EP0048873A2 - Dispositif de transfert de chaleur - Google Patents

Dispositif de transfert de chaleur Download PDF

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Publication number
EP0048873A2
EP0048873A2 EP81107194A EP81107194A EP0048873A2 EP 0048873 A2 EP0048873 A2 EP 0048873A2 EP 81107194 A EP81107194 A EP 81107194A EP 81107194 A EP81107194 A EP 81107194A EP 0048873 A2 EP0048873 A2 EP 0048873A2
Authority
EP
European Patent Office
Prior art keywords
tubes
heat exchanger
tube
exchanger according
chamber
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
EP81107194A
Other languages
German (de)
English (en)
Other versions
EP0048873A3 (en
EP0048873B1 (fr
Inventor
Klaus-Dieter Brocks
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.)
Lorowerk Kh Vahlbrauk GmbH
Original Assignee
Lorowerk Kh Vahlbrauk GmbH
VAHLBRAUK LOROWERK
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 Lorowerk Kh Vahlbrauk GmbH, VAHLBRAUK LOROWERK filed Critical Lorowerk Kh Vahlbrauk GmbH
Priority to AT81107194T priority Critical patent/ATE7960T1/de
Publication of EP0048873A2 publication Critical patent/EP0048873A2/fr
Publication of EP0048873A3 publication Critical patent/EP0048873A3/de
Application granted granted Critical
Publication of EP0048873B1 publication Critical patent/EP0048873B1/fr
Expired legal-status Critical Current

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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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits

Definitions

  • the invention relates to a heat exchanger for transferring heat between flowing media which are separated from one another by heat transfer surfaces.
  • Heat exchangers of this type are becoming increasingly important in the context of increasing energy shortages. This arises from the tendency of rising energy prices, on the basis of which it is increasingly proving to be worthwhile to use, for example, previously unused residual energy via an exchange process. In addition, efficient and inexpensive heat exchangers are required as part of the heat pump technology that is becoming increasingly important.
  • a large number of heat exchangers such as coaxial heat exchangers, tube bundle heat exchangers, plate heat exchangers, lamellar tube bundle heat exchangers, are known. It has been found, however, that when using plate heat exchangers, for example, a favorable heat transfer can be achieved due to large heat transfer surfaces, this advantage is countered by major manufacturing disadvantages. Because of the large specific load, it is necessary to use corset constructions that are highly resistant to static loads. Due to this necessity, the material expenditure is large and the con structure necessarily difficult. In addition, there is a need for a large number of surface interlinking points, which on the one hand make production more difficult and on the other hand cost-intensive. Tube heat exchangers also have this disadvantage.
  • the cost-intensive production is caused in particular by the high-quality material of the welded-in tube bundles and, furthermore, by complex distributor structures, such as spiders, throttles and regulators, which are necessary for optimal operation and which are expensive and result in high pressure losses.
  • the heat transfer surfaces are designed as at least two tubes arranged in a jacket tube and at least one guide tube extends through each of these tubes such that a gap is formed between each guide tube and the inner wall of the associated tube, and that both the casing tube and the guide tubes are connected to one another for a first medium via a distributor space on the one hand and a collector on the other hand, each of which is separated from a distributor chamber or collector chamber for a second medium connecting the tubes and the gap spaces.
  • This structure allows economical production. It is essential here that the individual connection points, in particular welding points, are easily accessible and, on the other hand, that the individual parts can be joined together in the simplest way. Because of their dimensional stability, the pipes that are joined together meet high strength requirements. Furthermore, it makes itself noticeably noticeable that inexpensive semi-finished products can also be used within the structure.
  • the compact design has the advantage that the heat exchanger has a large heat-transfer surface with a small space requirement.
  • flow-guiding devices extend in a gap space arranged between the tubes.
  • baffles in the liquid space due to the design enables desired flow effects to be produced with little manufacturing effort.
  • This makes it possible to pass the liquid through the heat exchanger in a manner that ensures very favorable heat transfer.
  • the tubes support each other through such baffles, so that a honeycomb structure is created in this way. With small wall thicknesses of the individual tubes, this has a high overall strength.
  • the heat exchanger can therefore be used at a high pressure level without the need for high-strength materials for its formation.
  • the basic components of the heat exchanger are a jacket tube 1, tubes 2 and guide tubes 3.
  • the casing tube 1 has a round, rectangular or suitably profiled, preferably a square cross section.
  • the tubes 2 extend through this jacket tube 1 in the longitudinal direction and may have a preferably square cross section corresponding to the cross section of the jacket tube 1, so that four tubes 2 are distributed over the cross section of the jacket tube 1.
  • the guide tubes 3 extend parallel to these through the tubes 2. These have an only insignificantly smaller cross-section than the tubes 2.
  • the guide tubes 3 are provided with outer surfaces, between which and the inner surfaces of the tubes 2 opposite them a relatively small gap space 13 is provided , which has a small flow cross-section.
  • the casing tube 1 is closed at both ends with covers 8, 8a. These covers 8, 8a delimit anterooms 7, 7a on their inner sides facing the tubes 2, into which the guide tubes 3 open. In the area of the mouths of the guide tubes 3, these are connected to one another via tube plates 6, 6a. These tube sheets 6, 6a delimit the vestibules 7, 7a in the casing tube 1 on the side opposite the covers 8, 8a.
  • the anterooms 7, 7a are connected to inlet ports 11, 11a via inlet openings 20, 21. Depending on the circuit provided in each case, a medium enters or exits the heat exchanger in these inlet connections 11, 11a.
  • the medium entering through the inlet nozzle 11 flows through the inlet opening 20 into the antechamber 7, flows through the interior of the guide tubes 3, collects in the antechamber 7a and exits via the inlet opening 21 through the outlet nozzle 11a.
  • the tube plates 6, 6a delimit a distributor chamber 5a or a collector chamber 5 on their underside facing away from the ante-rooms 7, 7a.
  • This distributor chamber 5a or collector chamber 5 is delimited on its side facing away from the tube sheets 6, 6a by orifices 22, 23 which are formed by flaring the ends 24, 25 of the tubes 2 facing the distributor chamber 5a or collector chamber 5.
  • These ends 24, 25 are connected to one another via welds 4.
  • all other connection options of the ends 24, 25 can also be used, for example adhesive connections.
  • the ends 24, 25 are also connected to the casing tube 1 on the sides thereof by means of weld seams 4. Other connection options can also be used here.
  • the distributor chamber 5a and the collector chamber 5 are each connected via openings 26, 27 to an outlet nozzle 9 and an inlet nozzle 9a.
  • a second medium acting on the guide tubes 3 on their outer sides passes through these openings 26, 27. This medium flows through gap spaces 13 so that it achieves a relatively high passage speed in view of the small passage cross section of these gap spaces 13.
  • the inlet connector 11 and the outlet connector 11a are each connected via a distributor space 10 and 15 to the inlet openings 20 and 21 as well as to another inlet opening 28 and 29 which are arranged in% in the casing tube 1.
  • the medium flowing in through the inlet connection 11 or flowing out of the outlet connection 11a can enter or exit an interior space 30 formed by the casing tube 1.
  • This interior space 30 is traversed by the tubes 2, so that only gap spaces 14 remain from it, through which the medium flowing through the nozzles 11, 11a through the inlet opening 28, flows through the gap spaces 14 and merges via the outlet opening 29 with the medium emerging from the vestibules 7, 7a in the region of the distributor spaces 10, 15.
  • the gap spaces 14 are traversed by flow-guiding devices 12.
  • These can be meander wires, the diameter of which corresponds approximately to the clear width of the gap spaces 14. In this way it is achieved that the tubes 2 are mutually supported.
  • the flow-guiding devices 12 provide support for the pipes 2 with respect to the casing pipe 1.
  • the flow-guiding device is laid in the manner that is most favorable for the respective heat transfer purpose. For example, it is conceivable to wind the meander wires spirally around the tubes 2, so that a cross or cross flow of the second medium passing through the jacket tube 1 is achieved with respect to the medium passing through the guide tubes 3.
  • any other type of fastening can also be considered, so that any type of mutual flow conditions can be realized in the heat exchanger.
  • any other arrangement of pipes 2 in the casing pipe 1 can also be carried out. It is essential that the respective gap spaces 13 and 14 are provided with such a narrow passage cross-section that the media passing through them are suitable for the respective gap spaces 13 and 14 by appropriate selection of cross sections of both the casing tube 1 and the tube 2 and the guide tubes 3 optimal heat transfer necessary passage ge get speed.
  • tubes 2 it is conceivable to arrange tubes 2 to be dimensioned in a jacket tube 1 with a square cross-section in a number that corresponds to the square number of the basic numbers.
  • the jacket tube 1 a rectangular cross section with a corresponding number of tubes 2. In any case, the dimensioning of both the casing tube 1 and the tube 2 and the guide tubes 3 will have to be based on the dimensions in which the corresponding tubes can be obtained cheaply, for example as semi-finished products.
  • the heat exchanger works as follows: A medium, for example cooling water, enters both the antechamber 7 and the interior 30 through the inlet connection 11 and the distributor space 10. It is distributed over the inner spaces of the guide tubes 3 and is simultaneously guided past the outer walls of the tubes 2 by the flow-guiding devices 12. This medium portion pouring out through the interior 30 of the heat exchanger enters the distribution space 15 through the outlet opening 29 and is forwarded by the latter in the direction of the outlet opening 11a. The medium portion passing through the guide tubes 3 collects in the vestibule 7a, enters the distribution space 15 through the opening 21 and is also discharged through the outlet opening 11a.
  • a medium for example cooling water
  • the other medium for example hot gas
  • the other medium for example hot gas
  • the heat exchanger can be used both as an evaporator and as a condenser.
  • Evaporator has an optimal gas distribution as a partial pipe apparatus and works due to its design features such. B. in the prechambers 7, 7a even in the flooded operation of the distributor with evenly distributed, pressure losses.
  • condenser all surfaces involved in the heat transfer are evenly acted upon and utilized by uniform evaporation and condensate drainage on the hot gas side. The application of these heat transfer surfaces is arithmetically uniform due to the constructive arrangement of the parallel fluid paths.
  • the heat exchanger can also be used in a variety of applications because it as countercurrent, cocurrent.
  • Cross-current or cross-current transformer can be used.
  • the tubes used for heat transfer namely jacket tube 1, tubes 2 and guide tubes 3, can have a round or otherwise profiled cross section, for. B. rectangular, prismatic and for strength and functional reasons also hexagonal, and tubes with different cross-sectional design depending on the application or the media used can be combined.
  • the heat exchanger can be used as a tertiary exchanger with three separate heat transfer media.

Landscapes

  • 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)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
  • Gloves (AREA)
  • Power Steering Mechanism (AREA)
EP81107194A 1980-09-26 1981-09-11 Dispositif de transfert de chaleur Expired EP0048873B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81107194T ATE7960T1 (de) 1980-09-26 1981-09-11 Waermeuebertrager.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3036334 1980-09-26
DE3036334A DE3036334C2 (de) 1980-09-26 1980-09-26 Wärmeübertrager

Publications (3)

Publication Number Publication Date
EP0048873A2 true EP0048873A2 (fr) 1982-04-07
EP0048873A3 EP0048873A3 (en) 1982-09-01
EP0048873B1 EP0048873B1 (fr) 1984-06-13

Family

ID=6112927

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107194A Expired EP0048873B1 (fr) 1980-09-26 1981-09-11 Dispositif de transfert de chaleur

Country Status (3)

Country Link
EP (1) EP0048873B1 (fr)
AT (1) ATE7960T1 (fr)
DE (2) DE3036334C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110608623A (zh) * 2019-07-09 2019-12-24 广东焕能科技有限公司 一种无油螺杆空压机余热回收器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE44091C (fr) *
US2633338A (en) * 1947-02-19 1953-03-31 Continental Aviat & Engineerin Heat exchanger
DE1117148B (de) * 1958-01-04 1961-11-16 Gea Luftkuehler Happel Gmbh Waermeaustauscher, insbesondere fuer fluessige Medien, die nicht miteinander in Beruehrung kommen duerfen
FR1501741A (fr) * 1965-05-21 1967-11-18 English Electric Co Ltd échangeur de chaleur pour transfert indirect de chaleur
DE2029910A1 (de) * 1969-06-18 1971-01-07 Rossi, Giuhano, Piove di Sacco, Padua (Italien) Rohre fur Wärmeaustauscher
DE2143276A1 (de) * 1971-08-30 1973-03-15 Parca Waermeprodukte Gmbh Doppelrohr-waermetauscher
DE2819777A1 (de) * 1977-05-09 1978-11-23 Pressure Vessels Inc Geraet zum austauschen von waerme zwischen zwei fluids

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB260066A (en) * 1925-08-12 1926-10-28 Emilio Storoni Heat exchange apparatus
FR725413A (fr) * 1931-02-12 1932-05-12 Perfectionnements aux appareils échangeurs de chaleur
DE814159C (de) * 1949-07-08 1951-09-20 Otto H Dr-Ing E H Hartmann Waermeaustauscher

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE44091C (fr) *
US2633338A (en) * 1947-02-19 1953-03-31 Continental Aviat & Engineerin Heat exchanger
DE1117148B (de) * 1958-01-04 1961-11-16 Gea Luftkuehler Happel Gmbh Waermeaustauscher, insbesondere fuer fluessige Medien, die nicht miteinander in Beruehrung kommen duerfen
FR1501741A (fr) * 1965-05-21 1967-11-18 English Electric Co Ltd échangeur de chaleur pour transfert indirect de chaleur
DE2029910A1 (de) * 1969-06-18 1971-01-07 Rossi, Giuhano, Piove di Sacco, Padua (Italien) Rohre fur Wärmeaustauscher
DE2143276A1 (de) * 1971-08-30 1973-03-15 Parca Waermeprodukte Gmbh Doppelrohr-waermetauscher
DE2819777A1 (de) * 1977-05-09 1978-11-23 Pressure Vessels Inc Geraet zum austauschen von waerme zwischen zwei fluids

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110608623A (zh) * 2019-07-09 2019-12-24 广东焕能科技有限公司 一种无油螺杆空压机余热回收器
CN110608623B (zh) * 2019-07-09 2024-04-09 广东焕能科技有限公司 一种无油螺杆空压机余热回收器

Also Published As

Publication number Publication date
DE3036334C2 (de) 1985-09-12
EP0048873A3 (en) 1982-09-01
EP0048873B1 (fr) 1984-06-13
ATE7960T1 (de) 1984-06-15
DE3036334A1 (de) 1982-07-29
DE3164193D1 (en) 1984-07-19

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