EP3017261A1 - Asymmetrical exchanger with ancillary channels for connecting turns - Google Patents

Asymmetrical exchanger with ancillary channels for connecting turns

Info

Publication number
EP3017261A1
EP3017261A1 EP14747721.0A EP14747721A EP3017261A1 EP 3017261 A1 EP3017261 A1 EP 3017261A1 EP 14747721 A EP14747721 A EP 14747721A EP 3017261 A1 EP3017261 A1 EP 3017261A1
Authority
EP
European Patent Office
Prior art keywords
plate
type
hollows
ridges
channels
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14747721.0A
Other languages
German (de)
French (fr)
Other versions
EP3017261B1 (en
Inventor
Ugo Benettolo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zilmet SpA
Original Assignee
Zilmet SpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zilmet SpA filed Critical Zilmet SpA
Priority to SI201431155T priority Critical patent/SI3017261T1/en
Priority to PL14747721T priority patent/PL3017261T3/en
Publication of EP3017261A1 publication Critical patent/EP3017261A1/en
Application granted granted Critical
Publication of EP3017261B1 publication Critical patent/EP3017261B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • 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

Definitions

  • Prior art includes plate heat exchangers comprising at least two separate circuits respectively for the circulation of a primary fluid and a secondary fluid, where those paths are defined by a plurality of exchange plates with facing surfaces, featuring ridges and hollows, generally distributed in a herringbone pattern.
  • Prior art heat exchangers are made by stacking the plates in question alternating the rotation of every other one by 180° so that the ridges and hollows of one plate are crossed with respect to the ridges and hollows of the adjacent plate.
  • the plates are called symmetric when the ridges and hollows are such that the sections of the channels of both paths used by the two fluids are substantially equal, that is, resulting in equal head loss with equal flows.
  • These heat exchangers are commonly used to heat water for domestic use using the hot water of the heating system.
  • the temperature of the heating system fluid must be much higher than that of the domestic water.
  • the heating water inlet temperature is 75°C and the outlet temperature may be about 60°C.
  • the inlet water temperature for domestic use may be about 10°C and the outlet temperature about 55°C.
  • Prior art also includes plates specially shaped in such a way that the section for the heating fluid is wider than the section for the domestic hot water, and therefore the head losses are differentiated.
  • the prior art includes the so-called asymmetric heat exchangers, that is, formed by plates comprising ridges with a different shape than the hollows, such as, for example, flat ridges to make the section of the channel even wider.
  • asymmetric heat exchangers that is, formed by plates comprising ridges with a different shape than the hollows, such as, for example, flat ridges to make the section of the channel even wider.
  • Plates having different head losses with equal flows are also known, obtained by increasing the pitch of the ridges, that is, the distance between the ridges of two adjacent channels.
  • This type of heat exchanger is suitable for the exchange between water and cooling fluid, where the water flows through the path having lower head losses.
  • the narrowest channels are excessively smaller than the wider channels.
  • Heat exchangers with plates where the depth of the secondary hollow is at least 40% and preferably 50% of the depth of the larger hollow are known. Heat exchangers where the depth of the secondary hollows is diversified on different plates are also known.
  • exchangers where a single plate has secondary hollows having two different depths used in two different areas of the plate are also known.
  • One drawback is the fact that the pitch of the welding points is not constant and therefore there are areas where the plates may be less rigid, giving rise to localized deformations that impair the functioning and efficiency of the exchanger.
  • the main object of the present invention is to create paths with different head losses, while maintaining symmetrically distributed welding points as in the heat exchangers of the known type, to the benefit of resistance to pressure.
  • Another object of the present invention is to increase the turbulence of the flow in at least one path.
  • the new asymmetric plate heat exchanger includes in its main parts at least one series of superimposed plates in a pack, brazed together with possible perimeter seals to confine the fluids inside, and passage holes for at least two exchange fluids, these holes also having seals alternately arranged so as to convey the two fluids in the spaces between the plates, following at least two hydraulically isolated paths.
  • the heat exchanger therefore comprises at least two separate paths for a primary fluid and a secondary fluid, each of these two paths being defined by a pair of the facing plates, equipped with alternating ridges and hollows arranged substantially in a herringbone pattern, that is, arranged in two directions which intersect with each other, and where those two paths have different head losses.
  • the heat exchanger includes, in particular, two different types of plates, arranged alternately in the pack forming the heat exchanger, where the first type of plate comprises ridges and hollows at a constant pitch and constant height or depth.
  • the second type of plate also comprises ridges and hollows at a constant pitch and constant height or depth but has a particular shape as hereinafter described and claimed.
  • all the hollows of the plate have a constant depth, except for localized raised portions, that is, having a length much shorter than the length of the hollow.
  • One or more of the elevations are distributed along each hollow and variously distributed. These localized raised portions of one side of the plate correspond, on the opposite side of the plate, to localized lowered portions on the ridges.
  • a secondary path is created, with a greater head loss, formed by main channels, along the hollows of the two facing plates, where there are constrictions in the channels created by the raised portions, suited to increase the turbulence of the fluid and increase the head loss.
  • a primary path with a lower head loss is created between them, formed by two series of channels, a first series of main channels along the hollows, and a second series of ancillary channels, transverse to the main channels, created by the lowered portions that put the main channels in communication transversely.
  • These main channels and the ancillary transverse channels in fact increase the section for the passage of the flow, thus reducing the head loss.
  • these hollows and ridges are arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane, thus creating two directions which intersect each other.
  • These raised portions and corresponding lowered portions are distributed preferably aligned along directions not intersecting the direction of the ridges and hollows.
  • these raised portions and lowered portions are aligned in a direction parallel to the direction of the ridges and hollows of the specular half.
  • Each type of plate is in fact made on a dedicated line so that, from each line, the plate obtained is already correctly positioned to be superimposed on the plate coming from the second line. Therefore, the need to rotate the plate 180° as in the assembly procedures of the known type of heat exchangers which use plates which are all the same is eliminated.
  • Figure 1 shows a side view (Al 1) of a plate (A) of the first type, with ridges
  • Figure la shows a side view of the plate (A) of the first type.
  • Figure 2 shows a side view (B l l) of a plate (B) of the second type, with ridges (B2) and hollows (B3) arranged in a herringbone pattern, with lowered portions (B21) located on the ridges (B2), corresponding to raised portions (B31) located in the hollows (B3) of the opposite side (B12).
  • Figure 3 shows a cross-section of a pack obtained by the superimposition of four plates, where two plates (A) of the first type are alternated with two plates (B) of the second type.
  • Figure 3a shows a detailed view of the cross-section in Figure 3.
  • Figure 4 shows a perspective drawing of a plate (A) of the first type
  • Figure 5 shows a perspective drawing of a plate (B) of the second type.
  • the ridges and hollows on one side of the plate are hollows and ridges on the opposite side.
  • the raised portions provided for in this patent may be placed on both the hollows and the ridges with an opposite effect on the opposite side of the same plate.
  • the main parts of the new asymmetric plate exchanger comprise plates (A, B) superimposed in a pack, brazed together with possible perimeter seals, to confine the fluids inside, and holes (C) for the passage of the exchange fluids, these holes (C) are themselves brazed together at the edges or equipped with seals alternately arranged so as to convey the two fluids in question in the spaces between the plates along at least two hydraulically isolated paths (1, 2) with different head losses.
  • the heat exchanger comprises at least two paths (1, 2) separated respectively for a primary fluid and a secondary fluid, each of the two paths (1, 2) being defined by a pair (A, B) of the aforementioned facing plates.
  • the heat exchanger includes two different types of plates, arranged alternately in the pack making up the heat exchanger, as shown for example in Figure 3.
  • the first type of plate (A) comprises a plurality of alternating ridges (A2) and hollows (A3), arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane (A4) according to two directions (XI, X2) intersecting each other.
  • Said ridges (A2) and hollows (A3) have a modular or constant pitch (A5) and have a constant height or depth, that is, the distance (A6) between the top of the ridges and the bottom of the hollows is constant.
  • the second type of plate (B) comprises a plurality of alternated ridges (B2) and hollows (B3), arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane (B4) according to two directions (XI, X2) intersecting each other.
  • Said ridges (B2) and hollows (B3) have a modular or constant pitch (B5), equal to or different from the pitch (A5) of the first type of plate (A).
  • (B3) of the plate (B) have a constant depth (B6), with the exception of localized raised portions (B31), that is, having a length much shorter than the length of the hollows (B3).
  • These raised portions (B31) or lowered portions (B21) are distributed along each hollow (B3) or ridge (B2), for example, one or more for each hollow (B3) or ridge (B2), at a modular or constant distance.
  • Each of these paths (1, 2) of the two fluids is created by placing one plate of the first type (A) with one plate of the second type (B), so that the hollows (A3, B3) and ridges (A2, B2 ) of the two plates are crossed.
  • the path in which the primary fluid circulates, or the primary path (1) is obtained by placing a plate of the first type (A) with a plate of the second type (B) on the side of the lowered portions (B21) of the ridges (B2).
  • This primary path (1) has a lower head loss and is formed by two series of channels (11, 12).
  • the first series of channels, or the main channels (1 1) are formed by the hollows (B3, A3) of the two plates (B, A) facing each other, while the second series of channels, or ancillary channels (12) are transverse to the main channels (11) and created by the lowered portions (B21) that put the main channels (11) in communication transversely.
  • the raised portions (B31) and corresponding lowered portions (B21) are distributed preferably aligned along directions (Yl, Y2) intersecting the direction of the ridges (B2) and hollows (B3).
  • the lowered portions (B21) are aligned in a direction (Yl, Y2) parallel to the direction (XI, X2) of the hollows (B3) of the opposite specular half, and in particular are aligned with the extension of the lowered portion (B3) of the opposite specular half, thereby creating a network of main (11) and crossed secondary (12) channels.
  • This path in which the secondary fluid circulates, or the secondary path (2) is obtained by placing the plate of the first type (A) with the plate of the second type (B) on the side of the raised portions (B31) of the hollows (B3).
  • This secondary path (2) has a greater head loss and is formed by a series of channels (21) formed by the hollows (B3, A3) of the two facing plates (B,

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

Abstract

The invention is a new asymmetrical plate-type exchanger whose primary path (1) has lower flow resistance than the secondary path, with plates provided with ridges forming two series of turns or channels, of which a first series of main channels (11) defined by said ridges on the two facing plates (A, B), and a second series of ancillary channels (12), positioned crosswise with respect to said main channels (11), defined by lowered portions (B21) that place said main channels (11) in communication crosswise and are aligned according to a direction (Y1, Y2) that is parallel to and/or coinciding with the extension of the hollow (B3) in the opposite specular half, thus defining a network of said main (11) and secondary (12) crossed channels.

Description

ASYMMETRICAL EXCHANGER WITH ANCILLARY CHANNELS FOR CONNECTING TURNS
DESCRIPTION
This patent relates to plate heat exchangers and in particular to a new asymmetrical plate heat exchanger with ancillary connection channels. Prior art includes plate heat exchangers comprising at least two separate circuits respectively for the circulation of a primary fluid and a secondary fluid, where those paths are defined by a plurality of exchange plates with facing surfaces, featuring ridges and hollows, generally distributed in a herringbone pattern.
Prior art heat exchangers are made by stacking the plates in question alternating the rotation of every other one by 180° so that the ridges and hollows of one plate are crossed with respect to the ridges and hollows of the adjacent plate.
Usually the plates are called symmetric when the ridges and hollows are such that the sections of the channels of both paths used by the two fluids are substantially equal, that is, resulting in equal head loss with equal flows. These heat exchangers are commonly used to heat water for domestic use using the hot water of the heating system.
To achieve the heat transfer, the temperature of the heating system fluid must be much higher than that of the domestic water. Generally the heating water inlet temperature is 75°C and the outlet temperature may be about 60°C. The inlet water temperature for domestic use may be about 10°C and the outlet temperature about 55°C.
Prior art also includes plates specially shaped in such a way that the section for the heating fluid is wider than the section for the domestic hot water, and therefore the head losses are differentiated.
For this purpose the prior art includes the so-called asymmetric heat exchangers, that is, formed by plates comprising ridges with a different shape than the hollows, such as, for example, flat ridges to make the section of the channel even wider. With these types of plates, however, the heat exchange surface between the two fluids is reduced.
Plates having different head losses with equal flows are also known, obtained by increasing the pitch of the ridges, that is, the distance between the ridges of two adjacent channels. This type of heat exchanger is suitable for the exchange between water and cooling fluid, where the water flows through the path having lower head losses.
In this case, however, the contact area between the plates themselves are relatively large and therefore underutilized for the heat exchange between the fluids, thus reducing the efficiency of the heat exchanger.
These solutions, however, compromise the rigidity of the plates due to the reduced number of contact points between the plates making the heat exchanger unsuitable for high pressures.
In addition, the narrowest channels are excessively smaller than the wider channels.
Heat exchangers with plates where the depth of the secondary hollow is at least 40% and preferably 50% of the depth of the larger hollow are known. Heat exchangers where the depth of the secondary hollows is diversified on different plates are also known.
Furthermore, exchangers where a single plate has secondary hollows having two different depths used in two different areas of the plate are also known. One drawback is the fact that the pitch of the welding points is not constant and therefore there are areas where the plates may be less rigid, giving rise to localized deformations that impair the functioning and efficiency of the exchanger.
To overcome all the drawbacks mentioned above, a new type of asymmetric heat exchanger with plates provided with ancillary connection channels between the main channels was designed and constructed.
The main object of the present invention is to create paths with different head losses, while maintaining symmetrically distributed welding points as in the heat exchangers of the known type, to the benefit of resistance to pressure.
Another object of the present invention is to increase the turbulence of the flow in at least one path.
These and other aims, direct and complementary, are achieved by the new type of heat exchanger with asymmetrical plates with ancillary connection channels between the main channels.
The new asymmetric plate heat exchanger includes in its main parts at least one series of superimposed plates in a pack, brazed together with possible perimeter seals to confine the fluids inside, and passage holes for at least two exchange fluids, these holes also having seals alternately arranged so as to convey the two fluids in the spaces between the plates, following at least two hydraulically isolated paths.
The heat exchanger therefore comprises at least two separate paths for a primary fluid and a secondary fluid, each of these two paths being defined by a pair of the facing plates, equipped with alternating ridges and hollows arranged substantially in a herringbone pattern, that is, arranged in two directions which intersect with each other, and where those two paths have different head losses.
The heat exchanger includes, in particular, two different types of plates, arranged alternately in the pack forming the heat exchanger, where the first type of plate comprises ridges and hollows at a constant pitch and constant height or depth.
The second type of plate also comprises ridges and hollows at a constant pitch and constant height or depth but has a particular shape as hereinafter described and claimed. Considering one side of the plate of the second type, all the hollows of the plate have a constant depth, except for localized raised portions, that is, having a length much shorter than the length of the hollow. One or more of the elevations are distributed along each hollow and variously distributed. These localized raised portions of one side of the plate correspond, on the opposite side of the plate, to localized lowered portions on the ridges.
Placing one plate of the first type facing one plate of the second type, so that the hollows and ridges of the two plates are crossed, a flow path of one of the two fluids is created between them.
In particular, placing one plate of the first type with one plate of the second type on the side with the raised portions, a secondary path is created, with a greater head loss, formed by main channels, along the hollows of the two facing plates, where there are constrictions in the channels created by the raised portions, suited to increase the turbulence of the fluid and increase the head loss.
In contrast, placing one plate of the first type with one plate of the second type on the side with the lowered portions, a primary path with a lower head loss is created between them, formed by two series of channels, a first series of main channels along the hollows, and a second series of ancillary channels, transverse to the main channels, created by the lowered portions that put the main channels in communication transversely. These main channels and the ancillary transverse channels in fact increase the section for the passage of the flow, thus reducing the head loss.
As noted, these hollows and ridges are arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane, thus creating two directions which intersect each other.
These raised portions and corresponding lowered portions are distributed preferably aligned along directions not intersecting the direction of the ridges and hollows. In particular, on each of the two halves of the plate, these raised portions and lowered portions are aligned in a direction parallel to the direction of the ridges and hollows of the specular half.
Since the new heat exchanger is assembled using two types of alternating plates, the assembly procedures are faster and simplified.
Each type of plate is in fact made on a dedicated line so that, from each line, the plate obtained is already correctly positioned to be superimposed on the plate coming from the second line. Therefore, the need to rotate the plate 180° as in the assembly procedures of the known type of heat exchangers which use plates which are all the same is eliminated.
The characteristics of the present invention will be better clarified by the following description with reference to the drawings, attached by way of non-limiting example.
Figure 1 shows a side view (Al 1) of a plate (A) of the first type, with ridges
(A2) and hollows (A3) arranged in a herringbone pattern.
Figure la shows a side view of the plate (A) of the first type.
Figure 2 shows a side view (B l l) of a plate (B) of the second type, with ridges (B2) and hollows (B3) arranged in a herringbone pattern, with lowered portions (B21) located on the ridges (B2), corresponding to raised portions (B31) located in the hollows (B3) of the opposite side (B12). Figure 3 shows a cross-section of a pack obtained by the superimposition of four plates, where two plates (A) of the first type are alternated with two plates (B) of the second type.
Figure 3a shows a detailed view of the cross-section in Figure 3.
Figure 4 shows a perspective drawing of a plate (A) of the first type and Figure 5 shows a perspective drawing of a plate (B) of the second type. It is appropriate to note that the ridges and hollows on one side of the plate are hollows and ridges on the opposite side. Thus ridges and hollows are relative to the side being observed. Therefore, the raised portions provided for in this patent may be placed on both the hollows and the ridges with an opposite effect on the opposite side of the same plate.
The main parts of the new asymmetric plate exchanger comprise plates (A, B) superimposed in a pack, brazed together with possible perimeter seals, to confine the fluids inside, and holes (C) for the passage of the exchange fluids, these holes (C) are themselves brazed together at the edges or equipped with seals alternately arranged so as to convey the two fluids in question in the spaces between the plates along at least two hydraulically isolated paths (1, 2) with different head losses.
Therefore, the heat exchanger comprises at least two paths (1, 2) separated respectively for a primary fluid and a secondary fluid, each of the two paths (1, 2) being defined by a pair (A, B) of the aforementioned facing plates. In particular the heat exchanger includes two different types of plates, arranged alternately in the pack making up the heat exchanger, as shown for example in Figure 3.
The first type of plate (A) comprises a plurality of alternating ridges (A2) and hollows (A3), arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane (A4) according to two directions (XI, X2) intersecting each other.
Said ridges (A2) and hollows (A3) have a modular or constant pitch (A5) and have a constant height or depth, that is, the distance (A6) between the top of the ridges and the bottom of the hollows is constant.
The second type of plate (B) comprises a plurality of alternated ridges (B2) and hollows (B3), arranged in a herringbone pattern, that is, arranged specularly with respect to a central plane (B4) according to two directions (XI, X2) intersecting each other.
Said ridges (B2) and hollows (B3) have a modular or constant pitch (B5), equal to or different from the pitch (A5) of the first type of plate (A).
Considering one side (B 12) of the second type of plate (B), all the hollows
(B3) of the plate (B) have a constant depth (B6), with the exception of localized raised portions (B31), that is, having a length much shorter than the length of the hollows (B3).
These localized raised portions (B31) on the side (B12) of the plate (B) correspond, on the opposite side (B l l) of the plate (B), with the localized lowered portions (B21) on the ridges (B2).
These raised portions (B31) or lowered portions (B21) are distributed along each hollow (B3) or ridge (B2), for example, one or more for each hollow (B3) or ridge (B2), at a modular or constant distance.
Each of these paths (1, 2) of the two fluids is created by placing one plate of the first type (A) with one plate of the second type (B), so that the hollows (A3, B3) and ridges (A2, B2 ) of the two plates are crossed.
In particular, the path in which the primary fluid circulates, or the primary path (1) is obtained by placing a plate of the first type (A) with a plate of the second type (B) on the side of the lowered portions (B21) of the ridges (B2). This primary path (1) has a lower head loss and is formed by two series of channels (11, 12). The first series of channels, or the main channels (1 1) are formed by the hollows (B3, A3) of the two plates (B, A) facing each other, while the second series of channels, or ancillary channels (12) are transverse to the main channels (11) and created by the lowered portions (B21) that put the main channels (11) in communication transversely.
These main channels (1 1) and these transverse ancillary channels (12) in fact increase the section for the passage of the flow, thus reducing the head loss.
In the preferred embodiment, as shown in Figure 2, the raised portions (B31) and corresponding lowered portions (B21) are distributed preferably aligned along directions (Yl, Y2) intersecting the direction of the ridges (B2) and hollows (B3).
On each of the two specular halves of the plate (B) of the second type, the lowered portions (B21) are aligned in a direction (Yl, Y2) parallel to the direction (XI, X2) of the hollows (B3) of the opposite specular half, and in particular are aligned with the extension of the lowered portion (B3) of the opposite specular half, thereby creating a network of main (11) and crossed secondary (12) channels.
This path in which the secondary fluid circulates, or the secondary path (2) is obtained by placing the plate of the first type (A) with the plate of the second type (B) on the side of the raised portions (B31) of the hollows (B3).
This secondary path (2) has a greater head loss and is formed by a series of channels (21) formed by the hollows (B3, A3) of the two facing plates (B,
A), where in the main channels (21) of the secondary path (2) there are narrowed portions (22) created by the raised portions (B31), which reduce the section for the passage of the fluid, increasing the turbulence of the fluid and increasing the head loss. Therefore, with reference to the preceding description and the attached drawings the following claims are made.

Claims

1. Asymmetrical plate-type exchanger comprising several stacked plates (A, B) forming a pack, welded and provided with holes (C) for the passage of at least two fluids, a primary fluid and a secondary fluid, said holes (C) being suited to convey said two fluids into the spaces between pairs (A, B) of facing plates following at least two hydraulically insulated paths (1, 2), each one of said plates (A, B) being provided with alternating ridges (A2, B2) and hollows (A3, B3), and wherein said two paths (1, 2) have different flow resistance in the presence of the same flow, characterized in that it comprises at least one plate (B),
■ wherein said hollows (B3) on one side (B 12) of said plate (B) have all constant depth (B6), except for one or more localized raised portions (B31) that are shorter than the hollow (B3),
■ and wherein said localized raised portions (B31) on said side (B 12) correspond, on the opposite side (B l l) of the same plate (B), to localized lowered portions (B21) in the ridges (B2).
2. Asymmetrical plate-type exchanger according to claim 1, characterized in that the raised portions provided can be positioned both on the hollows and on the ridges, with opposite effect on the opposite side of the same plate.
3. Asymmetrical plate-type exchanger according to claim 1, characterized in that it comprises two types of alternating stacked plates (A, B), wherein:
■ the first type of plate (A) comprises a plurality of said alternating ridges (A2) and hollows (A3) having constant height or depth (A6),
■ the second type of plate (B) comprises a plurality of said alternating ridges (B2) and hollows (B3), with said lowered portions (B21) on said ridges (B2) and said raised portions (B31) on said hollows (B3).
4. Asymmetrical plate-type exchanger according to claim 1 or 2, characterized in that one or more of said raised portions (B31) or lowered portions (B21) are distributed along each hollow (B3) or ridge (B2) at a modular or constant distance.
5. Asymmetrical plate-type exchanger according to claim 3, characterized in that said ridges (A2) and hollows (A3) of said plate (A) of the first type are positioned at a modular or constant pitch (A5).
6. Asymmetrical plate-type exchanger according to claim 4, characterized in that said ridges (B2) and hollows (B3) of said plate (B) of the second type are positioned at a modular or constant pitch (B5), equal to or different from said pitch (A5) present in the plate (A) of the first type.
7. Asymmetrical plate-type exchanger according to claim 3, characterized in that said ridges (A2, B2) and hollows (A3, B3) on said plates (A, B) of the first and second type are arranged according to a fish bone pattern, that is, are arranged specularly with respect to a centre plane (A4, B4) according to two directions (XI, X2) intersecting each other.
S. Asymmetrical plate-type exchanger according to the preceding claims, characterized in that the primary path (1) with lower flow resistance, in which said primary fluid circulates, obtained in said plate (A) of the first type, facing said plate (B) of the second type on the side of said lowered portions (B21) in the ridges (B2), is formed by two series of channels, of which a first series of main channels (1 1) defined by said hollows (A3, B3) in the two facing plates (A, B), and a second series of ancillary channels (12), arranged crosswise to said main channels (1 1), defined by said lowered portions (B21) that place said main channels (1 1) in communication crosswise.
9. Asymmetrical plate-type exchanger according to claim 7, characterized in that said raised portions (B31) on the plate (B) of the second type are distributed so that they are aligned along directions (Yl, Y2) intersecting the direction (XI, X2) of said ridges (B2) and hollows (B3).
10. Asymmetrical plate-type exchanger according to claim 8, characterized in that, on each one of the two specular halves of the plate (B) of the second type, said lowered portions (B21) are aligned according to a direction (Yl, Y2) parallel to and/or coinciding with the extension of the hollow (B3) in the opposite specular half, thus defining a network of said main (11) and secondary (12) crossed channels.
11. Asymmetrical plate-type exchanger according to the preceding claims, characterized in that the secondary path (2) with higher flow resistance, in which said secondary fluid circulates, obtained in said plate (A) of the first type, facing said plate (B) of the second type on the side of said raised portions (B31) on the hollows (B3), is formed by a series of main channels (21), defined by said hollows (A3, B3) in the two facing plates (A, B), wherein in said main channels (21) of the secondary path (2) there are narrowed portions (22) defined by said raised portions (B31).
EP14747721.0A 2013-07-03 2014-07-03 Asymmetrical exchanger with ancillary channels for connecting turns Active EP3017261B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SI201431155T SI3017261T1 (en) 2013-07-03 2014-07-03 Asymmetrical exchanger with ancillary channels for connecting turns
PL14747721T PL3017261T3 (en) 2013-07-03 2014-07-03 Asymmetrical exchanger with ancillary channels for connecting turns

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000187A ITPD20130187A1 (en) 2013-07-03 2013-07-03 ASYMMETRICAL EXCHANGER WITH AUXILIARY LINKING BETWEEN SPIRE
PCT/IB2014/062817 WO2015001506A1 (en) 2013-07-03 2014-07-03 Asymmetrical exchanger with ancillary channels for connecting turns

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EP3017261A1 true EP3017261A1 (en) 2016-05-11
EP3017261B1 EP3017261B1 (en) 2019-01-02

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EP (1) EP3017261B1 (en)
IT (1) ITPD20130187A1 (en)
PL (1) PL3017261T3 (en)
SI (1) SI3017261T1 (en)
TR (1) TR201904569T4 (en)
WO (1) WO2015001506A1 (en)

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JP6963957B2 (en) * 2017-09-28 2021-11-10 株式会社日阪製作所 Plate heat exchanger
DE102018002201B4 (en) 2018-03-19 2021-03-18 EAW Energieanlagenbau GmbH Westenfeld Water-lithium bromide absorption refrigeration system
CN108645267A (en) * 2018-04-30 2018-10-12 南京理工大学 Novel fishbone adds the plate-type heat exchanger slab of fusiformis protrusion
CN108801035A (en) * 2018-04-30 2018-11-13 南京理工大学 Novel fishbone adds the plate-type heat exchanger slab of semi-cylindrical protrusion
CN108645268A (en) * 2018-04-30 2018-10-12 南京理工大学 Add the plate-type heat exchanger slab of semicolumn protrusion
CN108827058A (en) * 2018-04-30 2018-11-16 南京理工大学 A kind of plus shuttle shape protrusion plate-type heat exchanger slab
SE545690C2 (en) * 2020-01-30 2023-12-05 Swep Int Ab A brazed plate heat exchanger and use thereof
SE2250767A1 (en) * 2022-06-22 2023-12-23 Alfa Laval Corp Ab Plate heat exchanger

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Publication number Priority date Publication date Assignee Title
AT406301B (en) * 1998-06-24 2000-04-25 Ernst P Fischer Maschinen Und PLATE HEAT EXCHANGER
EP2233873A1 (en) * 2009-03-12 2010-09-29 Robert Bosch GmbH Plate Heat Exchanger
EP2267391B1 (en) * 2009-06-26 2018-04-11 SWEP International AB Asymmetric heat exchanger

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Title
See references of WO2015001506A1 *

Also Published As

Publication number Publication date
ITPD20130187A1 (en) 2015-01-04
SI3017261T1 (en) 2019-07-31
PL3017261T3 (en) 2019-08-30
EP3017261B1 (en) 2019-01-02
TR201904569T4 (en) 2019-04-22
WO2015001506A1 (en) 2015-01-08

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