• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:SE1050690A1
    申请号:SE1050690
    申请日:2010-06-24
    公开日:2011-12-25
    发明作者:Jens Romlund
    申请人:Alfa Laval Corp Ab；
    IPC主号:
    专利说明:

    SUMMARY OF THE INVENTION The object of the present invention is to provide a heat exchanger plate and a plate heat exchanger, which help to reduce the size of the contact points or contact areas.
    A special effort is being made to reduce the size of the contact areas in asymmetric plate heaters.
    This object is achieved with the initially stated heat exchanger plate, which is characterized in that the support surface of the valleys slopes in relation to the plane of propagation. As the support surface of the valleys slopes, the contact point formed with a corresponding heat exchanger plate will become a small contact area in comparison with when the support surface is parallel to the plane of propagation.
    According to an embodiment of the invention, the second width is longer than the first width, i.e. the support surface of the valleys is wider than the support surface of the ridges, which enables asymmetric plate heat exchangers to be achieved. The size of the contact area at the relatively wide support surfaces in the valleys can be reduced in an elegant manner by the specified slope.
    According to a further embodiment of the invention, the first width approaches zero, i.e. the support surface of the ridges approaches zero and can be formed by a rounding. Such a rounding can have a radius of curvature, which is then relatively short.
    According to a further embodiment of the invention, the support surface of the valleys is substantially flat. It should be noted, however, that the support surface may have a certain curvature, concave or convex, but still a slope from one of the edge surfaces to the other of the edge surfaces.
    According to a further embodiment of the invention, the support surface of the valleys is inclined relative to the plane of distribution with an inclination angle which is 3-15 °, preferably 3-7 °. The object is also achieved with the initially indicated plate heat exchanger, which is characterized in that the support surface of the valleys of the primary plates is inclined in relation to the plane of propagation and that the support surface of the ridges of the secondary plates is inclined in relation to the plane of propagation.
    Because the support surface of the valleys of the primary plates and the support surface of the axes of the secondary plates are inclined, the contact point formed between these support surfaces of the primary plates and the secondary plates will become a small contact area compared with when these support surfaces are parallel to the plane of propagation.
    According to an embodiment of the invention, the second width of the primary plates is longer than the first width of the primary plates, the first width of the secondary plates being longer than the second width of the secondary plates. With such a configuration of the ridges and valleys of the primary plates and the secondary plates, an asymmetric plate heat exchanger is obtained.
    According to a further embodiment of the invention, the first width of the primary plates and the second width of the secondary plates approach zero. This means that the support surface of the ridges of the primary plates and the support surface of the valleys of the secondary plates approach zero and can be formed by a rounding. Such a rounding can have a radius of curvature, which is then relatively short.
    According to a further embodiment of the invention, the support surface of the valleys of the primary plates and the support surface of the ridges of the secondary plates are substantially flat. It should be noted that these support surfaces may have a certain curvature, concave or convex, but still a slope from one of the edge surfaces to the other edge surface.
    According to a further embodiment of the invention, the support surface of the valleys of the primary plates and the support surface of the ridges of the secondary plates are inclined relative to the plane of propagation with an inclination angle of 3-15 °, preferably 3-7 °. Such an angle is advantageous in order to effectively reduce the size of the contact area and at the same time enable a sufficient asymmetry of the plate heat exchanger.
    According to a further embodiment of the invention, the support surface of the valleys of one of the primary plates and the support surface of the ridges of one of the secondary plates abut each other, this primary plate and this secondary plate enclosing one of the first plate spaces with a first flow volume, while ridges the support surface of one of the primary plates and the support surface of the valleys of one of the secondary plates abut each other, said primary plate and this secondary plate enclosing one of the second plate gaps with a second flow volume, the ratio between the first flow volume and the second flow volume but is between 1.2 and 3, preferably between 1.5 and 2.5 and more preferably between 1.8 and 2.1.
    According to a further embodiment of the invention, the primary plates and the secondary plates are formed by different heat exchanger plates. Such a design of particularly advantageous in soldered, or otherwise permanently connected heat exchanger plates which may possibly have an outer flank extending around all or part of the heat exchanger plate away from the plane of propagation. The primary plates and the secondary plates are manufactured here separately, whereby the support surfaces of the ridges of the primary plates have a smaller width than the support surfaces of the ridges of the secondary plates. According to a further embodiment of the invention, the primary plates and the secondary plates are identical, each other heat exchanger plate in the plate package being turned 180 ° in such a way that the support surface of the ridges of every other heat exchanger plate abuts and crosses the ridges. support surface of the intermediate heat exchanger plates and wherein the heat exchanger plates are pressed against each other with clamping means. The invention is advantageous also for this type of plate heat exchanger as the pressing of the heat exchanger plates against each other leads to a certain deformation of the contact points so that they form a contact area. With the invention according to the invention and the inclination of the support surfaces of the valleys of the primary plates and of the ridges of the secondary plates, the size of the contact areas will be reduced in relation to whether these support surfaces had extended parallel to the plane of distribution.
    According to a further embodiment of the invention, each heat exchanger plate has a first end and a second opposite end with respect to the center axis, the first edge surfaces of the primary plates and the secondary plates facing the first end while the second edge surfaces of the primary plates and the secondary plates face the the other end.
    According to an advantageous variant of this embodiment, the support surface of the valleys of the primary plates slopes from the first edge surfaces towards the plane of propagation and towards those edge surfaces, while the support surface of the axes of the secondary plates slopes from the first edge surfaces towards the plane of spread and towards the second edge. - the surfaces. If the heat exchanger plates are arranged in this way, the flow resistance in the first plate gaps will be relatively small in one flow direction but relatively large in a second opposite flow direction.
    According to a second variant of this embodiment, the support surface of the valleys of the primary plates slopes from the first edge surfaces towards the spreading plane and towards the second edge surfaces while the support surface of the axes of the secondary plates slopes from the second edge surfaces towards the spreading plane and the first edge surfaces. In this variant, the flow resistance in the first plate gaps becomes substantially equal in both flow directions.
    BRIEF DESCRIPTION OF THE DRAWINGS The present invention will now be further elucidated by a description of various embodiments and with reference to the accompanying drawings. 10 15 20 25 30 35 FIG.
    FIG.
    FIG.
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    Fig. 10 schematically shows a front view of a plate heat exchanger according to a first embodiment of the invention. schematically shows a side view of the plate heat exchanger in Fig. 1. schematically shows a front view of a plate heat exchanger according to a second embodiment of the invention. schematically shows a side view of the plate heat exchanger in Fig. 3. schematically shows a plan view of a heat exchanger plate in the form of a primary plate of the plate heat exchanger in Fig. 1. schematically shows a plan view of a heat exchanger plate in the form of a secondary plate of the plate heat exchanger in Fig. 1. schematically a view of the primary plate in Fig. 5 and the secondary plate in Fig. 6 arranged on each other. schematically shows a cross section through four of the heat exchanger plates in the plate heat exchanger in Figs. 1-4. shows schematically a view of the pattern of a primary plate and a secondary plate according to a first variant. shows schematically a view of the pattern of a primary plate and a secondary plate according to a second variant.
    DETAILED DESCRIPTION OF DIFFERENT EMBODIMENTS OF THE INVENTION Referring to the accompanying figures, a plate heat exchanger is shown, see Figs. 1 and 2 and 3 and 4, respectively. for a first medium and second plate spacer 4 for a second medium. The first plate gaps 3 and the second plate gaps 4 are arranged in an alternating order in the plate package 10 15 20 25 30 35 2, i.e. every second plate gap is a first plate gap 3 and every other a second plate gap 4, see Fig. 8.
    The plate heat exchanger shown in Figs. 1 and 2 has heat exchanger plates 1 which are permanently connected to each other, preferably by soldering. The heat exchanger plates 1 can also be permanently connected to each other by gluing or welding. The two outermost heat exchanger plates can form or be replaced by end plates 5 and 6.
    In the plate heat exchanger shown in Figs. 3 and 4, the heat exchanger plates 1 are pressed against each other to the plate package 2 by means of clamping means 5, which are formed as clamping bolts extending through two end plates 6 and 7, between which the heat exchanger plates 1 are arranged.
    The plate heat exchangers also comprise inlet and outlet channels 11-14, which are arranged to lead the first medium into the first plate melt spaces 3 and out of them and to lead the second medium into the second plate spaces 4 and out of the same.
    The heat exchanger plates 1 to be described in more detail refer to heat exchanger plates 1 for the plate heat exchanger according to the first embodiment shown in Figs. 1 and 2. Each heat exchanger plate 1 propagates in a spreading plane, or a main spreading plane p, see Fig. 8, and includes a heat transfer area 15 and an edge area 16 extending around the heat transfer area 15. The expansion plane p also forms a center plane of each heat exchanger plate, at least with respect to the heat transfer area 15. Each heat exchanger plate 1 also includes two port hole areas 17 and 18, which are arranged at a first end 1A of the heat exchanger plate 1 and a second end 1B, respectively, of the heat exchanger plate 1 ". The porthole areas 17 and 18 are located inside the edge area 16, and more specifically between the edge area 16 and the heat transfer area 15.
    Each gate health area 17, 18 comprises two gate holes 19 which are aligned with the respective inlet and outlet channels 11-14. Each heat exchanger plate 1 also comprises a circumferential outer flank 20 extending away from the propagation plane p, see Fig. 1.
    The flank 20 is arranged outside or forms an outer part of the edge area 16. It should be noted that the heat exchanger plates 1 according to the first embodiment may also lack such an outer flank 20 or have an outer flank extending along a part of the heat exchanger plate. 1 circumference.
    In the embodiments shown, each heat exchanger plate 1 has an elongate shape from the first end 1A to the second end 1B. Thus, each heat exchanger plate 1 defines a longitudinal center axis x which lies in the plane of propagation p and extends through the first end 1A and the second end 18. More specifically, the center axis x lies midway between the two port holes 19 of the first port neck region 17 and the center emetic port holes 19. at the second port area 18.
    The heat transfer area 15 comprises a corrugation of ridges 30 and valleys 40, each of which extends in a longitudinal direction r which in the embodiments shown forms an angle d, see Fig. 5. The angle d may be between 25 and 70 °, preferably between 45 and 65 °, especially about 60 °. In the embodiments shown, the corrugation is designed as an arrow pattern. It should be noted, however, that other patterns are possible within the scope of the invention, for example a corrugation with ridges 30 and valleys 40 extending diagonally across the entire heat transfer area 15.
    As can be seen from Fig. 8, the ridges 30 have a first edge surface 31, a. second edge surface 32 and a support surface 33 extending between the first edge surface 31 and the second edge surface 32. The ridges 30 have a first width 34 across the longitudinal direction r. The parts 40 also have a first edge surface 41, a second edge surface 42 and a support surface 43 extending between the first edge surface 41 and the second edge surface 42. The support surface 43 of the valleys has a second width 44 across the longitudinal direction r. As shown in Fig. 8, the first edge surface 31 of the ridges 30 merges into These first edge surfaces 31 and 41 are separated at the spreading plane p .. Similarly, the second edge surface 32 of the ridges 30 merges into the second edge surface 42 of the valleys 40 and is separated by the spreading plane p. Fig. 8 are the boundaries between support surfaces 33; 43 and the edge surfaces 31, 32; 41, 42, relatively sharp. It should be noted, however, that both of these or one of them may be rounded.
    As shown in Figs. 5-8, the heat exchanger plates 1 in the plate package 2 comprise primary plates 1 ', see Fig. 5, and secondary plates 1 ", see Fig. 6; These are arranged in such a way that every other heat exchanger plate 1 in the plate package forms a primary plate 1 'and every other intermediate heat plate 1 forms a secondary plate 1', see Figs. 7 and 8.
    The second width 44, i.e. the width of the support surfaces 43, of the primary plates 1 'is longer, or considerably longer, than the first width 34, i.e. the width of the support surfaces 33, of the primary plates 1 ”. Likewise, the first width is 34, ie. the width of the support surfaces 33, of the secondary plates 1 ”longer, or considerably longer, than the second width 44, i.e., the width of the support surfaces 43, of the secondary plates 1”. More specifically, the first width 34 of the primary plates 1 'can approach zero as well as the second width 44 of the secondary plates 1'. In this way an asymmetric plate heat exchanger is obtained where the flow area, or flow volume, of the second plate gaps 4 is larger than the flow area, or flow volume, of the first plate gaps 3.
    This asymmetry is illustrated in Fig. 8 where it appears that the first plate gaps 3 have a larger flow area, or flow volume, than the second plate gaps 4. As further shown in Fig. 8, the support surface 43 of the valleys 40 lies at one of the primary plates 1 'and the ridges 30 support surface 33 of one of the secondary plates 1 "facing each other. This primary plate 1 'and this secondary plate 1" enclose one of the first plate gaps 3 which thus has the first flow volume. Likewise, the support surface 33 of the ridges 30 of one of the primary plates 1 'abuts the support surface 43 of the valleys 40 of one of the secondary plates 1 ". This primary plate 1' and this secondary plate 1" enclose one of the second plate gaps 4 thus having the second flow volume. The ratio between the first flow volume and the second flow volume is between 1.2 and 3, preferably between 1.5 and 2.5 and more preferably between 1.8 and 2.1.
    As further shown in Fig. 8, the support surface 43 of the valleys 40 of the primary plates 1 'is inclined relative to the plane of propagation p. Likewise, the support surface 33 of the ridges 30 of the secondary plates 1 "is inclined relative to the plane of propagation p. 43 and 33 will extend over a relatively small contact area 50, especially in comparison with if the support surfaces 43 and 33 had extended parallel to the spreading path p. These support surfaces 33 and 43 are inclined at an inclination angle ß relative to the spreading plane p.
    The angle of inclination ß is 3-15 °, preferably 3-7 °, for example 5 ° or about 5 °.
    As further illustrated in Fig. 8, the support surfaces 33 and 43 are substantially flat. It should be noted, however, that these surfaces do not have to be flat but may have a curved or otherwise irregular shape within an overall slope from one of the edge surfaces 41, 42 and 31, 32, respectively, to the other of the edge surfaces 41, 42 and 31, 32. The inclination of the support surfaces 33 and 43 can be arranged in different ways on the primary plates 1 'and the secondary plates 1 ". Figs. 5-8 show how the first edge surfaces 31, 41 of the primary plates 1' and the secondary plates 1" face the first end 1A while the other edge surfaces 32, 42 of the primary plates 1 'and the secondary plates 1' face the other end 1B. The support surface 43 of the valleys 40 of the primary plates 1 'slopes from the first edge surfaces 41 in the direction of the plane of propagation p and towards the second edge surfaces 42 of the valleys 40 of the primary plates 1'. The support surface 33 of the ridges 30 of the secondary plates 1 "slopes from the first edge surfaces 31 in the direction of the plane of expansion p and towards the second edge surfaces 32 of the ridges 30 of the secondary plates 1".
    With such an inclination to the same hole, contact areas 50 are obtained with an appearance illustrated in Fig. 9. The contact area 50 has a triangle-like shape and will contribute to a lower flow resistance when the flow goes in the direction of the arrow 51 compared to if the flow goes in the opposite direction. , i.e. in the direction of the arrow 52.
    It is also possible to tilt the support surfaces in different directions, the support surface 43 of the valleys 40 of the primary plates 1 'sloping from the first edge surfaces 41 towards the spreading plane p and towards the second edge surfaces 42 of the valleys 40 of the primary plates 1' and the support surface of the ridges 30 33 of the secondary plates 1 "slopes from the edge surfaces 32 in the direction of the plane of propagation p and towards the first edge surfaces 31 of the axes 30 of the secondary plates 31".
    With such an inclination of the support surfaces 33, 43, the contact areas 50 are obtained with the appearance illustrated in Fig. 10. Here, too, a triangle-like shape of the contact areas 50 is obtained, but the flow resistance in the opposite directions 51 and 52 is substantially equal. .
    Within the contact areas 5.0, the heat exchanger plates 1 will have contact with each other. In the illustrated embodiment with a soldered plate heat exchanger, the contact areas 50 will be formed, or substantially formed, of solder material. In the illustrated embodiment, the primary plates t 'and the secondary plates 1' are formed by different heat exchanger plates which are manufactured separately, each heat exchanger plate 1 having a circumferential flank 20 extending in a direction from the plane of propagation p. The primary plates 1 'then have a arrow pattern of the heat transfer area 15 in accordance with Fig. 5 while the secondary plates 1 "have an arrow pattern of the heat transfer area 15 directed in the opposite direction in accordance with Ftg.6. 10 '15 12 In the case that the heat exchanger plates have no circumferential flank, the primary plates 1 'and the secondary plates 1 "must be identical. In this case, the primary plate 1 'and the secondary plate 1 "are provided by inverting every other heat exchanger plate, for example the secondary plates 1" 180 ° in the plane of propagation. Thus, the heat transfer area 15 of the primary plates 1' will have a corrugation in accordance with an arrow pattern. with Fig. 5 and the heat transfer area 15 of the secondary plates 1 ”an arrow pattern of the correction according to Fig. 6. Such identical heat exchanger plates 1 can advantageously be used in plate heat exchangers where the heat exchanger plates 1 are pressed against each other by means of the clamping means 5, see Figs. 3 and 4.
    The invention is not limited to the embodiments shown but can vary and be modified within the scope of the appended claims.
    权利要求:
    Claims (17)
    [1]
    Heat exchanger plate (1) for a plate heat exchanger with a plurality of heat exchanger plates arranged next to each other to form first plate gaps (3) for a first medium and second plate gaps (4) for a second medium, the heat exchanger plate (1) extending in a major distribution plane (p) along a center axis (x) and includes a heat transfer region (15) and an edge region (16) extending around the heat transfer region (15), the heat transfer region (15) comprising a corrugation of ridges (30). ) and valleys (40), each extending in a longitudinal direction (s), the ridges (30) having a first edge surface (31), a second edge surface (32) and a support surface (33) extending between the first and second edge surfaces (31, 32) and has a first width (34) across the longitudinal direction (s), and the valleys (40) have a first edge surface (41), a second edge surface (42) and a support surface (43), which extends between the first and second edge surfaces (41, 42) and has a second width across the longitudinal direction (s), characterized in that the support surface (43) of the valleys (40) is inclined relative to the plane of propagation (p).
    [2]
    The heat exchanger plate according to claim 1, wherein the second width (44) is longer than the first width (34).
    [3]
    The heat exchanger plate according to claim 2, wherein the first width (34) approaches zero.
    [4]
    Heat exchanger plate according to one of the preceding claims, wherein the support surface (43) of the valleys (40) is substantially flat.
    [5]
    Heat exchanger plate according to any one of the preceding claims, wherein the support surface (43) of the valleys (40) is inclined relative to the plane of propagation (p) with an inclination angle (ß) which is 3-15 °, preferably - about 3-7 °.
    [6]
    Plate heat exchanger comprising a plurality of heat exchanger plates (-1) arranged next to each other to form a plate package (2) with first plate melian space (3) for a first medium and second plate melian space (4) for a second medium, the first and second the plate gaps (3, 4) are arranged in an alternating order in the plate package (2), each other heat exchanger plate (a) in the plate package (2) forming a primary plate (1 ') and every other intermediate heat exchanger plate (1) therebetween. 1) forms a secondary plate (1 "), each heat exchanger plate (1) extending in a main plane of propagation (p) along a center axis (x) and comprising a heat transfer area (15) and an edge area (16) extending around the heat transfer area (1). 15), the heat transfer area (15) comprising a corrugation of ridges (30) and valleys (40), each extending in a longitudinal direction (s), the ridges (30) having a first edge surface (31), a second edge surface (32) and a support surface (33), p extending between the first and second edge surfaces (31, 32) and having a first width (34) across the longitudinal direction (r), and the valleys (40) having a first edge surface (41), a second edge surface (42) and a support surface (43) extending between the first and second edge surfaces (41, 42) and having a second width (44) across the longitudinal direction (s), that the support surface (43) of the valleys (40) of the primary plates (1 ') is inclined relative to the plane of propagation (p) and that the support surface (33) of the ridges (30) of the secondary plates (1 ") is inclined relative to the plane of propagation (p).
    [7]
    A plate heat exchanger according to claim 6, wherein the second width (44) of the primary plates (1 ') is longer than the first width (34) of the primary plates (1') and wherein the first width (34) 15 of the secondary plates (1 ”) is longer than the other width (44) of the secondary plates (1”).
    [8]
    A plate heat exchanger according to claim 7, wherein the first width (34) of the primary plates (1 ') approaches zero and wherein the second width (44) of the secondary plates (1 ") approaches zero.
    [9]
    Plate heat exchanger according to any one of claims 6 to 8, wherein the support surface (43) of the parts (40) of the primary plates (1 *) is substantially flat and the support surface (33) of the ridges (30) of the secondary plates (1 ") is substantially flat.
    [10]
    Plate heat exchanger according to any one of claims 6-9, wherein the support surface (43) of the parts (40) of the primary plates (1 ') and the support surface (33) of the aces (30) of the secondary plates (1 ") are inclined relative to the plane of propagation (p ) with an angle of inclination (ß) which is 3 to 15 °, preferably 3 to 7 °.
    [11]
    Plate heat exchanger according to any one of claims 6-10, wherein the support surface (43) of one of the primary plates (1 ') of the valleys (40) and the support surface (33) of the ridges (30) of one of the secondary plates (1 ") lie facing each other, this primary plate (1 ') and this secondary plate (1 ") enclosing one of the first plate gaps (3) with a first flow volume, the support surface (33) of the ridges (30) of one of the primary plates (1') and the support surface (43) of the parts (40) of one of the secondary plates (1 ") abut against each other, said primary plate (1 ') and this secondary plate (1") enclosing one of the other plate gaps (4) with a second flow volume, and the ratio between the first flow volume and the second flow volume is between 1.2 and 3, preferably between 1.5 and 2.5 and more preferably between 1.8 and 2.1.
    [12]
    Plate heat exchanger according to one of claims 6 ~ 11, wherein the primary plates (1 ') and the secondary plates (1') are formed by different heat exchanger plates (1). 10 15 20 25 30 35 16
    [13]
    A plate heat exchanger according to claim 12, wherein each heat exchanger plate has a circumferential flank (20) extending away from the plane of propagation (p).
    [14]
    Plate heat exchanger according to one of claims 12 and 13, wherein the heat exchanger plates (1) are permanently connected to each other, for example by soldering.
    [15]
    Plate heat exchanger according to any one of claims 6-11, wherein the primary plates (1 ') and the secondary plates (1 ") are identical, each other heat exchanger plate (1) in the plate package (2) being turned 180 ° in such a way that the support surface (33) of the ridges (30) of every other heat exchange plate (1) abuts and crosses the support surface (33) of the ridges (30) of the intermediate heat exchanger plates (1) and the heat exchanger plates (1) being pressed against each other with clamps - organ (5).
    [16]
    Plate heat exchanger according to any one of claims 1-15, wherein each heat exchanger plate (1) has a first end (1A) and a second opposite end (1B) with respect to the center axis (x), the first edge surfaces (31, 41) of the primary plates (1 ') and the secondary plates (1 ") face the first end (1A) while the second edge surfaces (32, 42) of the primary plates (1') and the secondary plates (1") face the second end (1B), the support surface (43) of the valleys (40) of the primary plates (1 ') slopes from the first edge surfaces (31) in the direction of the plane of propagation (p) and towards the second edge surfaces (42) and the support surface (33) of the secondary plates (1 ”) slope from the first edge surfaces (41) towards the plane of propagation (p) and towards the second edge surfaces (42).
    [17]
    A plate heat exchanger according to any one of claims 1-15, wherein each heat exchanger plate (1) has a first end (1A) and a second opposite end (1 B) with respect to the center axis (x), the first edge surfaces (31, 41 ) of the primary plates (1 ') and the secondary plates (1 ") face the first end (1A) while the second edge surfaces (32, 42) of the primary plates (1') and the secondary plates (1") are facing the second end (1B), the support surface (43) of the valleys (40) of the primary plates (1 ') slopes from the first edge surfaces (41) towards the plane of propagation (p) and towards the second edge surfaces (42) and ridges (30). ) support surface (33) of the secondary surfaces (1 ") slopes from the second edge surfaces (32) towards the plane of propagation (p) and towards the first edge surfaces (31).
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1050690A|SE534918C2|2010-06-24|2010-06-24|Heat exchanger plate and plate heat exchanger|SE1050690A| SE534918C2|2010-06-24|2010-06-24|Heat exchanger plate and plate heat exchanger|
    SI201030817T| SI2585783T1|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    BR112012031888A| BR112012031888A2|2010-06-24|2010-09-06|heat exchanger plate and plate heat exchanger|
    RU2013103115/06A| RU2520767C1|2010-06-24|2010-09-06|Heat exchange plate and plate-type heat exchanger|
    PL10754810T| PL2585783T3|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    PT107548109T| PT2585783E|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    ES10754810.9T| ES2526998T3|2010-06-24|2010-09-06|Heat exchanger plate and plate heat exchanger|
    KR1020127033407A| KR101445474B1|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    DK10754810.9T| DK2585783T3|2010-06-24|2010-09-06|Exchanger plate and plate heat exchange|
    PCT/SE2010/050946| WO2011162659A1|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    CA2803776A| CA2803776C|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    US13/805,893| US9534854B2|2010-06-24|2010-09-06|Heat exchanger plate and a plate heat exchanger|
    CN201080067686.6A| CN102985780B|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    EP10754810.9A| EP2585783B1|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    AU2010356148A| AU2010356148B2|2010-06-24|2010-09-06|A heat exchanger plate and a plate heat exchanger|
    JP2013516522A| JP5612203B2|2010-06-24|2010-09-06|Heat exchanger plate and plate heat exchanger|
    TW100116815A| TWI445917B|2010-06-24|2011-05-13|A heat exchanger plate and a plate heat exchanger|
    ZA2012/08944A| ZA201208944B|2010-06-24|2012-11-27|A heat exchanger plate and a plate heat exchanger|
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