WO2007084063A1 - Procede d'echange de chaleur et dispositif echangeur de chaleur - Google Patents

Procede d'echange de chaleur et dispositif echangeur de chaleur Download PDF

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Publication number
WO2007084063A1
WO2007084063A1 PCT/SE2007/000059 SE2007000059W WO2007084063A1 WO 2007084063 A1 WO2007084063 A1 WO 2007084063A1 SE 2007000059 W SE2007000059 W SE 2007000059W WO 2007084063 A1 WO2007084063 A1 WO 2007084063A1
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WO
WIPO (PCT)
Prior art keywords
rotating
sector
medium
periphery
disc
Prior art date
Application number
PCT/SE2007/000059
Other languages
English (en)
Inventor
Eva Gudmundsson
Original Assignee
Eva Gudmundsson
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 Eva Gudmundsson filed Critical Eva Gudmundsson
Publication of WO2007084063A1 publication Critical patent/WO2007084063A1/fr

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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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller

Definitions

  • the present invention relates to ways and means to transfer heat utilizing rotating surfaces, in addition to what is described in European patent 0586402.
  • the invention also relates to embodiment of the method.
  • Embodiment providing a rotating part comprising internal cavities arranged for transport of gases or liquids.
  • Embodiment arranged for heat exchange between two gases, two liquids or between gas and liquid.
  • Embodiment of heat exchanger in heat recovery equipment, cooling in climate equipment or other applications utilizing heat exchange - between two fluids .
  • Heat exchanger part of a climate unit intended for cooling of telecom equipment is a usage example.
  • Another usage example is heat exchanger for energy saving in building ventilation system. It is easily understood that any type of heat exchange in varying applications is a possible usage of the invention.
  • heat exchanger can be arranged by embodiment with rotating disc surfaces and cavities between the disk surfaces such that heat exchange occurs between two or more medias, flowing in the cavities. Heat Exchange occurs by heat transfer from one medium to the other through the disc surfaces.
  • Patent EU 0586402 embodiment is characterized by cavities and rotating disc surfaces stacked at different axial levels along a rotating shaft. Heat- exchange basically occurs from one level along the rotating shaft - to another level. The intention is that the media for each level with cavities can move along the disc surfaces basically in a rotational symmetric cavity.
  • this embodiment could be implemented in such a way that one media (media 1) has a media-flow that, from the center channel inlet, enters a cavity between two rotating disc surfaces and, after passage of the cavity, exits the cavity in radial slots at the periphery, between two disc surfaces.
  • the other media flow enters another cavity, at another location along the rotating shaft between rotating disc surfaces from inlet channels arranged at the periphery and leaves the cavity in sector channels arranged in the center of the disc surfaces.
  • Medium 1 flows - if the complicated rotating streaming mechanical movement in the cavity is disregarded - mainly from the center and radially outward towards the periphery along the disc surfaces.
  • Medium 2 flows - if the complicated rotating streaming mechanical movement is disregarded, mainly from periphery and radially inwards towards the center, along the disc surfaces.
  • This system provides very good heat exchanging characteristics, provides a compact embodiment and additionally provides pump or fan function automatically - for the media flow that moves outwards and leaves the heat exchanger embodiment at the periphery of the disc surfaces.
  • a compact pump embodiment could be connected to the heat exchanger embodiment.
  • the system according to the patent EU0586402 has the drawback that the heat exchange is determined by the rotating flow mechanical movement of the two Medias . The heat exchange performance is good when the different media flows overlap each other at each side of the discs.
  • Fig 1 illustrating an embodiment of the present invention with a rotating part.
  • Fig 2 illustrating an embodiment of discs with divided sector areas (only a few sector areas are visualized with media flows) .
  • Fig 3 illustrating a divided sector area schematically with media flow entering from the centre sector channels to an outlet at the periphery.
  • Fig 4 illustrating another divided sector area schematically with a media flow entering the disc surfaces from peripheral channels than moving towards exit slots at the central sector channels .
  • Fig 5 illustrating schematically the axial location of 3 axially on each other stacked discs along a common central shaft.
  • Fig ⁇ illustrating an alternative design of curve- shaped sector areas of the discs.
  • the device comprises a rotating part 1 being symmetrical in rotation that can be revolved around an axis of rotation 2 by means of driving of an electrical engine or another driving arrangement.
  • the rotating part 1 consists of a package with several similar discs and stacked to each other axially along a shaft with cavities between discs.
  • the cavities in rotating part 1 communicate mutually such matter that they altogether are separated in two different volumes separated from each other.
  • One fluent medium in one volume cannot go into the other volume inside the heat exchanger package in rotating part 1. Two different mediums can then be kept separated from each other in the rotating part 1.
  • Fig. 2 shows a principal design of surface disc 3, which is mounted on the rotating shaft 2 and rotates with a certain rotational speed in rotating part 1.
  • Disc 3 which may consist of metal, plastic or another solid material, is the interface through which heat can be transferred between medium 4 and medium 5.
  • Surface or disc 3 is divided into sector areas 6 and 7 on surface or disc 3.
  • Fig. 3 shows a principal type of sector area 6 on surface of disc 3.
  • sector medium 4 flows from a vertical sector channel 8 in centre of rotating parti.
  • Medium 4 moves or flows mainly radially outwards towards opening 9 between disc 10 and disc 3 fig.5, where medium 4 leave the rotating part.
  • Medium 4 is enclosed in a sector area sector 6 by barriers 11 separating from sector channel 12, barriers 13 stretching from centre to periphery of disc radial barriers separating adjacent sector areas on surface or disc 3 and finally barrier 14 separating sector areas 8 from the axial 14 channel near the periphery of part 1. All barriers connects axially disc 3 and disc 10 and have thus the axial height that corresponds to the axial height of the cavity. Barriers 13 may or may not, for some special embodiments, connect axially disc 3 and disc 10 as described later in this technical description.
  • barriers sector area 6 describes a sector formed cavity between disc 10 and disc 3. The sector formed cavity connects to under side of disc above .
  • Fig. 4 shows the other type of sector area 7 on the disc 3.
  • This sector area medium 5 flows from the axial channel 15, at the periphery, mainly radial inwards towards centre of sector area 7 and leaves cavity through vertical channel 12.
  • the cavity over sector area 7 has radial barriers 13, stretching from centre to periphery of disc, for separating adjacent sector areas.
  • Barrier 16 at the periphery of part 1 encloses cavity over sector area 7 from environment radially outside cavity.
  • Barrier 17 separates from vertical sector channel 8. All barriers connects axially disc 3 and disc 10 and have thus the axial height that corresponds to the axial height of the cavity.
  • Barriers 13 may or may not, for some special embodiments, connect axially disc 3 and disc 10 as described later in this technical description.
  • With barriers sector area 7 describes a sector formed cavity between disc 10 and disc 3.
  • the sector formed cavity connects to under side of disc above.
  • Fig. 5 shows in principal how three discs in rotating part 1 from top disc 10, 3 and 18 are stacked on the same shaft axially over each other with common rotational centre, in rotating part 1, and are separated by the height of barriers described above.
  • Sector areas and barriers form sector formed cavities.
  • Disc 10 may have sector areas of both type 6 and 7.
  • Disc 3 may have sector areas of both type 6 and 7.
  • Disc 18 is identical to disc 10 and has the same arrangement of sector areas as disc 10. The number of sector areas 6 and 7 and placement of sector areas of disc 10, 3 and 18 is arranged that sector formed cavities on sector areas type 6 on disc 10 overlap sector formed cavities on sector areas type 7 on disc 3 below, and sector areas 7 on disc 10 overlap sector areas 6 on disc 3.
  • the same arrangement is repeated for the disc below. This arrangement is repeated until the lowest disc in disc stack of rotating part 1.
  • Discs in the rotating part 1 like disc 10, 3 or 18 can of course, for each disc, like disc 10 in fig. 5, have sector area of only one type.
  • barriers 13 can also be given for radial or curve formed barriers 13 when adjacent sector areas are of the same type, for example 6 or 7.
  • Barriers 13 can in such cases have not fully height in cavity between discs as the rest of barriers 11, 12, 14 and 16.
  • Barriers 13 may, for cases when adjacent sector areas are of same type, also have stretch, which is not full length from centre to periphery of disc. With these two possibilities of design adjacent sector areas of the same type are not fully separated and flow can pass between these adjacent cavities in these sector areas. It has a fluid mechanical positive effect as medium in sector areas is stirred and higher degree of media elements are exposed to disc surface. Together with increased resident time in rotating part 1, this gives improved heat transfer performance. Even with reduced height of barriers 13, they provide control of pathways of flow in cavity.
  • sector area 7 have medium flow mainly radial inwards from periphery towards rotational centre of disc in rotating part 1. Together With radial outward flow in sector area 6 the heat exchange is so called counter flow, a well known term for heat exchangers, which give high heat exchange performance.
  • the radial inward flow has however the drawback that pressure drop is higher for media 5 in sector area 7 than for media 4 in sector area 6.
  • flow for medium 5 in sector area 7 can have its inlet to the sector in centre from channels 12 in centre and flows mainly radial outward in sector area 7 and flow exit from the sector area 7 through axial channels 15, at the periphery of disc.
  • disc in the rotating part 1 can also be done where discs are pleated radially, which gives surface enlargement and because of that increased heat exchange. In this case there must also be all type of described above.
  • the invention is not limited to the various described and shown embodiments, but variations thereof are naturally possible within the scope of claim 1.

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)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)

Abstract

L'invention concerne un procédé d'échange de chaleur par récupération entre deux milieux, comportant l'introduction des milieux dans une partie (1) rotative pourvue d'espaces internes disposés dans des cavités séparées aménagées pour les milieux dans la partie (1) rotative où les milieux échangent de la chaleur en écoulement parallèle ou à contre-courant. Les cavités dans la partie (1) rotative sont disposées en secteurs entre des surfaces ou disques rotatifs disposés axialement le long d'un arbre. La chaleur est échangée entre les milieux à travers les surfaces rotatives.
PCT/SE2007/000059 2006-01-23 2007-01-23 Procede d'echange de chaleur et dispositif echangeur de chaleur WO2007084063A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0600133A SE0600133L (sv) 2006-01-23 2006-01-23 Sätt och anordning att ordna kaviteter i en kvopp
SE0600133-3 2006-01-23

Publications (1)

Publication Number Publication Date
WO2007084063A1 true WO2007084063A1 (fr) 2007-07-26

Family

ID=38287912

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2007/000059 WO2007084063A1 (fr) 2006-01-23 2007-01-23 Procede d'echange de chaleur et dispositif echangeur de chaleur

Country Status (3)

Country Link
CN (1) CN101371095A (fr)
SE (1) SE0600133L (fr)
WO (1) WO2007084063A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110425911B (zh) * 2019-08-30 2024-04-19 中国科学院理化技术研究所 一种三介质换热器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1030203A (en) * 1911-07-31 1912-06-18 Christen Paulsen Pasteurizing apparatus.
US1728204A (en) * 1927-11-29 1929-09-17 Edge Moor Iron Company Double-flow fan
US2596622A (en) * 1944-09-25 1952-05-13 Vannerus Torbjorn Recuperative heat exchanger of the counterflow type for gaseous media
US2794135A (en) * 1953-02-05 1957-05-28 Swendsen Johan Walfred Heat exchanger for fluids
US3650319A (en) * 1970-04-24 1972-03-21 Monsanto Co Heat exchange device
US4073338A (en) * 1973-06-26 1978-02-14 Toyota Chuo Kenkyusho Heat exchangers
US4640345A (en) * 1984-10-10 1987-02-03 Jinichi Nishimura Rotating heat exchanger
DE3608797A1 (de) * 1986-03-15 1987-10-22 Rudolf Kiesslinger Waermeuebertrager fuer ultraschnelle, verlustarme fluid-aufheizung und -kuehlung, insbesondere in heissgasmotoren, stirlingmotoren und kaeltemaschinen
EP0586402B1 (fr) * 1991-04-17 1999-03-31 Björn GUDMUNDSSON Procede et dispositif de transfert de chaleur ou de matiere
SE527867C2 (sv) * 2004-11-12 2006-06-27 Bjoern Gudmunsson Kylanordning

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1030203A (en) * 1911-07-31 1912-06-18 Christen Paulsen Pasteurizing apparatus.
US1728204A (en) * 1927-11-29 1929-09-17 Edge Moor Iron Company Double-flow fan
US2596622A (en) * 1944-09-25 1952-05-13 Vannerus Torbjorn Recuperative heat exchanger of the counterflow type for gaseous media
US2794135A (en) * 1953-02-05 1957-05-28 Swendsen Johan Walfred Heat exchanger for fluids
US3650319A (en) * 1970-04-24 1972-03-21 Monsanto Co Heat exchange device
US4073338A (en) * 1973-06-26 1978-02-14 Toyota Chuo Kenkyusho Heat exchangers
US4640345A (en) * 1984-10-10 1987-02-03 Jinichi Nishimura Rotating heat exchanger
DE3608797A1 (de) * 1986-03-15 1987-10-22 Rudolf Kiesslinger Waermeuebertrager fuer ultraschnelle, verlustarme fluid-aufheizung und -kuehlung, insbesondere in heissgasmotoren, stirlingmotoren und kaeltemaschinen
EP0586402B1 (fr) * 1991-04-17 1999-03-31 Björn GUDMUNDSSON Procede et dispositif de transfert de chaleur ou de matiere
SE527867C2 (sv) * 2004-11-12 2006-06-27 Bjoern Gudmunsson Kylanordning

Also Published As

Publication number Publication date
SE0600133L (sv) 2007-07-24
CN101371095A (zh) 2009-02-18

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