EP0629276B1 - Apparatus for the heating or cooling of a gaseous or liquid medium - Google Patents

Apparatus for the heating or cooling of a gaseous or liquid medium Download PDF

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Publication number
EP0629276B1
EP0629276B1 EP93906903A EP93906903A EP0629276B1 EP 0629276 B1 EP0629276 B1 EP 0629276B1 EP 93906903 A EP93906903 A EP 93906903A EP 93906903 A EP93906903 A EP 93906903A EP 0629276 B1 EP0629276 B1 EP 0629276B1
Authority
EP
European Patent Office
Prior art keywords
distribution chamber
evaporator
condenser
damper blade
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.)
Expired - Lifetime
Application number
EP93906903A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0629276A1 (en
Inventor
Arnfinn C/O Liv Sakki 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.)
ACO KLIMATTEKNIK AB
Original Assignee
ACO Klimatteknik AB
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 ACO Klimatteknik AB filed Critical ACO Klimatteknik AB
Publication of EP0629276A1 publication Critical patent/EP0629276A1/en
Application granted granted Critical
Publication of EP0629276B1 publication Critical patent/EP0629276B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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 conditioning and heating of both gases, such as room air and liquids.
  • a heat pump circuit including a compressor, a throttle means, a condenser and an evaporator, the condenser and evaporator defining generally parallel main confining surfaces of a distribution chamber, a driving device located outside the distribution chamber and arranged to cause the fluid to be driven into or drawn from the distribution chamber, and a single unitary separating damper blade pivotally mounted within the distribution chamber, and movable to any position between and including two extreme positions in which the ends of the damper blade engage the main confining surfaces of the distribution chamber.
  • an apparatus comprises a heat pump circuit including a compressor, a throttle means, a condenser and an evaporator, the condenser and evaporator defining generally parallel main confining surfaces of a distribution chamber, the distribution chamber including two fluid inlets each directed substantially in parallel to the main confining surfaces of the distribution chamber, a driving device located outside the distribution chamber and arranged to cause the fluid to be driven into or drawn from the distribution chamber, and a single, unitary, separating damper blade pivotally mounted within the distribution chamber, and movable to any position between and including two extreme positions in which the ends of the damper blade engage the main confining surfaces of the distribution chamber, arranged such that the driving device drives fluid into the distribution chamber through the fluid inlets, generally in parallel to the main confining surfaces of the distribution chamber, the fluid being mixed in the distribution chamber and being discharged from the distribution chamber through the condenser and evaporator depending upon the angular position of the damper blade.
  • 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 advantageous properties in the case of the medium to be heated or cooled, is a liquid, for example water.
  • a conventional heat pump circuit is represented by a condenser 1 and an evaporator 2 only. Between these there is formed a distribution chamber 4 having more or less opposed inlets 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 illustrated in the form of fans.
  • the condenser 1 and the evaporator 2 constitute two main confining surfaces 1A and 2A for the chamber 4, these confining surfaces being mutually substantially opposed, whereas the inlets 5 and 6 are directed essentially in parallel to the main confining surfaces 1A and 2A.
  • the flow direction through the condenser 1 and the evaporator 2 respectively will be generally at right angles to the flow direction through the inlets 5 and 6.
  • the chamber 4 normally has walls (not shown) that in a more or less fluid-tight manner enclose the rest of the chamber.
  • a pivotable separating damper blade 10 has two oppositely located edge portions being adapted to engage marginal portions of the respective main confining surfaces 1A and 2A substantially directly in two extreme positions of the damper blade.
  • damper blade 10 is shown in an intermediate position, wherein for example air flowing in through inlets 5 and 6 to a certain degree will be mixed in chamber 4. The degree of such mixing will depend on the angular position of the damper blade, and different configurations in this respect will be explained more closely below.
  • advantageously damper blade 10 is pivotable, i.e.
  • damper blade 10 can be angularly adjusted about a central axis 10A, and the whole arrangement of distribution chamber 4 with main confining surfaces 1A and 2A, inlet 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 damper blade 10, as will appear from the following description.
  • Fig. 2 shows an apparatus according to the invention in an 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 respectively.
  • An essential structural part in fig. 2 as in the embodiment of fig. 1, is the adjustable damper blade 10 that in its position as illustrated in fig. 2, subdivides the distribution chamber into two chamber portions 14A and 14B that very well can be approximately equally large.
  • damper blade 10 With generally planar main confining surfaces of condenser 11 and evaporator 12 respectively, facing the chamber 14A/14B, it can be desirable to put damper blade 10 in a normal position centrally between and in parallel to these main confining surfaces. In this position air flowing in from both sides is mixed in an optimal manner and approximately as if damper blade 10 were not present at all. 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. 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.
  • a quite conventional heat pump effect is established, utilizing the outdoor air as a heat source, for the purpose of heating the room.
  • 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.
  • a criterion for changing from operation 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 mentioned here are pure examples, and that the temperature relationships in practical installations can vary considerably, 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 position, i.e. as in fig. 2.
  • damper blade 10 is placed in a normal or central position, i.e. as in fig. 2.
  • Fig. 5 shows a configuration which is directed to exclusive 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 condenser 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 blade 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 advantageous 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 distribution 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 considered 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 condenser and the evaporator.
  • the air flow pattern and distribution within the chamber will of course be influenced by the setting of damper blade 40. With the mutual arrangements of outlets from fans 47 and 48, the chamber and the damper blade 40 as shown, it will be realized that rotation of the damper blade about axle 40A will have a quite corresponding effect on the air distribution, as damper blade 10 in figs. 2 - 6.
  • 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, 51B, 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.
  • duct unit 50 can be varied quite a lot depending upon the conditions and requirements at the installation site concerned, for example whether or not a wall mounting is aimed at.
  • a shape of an internal part 55 for the purpose of obtaining good flow relationships when the re-circulation duct 49 shall be established.
  • figs. 9 - 11 has a basic geometry having a high degree of symmetry as in the fundamental arrangement of fig. 1 and in all the preceding figures of drawings.
  • 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 distribution 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 directed 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 and 79B For the purpose of providing for a more favourable air flow and distribution in chamber 74 in figs. 9, 10, and 11, it can be an advantage to provide a particular guide plate 79A and 79B as shown in fig. 12. This particular guide plate is also shown in fig. 11. Guide plate 79A-79B extends obliquely from one side edge to another on damper blade 70 and is comparatively narrow, which inter alia is related to the dimensions of the distribution chamber 74, in particular the distance between two main confining surfaces 71A and 72A. 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.

Landscapes

  • 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)
  • Sorption Type Refrigeration Machines (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Constitution Of High-Frequency Heating (AREA)
  • Furnace Details (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP93906903A 1992-03-13 1993-03-10 Apparatus for the heating or cooling of a gaseous or liquid medium Expired - Lifetime EP0629276B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
NO92921006A NO921006L (no) 1992-03-13 1992-03-13 Anordning for oppvarming av et gass- eller vaeskeformig medium
NO921006 1992-03-13
NO923527 1992-09-11
NO923527A NO174306C (no) 1992-03-13 1992-09-11 Anordning for oppvarming evt. avkjöling av et gass- eller væskeformig medium
PCT/NO1993/000039 WO1993018351A1 (en) 1992-03-13 1993-03-10 Apparatus for the heating or cooling of a gaseous or liquid medium

Publications (2)

Publication Number Publication Date
EP0629276A1 EP0629276A1 (en) 1994-12-21
EP0629276B1 true EP0629276B1 (en) 1999-12-01

Family

ID=26648339

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93906903A Expired - Lifetime EP0629276B1 (en) 1992-03-13 1993-03-10 Apparatus for the heating or cooling of a gaseous or liquid medium

Country Status (7)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100208144B1 (ko) * 1997-06-05 1999-07-15 윤명혁 공기흐름전환식 냉난방겸용 공기조화기
DE20204746U1 (de) * 2002-03-26 2003-08-07 Kreutzfeldt, Nils, 23966 Wismar Luftaufbereitungsgerät zur Regulierung der Wärme und der Luftfeuchtigkeit in geschlossenen Räumen
LU90926B1 (en) * 2002-05-28 2003-12-01 Uniflair Int Sa Compact air-cooling device for a closed technical cabinet
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

Family Cites Families (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

Also Published As

Publication number Publication date
DE69327160T2 (de) 2000-07-20
ATE187239T1 (de) 1999-12-15
NO174306B (no) 1994-01-03
EP0629276A1 (en) 1994-12-21
NO923527L (no) 1993-09-14
NO923527D0 (no) 1992-09-11
NO174306C (no) 1994-04-13
JPH07506178A (ja) 1995-07-06
JP3178722B2 (ja) 2001-06-25
WO1993018351A1 (en) 1993-09-16
ES2142862T3 (es) 2000-05-01
DE69327160D1 (de) 2000-01-05

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