• 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:
    A plate heat exchanger provided in particular for absorption refrigeration systems with alternating solution channels and coolant channels is formed in two parts by means of heat exchanger plates consisting of two plate parts (15, 16) such that two adjacent juxtaposed, separate, however, exist in the flow channel between two plate front sides (V) Solution channel portions connected by an overflow opening and two adjacent coolant passage portions adjacent to one another are present in the adjacent flow channel. Each channel part is assigned inlets and outlets for the respective medium. Due to the overflow opening between the two solution channel parts, steam generated in one of the solution channel part functioning as an evaporator or generator can flow into the second solution channel part, which then has the function of an absorber or a condenser. As a result, with less space required, the expenditure on equipment and assembly costs can be reduced and the heat transfer capacity of the plate heat exchanger can be increased.
    公开号:AT513177A2
    申请号:T640/2013
    申请日:2013-08-12
    公开日:2014-02-15
    发明作者:Michael Rehberg
    申请人:Ttz Thermo Technik Zeesen Gmbh & Co Kg；
    IPC主号:
    专利说明:

    5 5 • ···· • · • • • • • • • • • • • · · · · ·
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    Plate heat exchangers, in particular for absorption refrigeration systems
    Description 10
    The invention relates to plate heat exchangers with solution channels and coolant channels formed alternately between stacked heat exchanger plates for evaporation, absorption, desorbing or condensing of a medium flowing in the solution channels, in particular absorption refrigerators comprising a generator and a condenser and an evaporator and an absorber. In absorption refrigeration systems operated, for example, with a solution of lithium bromide and water, the water serving as the refrigerant is evaporated at low pressure in an evaporator. The evaporation heat required for evaporation is withdrawn from a cooling water flow (cooling medium flow), which supplies the usable cold. In order not to interrupt the evaporation process by reaching the saturation pressure, the refrigerant vapor is bound (absorbed) in a subsequent step in another apparatus, the absorber, in the solution. Since a saturation of the solution with the refrigerant would interrupt the Abr sorption process, the refrigerant is expelled from the solution in a further step under heat and at a higher pressure level in a generator. While the concentrated solution is again supplied to the absorber 30, the refrigerant vapor is liquefied under heat to a heating or cooling medium in a condenser and then passed back into the evaporator. In addition to lithium bromide and water, a water-ammonia solution with ammonia 35 as refrigerant and water as solvent also belongs to the frequently used combinations of substances in absorption refrigeration systems. For the steps required in the absorption cooling process, separate apparatuses are used in each case, wherein an apparatus combination of evaporator and absorber as well as generator and condenser to ensure the required pressure conditions is arranged in each case in a vacuum-tight housing. The arrangement of two apparatuses for the evaporation and absorption process or the evaporation and condensation process is associated with a high space requirement and high installation and installation costs. Furthermore, the formation of the evaporator or generator as a plate heat exchanger is disadvantageous in that the refrigerant vapor generated in each case occupies a large volume and in the individual plates of the respective Plattenwärmeübertragers correspondingly large passage openings for the steam and in the adjoining the evaporator apparatus (condenser, absorber ) must be provided. For a loss of material and on the other a reduction of the heat exchange surface are connected. According to the number of plates of Plattenwärmeübertragers increase the vapor volume and thus the size of the openings and the consequent losses.
    The invention has for its object to develop a plate heat exchanger for absorption refrigeration systems, which can be created with low equipment and installation costs and ensures effective heat transfer.
    According to the invention the object is achieved with a trained according to the features of claim 1 plate heat transfer system. - 3 - • ···
    Advantageous and advantageous developments of the invention are the subject of the dependent claims.
    The basic idea of the invention is that a single plate heat exchanger is formed in two parts, in such a way that in the present between two heat exchanger plates flow channel for the solution two adjacent, separate, but connected by an overflow solution channel portions 10 and in the of the Refrigerants flowed through adjacent channel two adjacent, separate coolant channel parts are provided. Each channel part is assigned inlets and outlets for the respective medium. Due to the overflow opening between the two solution channel part len generated in the one - acting as an evaporator or generator - solution channel part steam flow into the second solution channel part, which then has the function of an absorber or a capacitor. 20 For the evaporator and the absorber or for the generator and the condenser, only one plate heat exchanger is thus required in each case, so that the expenditure on equipment and the assembly costs can be reduced and also the space requirement is reduced. Compared with the respective 25 designed as a separate component evaporators or generators with their large vapor volume due to the large vapor outlet cross sections in the heat exchanger plates need in the inventively designed Plattenwärmeübertragern the cross sections for the medium passage 30 of the steam are not taken into account, so that the heat transfer efficiency between the past each other flowing media is significantly improved. The plate area provided in each plate gap for the vapor-transfer step can be comparatively small, since only the 35 vapor quantity arising in this one gap must be conducted from one solution channel part into the next, and 4/18 - 4 - ··· · - 4 - ··· ·
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    In an embodiment of the invention, structures for influencing the flow and thus improving the heat transfer and the evaporation, absorption and condensation processes can be provided in the coolant 5 and solution channels. 10 According to a further feature of the invention, the heat exchanger plates are identical. They have in a lower plane of the plate an outer peripheral connecting edge and an outgoing therefrom, up to an upper plate plane elevated circumferential connecting bead 15 and an outgoing from the peripheral connecting bead, along a longitudinal axis of the heat exchanger plate extending central connecting bead on. However, the middle connection bead does not extend over the entire plate length, so that between the free end 20 and the opposite part of the peripheral connecting bead an overflow gap is generated.
    First and second plate parts are created by the middle connecting bead, in each of which first 25 and second solution inlet openings and first and second solution outlet openings and respectively first and second coolant inlet openings and first and second coolant outlet openings are provided. In an embodiment of the invention, in the same direction oblique and parallel waves are formed in the first and second plate parts as flow control structures. On the side provided with the solution outlet openings, the circumferential connecting seam to the central connecting bead is gradually widened in order to guide the solution 5/18 better to the solution outlet openings in the respective plate part. To further influence the flow or flow distribution on the surface wave-shaped intermediate structures can be formed with a lesser embossing depth between the waves or inserted in the plate assembly parts.
    The inventively embodied heat exchanger plates are stacked in the plate heat exchanger in each case rotated through 180 ° about its longitudinal axis, so that in each case the front sides and the back sides of the heat exchanger plates adjoin one another. To form the respective divided solution channels, the front sides of the heat transfer plates for external sealing in the contact region of the circumferential connecting beads and in the contact region of the middle connecting beads to form the respective solution channel while leaving the Überströmspaltes dividing partition connected to each other. The coolant channels are formed between the adjoining rear sides of the heat exchanger plates in the contact region of the peripheral connection edges and in a contact region extending along the entire longitudinal axis. Furthermore, the heat transfer plates are connected to each other at the front and rear sides of the plates to form the solution and coolant inlets and outlets to the solvent and coolant channels at the respective contact areas at the edge of the coolant and solution inlets and outlets.
    An embodiment of the invention will be described with reference to the drawing, in which
    Fig. 1 is an exploded view of the plate stack of acting as an evaporator and absorber plate heat exchanger; - 6 - · · · · · · · · · · · ····································································
    Fig. 2a is a rear view of a heat exchanger plate of the plate heat exchanger; and
    FIG. 2b shows a front view of the heat transfer plate according to FIG. 2a; FIG. and
    Fig. 3 shows an enlarged front view of the heat exchanger plate, explained in more detail.
    In the present exemplary embodiment, a plate heat exchanger system for the evaporator and the absorber of an absorption refrigeration system operated with a lithium bromide sol as solvent and with water or steam as refrigerant is described. The Plattenwärmeübertragersystem shown here can be operated in the same design as a generator and condenser for expelling the water vapor and for its liquefaction. There are also other combinations of substances, such as ammonia as a refrigerant and water as a solvent, conceivable.
    As shown in FIG. 1, the plate heat exchanger comprises a plurality of identically formed, each two plate members 15, 16 having heat exchanger plates 1, which - each rotated about a longitudinal axis 5 - stacked übereinan and sealingly joined together at the contact points. As can be seen from the comparison of FIGS. 2 a and 2 b, the heat exchanger plates 1 have a profiling which is correspondingly different from that formed on a flat sheet metal plate on the front plate side (FIGS. 2 b, 3) and the rear side of the plate (FIG. 2 a). With regard to the front side of the panel, the profiling, starting from a first, lower plate plane 1 ', forms a second, upper one Plate level 1 '' formed.
    The heat exchanger plate 1 formed by two plate parts 15, 16 has a peripheral connecting edge 2 and a peripheral connecting bead 3 adjoining the latter towards the inside of the plate, which on the plate front side an elevation up to the upper plate level 1 '' and on the plate rear side a circumferential recess forms. Another - middle - compound bead 4 extends in the longitudinal axis 5 of the rectangular heat exchanger plate 1 in the upper plate level 1 '', starting from the peripheral compound bead 3, but not to the opposite side, but only over a certain distance. The free space remaining between the free end of the middle connecting bead 4 and the peripheral connecting bead 3 aligned transversely thereto forms an overflow gap 14 between the two plate parts 15, 16 separated by the middle connecting bead 4 and the longitudinal axis 5. In the two plate parts 15, 16 are formed in the same direction obliquely and parallel to each other, up to the upper plate level 1 '' increased waves 17, the free ends reach close to the circumferential connecting bead 3 and the middle connecting bead 4 and the longitudinal axis 5.
    In the limited by the peripheral compound bead 3 and the middle connecting bead 4 plate members 15, 16 are in the corners of the heat exchanger plate 1 each in the lower plate level 1 'lying first and second solution outlet openings 6 and 7 are formed, which on the opposite side of the heat exchanger plate 1 respectively a in the upper plate plane 1 '' formed first and second coolant outlet opening 8 and 9 opposite. To the solution outlets 6 and 7 in 8/18 8 ·· v · ··
    • «I» · · ··· • ♦ 4 ► ··
    Offset in the direction of the middle connection bead 4 are in the upper plate plane 1 '' respectively a first and second coolant inlet opening 10 and 11 formed, which on the opposite side of the heat transfer plate 1, that is in the not separated by the middle connecting bead 4 Area of the plate members 15, 16, in the lower plate level 1 ', a first and second solution inlet opening 12 and 13 facing. In the illustrated in Fig. 2a back of 10 rotated about the longitudinal axis 5 heat exchanger plate 1 of Fig. 2b and Fig. 3, the circumferential and the middle connecting bead 2, 3 and the shafts 17 each wells in the formed sheet metal plate According to the in Fig. 1 in an exploded view - but without end plates and nozzles for the supply and discharge of the solution (here: lithium bromide solution) and the coolant (here: cold water) - a Plattenwärmeübertragers a plurality of the previously described 20 heat exchanger plates. 1 - In each case rotated by 180 ° about the longitudinal axis 5 - stacked on each other, so that in each case the front sides V and the backs R of the heat exchanger plates lie on each other. The front sides V of the heat exchanger plates 1 are at the mutually opposite-lying circumferential connecting beads 2 and the middle connecting beads 3 to form a (non-continuous) partition wall and at the intersection of the shafts 7 and in the edge region of lying in an upper plate plane 1 '' coolant inlet openings 10, 11 and 30 coolant outlet openings 8, 9 connected to each other.
    The rear sides R of the heat exchanger plates 1 are connected to one another at the connection edges 2 and the flat region along the longitudinal axis 5 as well as at the wave crossing points and in the edge region of the solution outlet openings 6, 7 and solder entry openings 12, 13. 9.18
    • l »Y ··· ··· - 9 -
    Between the plate stacks R which are opposite one another in the plate stack, two coolant channels (coolant channel parts) which are separate from one another in the longitudinal direction are formed, through which a coolant (here: cold water) flows via the coolant inlet openings 5, 10, 11 and the coolant outlet openings 8, 9. Between the contiguous front panels V two by the peripheral connecting beads 3 to the outside pressure-tight and partially formed by the middle Verbin-10 dungssicken 4 formed partition partially separate, but interconnected by the Überströmspalt 14 solution channels (solution channel parts) formed via the solution inlet openings 12th , 13 and the solution outlet openings 6, 7 are flowed through by the solution. One of the two (here formed by the plate members 16) dissolution channels acts as a refrigerant evaporator, wherein the required heat of vaporization of the useful cold supplied, in the coolant channel between two plate backs flowing coolant 20 is removed. The absorption of the refrigerant vapor (here: water vapor) required for the maintenance of the evaporation process takes place in the second solution channel functioning as absorber (in this case the first plate parts 15) into which a portion of the refrigerant vapor generated in the evaporator passes through the overflow gap 25 14 and is absorbed by the flowing in this solution. The in the evaporator part (16) and in the absorber part (15) of the plate heat exchanger flowing to refrigerant poor or rich solution passes - distributed 30 through the in the two adjacent solution channels (formed by the plate members 15, 16 solution channel parts) waves 17 - the solution inlet openings 12 and 13 via the formed as a slope portion of the peripheral connecting bead 3 to the 35 solution outlet openings 6 and 7 and from there to the generator and the condenser of the absorption refrigeration system. 10/18 - 10 - 10
    ················································
    The illustrated in the previous embodiment plate heat exchanger has been described in the function as an evaporator and absorber for an absorption refrigeration system. The thus configured with two juxtaposed solution channels (16, 15) and an overflow (14) heat exchanger can be operated in an absorption refrigeration plant equally as a generator for expelling and as a condenser for liquefying the refrigerant.
    Due to the two-part design of the flows between adjacent heat exchanger plates in alternation of the refrigerant solution and the coolant flow channels, but with a provided in the flow channel for the refrigerant solution overflow opening for the refrigerant vapor in acting as an absorber or condenser sub-channel, which accounts for the conventional, only as Evaporator serving plate heat exchangers required steam channels with due to the large volume of vapor correspondingly large openings in the heat exchanger plates. That is, the heat transfer plates have a much larger heat transfer area and the heat transfer efficiency of the plate heat exchanger is improved. The integration of the evaporator and the absorber or the generator and the capacitor in each case only one plate heat exchanger reduces the material and installation costs and beyond also the space required. In addition, can be dispensed with by the formation of the evaporator and absorber or the generator and the capacitor in each case a single plate heat exchanger on the usually necessary accommodation in a separate, vacuum-tight housing. 11/18 5 - 11 · »· · * # > ··· φ 0 · · · · ♦ · ···············································
    1 heat exchanger plates 1 'lower plate level 1' 'upper plate level 2 circumferential connecting edge (sealing edge of the coolant channel) 10 3 circumferential connecting bead (sealing edge of the Lö sungskanäle) 4 middle connecting bead (partition wall between two solution channels) 5 longitudinal axis of 1 15 6 first solution outlet opening 7 second solution outlet opening 8 first coolant outlet opening 9 second coolant outlet opening 10 first coolant inlet opening 20 11 second coolant inlet opening 12 first solution inlet opening 13 second solution inlet opening 14 overflow gap 25 15 first plate part (solution channel 1: absorber, condenser) 16 second plate part (solution channel part: evaporator, generator) 17 shaft 18 slope of 3 30 12/18
    权利要求:
    Claims (5)
    [1]
    - 12 - • • • ····· • 0 ••• • • • • • • • • • • • • • • • • • • • • • • • • • 1. Plate heat exchanger with between mutually stacked heat exchanger plates (1) alternately formed solution channels and coolant channels for vaporizing, absorbing, desorbing or condensing a flowing in the solution channels medium , in particular for a generator and a condenser as well as an evaporator and an absorber comprehensive absorption refrigeration systems, characterized in that the coolant and dissolution channels are formed in two parts by a longitudinal axis extending in the partition wall and two adjacent, as an evaporator and absorber or as an evaporator and Condenser or as a desorber and condenser acting channel parts associated with each channel part inlet and outlet for the respective medium, wherein the partition wall provided in the solution channels has an overflow opening for the steam generated in one channel part and the vapor to be absorbed or condensed in the adjacent channel part.
    [2]
    2. Plate heat exchanger according to claim 1, characterized in that in the coolant and solution channels structures for improved distribution of the media and their better temperature control are provided.
    [3]
    3. Plate heat exchanger according to claim 1, characterized in that the heat exchanger plates (1) are formed identically and an outer circumferential connecting edge (2) in a lower plate level (1 '), one to an upper Plattenebe- 13/18 13 ·· · 10 15 ne (1 '') increased circumferential connecting bead (3) as well as along one Longitudinal axis (5) one of the peripheral connecting bead (3) outgoing, but leaving a Überströmspaltes (14) not extending to the opposite side extending central connecting bead (4), wherein in through the central connecting bead (4) created first and second plate parts (15, 16) in the lower plate level (1 ') first and second solution inlet openings (12, 13) and first and second solution outlet openings (6, 7) and in the upper plate plane (1' ') first and second Kühlmitteleintri openings (10, 11) and first and second coolant outlet openings (8, 9) are formed from. 20
    [4]
    4. Plate heat exchanger according to claim 2 or 3, characterized in that in the first and second plate parts (15, 16) in the same direction inclined and parallel shafts (17) are formed as structures for influencing the flow. 25
    [5]
    5. Plate heat exchanger according to claim 4, characterized in that extending parallel to the waves wavy indentations are formed with a smaller embossing depth than intermediate structures for further flow control. The plate heat exchanger according to claim 1 or 3, characterized in that the heat exchanger plates (1) are each rotated 180 ° about their longitudinal axis (5) superimposed; and for forming the dissolution channels on their front sides (V) in the contact area of the peripheral connection 14/18 35 14 • ··· * · · · ············································· • · • '

    10 beads (3) are connected to the outer sealing of the solution channels and in the contact region of the central connecting beads (4) for forming the dividing wall dividing the respective solution channel while leaving the Überströmspaltes; and to form the coolant channels on their rear sides (R) in the contact region of the peripheral connection edges (2) and in a contact region extending along the longitudinal axis (5); and 4 are connected to the solution and coolant channels at the respective contact areas at the edge of the coolant and solution inlets and outlets (6 to 13) to form the solution and coolant inlets and outlets. 15/18
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    同族专利:
    公开号 | 公开日
    AT513177B1|2015-05-15|
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JP2004197984A|2002-12-17|2004-07-15|Toyo Radiator Co Ltd|Integrated multiple plate type heat exchanger|
    US3631923A|1968-06-28|1972-01-04|Hisaka Works Ltd|Plate-type condenser having condensed-liquid-collecting means|
    US3759308A|1970-06-15|1973-09-18|Parkson Corp|Plate evaporator for removing volatiles from liquids|
    JPS56993A|1979-06-13|1981-01-08|Hisaka Works Ltd|Plate-type heat exchanger|
    US5390507A|1992-09-17|1995-02-21|Nippondenso Co., Ltd.|Refrigerant evaporator|
    WO2000057121A1|1999-03-24|2000-09-28|Ebara Corporation|Plate type heat exchanger|
    JP2002277090A|2001-03-22|2002-09-25|Tokyo Gas Co Ltd|Plate type heat exchanger for absorption refrigerator|DE102018200809A1|2018-01-18|2019-07-18|Mahle International Gmbh|The stacked-plate heat exchanger|
    DE102018002201B4|2018-03-19|2021-03-18|EAW Energieanlagenbau GmbH Westenfeld|Water-lithium bromide absorption refrigeration system|
    DE202019106674U1|2019-11-29|2021-03-02|Hochschule für angewandte Wissenschaften München|Plate apparatus for mass and heat transfer in sorption heat pumps with separation of liquid and vapor flow|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE201210107381|DE102012107381A1|2012-08-10|2012-08-10|Plate heat exchanger for absorption refrigerating plants, has solution channels and coolant channels for evaporating, absorbing, desorbing or condensing medium, where solution channels are formed between heat exchanger plates|
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