WO1988004756A1 - Turbomachine pour refoulement de deux milieux avec transfert thermique entre ces derniers - Google Patents

Turbomachine pour refoulement de deux milieux avec transfert thermique entre ces derniers Download PDF

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Publication number
WO1988004756A1
WO1988004756A1 PCT/EP1987/000737 EP8700737W WO8804756A1 WO 1988004756 A1 WO1988004756 A1 WO 1988004756A1 EP 8700737 W EP8700737 W EP 8700737W WO 8804756 A1 WO8804756 A1 WO 8804756A1
Authority
WO
WIPO (PCT)
Prior art keywords
channels
media
impeller
hollow cylinder
housing
Prior art date
Application number
PCT/EP1987/000737
Other languages
German (de)
English (en)
Inventor
Wolfgang Reichel
Original Assignee
Ingenieurbüro Timmer Gmbh
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 Ingenieurbüro Timmer Gmbh filed Critical Ingenieurbüro Timmer Gmbh
Publication of WO1988004756A1 publication Critical patent/WO1988004756A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • Fluid machine for conveying two media with heat transfer between the. media
  • the present invention relates to a turbomachine for conveying two media via two separate flow paths, in particular for conveying two media of the same type with different heat contents and for transferring thermal energy from the respectively warmer to the respectively colder medium, with a housing with two inlets and two outlets for the media, within the housing arranged fluids for sucking in and compressing or displacing the media, and with channels adjacent to and through which the media flow so that the partition walls form heat exchange surfaces for heat transfer between the media .
  • Such a turbomachine is known from DE-GM 82 36 459.
  • This is a device for heat exchange between two gaseous media, in particular fresh air and exhaust air in rooms.
  • the fluids consist of two separate radial fans which are arranged on the same shaft within the housing and which convey the two media through the channels of a separate countercurrent heat exchange unit. The heat exchange between the media takes place via the partitions separating the channels, which thus form heat exchange surfaces.
  • this known turbomachine is structurally complex and consequently also relatively expensive.
  • the heat exchange unit at least partially surrounds the fans, which results in the further disadvantage of large dimensions.
  • a further disadvantage is that the efficiency of the heat transfer is dependent on the length of the heat exchange unit through which a reduction in the size of the machine would lead to a deterioration in the efficiency or an improvement in the efficiency would lead to a further increase in the size of the machine.
  • a so-called capillary fan is described, a rotor made of porous mass serving simultaneously as a fan and storage .
  • the interior of the rotor is divided into two chambers by a partition.
  • the rotating porous storage mass of the rotor compresses or displaces the gaseous medium flowing into the chamber and transfers the energy content including the moisture content of one gaseous substance to the other.
  • the disadvantage here is the inexact separation of the two gaseous media, which causes mixing effects.
  • the porous mass filters out dirt particles, which requires frequent cleaning of the rotor.
  • the present invention is based on the object, based on the prior art described at the outset, of specifying a structurally simple and compact turbomachine in which the outlay for conveying the media and for the heat transfer between the media is reduced and the efficiency of the heat transfer is increased.
  • the fluid is formed by a double-sided suction radial impeller, and in that the channels on the circumference of the impeller run in an essentially axial direction and the partition walls arranged between the channels as radial blades of the impeller are formed. Due to this advantageous embodiment, the two separate wheels previously required d -
  • the turbomachine according to the invention is extremely compact.
  • the heat transfer between the media takes place via the partition walls or moving blades, which thus form the heat exchange surfaces.
  • intermediate walls are arranged within the channels of the impeller in such a way that the axial direction of flow of the media within the channels reverses at least once by 180 °.
  • this advantageous embodiment also makes it possible to further reduce the dimensions of the turbomachine according to the invention, in particular by axially shortening the impeller, while maintaining the efficiency.
  • FIG. 1 shows a longitudinal section through a first embodiment of a turbomachine according to the invention along the section line I-I in FIG. 2,
  • FIG. 2 shows a cross section of the turbomachine along the line II-II according to FIG. 1,
  • FIG. 3 shows a longitudinal section through a further embodiment of a turbomachine according to the invention
  • Fig. 4 is a cross section along the line IV-IV of FIG. 3 and
  • Fig. 5 shows an alternative embodiment of an impeller of a turbomachine according to the invention.
  • FIGS. 1 to 4 Two embodiments of a turbomachine according to the invention are shown in FIGS. 1 to 4.
  • a housing 1 has an inlet 2 and an outlet 3 for a first medium I and an inlet 4 and an outlet 5 for a second medium II.
  • a single radial impeller 11 is arranged within the housing 1, rotatably mounted about an axis 7 and driven in the arrow direction 8 (FIG. 2) by a motor 9.
  • channels 12, 13 extending in the axial direction are formed on the circumference of the impeller 11 such that two channels 12, 13 adjacent in the circumferential direction via an essentially radially arranged partition 14 each one of the Guide both media I, II in axial flow directions and displace them radially.
  • the medium I flows through the channels 12 and the medium II flows through the channels 13 between the channels 12, the partitions 14, which act as radial blades, form heat exchange surfaces for heat transfer between the media I, II.
  • the impeller 11 consists of an inner hollow cylinder 16 and an outer hollow cylinder 17 which is concentric with this. These two hollow cylinders 16, 17 are connected to one another via the partition walls 14 to form the channels 12, 13. This results in an annular opening between the two hollow cylinders 16, 17 on each end face, which, however, is closed, for example, by a disk ring.
  • the inner hollow cylinder 16 At the entry of the Media I, II into the channels 12, 13 has the inner hollow cylinder 16 in its two areas adjoining its end faces with slot-shaped inlet openings 19 opening radially into the channels 12, 13. These inlet openings 19 open into the channels 12 for the medium I on the side arranged in the region of the inlet 2 and into the channels 13 for the medium II on the side arranged in the region of the inlet 4.
  • intermediate walls 21 are arranged within the channels 12, 13 in such a way that the axial flow direction of the media I, II within the channels 12, 13 reverses at least once by 180 °. This results in an extension of the effective flow path and thus an improvement in the efficiency of the heat exchange.
  • an intermediate wall 21 is arranged in each channel 12, 13.
  • the intermediate walls 21 lie on a cylindrical surface which is concentric with the axis of rotation 7, so that the channels 12 r 13 are each divided into inner partial channels 12a, 13a and outer partial channels 12b, 13b.
  • the intermediate walls 21 of the channels 12 for the medium I each extend axially through the channel 12 from the closed end of the channel 12 facing the inlet 2, but end at a distance in front of the opposite end, so that flow reversal openings between the Subchannels 12a, 12b are formed.
  • the intermediate walls 21 of the channels 13 for the medium II extend axially through the closed end face of the channels 13 facing the inlet 4 and end at a distance in front of the opposite end face, so that flow reversal openings between the partial channels 13 a , 13b are formed.
  • At least one partition wall 23 which is preferably perpendicular to the impeller axis, is arranged in the inner hollow cylinder 16 in the axial direction between the inlet openings 19, which prevents that the axially sucked media I, II mix within the inner hollow cylinder 16.
  • two partition walls 23 are arranged within the inner hollow cylinder 16 directly adjoining the inlet openings 19. The media I, II are thereby axially sucked in and subsequently flow radially through the inlet openings 19 into the channels 12, 13, ie into the inner subchannels 12a, 13a.
  • an annular inlet nozzle 25, 26 advantageously opens into each of the two end faces.
  • the outer hollow cylinder 17 has slot-shaped outlet openings 27 in its two regions adjacent to its end faces , which are arranged at the end (as seen in the direction of flow of the media I, II) of the channels 12, 13 and the sub-channels 12b, 13b.
  • the outlet openings 27 In its axially between the outlet openings 27 administrat ⁇ the area is the "outer hollow cylinder 17 sealingly surrounded by at least one radial housing wall 29, which ensures the separation of the radially from the outlet openings 27 discharged media I, II.
  • Medium I inlet 2, inlet nozzle 25, inlet openings 19, subchannels 12a, flow reversal opening (reversal through 180 °), subchannels 12b, outlet openings 27, pressure chamber 32, outlet 3.
  • inlet 4 inlet nozzle 26, inlet openings 19, subchannels 13a, flow reversal opening (reversal through 180 °), subchannels 13b, outlet openings 27, pressure chamber 33, outlet 5.
  • intermediate walls 21 are provided. are to increase the flow path and thus the effective heat exchange area.
  • the intermediate walls 21 can, however, also be omitted, the flow paths then resulting as follows without reversing the flow:
  • the heat exchange achieved in the flow machine according to the invention is often not sufficient to sufficiently heat or cool the supply air (medium I) flowing into the room.
  • the required residual heat is supplied or extracted from the supply air by the additional heat exchanger 34.
  • the additional heat exchanger 34 is preferably integrated into the housing 1 in the region of one of the outlets 3, 5, which ensures a compact design of the turbomachine. The corresponding outlet 3 or 5 is then omitted.
  • FIGS. 3 and 4 The flow machine shown in FIGS. 3 and 4 is shown exclusively as a compressor / heat exchanger unit without an additional heat exchanger.
  • a shaft 35 which is rotatably mounted in the housing 1 about the impeller axis 7 and can be driven by the motor 9, extends axially centrally through the dividing walls 23 and projects beyond the impeller 11 on both end faces in the axial direction.
  • a central shaft piece 36 which extends axially beyond the impeller 11 on the end face and which is rotatably mounted in the housing 1 about the impeller axis 7 and can be driven by the motor 9, can also be attached to each partition 23.
  • the region of the hollow cylinder 16 arranged between the partition walls 23 assumes the supporting functions of a shaft.
  • the essentially radial partitions 14 - as already stated - act as radial blades.
  • the partition walls 14 can be designed as forwardly curved blades or, as shown in FIG. 4, as rearwardly curved blades. In addition, however, it is also within the scope of the invention to design the partition walls 14 as straight-running blades.
  • FIG. 5 shows an alternative embodiment of an impeller 11a according to the invention.
  • This impeller 11a consists of a shaft 41 and a hollow cylinder 42 concentrically enclosing the shaft 41. Between the shaft 41 and the hollow cylinder 42, the partitions extend in an essentially radial direction to form the channels, which means that radial rotor blades also in this case are formed.
  • axial rotor blades 44 are provided on the end face, which rotate together with the impeller 11a and thus axially displace the media I, II into the channels.
  • the axial rotor blades 44 are arranged in the area of the inner partial channels, so that the media " flow into the inner partial channels and exit the outlet openings 27 of the outer partial channels after the flow has been reversed.
  • the advantage This design lies in particular in the enlarged heat exchanger area, which results from the fact that the partition walls between the channels extend from the hollow cylinder 42 to the shaft 41, that is to say are made wider in the radial direction.
  • the present invention is not limited to the exemplary embodiments shown and described, but also encompasses all features having the same effect in the sense of the invention.
  • it is also Examples according to FIGS. 1 to 4 conceivable to provide additional axial impellers which are arranged in front of the end faces of the impeller 11 and rotate together therewith, which axially convey the media I, II into the region of the inner hollow cylinder 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Turbomachine pour refouler deux milieux par l'intermédiaire de deux voies d'écoulement séparées, notamment pour refouler deux milieux de même type ayant des capacités caloriques différentes et pour transférer de l'énergie thermique du milieu le plus chaud au milieu le plus froid. Ladite machine comporte un carter avec deux orifices d'admission et deux orifices de sortie pour les milieux, des moyens de circulation agencés à l'intérieur du carter pour aspirer et pour comprimer ou refouler les milieux, ainsi que des canaux contigus par l'intermédiaire de parois de séparation et parcourus par les milieux de manière telle que les parois de séparation forment des surfaces d'échange thermique permettant le transfert de chaleur entre les milieux. Ces moyens de circulation sont formés par une roue à aubes (11) radiale à aspiration des deux côtés, et les canaux (12, 13) s'étendent à la périphérie de la roue à aubes (11) dans une direction sensiblement axiale, et les parois de séparation (14) disposées entre les canaux (12, 13) se présentent sous forme d'aubes radialement mobiles de la roue (11, 11aa). Cette configuration permet de créer une turbomachine compacte de conception simple.
PCT/EP1987/000737 1986-12-19 1987-11-27 Turbomachine pour refoulement de deux milieux avec transfert thermique entre ces derniers WO1988004756A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3643496A DE3643496C2 (de) 1986-12-19 1986-12-19 Strömungsmaschine zum Fördern von zwei Medien mit Wärmeübertragung zwischen den Medien
DEP3643496.5 1986-12-19

Publications (1)

Publication Number Publication Date
WO1988004756A1 true WO1988004756A1 (fr) 1988-06-30

Family

ID=6316626

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1987/000737 WO1988004756A1 (fr) 1986-12-19 1987-11-27 Turbomachine pour refoulement de deux milieux avec transfert thermique entre ces derniers

Country Status (2)

Country Link
DE (1) DE3643496C2 (fr)
WO (1) WO1988004756A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993004332A1 (fr) * 1991-08-12 1993-03-04 Raymond Leroy Anderson Echangeur de chaleur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8918446D0 (en) * 1989-08-12 1989-09-20 Stokes Keith H Heat exchange apparatus
DE10228595B4 (de) * 2002-06-26 2005-03-17 Enginion Ag Aufheizeinrichtung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5896989A (ja) * 1981-12-04 1983-06-09 Toshiba Corp 熱交換器

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3903961A (en) * 1973-11-08 1975-09-09 Morrison Machine Co Hot oil drum
DE2420733C2 (de) * 1974-04-29 1985-11-28 R.E. Dupont Research and Investment Services Ltd., Douglas, Isle of Man Vorrichtung zum Be- und Entlüften von Räumen, Gebäuden und dergleichen
DE2717462A1 (de) * 1977-04-20 1978-10-26 Schrag Heizungs Lueftungs Klim Radialgeblaese, insbesondere fuer die klimatechnik
AT372187B (de) * 1981-12-30 1983-09-12 Wagner Wilfried Ing Einrichtung zum waermeaustausch zwischen zwei gasfoermigen medien

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5896989A (ja) * 1981-12-04 1983-06-09 Toshiba Corp 熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Vol. 7, No. 197, (M-239)[1342], 27 August 1983; & JP,A,58 096 989 (TOKYO SHIBAURA DENKI K.K.), 9 June 1983. *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993004332A1 (fr) * 1991-08-12 1993-03-04 Raymond Leroy Anderson Echangeur de chaleur

Also Published As

Publication number Publication date
DE3643496A1 (de) 1988-06-30
DE3643496C2 (de) 1994-06-09

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