• 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:
    Heat exchanger for heat exchange between two separated countercurrently flowing media, especially suited to gas/gas heat exchange but also for gas/liquid and liquid/liquid heat exchange. The heat exchanger operates entirely within the laminar range. Separating walls (16, 16a, 16b) which are common to adjacent slots (12) and are provided with oblique, mutually parallel profiles with intermediate flat sheet metal portions (31), constitute the heat exchange surfaces. The profiles consist of a ridge (18), the angle of incline (//c) of which in the flow direction should not exceed 10`, and a depression (19), the angle of incline (ss) of which in the flow direction should not exceed about 20`. The profile is symmetrical about the plane of the separating wall (16). The distance (c) between the top (33) of the ridge and the bottom (34) of the depression should be half to twice the distance between the foot (32) of the ridge and its top (33), depending on the Reynolds number in question, with the distance increasing as the Reynolds number increases to obtain maximum circulation effect. The transition point for circulation lies at a distance corresponding to 9/7 of the distance (c) between the top (33) of the ridge and the bottom (34) of the depression where both positive and negative flow rates occur. Each media particle will thereby touch the heat exchanger surfaces at least 5-10 times.
    公开号:SU1091860A3
    申请号:SU803222500
    申请日:1980-12-22
    公开日:1984-05-07
    发明作者:Зигурд Херман Хултгрен Карл
    申请人:Карл Зигурд Херман Хултгрен (Швеци )；
    IPC主号:
    专利说明:

    The invention relates to heat exchanging apparatus and can be used in countercurrent heat exchange between heat transfer fluids in a thin sheet metal heat exchanger. Heat exchangers with corrugated heat exchanging surfaces are known. The disadvantages of the heat transfer methods are the presence of a boundary layer and a low heat transfer coefficient during the flow of gaseous media. The closest technical solution to the тdraglabsemsmму is a counter-flow heat exchanger made of thin sheet metal, mainly aluminum, with separate flow-through heat exchangers of the content-cleaver housing with parts of the gadget code and compression code and spacers in the form of heat. sheet, folded li li folds with the formation, when rotated by 180 channels j, flat side portions of which are equipped with oblique parallel corrugations that are in contact with each other when they cross each other with adjacent portions L2 J, .The disadvantage of the headroom is a low coefficient (|) of heat transfer, which reduces the intensity of heat transfer and increases the dimensions of heat about 1. e. And the purpose of the new is intensity symphony1. heat exchange. This goal is achieved by the fact that in a thin sheet metal heat exchanger, it is advantageous from aluminum, with separate heat transfer fluids containing a body with heat exchangers inlet and outlet nozzles and a heat meter inside the body folded into folds to form rotation on ISO of channels 5, the flat side portions of which are equipped with nakloinmi parallel corrugations, contacting each other when they are reciprocated on adjacent portions, corrugations of the group of wapons in a pair of protrusion-valleys separated by surfaces of a flat section, with each pair having a distance of 5 horizontally from the separator surfaces of the flat portion to the tops of the protrusion and the depression are equal, and the distance between the tops of the tops is 0.5-2S. In addition, the corrugation walls between the vertices in each pair are placed at an angle to the dividing surface of the flat section, not exceeding 2 (} °, the angle of the corrugations to the plane of the lateral sections of the channels is 5, and the corrugation walls between the tops and the separating surfaces of the flat sections placed at an angle to the latter, not exceeding 10. Fig. I schematically shows the proposed countercurrent heat exchanger; Fig. 2 shows the side portions of the heat exchange channel, the cross section; Fig. 3 shows the preparation of a metal sheet before it is folded. 4 - heat exchange channel sech.chi, Countercurrent heat exchanger includes a housing 1 with inlets 2 and 3 and outlet 4 and 5 of heat carriers and placed in the housing 1 heat exchange surface in the form of a sheet 6, folded in folds 7 with beaming when turning 180 channels 8j flat lateral sections 9 of which are provided with inclined parallel corrugations 10, which are in contact with each other when they cross each other at adjacent sites and are grouped in a pair of ledge-depression separated by surfaces of a flat section or 5 to go-, rizoktali of dividing}; the surfaces of the flat portion 11 to the tops of the protrusion and the trough are equal, and the distance to the edges of the peaks is 0.5-25. The corrugation walls 10 between the tops in each pair are placed at an angle to the separating surface of the flat section 11 not exceeding 20, the angle of the corrugations 10 to the plane of the lateral sections 9 of the channels 8 is 5, and the walls of the corrugations 10 between the vertices and separating surfaces flat portions 11 are placed at an angle to the latter, not exceeding 10 ° CM. In the case of the heat exchanger there is a folded sheet 6, which forms the channels 8 of the flow path of the medium. The channels 8 through one open in the direction of the inlet 2 and outlet 4, the other channels open in the direction of the inlet 3 and outlet 5. The walls of the case t are seals, preferably molded from plastic, which is welded to the edge of the sheet 6, thus sealing the channels 8 .
    In the production of the heat exchanger, a metal sheet 6 is preliminarily profiled, the length of which is limited by the tool used, then the profiled sheets are joined together to the required length. The corrugations 10 are parallel to each other and are angled relative to the plane of the sheet 6. After folding sheet 6 into folds 7, the corrugations 10 cross each other on adjacent side sections 9 and contact at intersection points.
    When the heat exchanger is working, the working media enter the corresponding inlet pipes 2 and 3, the heat exchangers pass through channels 8 and exit through the pipes A and 5. When the flute 10 is washed in channels 8, the heat transfer coefficient of working media increases and the heat exchange process is intensified.
    The flow of working media has a laminar flow throughout their cross section,
    The value of the heat transfer coefficient is determined both by the distance of the peaks from each other, and by the inclination of the corrugations and their walls relative to the plane of the sheet. The optimum values are obtained with the same distance S of the peaks of the projections and depressions from the separation of the surfaces of the flat portion and the distance between the peaks. In this case, the angle of inclination of the corrugation walls between the vertices does not exceed 20 °, the angle of inclination of the corrugations to the planes of the side portions of the channels is 3, and the angle of the aclone of the corrugations between the corrugations of the I and flat portions does not exceed 10 °,
    The described device intensifies the process of heat exchange and reduces the dimensions of the heat exchanger as a whole.
    权利要求:
    Claims (4)
    [1]
    1. A counterflow heat exchanger made of thin sheet metal, mainly aluminum, with separately flowing heat transfer fluids, comprising a housing with heat carrier inlet and outlet nozzles and a heat exchange surface in the form of a sheet folded into folds to form channels when turned through 180 °, flat lateral sections of which are equipped with inclined parallel corrugations in contact with each other at their intersection. on adjacent sections, characterized in that, in order to intensify heat transfer, the corrugations We are grouped into pairs of protrusion of the depression, separated by the surfaces of the flat section, and in each pair, the horizontal distances from the dividing surfaces of the flat section to the peaks of the protrusion and the depression are equal, and the distance between the vertices is 0.5-25.
    [2]
    2. The heat exchanger according to claim 1, characterized in that the walls of the corrugations between the peaks in each pair are placed at an angle to the dividing surface of the flat section, not exceeding 20 °. ·
    [3]
    3. The heat exchanger according to claims 1 to 2, characterized in that the angle of inclination of the corrugations to the plane of the side sections of the channels is 5 °.
    [4]
    4. The heat exchanger according to claims 1 to 3, relieved by the fact that the walls of the corrugations between the vertices and the dividing surfaces of the flat sections are placed at an angle to the latter, not exceeding 10 °.
    >
    类似技术:
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    GB1128018A|1968-09-25|Heat exchanger
    SU909559A1|1982-02-28|Heat-exchanging element
    SU1121575A1|1984-10-30|Plate-type heat exchanger
    同族专利:
    公开号 | 公开日
    EP0027456B1|1982-04-21|
    NO149790B|1984-03-12|
    DE3060303D1|1982-06-03|
    WO1980002322A1|1980-10-30|
    JPS56500425A|1981-04-02|
    DK535280A|1980-12-16|
    SE7903535L|1980-10-24|
    NO149790C|1984-06-20|
    DK149721C|1987-12-14|
    DK149721B|1986-09-15|
    EP0027456A1|1981-04-29|
    JPH0226159B2|1990-06-07|
    NO803787L|1980-12-16|
    US4407357A|1983-10-04|
    BR8008646A|1981-03-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    SE147334C1|
    US2019351A|1934-11-17|1935-10-29|Gen Electric|Air conditioning apparatus|
    US2940736A|1949-05-25|1960-06-14|Svenska Rotor Maskiner Ab|Element set for heat exchangers|
    US3151675A|1957-04-02|1964-10-06|Lysholm Alf|Plate type heat exchanger|
    US3216495A|1963-08-07|1965-11-09|Gen Motors Corp|Stacked plate regenerators|
    US3451474A|1967-07-19|1969-06-24|Gen Motors Corp|Corrugated plate type heat exchanger|
    US3545062A|1967-07-19|1970-12-08|Gen Motors Corp|Method of fabricating a heat exchanger from corrugated sheets|
    GB1166696A|1967-08-29|1969-10-08|Smidth & Co As F L|Processes and Plants in which Cement Raw Material or similar Material is Burnt in a Rotary Kiln|
    US3640340A|1970-11-20|1972-02-08|Baxter Laboratories Inc|Heat exchange device with convoluted heat transfer wall|
    DE2408462A1|1974-02-22|1975-08-28|Kernforschungsanlage Juelich|Heat exchanger for use with helium - has adjacent chambers separated by continuous strip suitably bent and folded|
    DE2420920C3|1974-04-30|1979-08-02|Kernforschungsanlage Juelich Gmbh, 5170 Juelich|Frontal closure for a heat exchanger, the heat exchanger matrix of which is formed by the folds of a band with uniform folds|
    JPS5322292A|1976-08-11|1978-03-01|Ishikawajima Harima Heavy Ind Co Ltd|Water surface cleaning ship|US4699209A|1986-03-27|1987-10-13|Air Products And Chemicals, Inc.|Heat exchanger design for cryogenic reboiler or condenser service|
    DE3741869A1|1987-12-10|1989-06-22|Juergen Schukey|COUNTERFLOW HEAT EXCHANGER|
    US6082445A|1995-02-22|2000-07-04|Basf Corporation|Plate-type heat exchangers|
    AUPN697995A0|1995-12-04|1996-01-04|Urch, John Francis|Metal heat exchanger|
    DE29607547U1|1996-04-26|1996-07-18|Sks Stakusit Kunststoff Gmbh|Plate-type heat exchanger|
    US6186223B1|1998-08-27|2001-02-13|Zeks Air Drier Corporation|Corrugated folded plate heat exchanger|
    SE520267C3|2000-10-04|2003-08-13|Volvo Teknisk Utveckling Ab|Heat Energy Recovery Device|
    TWI326760B|2007-08-31|2010-07-01|Chen Cheng-Tsun|Heat exchanger|
    US20140290921A1|2011-11-21|2014-10-02|Mitsubishi Electric Corporation|Plate-type heat exchanger and refrigeration cycle apparatus using the same|
    CN108700387B|2016-02-03|2020-12-15|摩丁制造公司|Battery cooling plate heat exchanger and plate assembly|
    FR3095692B1|2019-04-30|2021-06-25|Stiral|Element for heat exchanger or heat pipe, and method of manufacture|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE7903535A|SE7903535L|1979-04-23|1979-04-23|VERMEVEXLARE|
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