between their walls, a spacing (1 to 2 mm), free of any shim, virtually constant. Such channels are adapted to perform efficient heat exchange between two fluids.
• edges of the dihedrons, formed between them by the sloping facets of these plates, provide another particularly interesting result, that of notably increasing (+ 60%) the apparent thermal conductivity of the fluid which circulates between these hollow plates, stacked to form a heat exchanger thermal.
• a heat exchanger is perfectly satisfactory for many applications, but its manufacturing process gives it a relatively high production cost. This imposes a very limited diffusion and, consequently, justifies the development and realization, by another manufacturing process, of hollow elemental heat exchange plates, having the same functional characteristics as the previous ones but none of their defects.
• the manufacture of a hollow heat exchange plate is a particularly interesting technology transfer by significantly lowering the cost of manufacturing such hollow plates produced in series.
• it is interesting by the wide scope of use it provides hollow plates embossed walls made of polymer.
• the extruded-blown hollow plates with embossed walls, made of glass they can be manufactured according to specific steps, derived from those implemented for hollow polymer plates. But as the areas of application of heat exchangers, incorporating such hollow glass plates, are now indeterminate, the subject will not be further treated here.
• the open ends of the external collectors of such a heat exchanger are then provided with connections, generally threaded, welded in the same way as the faces of the collector sections.
• the diameter of these connections is adapted to the flow rate of the fluid to flow in the hollow plate.
• the thickness of the outer collector sections determines the width of the gap between the bosses belonging to two contiguous plates stacked at constant pitch to form a heat exchanger between fluids. From a standard manufacturing thickness, it is easy to weld an intermediate ring to each section, to obtain any particular gap separating the bosses of two adjacent plates. As for the appropriate mold, it consists of two symmetrical jaws of relatively simple design.
• the facets of the alternating bosses of each channel of its central part are in the form of trapezoids and isosceles triangles, assembled to form an alignment of alternating reliefs and valleys, in the form of roofs with four slopes, with slightly leveled edges;
• each of these facets comprises at least one elongate welded nip, arranged in the fluid flow direction, for dividing the surfaces of these facets into at least two parts subjected to substantially equal reduced bending stresses.
• the two walls of the channels of the hollow plate have facets comprising in their centers elongated external reliefs of determined height, having a length that is small compared with the dimensions of these facets;
• these external reliefs have oblique orientations with respect to the alignment of the bosses of the walls and the reliefs of the facets of one wall have an orientation opposite to that of the reliefs of the corresponding facets of the other wall;
• the external reliefs facing two adjacent plates are adapted to be joined together, so as to constitute a constant spacer between the plates and a double flow deflector; of fluid, in the form of braces.
• the thicknesses of the walls of the channels of these hollow plates are uniform, even along these ridges. This prevents the formation of mechanically weak areas in the walls of the hollow plates and thus allows them to operate at relatively high differential pressures.
• any heat exchanger incorporating hollow plates made of a polymer with a known limit of use, can maintain its efficiency in the presence of a maximum differential pressure allowed about four times stronger than in the absence of these welded nips.
• the authorized value of the internal overpressure of these plates is notably increased.
• the external reliefs corresponding facets of two adjacent hollow plates are joined and form braces constituting abutments for the walls of these plates. This prevents any increase in the initial gap between hollow plates, caused by an internal overpressure, greater than that normally allowed by the stiffeners of the walls and by the welded nips of the facets. In this way, this internal overpressure is practically doubled.
• the turbulence of the fluid flowing between the hollow plates is greater because of the deflecting obstacles, constituted by the two contiguous external reliefs forming braces; which results in an increased thermal coupling between the two fluids concerned and therefore in a complementary increase in the heat conductance of the exchanger.
• the dimensions of the central portions of the hollow-walled polymer hollow plates vary greatly depending on the intended applications: a total thickness of between 3 and 10 mm, thick walls of 0.6 to 2 mm, a width and a length of 5 mm. about 100 cm or more if the extrusion blow molding machines available allow it.
• such a hollow plate may comprise short channels ( ⁇ 10 cm), medium or long (2 m) for each of its possible widths: small ( ⁇ 10 cm), medium or large (1 m).
• the width of these embossed-wall channels will be about 2.5 cm for small-area plates and at most about 10 cm for large-area plates.
• the thickness of the polymer walls of the hollow plates according to the invention is in practice determined by their particular applications (thermal conductance, differential pressure and temperature) and by reasons of mechanical strength, weight and cost.
• the number of channels of a hollow plate with embossed walls can go from the unit when it is narrow to a dozen or more when it is wide.
• the bosses their width is that of the channels of the hollow plate and their height, about 15% of this width.
• the number of welded pinches to be made in the facets of these bosses may equal 2 for the largest (at most 10 cm wide) and for smaller ( ⁇ 2 cm wide), it can be zero.
• a simple modeling makes it possible to optimize the combination, thickness of the walls and number of nips per facet, to minimize the deflection and the stresses. The calculation shows that one or two welded pinches, arranged in its trapezoid and triangular facets, divide by ten the maximum deflection of these facets, which would result from their absence.
• the internal thickness to be given to the hollow plates with embossed walls of a heat exchanger varies with the nature of the fluid circulating inside, this internal thickness being significantly lower for the liquids than for the gases.
• the range of these internal thicknesses, as well as the range of the gaps between the stacked hollow plates of a heat exchanger, generally ranges from 0.5 to 3 mm for a liquid and from 2 to 12 mm for a gas.
• the temperature is relatively low (T ⁇ 100 ° C)
• the following areas are concerned: heating of swimming pools, heat pumps, condensation of water vapor, cooling of various liquids, corrosive or not, cooling of thermal engines and recovery energy from liquids or hot gases discharged.
• the temperature is relatively high (100 ⁇ T ⁇ 300 ° C)
• the polymer heat exchangers used will have undergone prior crosslinking and the areas will then be: recovery of the energy of the fumes and cooling of the exhaust gases of the diesel engines (EGR).
• EGR exhaust gases of the diesel engines
• these different heat exchangers may be assembled in series and in parallel to form assemblies having thermal conductances volume of several tens of kilowatts per degree and per m 3 .
• the hollow polymer plates according to the invention Due to their relatively thin walls, the hollow polymer plates according to the invention have a reduced weight, which minimizes the cost of the heat exchangers that incorporate them. Moreover, despite the reduced thermal conductivity of the polymers, the reduced wall thickness of these heat exchangers actually gives them a thermal conductance comparable to that of water, which is also of low conductivity and of much greater thickness, which circulates inside. In addition, since the polymers are indifferent to most corrosive fluids, the heat exchangers that use them are authorized for use in fields hitherto reserved for heat exchangers made of titanium or specific alloys, relatively expensive. According to the invention, a second type of hollow heat exchange plate, made by extrusion blow molding of a parison, made of polymer or glass, between the jaws of a suitable mold, is characterized in that:
• the thickness and the width of the walls of the channels are coordinated to give these walls a rigidity adapted to the particular use of the plate;
• the connecting heads are necks, adapted to be sealingly connected to external conduits.
• such an extruded-blown hollow plate made of glass or polymer, is further characterized in that: - The front face of the central portion of the hollow plate is a smooth surface continuous, flat or arched;
• partition walls of the channels are segmented and welded to the wall of this front face by unilateral pinching of the parison;
• the openings between channels, formed between two segments of partitions, are arranged staggered to give a certain transverse rigidity to the hollow plate.
• these new hollow heat exchange plates with flat or arched walls, satisfactory longitudinal and transverse stiffness (staggered trough), are likely to be suitable for many applications in very different industrial fields. others.
• these extruded-blown hollow plates, with flat polymer walls are immediately usable right out of the mold.
• appropriate values will be chosen for the surfaces of the hollow plates as well as for the number and internal sections of their channels.
• the walls will be in a glass more or less thick (1 to 3 mm) or a more or less thin polymer (0.5 to 1, 5 mm).
• the hot springs concerned are not necessarily fluids but also heat dissipating surfaces or radiation, solar or infrared.
• the hollow plates of polymer, flat-walled, arched or embossed may be used alone or juxtaposed (and no longer stacked) to form the thermal sensors of various conventional devices perfected.
• an improved solar water heater is characterized in that its thermal sensor is an extruded-blown hollow plate, with flat walls, in dark polymer, in particular black
• such a solar water heater is particularly interesting because it has replaced the black heat sensor, universally used until now (metal pipes and fins), by a thin hollow plate (typically thick 0.5 at 1 cm) with an appropriate unit area (typically 100 dm 2 ), made of less heavy polymer, less expensive and just as effective, because of the small thicknesses of the polymer walls of the hollow plate and the water flowing therethrough.
• a thin hollow plate typically thick 0.5 at 1 cm
• an appropriate unit area typically 100 dm 2
• such a water heater has a good efficiency and, moreover, a great ease of use. installation, due to the reduced total weight of the assembly. In this context, we will notice two neighboring situations.
• An extruded-blown hollow plate, with black polymer embossed walls, provided with a pair of connectors, makes it possible to produce a water heater equivalent to the previous one.
• a device, similar to this flat-wall solar water heater, comprising a hollow plate and, if appropriate, solid protective plates, made of suitable glass, may be suitable if it is desired to recover a portion of the thermal energy of the infrared radiation. at elevated temperatures, produced in some industries processing molten solids.
• a panel for mounting and cooling, for a photovoltaic module is characterized in that:
• this panel is an extruded-blown hollow plate, made of glass or polymer, with a perfectly flat front face;
• this hollow plate is adapted to receive a suitable flow rate of ambient air, circulating in open circuit, or water at a temperature close to ambient, circulating in open or closed circuit.
• a photovoltaic module is a special glass plate resistant to hailstones, in which the fragile photovoltaic cells are incorporated.
• any photovoltaic module is glued on a single tempered glass plate of appropriate thickness, in order to give good mechanical strength to the photovoltaic panel thus formed.
• the electric power, available per unit area is significantly increased. Indeed, it is estimated that the electric power produced by a standard photovoltaic cell, which is at best about 18% of the solar power captured, decreases by about 0.5% per degree when its temperature rises above of 20 ° C. With conventional cooling, by air flow circulating in natural convection, the cell temperature stabilizes at about 60 ° C. With improved photovoltaic panels according to the invention, by stabilizing the temperature of the cells at 25 ° C for example, the increase in available electrical power is close to 20%. This represents a particularly interesting return on investment.
• the means associated with the hollow plate may be a simple fan of appropriate power, installed upstream of one of the connection necks.
• a cooler will be used which advantageously comprises a water / air heat exchanger of the type described above: a stack of extruded-blown hollow plates in polymer, with embossed walls.
• a mounting and cooling panel in particular for electronic circuits, is characterized in that:
• this panel comprises a hollow extruded-blown polymer plate with a perfectly flat front face
• this hollow plate is adapted to receive a suitable flow rate of ambient air, circulating in open circuit, or water at a temperature close to ambient, circulating in open or closed circuit.
• such a panel is particularly effective and inexpensive, especially for mounting and cooling processors.
• FIG. 1 represents:
• FIG. 2 represents:
• FIG. 3 represents the front view of a second hollow plate with embossed walls, according to the invention.
• FIG. 4 represents a perspective view of a heat exchanger formed by the assembly of hollow plates of FIG. 1;
• FIG. 5 represents the rear face of a flat-faced hollow plate according to the invention.
• FIG. 6 represents the profile of a flat-faced hollow plate according to the invention.
• FIG. 1A represents the front view of a hollow plate 12 with embossed walls made of extruded-blown polymer.
• FIG. 1B is the section of this plate according to a BB line.
• the central zone of the hollow plate 12 has a generally rectangular shape and measures 300 mm between its parallel edges 14-16 and 200 mm between its lateral edges 18-20, with 360 mm between them. extreme edges of its two sections of external collectors 22-24.
• the hollow plate 12 comprises two embossed-walled channels 26-28 forming two identical contiguous alignments of alternating bosses, separated by a rectilinear central nip 30, 3 mm wide.
• each boss alignment comprises seven alternations, four recesses 32 1-4 and three bumps 32 5-7 , the hollows being represented in gray in the front view A.
• the thickness of the embossed walls 13a-b of the hollow plate 12 (section B) is 1 mm and its internal thickness 13c is 3 mm.
• each recess and bump is in the form of a roof with four slopes having four oblique edges 33, strongly inclined, and four facets comprising (1) two symmetrical lateral trapezoids 34 1-2 for the recesses and 36i - 2 for bumps, all with a large base of 40 mm, (2) between the peaks of two contiguous bosses, a connecting rhombus formed by two flattened isosceles triangles coplanar, respectively referenced 38i -2 for the hollows and 40i -2 for bumps, all with a large side of 90 mm, (3) a longitudinal ridge slightly leveled 42, between two symmetrical trapezes, for the hollows and 44 for the bumps, these two peaks being 15 mm long and 14 mm high.
• the lateral edges 18-20 of the hollow plate 12 are separated from the large bases of the trapeziums 34-36 by a welded-walled edge 19, 5 mm wide, followed by two connecting ramps 21 with the interior of the plate.
• the side edges of the corners, the quasi rectangle formed by the plate 12, are cut to form hooks 23 for easy suspension of the plate.
• each of the connecting ramps 21 bypasses a flexible external relief 25 of one of the walls of the plate 12.
• the difference between two vertices facing these external reliefs 25 is very small. slightly greater than the assembly pitch of the hollow plates, which makes these reliefs contiguous and improves the mechanical strength of the exchanger.
• FIG. 1C The view along the line of cross-section CC (FIG. 1A) of two hollow plates 12 12 2 , juxtaposed in a heat exchanger, is represented in FIG. 1C.
• This figure shows the internal thickness 13c (2 mm) of these plates. , the thickness of their walls 13a-b (1mm), the welded nips 48 made in the four trapeziums 36 of two bumps, belonging to the two rows 26-28, and the gap 54, 6mm wide, which separates these two plates 1-2 1-2 juxtaposed.
• each of the sections 22-24 of external collectors, of the hollow plate 12 incorporates a pair of circular inserts 58-60 which, after having been welded to the external faces of the walls of this plate, have an internal diameter final 30 mm.
• Each pair of inserts is divided into two semi-circular parts, respectively external and internal to the hollow plate 12.
• the inner portion comprises lateral radial ducts 62a-b and central 63a-b.
• the lateral ducts 62a-b open out in front and along oblique nips 64a-b and 66a-b, arranged welded in the two connection zones 68-70 of these sections 22-24 and isosceles triangular ends 38 of the part embossed central hollow plate 12.
• the central ducts 63a-b open on either side of the central nip 30.
• the recesses 32 1-4 and the alternating bumps 32 5-7 of a plate 12 appear on each side of its rectilinear central portion 56, which has at its two ends the inserts 58 -60 which form the individual sections 22-24 of the external collectors of this plate.
• the thickness of this central portion 56 is 4 mm and that of these collector sections 22-24, 10 mm, the latter thickness being the assembly pitch of the hollow plates 12, stacked in a heat exchanger.
• the profile view D shows that, from each section of collector, formed by the assembly of the inserts 58-60, the protruding edge 19 of the walls of the hollow plate 12 spring, welded between these inserts.
• FIG. 2 shows, at A, a circular ring insert 58, made of polymer, intended to be assembled in pairs, to form an individual section 22-24 of external collector of a hollow plate 12.
• a circular ring insert 58 made of polymer, intended to be assembled in pairs, to form an individual section 22-24 of external collector of a hollow plate 12.
• the inner semi-circular portion 76 comprises two pairs of radial grooves, lateral 78a b and central 80a-b and three partition walls 82, 84, 86 between these grooves, the central partition 84 having a lug 85 which allows a perfect placement of each insert 58 in a jaw of the plate manufacturing mold.
• B in this figure 2 is shown a sectional view of the insert 58, in which the central opening 72 appears, as well as the lateral groove 78b and the central groove 80b. On the outer face of this insert 58, there appears a circular relief 88, intended to be welded to an identical circular relief of the collector section of the contiguous hollow plate.
• FIG. 2C is shown (transparent), the front view of the end 61 of a rela-tively large extruded-blown hollow plate, six wide channels of 10 cm.
• This end 61 comprises an elongate collector section and a connection zone 57.
• Two elongated inserts, with walls welded by the parison, constitute this section, which has an oblong central opening 73, with a periphery comprising two parts, the one rounded 75, external to the hollow plate, and the other 77, elongate internal, which comprises twelve conduits 79 1-12 , of the same section, regularly distributed and separated from each other by eleven partitions 83i-n.
• connection zone 57 Eleven substantially parallel and equidistant welded oblique nips formed in the connection zone 57 follow these eleven partitions 83-1-11 and connect the collector section 73-75-77 to the central zone of the hollow plate. .
• This second embodiment of the manifold sections of the extruded-blown hollow plates is suitable for hollow plates having a number of channels greater than two.
• an improved distribution of the flow of the external fluid is ensured in the spaces separating the hollow plates.
• FIG. 3 is the front view of a hollow plate 92 with embossed walls, according to the invention, which has the dimensions and all the functional characteristics of the hollow plate 12 of FIG. 1.
• the embossed central portion of this second Hollow plate 92 has two channels 94-96, forming two contiguous identical alignments of alternating bosses, separated by a narrow rectilinear partition 98 (3 mm).
• Each boss has the shape of a roof with four slopes having four oblique edges, such as 99, strongly inclined and four facets constituted by (1) two isosceles lateral flattened triangles, such 100 for the hollows and 102 for the reliefs, (2) two coplanar trapezoids 104-106 forming a hexagon link, such as 105, between the extreme peaks of two alternating bosses, (3) a transverse ridge, such as 108, for the recessed bosses and 1 10 for the raised bosses. These two bosses have the same height.
• the hollows of this plate 92 are shown in gray.
• each of the trapezoids 104-106 of a connecting hexagon such as 05 and 107, two welded nips 1 14-1 16 are formed, which substantially connect the peaks of the bosses, are parallel to the flow direction of the fluid and share these hexagons in three substantially equal areas.
• a welded pinch 1 18-120 therein arranging two substantially equal surfaces.
• the functions of the hollow plate 92 differ from those of the hollow plate 12 of FIG. 1 by the presence, in the center of the connecting hexes 105 and 107, of oblique elongated external reliefs, such as 1 15 and 1 17.
• 105-107 connecting hexes have 10 cm wide and the welded nips 1 14-1 16, 4 cm apart.
• the outer reliefs 15 and 17 are 10 mm long, 5 mm wide, 2.6 mm high and 30 ° orientations, relative to the direction of flow of the fluid between the hollow embossed plates 92. a heat exchanger. Their spacing in such an exchanger is 5 mm, slightly less than twice the height of these external reliefs.
• the external reliefs in reverse orientations 1 15-1 17, belonging to two adjacent hollow plates of a heat exchanger are found contiguous and they then form a brace whose branches are at the same time shims between the hollow plates of this heat exchanger and the double fluid flow deflectors.
• This increases the allowable internal overpressure as well as the flow turbulence which improves the thermal coupling between the two fluids passing through the heat exchanger.
• the presence of these dual-function external reliefs 1 15-1 17 is particularly advantageous when the hollow plates 12, with lateral trapezoids and connecting rhombus according to FIG. 1, or the hollow plates 92, with lateral triangles and connecting hexagons according to FIG. Figure 3, have large dimensions, 100 x 200 cm for example. Improved thermal conductance and satisfactory overall rigidity are thus ensured for high-power heat exchangers formed by the stacking of large hollow plates comprising such external reliefs.
• a heat exchanger 122 is constituted by the welded stack of the collector sections 22-24 of nineteen hollow plates 12 (or 92) made of polymer.
• the sections of the last plate are equipped with threaded pipes 124.
• Each plate 12 comprises two rows of alternating bosses, in four-pitched roofs, consisting of pairs of trapezoids 36 and pairs of coplanar isosceles triangles 38, forming transition diamonds between a hollow and a bump. These triangles and trapezes have internal pinching 48-50 increasing their stiffness.
• This exchanger 122 is a compact block in the form of a parallelepiped of 12 dm 3 , having a thermal conductance between water and air of about 200 W / ° C and 400 W / ° C between water and water.
• this heat exchanger can treat fluids at high temperatures (150 ° C for a polyethylene HDPE and 400 ° C for a polyamide) significantly larger than the melting temperature before crosslinking.
• Several techniques are available for effecting this crosslinking, in particular ionizing radiation.
• the differential pressure allowed for the heat exchanger 122 having walls 1 mm thick is about 4 bars, when the polymer used for the parison is loaded with fiberglass or carbon. But these maximum possible values of temperature and differential pressure can not be simultaneous, the ranges of these two values being necessarily reversed. A compromise will be necessary in each particular case.
• FIG. 5 shows the view of the rear face of an extruded-blown hollow plate 130, comprising a central portion 132 devoid of any stiffening relief, two transition zones 134 1-2 and two necks 136i -2 , with circular section.
• the central flat and smooth 132 to 80 cm long, 40 cm wide a total thickness of 5 mm.
• This central portion 132 is occupied by sixteen narrow channels 138i-i 6 , with thick walls of 1 mm.
• These sixteen channels 138 are 22 mm wide and 3 mm internal thickness.
• These channels 138 are separated from each other by fifteen 140i_i lines 5 of segmented double walls 142, resulting welded pinching of the parison.
• These double partitions 142 are 18 cm long, wide and 3 mm high, their individual thickness and spacing being 1 mm.
• the gaps between two segments of a line of partitions constitute openings 144 between two adjacent channels, such as 138
• These openings 144 are arranged in staggered rows and are 6 cm long.
• the upstream and downstream transition zones 134 1-2 connect the ends of the central zone 132 to the two external connection necks 136i -2 .
• the 134i area is occupied by fifteen different partitions 146i_i 5 bordering sixteen conduits of uniform distribution of the incoming flow and lead to fifteen 140i_i lines 5 of partitions 142 separating the segments sixteen channels 138i-i 6.
• the downstream transition zone 134 2 is identical to the upstream zone 134 and occupied by fifteen convergent partitions 148i-i 5 .
• the profile view of a hollow plate 130 shows a central portion 132 and two threaded necks 136i -2 .
• the central portion 132 to 40 cm wide and 80 cm long, a thickness of 5 mm, a flat front wall and smooth, 1 mm.
• the necks 136i -2 are 4 cm in diameter and high and they are fixed perpendicularly to the rear wall of the plate.
• FIG. 7 which shows enlarged portions of three typical cross sections A, B, C of the hollow plate 1 30, this plate has a front face 150 perfectly flat, and a rear face 152 on which open the outer hollow segments 154 , 1 mm wide, internal double segmented partitions 142.
• each segment 142 separating two contiguous channels results from a unilateral nipping of the parison which has formed two internal partitions 158i -2 , 1 mm thick, spaced apart. 1 mm and 3 mm high.
• the common end 160 of these two partitions 158 is welded to the wall of the front face 150 of the hollow plate 130.
• FIG. 5 and the three sections A, B and C of FIG. 7 show that the staggered arrangement adopted for the openings 144 has the first result of inserting a wall end of the rear face 1 52 between two hollow segments. 1 54 belonging to two adjacent lines of segmented partitions 142 1-15 . This prevents the hollow segments 154 from opening and forces the hollow plate 130 to be able to take only a small transverse arrow, during handling.
• the second result of this staggered arrangement is to constitute continuous sequences (see section B), of contiguous portions of the offset segments 142 of the double partitions 140. These continuous sequences avoid any longitudinal stiffness defect in the hollow plate 130.
• the thermal sensor will be a hollow plate, according to the invention, with flat or embossed walls, black polymer.
• a hollow plate according to the invention with flat walls of polymer or glass, if necessary, quenched after molding.
• a hollow plate with flat polymer walls will be used.
• a cooler will be constituted, which will comprise an extruded-blown hollow plate, traversed by a current of ambient air, circulating in an open circuit, or by a water current at a temperature close to ambient, operating in open or closed circuit.
• the invention is not limited to the examples illustrated by the attached figures.
• the first embodiment of the invention is not limited to the dimensions of the hollow-walled hollow plates 10 and 92 described in FIGS. 1 and 3 or to the exchanger thermal 122 of Figure 4 which incorporates them. Indeed, when these hollow plates have significantly larger dimensions than those of these two plates, described by way of non-limiting examples, the number of channels increases since their maximum width is of the order of one decimeter, as the number of bosses in each channel. Moreover, the dimensions of these bosses can be modified depending on the differential pressures to be borne, and more generally the specifications of the exchanger to achieve. On the other hand, when the dimensions of the plates are appreciably lower than those of the two plates 12-92 described, the height of these bosses decreases accordingly.
• the fluid flows are laminar and the efficiency of the heat exchange performed is however large.
• these plates are large (typically> 50 dm 2 )
• these thicknesses and / or these deviations can be large (typically up to 2 cm for the deviations).
• the Reynolds number which derives from these dimensions and fluid velocities that pass through the exchanger, is such that the flows are turbulent.
• transition zones 134 1-2 may have variants.
• these zones can be incorporated in the hollow plate 130, in the form of internal collectors, in the form of two long, inverted, symmetrical right triangles into which the channels of a perfectly rectangular hollow plate, having a central part in parallelogram shape and necks arranged at both ends of a diagonal of the plate.
• Partitions similar to partitions 146-148, intended to distribute the flow rates evenly between the channels, will be arranged inside these internal reader columns.
• a modeling will optimize lengths and locations of the segments of these partitions.
• the two necks may have an oblong base, similar to that of the insert of Figure 2C, and a threaded cylindrical end of reduced diameter.
• the flat-wall extruded-blown hollow plate 130 may have dimensions different from those indicated.
• the Stammseu r 138i- walls of channels 16 of a hollow plate 130 will typically between 0.5 and 1.5 mm for a polymer plate and between 1 and 3 mm for a glass plate.
• the typical internal thickness of these channels it will be between 1 and 3 mm for a polymer plate and between 3 and 9 mm for a glass plate.
• the typical width of these channels will be between two and five centimeters
• the typical length of the partition segments 142 will be between one and two decimetres and that of the openings 144 between two channels, four to five times lower than the previous.
• the width and length of a hollow plate 130 may be increased depending on the capacities of the extrusion blow molding equipment available.
• An extruded-blown hollow plate with a polymer wall without any stiffening relief may have a central part with curved faces, one internal and smooth, and the other external and having the hollow of the internal partitions. These partitions may not be segmented to provide this curved hollow plate a certain transverse flexibility allowing it to be perfectly applied on a curved surface to cool.
• Such a curved hollow plate may in particular constitute a shell with hollow walls, adapted to be attached to identical shells, to form a cylindrical envelope with hollow walls.
• This envelope will constitute the thermal sensor of a water cooler, closely surrounding a hot cylindrical body, subjected to a temperature ceiling.
• This cylindrical body may be an electric motor of a few kW, to provide a mechanical power greater than that permitted by conventional cooling by natural convection of the ambient air.

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• Engineering & Computer Science (AREA)
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• Manufacturing & Machinery (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Blow-Moulding Or Thermoforming Of Plastics Or The Like (AREA)

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• 2011
  • 2011-05-18 WO PCT/IB2011/052181 patent/WO2011145065A1/fr active Application Filing
  • 2011-05-18 EP EP11724463A patent/EP2572152A1/de not_active Withdrawn

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