US20220146204A1 - Plate-type heat exchanger - Google Patents
Plate-type heat exchanger Download PDFInfo
- Publication number
- US20220146204A1 US20220146204A1 US17/433,822 US202017433822A US2022146204A1 US 20220146204 A1 US20220146204 A1 US 20220146204A1 US 202017433822 A US202017433822 A US 202017433822A US 2022146204 A1 US2022146204 A1 US 2022146204A1
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- Prior art keywords
- plate
- heat
- entry
- exchange
- heat exchanger
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- 239000012530 fluid Substances 0.000 claims abstract description 45
- 238000007688 edging Methods 0.000 claims abstract description 21
- 238000005219 brazing Methods 0.000 claims description 9
- 238000007373 indentation Methods 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 description 15
- 238000009826 distribution Methods 0.000 description 5
- 238000005057 refrigeration Methods 0.000 description 5
- 238000000465 moulding Methods 0.000 description 4
- 239000012808 vapor phase Substances 0.000 description 3
- 230000002860 competitive effect Effects 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000002051 biphasic effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 238000009877 rendering Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
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- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/14—Fastening; Joining by using form fitting connection, e.g. with tongue and groove
Definitions
- the present disclosure relates to a plate-type heat exchanger.
- plate-type heat exchangers In refrigeration systems that execute refrigeration cycles using vapor expansion, for air-conditioning or refrigeration applications, the use is known of plate-type heat exchangers to provide evaporators, in which a heat exchange occurs between a refrigerant fluid, which, flowing inside a series of passage channels defined in the plate-type heat exchanger, progressively evaporates, absorbing heat from a fluid to be cooled, typically water, which, flowing in channels adjacent to the channels flowed through by the refrigerant fluid, is in turn cooled.
- the plate-type heat exchangers that are used as evaporators in refrigeration systems are, typically, constituted by a “pack” of plates, i.e. by a plurality of plates that are mutually stacked, so as to face each other, and are joined together at various points of mutual contact, by way of brazing or welding, or are interconnected by way of the interposition of gaskets.
- the refrigerant fluid fed into the plate-type heat exchanger is, generally, in a mixed biphasic state, in which there are a liquid phase and a vapor phase of the coolant fluid.
- a technical problem associated with the use of plate-type heat exchangers as evaporators in refrigeration systems consists of ensuring that the entry distributor channel of the heat exchanger can evenly feed the various channels with refrigerant fluid, avoiding feeding some of them with only the vapor phase, with the obvious consequence of reducing the efficiency of the heat exchange between the refrigerant fluid and the fluid to be cooled, as the vapor phase offers a scant contribution to the heat exchange.
- plate-type heat exchangers have been proposed in which the entry distribution channel of the refrigerant fluid is connected to the corresponding passage channels through entry choke points or orifices, of calibrated dimensions, in order to control the passage of the refrigerant fluid from the entry distributor channel to the corresponding passage channels, ensuring an even distribution thereof in its two phases, so as to thus optimize the yield of the heat exchanger if it is used as an evaporator.
- a plate-type heat exchanger of this type is described in WO2006/110090 and has a plurality of heat-exchange plates, which face each other and have respective entry apertures that are mutually adjacent and are provided with a respective folded edging so as to form a collar that protrudes in a direction substantially parallel to the axis of the entry apertures, in order to create an entry distributor conduit for the refrigerant fluid that is cylindrical and substantially smooth, and is connected with the passage channels for the refrigerant fluid which are defined between the heat-exchange plates alternately with the passage channels for the fluid to be cooled through orifices or entry ports provided by slots, which are obtained by molding in the heat-exchange plates, at zones of mutual contact between two adjacent plates which extend around the entry apertures.
- a distance is specified between the edges of the collars of two mutually adjacent heat-exchange plates, so as to form a fissure between the edges of the collars facing each other, for the purpose of preventing interference between the edges of two adjacent plates, which can entail problems during the assembly of the heat exchanger.
- the aim of the present disclosure is to provide a plate-type heat exchanger which is capable of improving the known art in one or more of the above mentioned aspects.
- the disclosure provides a plate-type heat exchanger that is capable of ensuring an even distribution of the refrigerant fluid in the corresponding passage channels defined between the plates of the exchanger, without the risk of decanting the refrigerant fluid into the passage channels of the fluid to be cooled.
- the disclosure also provides a plate-type heat exchanger in which the plates can be provided with a simpler molding process and with a lesser increase in the costs of the mold with respect to the known art.
- the present disclosure provides a heat exchanger that can be easily assembled and which always allows a perfect brazing between adjacent plates.
- the present disclosure further provides a plate-type heat exchanger that is capable of ensuring that all of the incoming flow of refrigerant fluid passes solely through special orifices which are distributed along the extension of the entry distributor channel for the refrigerant fluid.
- the disclosure also provides a plate-type heat exchanger that, owing to the peculiar implementation characteristics, is capable of offering the highest guarantees of reliability and safety in its operation.
- the disclosure further provides a plate-type heat exchanger that can also be competitive from a purely economic viewpoint.
- FIG. 1 is a schematic perspective view of the plate-type heat exchanger according to the disclosure
- FIG. 2 is an exploded perspective view of the heat exchanger according to the disclosure
- FIG. 3 is an enlarged-scale detail of FIG. 2 ;
- FIG. 4 is a cutaway perspective view of a portion of the heat exchanger according to the disclosure.
- FIG. 5 is a cutaway perspective view of a detail of the heat exchanger according to the disclosure.
- FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG. 1 ;
- FIG. 7 is an enlarged-scale view of a detail of FIG. 6 ;
- FIG. 8 is a schematic cutaway perspective view of a possible variation of embodiment of the heat exchanger according to the disclosure.
- the plate-type heat exchanger which is generally designated by the reference numeral 1 , comprises a plurality of heat-exchange plates 2 which are mutually stacked and facing each other so as to define, in the space comprised between them, at least two passage channels, in particular at least one first passage channel 3 and at least one second passage channel 4 , which alternate with each other along the direction of stacking of the heat-exchange plates 2 and are flowed through by respective fluids that are adapted to exchange heat with each other.
- first and the second passage channels 3 and 4 are adapted to be passed through, respectively, by a first fluid, constituted in particular by a refrigerant fluid, and by a second fluid, constituted by a fluid to be cooled.
- the heat-exchange plates 2 are interposed between a first outer covering plate 5 and a second outer covering plate 6 and are, advantageously, provided with respective corrugations 7 which are constituted by mutually parallel ridges and recesses that can extend in directions of various kinds and which are, conveniently, arranged so that the corrugations 7 arranged on mutually adjacent heat-exchange plates 2 can intersect with each other.
- the heat-exchange plates 2 are, preferably, joined together hermetically by way of brazing and, to this end, along their perimeter, they are, advantageously, provided with a respective folded edging 8 which overlaps on the folded edging 8 of an adjacent heat-exchange plate 2 , in order to allow the execution of a perfect perimetric brazing between adjacent heat-exchange plates 2 .
- Each one of the heat-exchange plates 2 has, conveniently, at one of its ends, a respective entry aperture 9 , for one of the two fluids, in particular for the first fluid.
- the entry apertures 9 of the heat-exchange plates 2 are substantially adjacent, so as to define, inside the exchanger, an entry conduit 10 for the first fluid, which basically extends parallel to the direction of stacking of the heat-exchange plates 2 and which allows the first fluid to be distributed within the first passage channels 3 .
- the entry conduit 10 is, advantageously, connected to a first input connector 9 a , which is fixed, conveniently, to the first outer covering plate 5 of the exchanger.
- the entry conduit 10 is, furthermore, connected with the passage channels of the corresponding fluid, i.e., in the example illustrated, with the first passage channels 3 , through one or more orifices 11 , which have, conveniently, a reduced passage section, so as to provide a choked connection between the entry conduit 10 and the first passage channels 3 and thus enable a controlled evaporation of the first fluid, in order to avoid an uneven distribution of the liquid phase of the first fluid into the first passage channels 3 .
- the heat-exchange plates 2 also have respective exit openings 12 , which define, in the exchanger, an outlet manifold 13 for the second fluid, which is connected to the second passage channels 4 and, in turn, is connected to an exit connector 12 a of the second fluid, which is also fixed to the first outer covering plate 5 .
- the heat-exchange plates have, furthermore, respective second entry openings 14 which define, inside the exchanger, an inlet manifold for the second fluid, connected to a second entry opening 14 a , again fixed to the first outer covering plate 5 , and connected with the second passage channels 4 , and further exit openings 15 , which define an outlet manifold for the first fluid, connected to the first passage channels 3 and connected to an exit connector 15 a of the first fluid, and again fixed to the first outer covering plate 5 .
- first covering plate 5 is perforated at the connectors 9 a , 12 a , 14 a and 15 a , in order to allow the entry and the exit of the first and of the second fluid from the exchanger.
- the entry apertures 9 have, in particular, respective collar-like edgings 16 which extend from the edge of the entry apertures 9 along a direction that is substantially parallel to the axis of the entry apertures 9 and the function of which is to close the connection between the entry conduit 10 and the second passage channels 4 .
- Each collar-like edging 16 has, at its opposite end from the end connected to the edge of the corresponding entry aperture 9 , an abutment flange 17 which extends radially with respect to the axis of the entry apertures 9 and is adapted to engage, by contact, the abutment flange 17 of the collar-like edging 16 of an adjacent heat-exchange plate 2 .
- the abutment flange 17 provided on the collar-like edgings 16 makes it possible to ensure the perfect brazing between the collar-like edgings 16 of two adjacent heat-exchange plates 2 , thus ensuring that all of the flow of the first fluid passes through the orifices 11 , without risk of leaks of the first fluid into the second passage channels 4 .
- abutment flanges 17 can protrude from the collar-like edgings 16 for a length comprised, in ratio to the diameter of the entry apertures, of between 1% and 25%, thus giving the entry conduit 10 a light corrugation.
- abutment flanges 17 can easily be provided in the step of molding the heat-exchange plates 2 , at considerably reduced cost, since a dedicated mold to be added downstream is not necessary after the mold-forming of the plates.
- each one of the heat-exchange plates 2 extends, advantageously, between at least one first plane of arrangement 2 a and at least one second plane of arrangement 2 b , which are mutually parallel and spaced apart, and has, around the corresponding entry aperture 9 , at least one flat annular abutment zone 18 which is adapted to be in contact with a corresponding flat annular abutment zone 18 of an adjacent heat-exchange plate 2 .
- each heat-exchange plate 2 lies substantially at the corresponding first plane of arrangement 2 a
- the abutment flange 17 lies substantially at the corresponding second plane of arrangement 2 b.
- a ridge 19 is defined in relief and extends around at least one portion of the edge of the corresponding entry aperture 9 .
- Such ridge 19 is, in particular, adapted to engage a corresponding indentation 20 which is defined in the flat annular abutment zone 18 of the adjacent heat-exchange plate 2 against which the flat annular abutment zone 18 on which the ridge 19 is defined is adapted to make contact.
- the ridge 19 and the corresponding indentation 20 facilitate the operation of centering the heat-exchange plates 2 during the step of stacking them. In this manner, a perfect brazing is always ensured between the adjacent heat-exchange plates 2 at the flat annular abutment zones 18 .
- each orifice 11 is defined between the flat annular abutment zones 18 of two mutually adjacent heat-exchange plates 2 and, in particular, is provided by at least one slot 21 which extends radially with respect to the entry apertures 9 and which is defined on the flat annular abutment zone 18 of the mutually adjacent two heat-exchange plates 2 .
- the lightly-corrugated entry channel of the exchanger according to the disclosure makes it possible to increase the number of heat-exchange plates by over 50% with respect to conventional exchangers, thus making the exchanger according to the disclosure much more competitive, in that for the same exchange surface, it makes it possible to obtain a greater exchanged thermal power.
- the collar-like edgings 16 can be provided in a separate piece with respect to the remaining part of the corresponding plate 2 .
- the collar-like edgings 16 can be joined to the remaining part of the corresponding plates 2 by way of brazing and they can, conveniently, have a flat connection section 16 a , which protrudes radially from the end of the collar-like edging 16 that is adapted to be connected to the corresponding plate and which is designed to engage by contact on the opposite side of the flat annular abutment zone 18 of the corresponding plate 2 from the one against which the flat annular abutment zone 18 of the adjacent plate rests, so as to enable the joining by way of brazing of the flat connection section 16 a to the flat annular abutment zone 18 of the corresponding plate 2 .
- the collar-like edgings 16 can, optionally, have an inclined extension that progressively approaches the axis of the corresponding entry aperture 9 , going from the flat connection section 16 a toward the corresponding abutment flange 17 .
Abstract
A plate-type heat exchanger includes heat-exchange plates which are mutually stacked and facing each other so as to define, in the space between them, at least two passage channels. The heat-exchange plates have respective entry apertures which are substantially mutually adjacent so as to define an entry conduit. The entry conduit is connected with the passage channel of the corresponding fluid through at least one orifice. The entry apertures have respective collar-like edgings. Each one of the collar-like edgings has an abutment flange which extends radially with respect to the axis of the entry apertures and is adapted to engage, by contact, the abutment flange of the collar-like edging of an adjacent heat-exchange plate.
Description
- The present disclosure relates to a plate-type heat exchanger.
- In refrigeration systems that execute refrigeration cycles using vapor expansion, for air-conditioning or refrigeration applications, the use is known of plate-type heat exchangers to provide evaporators, in which a heat exchange occurs between a refrigerant fluid, which, flowing inside a series of passage channels defined in the plate-type heat exchanger, progressively evaporates, absorbing heat from a fluid to be cooled, typically water, which, flowing in channels adjacent to the channels flowed through by the refrigerant fluid, is in turn cooled.
- More specifically, the plate-type heat exchangers that are used as evaporators in refrigeration systems are, typically, constituted by a “pack” of plates, i.e. by a plurality of plates that are mutually stacked, so as to face each other, and are joined together at various points of mutual contact, by way of brazing or welding, or are interconnected by way of the interposition of gaskets.
- In these applications, the refrigerant fluid fed into the plate-type heat exchanger is, generally, in a mixed biphasic state, in which there are a liquid phase and a vapor phase of the coolant fluid.
- A technical problem associated with the use of plate-type heat exchangers as evaporators in refrigeration systems consists of ensuring that the entry distributor channel of the heat exchanger can evenly feed the various channels with refrigerant fluid, avoiding feeding some of them with only the vapor phase, with the obvious consequence of reducing the efficiency of the heat exchange between the refrigerant fluid and the fluid to be cooled, as the vapor phase offers a scant contribution to the heat exchange.
- In order to attempt to solve this problem, plate-type heat exchangers have been proposed in which the entry distribution channel of the refrigerant fluid is connected to the corresponding passage channels through entry choke points or orifices, of calibrated dimensions, in order to control the passage of the refrigerant fluid from the entry distributor channel to the corresponding passage channels, ensuring an even distribution thereof in its two phases, so as to thus optimize the yield of the heat exchanger if it is used as an evaporator.
- A plate-type heat exchanger of this type is described in WO2006/110090 and has a plurality of heat-exchange plates, which face each other and have respective entry apertures that are mutually adjacent and are provided with a respective folded edging so as to form a collar that protrudes in a direction substantially parallel to the axis of the entry apertures, in order to create an entry distributor conduit for the refrigerant fluid that is cylindrical and substantially smooth, and is connected with the passage channels for the refrigerant fluid which are defined between the heat-exchange plates alternately with the passage channels for the fluid to be cooled through orifices or entry ports provided by slots, which are obtained by molding in the heat-exchange plates, at zones of mutual contact between two adjacent plates which extend around the entry apertures.
- In an embodiment of the heat exchanger described in WO2006/110090, a distance is specified between the edges of the collars of two mutually adjacent heat-exchange plates, so as to form a fissure between the edges of the collars facing each other, for the purpose of preventing interference between the edges of two adjacent plates, which can entail problems during the assembly of the heat exchanger.
- As a consequence of the presence of this fissure, the mutually facing edges of the mutually opposite collars of mutually adjacent plates are not brazed together, since they are not in contact with each other.
- Furthermore, in order to ensure the presence of a distance between the edges of two mutually opposite collars, press-molding of the plates with very fine tolerances is required, with a consequent major impact on the cost of the mold.
- The aim of the present disclosure is to provide a plate-type heat exchanger which is capable of improving the known art in one or more of the above mentioned aspects.
- Within this aim, the disclosure provides a plate-type heat exchanger that is capable of ensuring an even distribution of the refrigerant fluid in the corresponding passage channels defined between the plates of the exchanger, without the risk of decanting the refrigerant fluid into the passage channels of the fluid to be cooled.
- The disclosure also provides a plate-type heat exchanger in which the plates can be provided with a simpler molding process and with a lesser increase in the costs of the mold with respect to the known art.
- The present disclosure provides a heat exchanger that can be easily assembled and which always allows a perfect brazing between adjacent plates.
- The present disclosure further provides a plate-type heat exchanger that is capable of ensuring that all of the incoming flow of refrigerant fluid passes solely through special orifices which are distributed along the extension of the entry distributor channel for the refrigerant fluid.
- The disclosure also provides a plate-type heat exchanger that, owing to the peculiar implementation characteristics, is capable of offering the highest guarantees of reliability and safety in its operation.
- The disclosure further provides a plate-type heat exchanger that can also be competitive from a purely economic viewpoint.
- This advantage and these and other advantages which will become better apparent hereinafter are achieved by providing a plate-type heat exchanger according to
claim 1, optionally provided with one or more of the characteristics of the dependent claims. - Further characteristics and advantages of the disclosure will become better apparent from the description of preferred, but not exclusive, embodiments of the plate-type heat exchanger according to the disclosure, which are illustrated for the purposes of non-limiting example in the accompanying drawings wherein:
-
FIG. 1 is a schematic perspective view of the plate-type heat exchanger according to the disclosure; -
FIG. 2 is an exploded perspective view of the heat exchanger according to the disclosure; -
FIG. 3 is an enlarged-scale detail ofFIG. 2 ; -
FIG. 4 is a cutaway perspective view of a portion of the heat exchanger according to the disclosure; -
FIG. 5 is a cutaway perspective view of a detail of the heat exchanger according to the disclosure; -
FIG. 6 is a cross-sectional view taken along the line VI-VI inFIG. 1 ; -
FIG. 7 is an enlarged-scale view of a detail ofFIG. 6 ; and -
FIG. 8 is a schematic cutaway perspective view of a possible variation of embodiment of the heat exchanger according to the disclosure. - With reference to the figures, the plate-type heat exchanger according to the disclosure, which is generally designated by the
reference numeral 1, comprises a plurality of heat-exchange plates 2 which are mutually stacked and facing each other so as to define, in the space comprised between them, at least two passage channels, in particular at least onefirst passage channel 3 and at least onesecond passage channel 4, which alternate with each other along the direction of stacking of the heat-exchange plates 2 and are flowed through by respective fluids that are adapted to exchange heat with each other. - More specifically, the first and the
second passage channels - Conveniently, the heat-
exchange plates 2 are interposed between a firstouter covering plate 5 and a secondouter covering plate 6 and are, advantageously, provided withrespective corrugations 7 which are constituted by mutually parallel ridges and recesses that can extend in directions of various kinds and which are, conveniently, arranged so that thecorrugations 7 arranged on mutually adjacent heat-exchange plates 2 can intersect with each other. - The heat-
exchange plates 2 are, preferably, joined together hermetically by way of brazing and, to this end, along their perimeter, they are, advantageously, provided with a respective folded edging 8 which overlaps on the folded edging 8 of an adjacent heat-exchange plate 2, in order to allow the execution of a perfect perimetric brazing between adjacent heat-exchange plates 2. - Each one of the heat-
exchange plates 2 has, conveniently, at one of its ends, arespective entry aperture 9, for one of the two fluids, in particular for the first fluid. - The
entry apertures 9 of the heat-exchange plates 2 are substantially adjacent, so as to define, inside the exchanger, an entry conduit 10 for the first fluid, which basically extends parallel to the direction of stacking of the heat-exchange plates 2 and which allows the first fluid to be distributed within thefirst passage channels 3. - In particular, the
entry conduit 10 is, advantageously, connected to afirst input connector 9 a, which is fixed, conveniently, to the firstouter covering plate 5 of the exchanger. - The
entry conduit 10 is, furthermore, connected with the passage channels of the corresponding fluid, i.e., in the example illustrated, with thefirst passage channels 3, through one ormore orifices 11, which have, conveniently, a reduced passage section, so as to provide a choked connection between theentry conduit 10 and thefirst passage channels 3 and thus enable a controlled evaporation of the first fluid, in order to avoid an uneven distribution of the liquid phase of the first fluid into thefirst passage channels 3. - It should be noted that, conveniently, at the same end where the
entry aperture 9 for the first fluid is, the heat-exchange plates 2 also haverespective exit openings 12, which define, in the exchanger, anoutlet manifold 13 for the second fluid, which is connected to thesecond passage channels 4 and, in turn, is connected to anexit connector 12 a of the second fluid, which is also fixed to the firstouter covering plate 5. - At their opposite end, the heat-exchange plates have, furthermore, respective
second entry openings 14 which define, inside the exchanger, an inlet manifold for the second fluid, connected to a second entry opening 14 a, again fixed to the firstouter covering plate 5, and connected with thesecond passage channels 4, andfurther exit openings 15, which define an outlet manifold for the first fluid, connected to thefirst passage channels 3 and connected to anexit connector 15 a of the first fluid, and again fixed to the firstouter covering plate 5. - It should be noted that the
first covering plate 5 is perforated at theconnectors - The
entry apertures 9 have, in particular, respective collar-like edgings 16 which extend from the edge of theentry apertures 9 along a direction that is substantially parallel to the axis of theentry apertures 9 and the function of which is to close the connection between theentry conduit 10 and thesecond passage channels 4. - Each collar-
like edging 16 has, at its opposite end from the end connected to the edge of thecorresponding entry aperture 9, anabutment flange 17 which extends radially with respect to the axis of theentry apertures 9 and is adapted to engage, by contact, theabutment flange 17 of the collar-like edging 16 of an adjacent heat-exchange plate 2. - In this manner, the
abutment flange 17 provided on the collar-like edgings 16 makes it possible to ensure the perfect brazing between the collar-like edgings 16 of two adjacent heat-exchange plates 2, thus ensuring that all of the flow of the first fluid passes through theorifices 11, without risk of leaks of the first fluid into thesecond passage channels 4. - It must be noted that the
abutment flanges 17 of the heat-exchange plates 2 protrude inward into theentry conduit 10, in so doing rendering theentry conduit 10 not perfectly smooth, as in the known art, but relatively corrugated. - It should be noted that the
abutment flanges 17 can protrude from the collar-like edgings 16 for a length comprised, in ratio to the diameter of the entry apertures, of between 1% and 25%, thus giving the entry conduit 10 a light corrugation. - It must also be noted that the
abutment flanges 17 can easily be provided in the step of molding the heat-exchange plates 2, at considerably reduced cost, since a dedicated mold to be added downstream is not necessary after the mold-forming of the plates. - In more detail, each one of the heat-
exchange plates 2 extends, advantageously, between at least one first plane ofarrangement 2 a and at least one second plane ofarrangement 2 b, which are mutually parallel and spaced apart, and has, around thecorresponding entry aperture 9, at least one flatannular abutment zone 18 which is adapted to be in contact with a corresponding flatannular abutment zone 18 of an adjacent heat-exchange plate 2. - In particular, the flat
annular abutment zone 18 of each heat-exchange plate 2 lies substantially at the corresponding first plane ofarrangement 2 a, while theabutment flange 17 lies substantially at the corresponding second plane ofarrangement 2 b. - Advantageously, on the flat
annular abutment zone 18 of at least one of the heat-exchange plates 2, aridge 19 is defined in relief and extends around at least one portion of the edge of thecorresponding entry aperture 9. -
Such ridge 19 is, in particular, adapted to engage acorresponding indentation 20 which is defined in the flatannular abutment zone 18 of the adjacent heat-exchange plate 2 against which the flatannular abutment zone 18 on which theridge 19 is defined is adapted to make contact. - The presence of the
ridge 19 and of thecorresponding indentation 20 on the flatannular abutment zones 18 makes it possible to prevent the first fluid, owing to the difference in pressure that is established between theentry conduit 10 and thefirst passage channels 3, from leaking radially between two adjacent heat-exchange plates 2, so entering thefirst passage channels 3 instead of passing through theorifices 11, with consequent loss of thermal yield of the exchanger. - Furthermore, the
ridge 19 and thecorresponding indentation 20 facilitate the operation of centering the heat-exchange plates 2 during the step of stacking them. In this manner, a perfect brazing is always ensured between the adjacent heat-exchange plates 2 at the flatannular abutment zones 18. - Advantageously, each
orifice 11 is defined between the flatannular abutment zones 18 of two mutually adjacent heat-exchange plates 2 and, in particular, is provided by at least oneslot 21 which extends radially with respect to theentry apertures 9 and which is defined on the flatannular abutment zone 18 of the mutually adjacent two heat-exchange plates 2. - In practice it has been found that the disclosure fully achieves the intended aim and objects.
- In particular, it has been experimentally verified that with the entry conduit of the exchanger according to the disclosure, even though it is not perfectly smooth, it is possible to improve and better control the distribution of the refrigerant fluid with respect to the known art.
- Furthermore, it has been experimentally verified that the lightly-corrugated entry channel of the exchanger according to the disclosure makes it possible to increase the number of heat-exchange plates by over 50% with respect to conventional exchangers, thus making the exchanger according to the disclosure much more competitive, in that for the same exchange surface, it makes it possible to obtain a greater exchanged thermal power.
- The disclosure thus conceived is susceptible of numerous modifications and variations, all of which are within the scope of the appended claims. Moreover, all the details may be substituted by other, technically equivalent elements.
- Thus, for example, as shown schematically in
FIG. 8 , the collar-like edgings 16 can be provided in a separate piece with respect to the remaining part of thecorresponding plate 2. - In this case, the collar-
like edgings 16 can be joined to the remaining part of thecorresponding plates 2 by way of brazing and they can, conveniently, have aflat connection section 16 a, which protrudes radially from the end of the collar-like edging 16 that is adapted to be connected to the corresponding plate and which is designed to engage by contact on the opposite side of the flatannular abutment zone 18 of thecorresponding plate 2 from the one against which the flatannular abutment zone 18 of the adjacent plate rests, so as to enable the joining by way of brazing of theflat connection section 16 a to the flatannular abutment zone 18 of thecorresponding plate 2. - Also in this case, the collar-
like edgings 16 can, optionally, have an inclined extension that progressively approaches the axis of thecorresponding entry aperture 9, going from theflat connection section 16 a toward thecorresponding abutment flange 17. - In practice the materials employed, provided they are compatible with the specific use, and the contingent dimensions and shapes, may be any according to requirements and to the state of the art.
- The disclosures in Italian Utility Model Application No. 202019000000665 from which this application claims priority are incorporated herein by reference.
Claims (7)
1-6 (canceled)
7. A plate-type heat exchanger comprises: a plurality of heat-exchange plates which are mutually stacked and facing each other to define, in a space comprised between said heat-exchange plates, at least two passage channels, which alternate with each other along a direction of stacking of the heat-exchange plates and are passed through by respective fluids adapted to exchange heat with each other, said heat-exchange plates having respective entry apertures which are substantially mutually adjacent to define an entry conduit for one of said fluids, said entry conduit being connected with the passage channel of the respective fluid through at least one orifice, said entry apertures having respective collar-like edgings which extend from the edge of said entry apertures along a direction that is substantially parallel to the axis of said entry apertures, wherein each one of said collar-like edgings has, at an opposite end thereof from an end connected to an edge of the corresponding entry aperture, an abutment flange which extends radially with respect to an axis of said entry apertures and is adapted to engage, by contact, the abutment flange of the collar-like edging of an adjacent heat-exchange plate.
8. The plate-type heat exchanger according to claim 7 , wherein each one of said heat-exchange plates extends between at least one first plane of arrangement and at least one second plane of arrangement, which are mutually parallel and spaced apart, and has, around the corresponding entry aperture, at least one flat annular abutment zone which is adapted to be in contact with a corresponding flat annular abutment zone of an adjacent heat-exchange plate, said at least one flat annular abutment zone lying substantially at said first plane of arrangement, said abutment flange lying substantially at said second plane of arrangement.
9. The plate-type heat exchanger according to claim 8 , wherein said flat annular abutment zone of at least one of said heat-exchange plates has a ridge in relief, which extends around at least one portion of the edge of the corresponding entry aperture and is adapted to engage a corresponding indentation defined in the corresponding flat annular abutment zone of the adjacent heat-exchange plate.
10. The plate-type heat exchanger according to claim 8 , wherein said at least one orifice is provided by at least one slot defined on the flat annular abutment zone of at least one of the mutually adjacent heat-exchange plates.
11. The plate-type heat exchanger according to claim 7 , wherein said collar-like edgings are provided in a separate piece with respect to a remaining part of the corresponding heat-exchange plate.
12. The plate-type heat exchanger according to claim 7 , wherein said collar-like edgings are joined to the remaining part of the corresponding heat-exchange plate by way of brazing.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT202019000000665U IT201900000665U1 (en) | 2019-02-27 | 2019-02-27 | PLATE HEAT EXCHANGER. |
IT202019000000665 | 2019-02-27 | ||
PCT/EP2020/054438 WO2020173797A1 (en) | 2019-02-27 | 2020-02-20 | Plate-type heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20220146204A1 true US20220146204A1 (en) | 2022-05-12 |
Family
ID=69714010
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US17/433,822 Pending US20220146204A1 (en) | 2019-02-27 | 2020-02-20 | Plate-type heat exchanger |
Country Status (4)
Country | Link |
---|---|
US (1) | US20220146204A1 (en) |
EP (1) | EP3931513B1 (en) |
IT (1) | IT201900000665U1 (en) |
WO (1) | WO2020173797A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220187031A1 (en) * | 2020-12-10 | 2022-06-16 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Distributor for plate heat exchanger and plate heat exchanger |
WO2024089125A1 (en) * | 2022-10-28 | 2024-05-02 | Alfa Laval Corporate Ab | Plate stack of substantially flat plates |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112648741A (en) * | 2021-01-08 | 2021-04-13 | 深圳市米惜智能电器科技有限公司 | Parallel heat exchanger |
CN114413662A (en) * | 2021-12-14 | 2022-04-29 | 浙江银轮机械股份有限公司 | Heat exchanger |
Citations (4)
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US5971065A (en) * | 1995-10-24 | 1999-10-26 | Alfa Laval Ab | Plate heat exchanger |
US6305466B1 (en) * | 1998-03-11 | 2001-10-23 | Swep International Ab | Three circuit plate heat exchanger |
US20050082049A1 (en) * | 2003-10-21 | 2005-04-21 | Viktor Brost | Plate heat exchanger |
US20080196874A1 (en) * | 2005-04-13 | 2008-08-21 | Alfa Laval Corporate Ab | Plate Heat Exchanger |
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---|---|---|---|---|
US4407359A (en) * | 1980-07-25 | 1983-10-04 | Commissariat A L'energie Atomique | Plate heat exchanger |
US20070089872A1 (en) * | 2005-10-25 | 2007-04-26 | Kaori Heat Treatment Co., Ltd. | Heat exchanger having flow control device |
US10907906B2 (en) * | 2016-02-12 | 2021-02-02 | Mitsubishi Electric Corporation | Plate heat exchanger and heat pump heating and hot water supply system including the plate heat exchanger |
-
2019
- 2019-02-27 IT IT202019000000665U patent/IT201900000665U1/en unknown
-
2020
- 2020-02-20 US US17/433,822 patent/US20220146204A1/en active Pending
- 2020-02-20 EP EP20707379.2A patent/EP3931513B1/en active Active
- 2020-02-20 WO PCT/EP2020/054438 patent/WO2020173797A1/en unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5971065A (en) * | 1995-10-24 | 1999-10-26 | Alfa Laval Ab | Plate heat exchanger |
US6305466B1 (en) * | 1998-03-11 | 2001-10-23 | Swep International Ab | Three circuit plate heat exchanger |
US20050082049A1 (en) * | 2003-10-21 | 2005-04-21 | Viktor Brost | Plate heat exchanger |
US20080196874A1 (en) * | 2005-04-13 | 2008-08-21 | Alfa Laval Corporate Ab | Plate Heat Exchanger |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220187031A1 (en) * | 2020-12-10 | 2022-06-16 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Distributor for plate heat exchanger and plate heat exchanger |
US11920876B2 (en) * | 2020-12-10 | 2024-03-05 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Distributor for plate heat exchanger and plate heat exchanger |
WO2024089125A1 (en) * | 2022-10-28 | 2024-05-02 | Alfa Laval Corporate Ab | Plate stack of substantially flat plates |
Also Published As
Publication number | Publication date |
---|---|
EP3931513A1 (en) | 2022-01-05 |
WO2020173797A1 (en) | 2020-09-03 |
EP3931513B1 (en) | 2023-10-25 |
IT201900000665U1 (en) | 2020-08-27 |
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