WO1993018351A1 - Appareil pour chauffer ou refroidir des milieux gazeux ou liquides - Google Patents

Appareil pour chauffer ou refroidir des milieux gazeux ou liquides Download PDF

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Publication number
WO1993018351A1
WO1993018351A1 PCT/NO1993/000039 NO9300039W WO9318351A1 WO 1993018351 A1 WO1993018351 A1 WO 1993018351A1 NO 9300039 W NO9300039 W NO 9300039W WO 9318351 A1 WO9318351 A1 WO 9318351A1
Authority
WO
WIPO (PCT)
Prior art keywords
damper blade
condenser
distribution chamber
medium
evaporator
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.)
Ceased
Application number
PCT/NO1993/000039
Other languages
English (en)
Inventor
Arnfinn Sakki
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.)
Individual
Original Assignee
Individual
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
Priority claimed from NO92921006A external-priority patent/NO921006L/no
Application filed by Individual filed Critical Individual
Priority to DE69327160T priority Critical patent/DE69327160T2/de
Priority to EP93906903A priority patent/EP0629276B1/fr
Priority to JP51556293A priority patent/JP3178722B2/ja
Priority to AU37696/93A priority patent/AU3769693A/en
Publication of WO1993018351A1 publication Critical patent/WO1993018351A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
    • F24F1/027—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle mounted in wall openings, e.g. in windows

Definitions

  • This invention relates to an apparatus for the heating or cooling of a gaseous or liquid medium, comprising a heat pump circuit having a structure as known per se, with a compressor or the like, a condenser, throttle means and an evaporator and further comprising at least one driving device for the flow of the medium.
  • Heat pumps are well known in connection with air con- ditioning and heating of both gases, such as room air and liquids.
  • gases such as room air and liquids.
  • GB Patent Pub ⁇ lication 2.203.830 As an example reference is made to GB Patent Pub ⁇ lication 2.203.830.
  • the present invention is the result of development work based on the heat pump principle and is primarily directed to room heating.
  • this apparatus should also have correspondingly advant ⁇ ageous properties in the case of the medium to be heated or cooled, is a liquid, for example water.
  • the apparatus comprises a distribution chamber adapted to communicate with the condenser and the evaporator as well as with an inlet or an outlet for the medium to or from the distribution chamber, and provided with an adjust ⁇ able control member for the flow of the medium in the distri- bution chamber.
  • the condenser and the evaporator form two sub ⁇ stantially mutually opposite main confining surfaces of the distributon chamber, that the inlet or outlet of the distri ⁇ bution chamber is directed substantially in parallel to the main confining surfaces and that said control member is in the form of a pivotable separating damper blade having two oppositely located edge protions which in the two extreme positions of the separating damper blade are adapted to sub ⁇ stantially directly engage marginal portions of the respect ⁇ ive main confining surfaces.
  • fig. 1 in a quite schematical cross section illustrates the priniciple of and the basic solution according to the invention
  • fig. 2 also schematically shows an arrangement correspond- ing to the one in fig. 1, mounted inside an outer wall and with various associated re-setable members shown in the form of plates or baffles for the utilization of the apparatus under varying con ⁇ ditions and time periods
  • figs. 3-6 show different operational positions of the appara ⁇ tus in fig. 2, made possible inter alia by means of the adjustable damper blade in the distribution chamber of the apparatus, fig.
  • FIG. 7 in a cross-sectional view analogous to the preceed- ing figures, somewhat more in detail shows a prac ⁇ tical example of the apparatus
  • fig. 8 in a sectional elevation shows main components in the apparatus of fig. 7, fig. 9 in a corresponding elevation as fig. 8 shows another exemplary embodiment somewhat related to the one in figs. 7 and 8
  • fig. 10 shows the embodiment of fig. 9 in a partial hori- zontal section
  • fig. 11 shows a vertical section through the embodiment of figs. 9 and 10, somewhat in analogy to the cross sectional view of fig. 7, fig. 12 shows a particular design of a damper blade which can be incorporated in the apparatus of fig. 11, fig.
  • fig. 14 is a schematical and simplified vertical section through an additional embodiment based on a single fan
  • fig.15 in vertical section shows the embodiment of fig. 14 with certain additional particular design features illustrated.
  • a conven- tional heat pump circuit is represented by a condenser 1 and an evaporator 2 only. Between these there is formed a dis ⁇ tribution chamber 4 having more or less opposed inlets or outlets 5 and 6 for the medium concerned, which can be in the gaseous or liquid phase.
  • the medium is considered to be a gas, for example air, wherby driving devices 7 and 8 associated with the inlets 5 and 6 respectively, are illus ⁇ trated in the form of fans.
  • the opposed openings 5 and 6 in chamber 4 can also be adapted to be outlets from the chamber, since the apparatus in principle is able to operate with one or the other of two opposite flow directions of the medium, for example air.
  • the following figs. 2-12 are all intended for inflow through the two opposed openings, whereas the embodiment of fig. 13 makes it possible to choose between the use of the two opposed openings either as inlets or as outlets, and in the embodiment of figs. 14 and 15, the main flow directions are arranged so that the two opposed openings 5 are outlets from the distribution chamber.
  • the different embodiments will be explained more closely below.
  • the chamber 4 normally has walls (not shown) that in a more or less fluid-tight manner enclose the rest of the chamber.
  • blade 10 has two oppositely located edge portions being adapted to engage marginal portions of the respective main confining surfaces IA and 2A substantially directly in two extreme positions of the damper blade.
  • damper blade 10 is shown in an intermediate position, wherein for
  • damper blade 10 is pivotable, i.e. can be angularly adjusted about a central axis 10A, and the whole.arrangement of distribution chamber 4 with main confining surfaces IA and 2A, inlet or outlet openings 5 and 6 as well as damper blade 10 in principle is symmetrical. This makes possible the many use-options, depending inter alia on the angular position of Samper blade 10, as will appear from the following description.
  • FIG. 2 shows an apparatus according to the invention in aa embodiment adapted for wall mouting and based on the arrangement as illustrated in principle in fig. 1.
  • fig. 2 there is also a condenser 11, an evaporator 12, a distribution or mixing chamber 14A - 14B, a first inlet 15 and a second inlet 16 with associated fans 17 and 18 respect- ively.
  • An essential structural part in fig. 2 as in the embodi ⁇ ment of fig. 1, is the adjustable damper blade 10 that in its position as illustrated in fig. 2, subdivides the distribu ⁇ tion chamber into two chamber portions 14A and 14B that very well can be approximately equally large.
  • the air mixture in both chamber portions 14A and 14B will enter into condensor 11 and evaporator 12 respectively.
  • the air flow arrows shown in fig. 2 indicate this.
  • fig. 2 there is also shown three baffles 21, 22, 23 which in the positions shown form a closed re-circulation duct 19 for air re-circulation, without having any communica ⁇ tion with the outdoor air at the righthand side of wall 29 as shown in fig. 2.
  • Fig. 3 shows a position of damper blade 10 in which incoming air from the room through inlet 16 is lead in its entirety through condenser 11, whereas baffles 21, 22, 23 are set for circulation of outdoor air through evaporator 12.
  • the apparatus being provided with an adjustable damper blade 10 can be adjusted for a very efficient heat pump function as in fig. 3, when the conditions are suitable for such a manner of operation, but with simple manual intervention can be moved for example to the particular manner of operation being shown in fig. 2.
  • the operational position in fig. 3 when the outdoor temperature is above a certain magnitude, but at lower outdoor tempera ⁇ tures the efficiency in operation as a pure heat pump will be so low that it becomes advantageous to change to the manner of operation in fig. 2.
  • a criterion for changing from opera- tion according to fig. 3 to the one in fig. 2 can be that the outdoor temperature is higher or lower than the desired average temperature in the distribution chamber.
  • the chamber temperature is approximately 14°C. It is obvious that the magnitudes men- tioned here are pure examples, and that the temperature relationships in practical installations can vary consider ⁇ ably, depending inter alia upon the general room temperature, the desired output temperature from the apparatus and the corresponding air flow volume as well as the flow pattern or distribution into and from the chamber.
  • Fig. 4 shows a mode of operation being almost similar to the one in fig. 3, but is distinguished from the latter in that damper blade 10 is placed in a normal or central pos- ition, i.e. as in fig. 2.
  • damper blade 10 is placed in a normal or central pos- ition, i.e. as in fig. 2.
  • a combinded function of heat pump effect and air exchange is obtained, since an optional or adjustable proportion of outdoor air can be introduced into the room through condenser 11.
  • Fig. 5 shows a configuration which is directed to exclu- sive ventilation or exchange of indoor air with outdoor air at the same time as the heat pump circuit provides for a certain heat recovery from the air being discharged outdoors.
  • fig. 6 shows an important mode of operation in connection with possible long term service according to fig. 2.
  • the manner of operation illustrated in fig. 2 may involve some formation of frost or ice in evaporator 12.
  • damper blade 10 With damper blade 10 positioned as in fig. 6 a full re-circulation of indoor air will take place first through evaporator 12 and then into and through conden- ser 11, so that a desired de-icing is performed.
  • This manner of de-icing is very advantageous since it takes place without any loss of heat, which is a drawback in more conventional methods. It is easy to realize that a manner of operation as shown in fig. 6 can only be of interest during short periods, i.e. for a sufficiently long time for de-icing or de-frosting to take place.
  • the adjustable damper blade 10 has a particularly great practical significance for the purpose of de-icing. In principle, however, such an adjustable damper blade can also be of much interest in installations or with manners of operation wherein the specific variant according to fig. 2 is not utilized, for example in situations as illustrated in fig. 3, 4, and 5. In all circumstances it is obvious that a stepless adjustability of damper blad 10 between extreme positions as represented by for example figs. 3 and 5, will be of high value. The positioning of damper blade 10 in freely chosen intermediate positions will give a very advant ⁇ ageous flexibility in operation of the installation under varying conditions.
  • Fig. 7 and 8 together illustrate somewhat more in detail a practical embodiment of an apparatus as schematically shown in the preceeding figures or drawings.
  • Fig. 7 is a cross section corresponding in principle to fig. 2 - 6, and shows a condenser 41, an evaporator 42, and between these a distribu ⁇ tion chamber 44A/44B.
  • a pivotable damper blade 40 which can be angularly adjusted by means of an axle 40A provided for example with a handle or the like outside the actual enclosure around the apparatus.
  • two fans 47 and 48 see fig.
  • the two inlets to the chamber can be consi- dered to be located in the region at the two lower corner portions of the mixing chamber, as seen from fig. 8. Also here the two inlets are directed generally in parallel to the main confining surfaces of the chamber formed by the con ⁇ denser and the evaporator.
  • Inlet 47A communicates with a duct unit 50 that with an appropriate setting of baffles 51 and 53 will be able to form a re-circulation duct 49 from an output side 54 of evaporator 42.
  • baffles 51 and 53 are shown in positions for operation of the installation as a heat pump. Openings being associated with the baffles are shown at 51A, 5IB, and 53A.
  • figs. 7 and 8 also show a compressor 43 with associated motor and conduits for the heat pump circuit that incorporates condenser 41 and evaporator 42.
  • the design of duct unit 50 can be varied quite a lot depending upon the conditions and requirements at the instal ⁇ lation site concerned, for example whether or not a wall mounting is aimed at.
  • figs. 9 - 11 has a basic geometry having a high degree of symmetry as in the fundamental arran ⁇ gement of fig. l and in all the preceding figures of draw ⁇ ings.
  • Figs. 10 and 11 show a condenser 71 and an evaporator 72 lateraly confining a distribution chamber 74 having an angularly adjustable damper blade 70 the pivot axis of which is shown at 70A. With full lines damper blade 70 is shown in a central position, whereas two opposite extreme positions respectively are shown with dashed lines. As will appear from fig.
  • damper blade 10 opposite edge portions of damper blade 10 in the respective extreme positions are brought to a substantially direct engagement against marginal portions of the main confining surfaces 71A and 72A respectively of condenser 71 and evaporator 72.
  • the damper blade 10 as such is shown separately and in perspective view in fig. 12, wherein the just mentioned two opposite edge portions of the damper blade are denoted 75A and 75B respectively. These edge portions therefore extend parallel to the pivot axis 70A for the damper blade.
  • FIGS. 9 and 10 in particular show the location of two fans 77 and 78 for supplying air to the distribution chamber 74.
  • the air fans are located with inlets adjacent corner regions in the distribu- tion chamber, but also here the inflow of air from these fans through associated inlets to chamber 74 is directed generally in parallel to the main confining surfaces 71A and 72A.
  • the air inlets from the pair of fans 77 and 78. besides are direc ⁇ ted substantially opposite to each other, as in the preceding embodiments.
  • FIGs. 9 and 11 also show the location of a compressor 73 in the apparatus.
  • the conduits for the whole heat pump circuit are only partially indicated in these figures. A number of arrows in fig.
  • Guide plate 79A-79B must be so dimensioned and located that it does not interfere with the surrounding surfaces, in the two extreme positions of damper blade 10 as referred to above. This is obtained with a design as illustrated and explained above, at the same time as a desired control or guide effect with respect to the air flow in the chamber is obtained. It is obvious that such a guide plate may have other shapes than what is seen in fig. 12, where the guide 5 plate is straight and is arranged approximately at a right angle to the major surfaces of damper blade 70.
  • Fig. 13 shows an embodiment the main features of which have much in common with the one in figs. 9 - 11, but a specific arrangement of fans 87 and 88 in fig. 13, makes it
  • both fans 87 and 88 can be turned around so that the fan outlets and inlets respectively can be selectively brought to correspond to respective openings 85 and 86 to the distribution chamber 84.
  • ible fans are components being know per se, and in an arran ⁇ gement as shown in fig. 13 can be very advantageous in cer ⁇ tain uses of the apparatus according to the invention.
  • the unit in fig. 14 can be regarded as a portable unit for use in living-rooms and the outlet 96 is adapted to be directed into the room, whereas outlet 95 possibly through a flexible duct or hose can discharge air out through a window or the like.
  • damper blade 90 in both its extreme positions has a downward slope in a direction towards one or the other respectively of the opposite edge portions of the blade. These are the same opposite edge portions which more or less directly engage marginal portions of the respctive main confining surfaces as discussed above. Accordingly condense water that under certain operational conditions will be formed in evaporator 92, will be gathered and lead on the upper side of damper blade 90 down to the lower edge portion thereof, i.e. the left-hand edge in fig. 14.
  • damper blade 90 has been set into an opposite extreme position of the one in fig. 14, so that collected condense water will be lead to the right-hand edge which is positioned over a collecting gutter 101 for condense water.
  • damper blade 90 has been set into an opposite extreme position of the one in fig. 14, so that collected condense water will be lead to the right-hand edge which is positioned over a collecting gutter 101 for condense water.
  • another collecting gutter 102 that will be in function in the position of damper blade 90 shown in fig. 14.
  • the downward main surface of damper blade 90 can have a coating 100 which is heat insulat ⁇ ing, which involves the advantage that heat conduction from the underside to the upper side of damper blade 90 will be reduced, so that condense water at the upper side of the blade will not receive any significant heat influence from the underside thereof.
  • the air flowing upwards from condenser 91 will be rather warm and thereby can evaporate condense water at the upper side of blade 90.
  • Such evaporation is undesired, because it is usually not of interest to introduce humid air into the room in the operation mode shown in fig. 15, i.e. during air conditioning with cooling.
  • the insulation 100 advantageously can consist of a somewhat hydroscopic material, that in the position shown in fig. 15 is adapted to contact condense water collected in gutter 101, so that the water will moisten the coating and leads to evaporation of such moisture under the influence of the hot air flow against the underside of damper blade 90.
  • this effect can further contribute to making the heat transfer from the underside to the upper side of damper blade 90 negligible.
  • humidity or condense water is removed from the system, so that a possibly resulting amount of condense water for final collecting, for example in a vessel 108 as shown in fig. 15, will be reduced.
  • discharge pipes 101A, 102A respectively running together into a common conduit 104.
  • condense water can be taken from gutter 101 and utilized for cooling the medium in the heat pump circuit at a convenient part thereof.
  • Discharge pipe 101A from the gutter is taken to a container or water jacket 105 being arranged in a close heat contact with a portion of a pipe connection 93W in the heat pump circuit between the condenser 91 and a throttle device 93X.
  • a cooling effect on the medium in the heat pump circuit will be obtained at this portion, which is a useful effect when the apparatus is adjusted for air conditioning, i.e. by discharging cooled air to the room.
  • the water jacket or container 105 can be closed or opened.
  • the heat exchange between condense water and cooling medium in the circuit as discribed here contributes to an improved total heat economy in the operation of the apparatus in figs. 14 and 15.
  • the insulating coating 100 at the underside of damper blade 90 does not necessarily have to utilize absorbed moisture from collecting gutter 101 for the evaporation effect explained above.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Constitution Of High-Frequency Heating (AREA)
  • Furnace Details (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un appareil pour chauffer ou refroidir des milieux gazeux ou liquides comprend un circuit de pompe à chaleur de structure connue en soi, comportant un compresseur, un condensateur (71), un dispositif d'étranglement et un évaporateur (72). L'appareil comprend en outre au moins un dispositif de propulsion (77, 78) pour le flux du milieu choisi, ainsi qu'une chambre de répartition (74) conçue pour communiquer avec le condensateur et l'évaporateur ainsi qu'avec une entrée (75) ou une sortie (76) destinée au milieu allant vers la chambre de répartition ou en venant. Celle-ci comporte un dispositif de réglage (70) agissant sur le flux qui y pénètre. Le condensateur (71) et l'évaporateur (72) présentent deux surfaces de confinement qui sont essentiellement opposées (71A, 72A) et qui forment les surfaces principales de la chambre de répartition (74). L'entrée (75, 76) ou la sortie (95, 96) de cette chambre est en pratique parallèle aux deux surfaces principales de confinement (71A, 72A) et le dispositif de réglage prend la forme d'une plaque de séparation et d'amortissement pivotante (70) dotée de deux arrêtes opposées (75A, 75B) qui, lorsqu'elles se trouvent aux deux positions extrêmes possibles grâce au pivotement de la plaque, sont conçues pour s'engager en pratique directement dans des parties marginales des surfaces principales de confinement correspondantes (71A, 72A).
PCT/NO1993/000039 1992-03-13 1993-03-10 Appareil pour chauffer ou refroidir des milieux gazeux ou liquides Ceased WO1993018351A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE69327160T DE69327160T2 (de) 1992-03-13 1993-03-10 Gerät zum erhitzen oder kühlen eines gasförmigen oder flüssigen mediums
EP93906903A EP0629276B1 (fr) 1992-03-13 1993-03-10 Appareil pour chauffer ou refroidir des milieux gazeux ou liquides
JP51556293A JP3178722B2 (ja) 1992-03-13 1993-03-10 流体の加熱または冷却装置
AU37696/93A AU3769693A (en) 1992-03-13 1993-03-10 Apparatus for the heating or cooling of a gaseous or liquid medium

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
NO921006 1992-03-13
NO92921006A NO921006L (no) 1992-03-13 1992-03-13 Anordning for oppvarming av et gass- eller vaeskeformig medium
NO923527A NO174306C (no) 1992-03-13 1992-09-11 Anordning for oppvarming evt. avkjöling av et gass- eller væskeformig medium
NO923527 1992-09-11

Publications (1)

Publication Number Publication Date
WO1993018351A1 true WO1993018351A1 (fr) 1993-09-16

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ID=26648339

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO1993/000039 Ceased WO1993018351A1 (fr) 1992-03-13 1993-03-10 Appareil pour chauffer ou refroidir des milieux gazeux ou liquides

Country Status (7)

Country Link
EP (1) EP0629276B1 (fr)
JP (1) JP3178722B2 (fr)
AT (1) ATE187239T1 (fr)
DE (1) DE69327160T2 (fr)
ES (1) ES2142862T3 (fr)
NO (1) NO174306C (fr)
WO (1) WO1993018351A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998055806A1 (fr) * 1997-06-05 1998-12-10 Meyong Hyek Yun Appareil de conditionnement d'air du type a commutation du debit d'air utilise pour le refroidissement et le rechauffement
LU90926B1 (en) * 2002-05-28 2003-12-01 Uniflair Int Sa Compact air-cooling device for a closed technical cabinet

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20204746U1 (de) * 2002-03-26 2003-08-07 Kreutzfeldt, Nils, 23966 Wismar Luftaufbereitungsgerät zur Regulierung der Wärme und der Luftfeuchtigkeit in geschlossenen Räumen
JP2007127374A (ja) * 2005-11-07 2007-05-24 Toshiba Kyaria Kk 一体型空気調和機
JP5714301B2 (ja) * 2010-11-11 2015-05-07 高砂熱学工業株式会社 冷却システム及び冷却方法
CN104214843A (zh) * 2014-08-06 2014-12-17 广东志高空调有限公司 一种整体式空调机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2466383A (en) * 1949-04-05 Air-conditioning apparatus for
US2920459A (en) * 1958-10-27 1960-01-12 Gen Electric Room air conditioner
US3995446A (en) * 1975-07-14 1976-12-07 Eubank Marcus P Reverse air cycle air conditioner
US4280443A (en) * 1979-12-04 1981-07-28 Xerox Corporation Roll fuser loading system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2466383A (en) * 1949-04-05 Air-conditioning apparatus for
US2920459A (en) * 1958-10-27 1960-01-12 Gen Electric Room air conditioner
US3995446A (en) * 1975-07-14 1976-12-07 Eubank Marcus P Reverse air cycle air conditioner
US4280443A (en) * 1979-12-04 1981-07-28 Xerox Corporation Roll fuser loading system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998055806A1 (fr) * 1997-06-05 1998-12-10 Meyong Hyek Yun Appareil de conditionnement d'air du type a commutation du debit d'air utilise pour le refroidissement et le rechauffement
US6216484B1 (en) 1997-06-05 2001-04-17 Meyong Hyek Yun Air flow switching type air conditioner for both cooling and heating
LU90926B1 (en) * 2002-05-28 2003-12-01 Uniflair Int Sa Compact air-cooling device for a closed technical cabinet
EP1367331A1 (fr) * 2002-05-28 2003-12-03 Uniflair International S.A. Appareil compact de climatisation pour une armoire de distribution

Also Published As

Publication number Publication date
JPH07506178A (ja) 1995-07-06
EP0629276B1 (fr) 1999-12-01
JP3178722B2 (ja) 2001-06-25
NO923527D0 (no) 1992-09-11
DE69327160D1 (de) 2000-01-05
NO923527L (no) 1993-09-14
NO174306B (no) 1994-01-03
EP0629276A1 (fr) 1994-12-21
ATE187239T1 (de) 1999-12-15
NO174306C (no) 1994-04-13
DE69327160T2 (de) 2000-07-20
ES2142862T3 (es) 2000-05-01

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