APPARATUS FOR THE HEATING OR COOLING OF A GASEOUS OR LIQUID MEDIUM

Abstract: Apparatus for heating or cooling of a gaseous or liquid medium, comprising a heat pump circuit having a structure as known per se, with a compressor, condenser (71), throttle means and evaporator (72). Further the apparatus comprises at least one driving device (77, 78) for the flow of the medium, and a distribution chamber (74) adapted to communicate with the condenser and the evaporator as well as with an inlet (75) or outlet (76) for the medium to or from the distribution chamber. This is provided with an adjustable control member (70) for the flow of the medium in the distribution chamber. The condenser (71) and the evaporator (72) form two substantially mutually opposite main confining surfaces (71A; 72A) of the distribution chamber (74). The inlet (75, 76) or outlet (95, 96) of the distribution chamber is directed substantially in parallel to the main confining surfaces (71A, 72A), and the control member is in the form of a pivotable separating damper blade (70) having two oppositely located edge portions (75A, 75B) which in the two extreme positions of the separating damper blade are adapted to substantially directly engage marginal portions of the respective main confining surfaces (71A, 72A).

Description: APPARATUS FOR THE HEATING OR COOLING OF A GASEOUS OR LIQUID MEDIUM. 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. 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. In this connection it has been found that a particular arrangement of components and air-flow paths results in significant improvements and a quite unexpected broadening of the functional possibilities and the flexibil¬ ity in the practical utilization of the apparatus. In prin- ciple 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. It is also an object of the invention to make possible designs being to a high degree compact and easy to handle, in particular when portable apparatuses are concerned. Whereas previously known room heating apparatus based on the heat pump principle have been subject to certain rather serious deficiencies in practice, in particular with respect to the formation of frost and ice, the apparatus according to this invention is free from such problems. In this connection it is a great advantage that heating apparatus based on the invention can be operated at a high efficiency being compar¬ able to that of good heat pumps, also during periods when the outdoor temperature and the air moisture make it difficult or impossible to operate common heat pumps of the air-to-air type. As will appear from the following description and from the drawings, 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. In an apparatus as stated above the novel and specific features according to the invention in the first hand consist therein that 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. The basic solution according to the invention as stated here, to a very substantial degree fulfils the prerequisites and objects mentioned above, and has particular advantages with respect to changing and adjusting the apparatus between various operational modes and conditions. In the following description with reference to the drawings the invention and various embodiments thereof shall be explained more closely, whereby in the drawings: 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. 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. 13 in partial horizonal cross section corresponding to fig. 10, shows a specific arrangement of fans, fig. 14 is a schematical and simplified vertical section through an additional embodiment based on a single fan, and fig.15 in vertical section shows the embodiment of fig. 14 with certain additional particular design features illustrated. In the highly schematic illustration of fig. 1 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. In fig. 1 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. As indicated above however 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. What is essential in the basic apparatus as illustrated in fig. 1, is the main features of the geometrical relation¬ ships in and around the distribution chamber 4. In the first 10 place the condenser 1 and the evaporator 2 constitute two main confining surfaces IA and 2A for the chamber 4, these confining surfaces being mutually substantially opposed, whereas the openings 5 and 6, which can be either inlets or outlets, are directed essentially in parallel to the main 15 confining surfaces IA and 2A. In other words the flow direc¬ tion through the condenser 1 and the evaporator 2 respec¬ tively will be generally at right angles to the flow direc¬ tion through the inlets or outlets 5 and 6. In addition to the main confining surfaces IA and 2A and the openings 5 and 20. 6, the chamber 4 normally has walls (not shown) that in a more or less fluid-tight manner enclose the rest of the chamber. Further it is essential to the basic arrangement being illustrated in fig. 1, that a pivotable separating or damper 25 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. In fig. 1 damper blade 10 is shown in an intermediate position, wherein for 30 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. Finally with reference to fig. 1 it is 35 remarked that advantageously 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. 48 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. Thus in 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. In the embodiment of fig. 2 and in association with a wall 29, for example in a building, there are shown various plates and baffle-like members 21-23 for reconfiguring or adjusting the apparatus for obtaining varying operational positions or relationships. These variants shall be ex¬ plained more closely with reference to the following figs. 3- 6. 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. With generally planar main confining surfaces of condenser 11 and evaporator 12 respectively, facing the chamber 14A/14B, it can be desir- able 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. In 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. This particular manner of operation is also discussed below with reference to fig. 3 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. Thus a quite conventional heat pump effect is established, utilizing the outdoor air as a heat source, for the purpose of heating the room. In this connection it is a substantial advantage according to the invention that 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. In many installations it will be advantageous to use 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. In the example of magnitudes given above, 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. In connection with the above it is also important to remark that the employment of two fans 17, 18 as driving devices each for its inlet to chamber 14A/14B represents a favourable possibility of regulation, since the fans can be driven with different or equal power, being chosen by taking into account the desired operational parameters. As indicated above the manner of operation according to fig. 2 has particular interest in connection with the one in fig. 3, namely during an initial or starting phase being introductory to the operational mode of fig. 3, when the outdoor temperature is low. When a heat pump apparatus as in fig. 1 is not in operation the three baffles 21, 22, 23, are closed as shown in fig. 2. Therefore during this starting phase only indoor air is introduced into the chamber which means that the pressure in the heat pump circuit will be more quickly raised to the desired level, which is of much interst when the outdoor temperature for example is down towards 0°C. This initial or start position is very advantageous and as a rule is more or less necessary in order to bring heat into the room when the outdoor fan 17 is put into operation. 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. Thus 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. Then fig. 6 shows an important mode of operation in connection with possible long term service according to fig. 2. During certain circumstances the manner of operation illustrated in fig. 2 may involve some formation of frost or ice in evaporator 12. 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. When setting damper blade 10 at an angle being the opposite of what is shown in fig. 6 but preferrably not quite in the opposite extreme position, there will be obtained a very good de-humidifying effect on the room air passing through the apparatus. 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. In the chamber there is mounted 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. Moreover there are shown two fans 47 and 48 (see fig. 8) directing input air flows somewhat at an inclination upwards into chamber 44A/44B between condenser 41 and evaporator 42, as indicated with arrows 47P and 48P respectively in fig. 8. Thus in this case 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. With these mutually and inclined air flows into the chamber these will be subjected to a very favourable and thorough mixing effect as indicated by arrows 60, in particular in the central region of chamber 44A/44B, with subsequent outflow of mixed air through condenser 41 and evaporator 42 respectively. 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 distribu¬ tion, as damper blade 10 in figs. 2 - 6. For fan 47 there is shown an inlet 47A and for fan 48 an inlet 48A. 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. With full lines in fig. 7, however, the two 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. For the sake of completeness 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. There is shown a shape of an internal part 55 for the purpose of obtaining good flow relationships when the re-circulation duct 49 shall be established. The embodiment of 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. 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. Further figs. 9 and 10 in particular show the location of two fans 77 and 78 for supplying air to the distribution chamber 74. As in the embodiment of fig. 8 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. 10 show how the air flow is directed at various places in the apparatus as well as into and out of the apparatus. With a damper blade 70 being continuously adjustable to different angular positions, it is obvious that the air flow pattern and distribution in chamber 74 and out through condensor 71 and evaporator 72 respec¬ tively, can be varied to a very significant degree. The description above with reference to figs. 1 - 6 has explained these possibilities. 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 obli¬ quely 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. 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 10 possible to completely reverse the general air flow direction in the apparatus. Thus 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. The air flow arrows 15 shown in fig. 13 indicate a main flow direction corresponding to the one for example in fig. 10, i.e. with inlets at 85 and 86 respectively. By turning around both fans 87 and 88 the flow direction can be reversed, so that openings 85 and 86 will represent outlets from chamber 84. This type of revers- 20. 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. In the embodiment of figs. 14 and 15 the general air flow direction is essentially the opposite of what is the 25 case in figs. 2 - 11. Besides fig. 14 shows that this embod¬ iment has only one fan 97 that from an outlet duct 97A is branched into two separate ducts 97B and 97C for supplying air to a condenser 91 and and evaporator 92 respectively. Accordingly air is supplied to distribution chamber 94 there- 30 between through condenser 91 and evaporator 92 respectively, and having outlets at 95 and 96 respectively, as indicated by the air flow arrows. The flow pattern illustrated by the arrows in fig. 14 is of course determined by the position of a damper blade 90 that can be pivoted about axis 90A. 35 Besides the lower part of the the apparatus in fig. 14 contains a compressor 93 and intake openings 99A and 99B respectively for air. 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. The relative position of evaporator 92 generally above distribution chamber 94 with condenser 91 underneath the chamber, has particular interest in connection with the additional structural details being illustrated relatively schematically in fig. 15, these being for simplicity not included in fig. 14. It is seen from figs. 14 and 15 that 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. In fig. 15,however, 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. Correspondingly at the opposite side there is provi- ded another collecting gutter 102 that will be in function in the position of damper blade 90 shown in fig. 14. As can be seen from fig. 15 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. It is to be noted in this connection that 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, however, 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. As an additional feature in connection with the above, 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. With a suitable choice of coating thickness, absorption capacity and evaporation properties, this effect can further contribute to making the heat transfer from the underside to the upper side of damper blade 90 negligible. At the same time 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. For leading condense water from the collecting gutter 101, 102 to vessel 108 there is shown discharge pipes 101A, 102A respectively running together into a common conduit 104. In the operational mode shown in fig. 15 collected and relatively cool 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. Thereby 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 possibility of reversing the general air flow direc- tion through the apparatus as seen inter alia from figs. 14 and 15, is here provided for in a very simple and advantage¬ ous way by the arrangement described within and around the distribution chamber, in particular by the damper blade being adjustable as to its angular position. When changing between the two extreme positions the apparatus can be changed from operating as a heating unit to operate as an air conditioning unit, i.e. with air cooling to the room, which is a change or reversed function that in conventional equipment has been provided for by reversing the flow direction of the medium in the heat pump circuit. This latter solution apparently is a much more complicated way of obtaining this function. Depending on the installation concerned or the practical arrangement of the apparatus, a smaller or higher number of the specific variants described above can be utilized in the actual constructions based upon the invention, and this perhaps in particular applies to the fearures of fig. 15. Thus it is obvious that 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. Among several other possible modifications in relation to what is illustrated in the drawings, the possibility of using various geometrical shapes in connection with the distribution chamber described, is mentioned here, since for example the condenser and the evaporator forming the main confining surfaces of the chamber, do not necessarily require a geometry based on generally planar surfaces, including the main confining surfaces. Moreover it is obvious that the multitude of possibilities of variations or re-structuring represented by the baffles shown in figs. 2 - 6, can be provided for also with other forms of duct changing members. Finally to be mentioned is the possibility of a heat pump circuit working without a compressor, but according to the absorption principle, which is well known within the field of refrigeration techniques.

Claims: C l a i m s 1. 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, condenser (11,41,71,81,91), throttle means (93X) and evaporator (12,42,62,72,82), and further comprising at least one driving device (7,8,17,18,47,48,77,78,87,88,97) for the flow of the medium, and a distribution chamber (4,14A,14B,44A,44B,74,84,- 94) adapted to communicate with the condenser and the evapo- rator as well as with an inlet (5,6,15,16,45,85) or outlet (86,95,96) for the medium to or from the distribution chamber, and provided with an adjustable control member (10,- 40,70,80,90) for the flow of the medium in the distribution chamber, c h a r a c t e r i z e d in - that the condenser (11,41,71,81,91) and the evaporator (12,42,72,82,92) form two substantially mutually opposite main confining surfaces (1A,2A,41A,42A) of the distribution chamber (4,14A,14B,44A,44B,74,84,94) , - that the inlet (5,6,15,16,45,85,86) or outlet (95,96) of the distribution chamber is directed substantially in paral¬ lel to the main confining surfaces (1A,2A,41A,42A,71A,72A) , and - that said control member is in the form of a pivotable separating damper blade (10,40,70,80,90) having two opp¬ ositely located edge portions (75A,75B) which in the two extreme positions of the separating damper blade are adapted to substantially directly engage marginal portions of the respective main confining surfaces (71A,72A). 2. Apparatus according to claim 1 wherein the medium flow out of the distribution chamber takes place through the evaporator (42) and the condenser (41) , c h a r a c t e r i z e d in that a first and a second inlet (47P,48P) to the distribution chamber (44A/44B) are directed at an inclination towards each other at an angle smaller than 180° so that mixing of two associated medium flows to a large extent takes place centrally in the distribution chamber (44A/44B) when the separating damper blade (40) is set in an intermediate position. 3. Apparatus according to claim 1 or 2, wherein the medium flow out of the distribution chamber takes place through the evaporator (42) and the condenser (41) , • c h a r a c t e r i z e d in that the separating damper blade (10,40,70,80) preferably in a stepless manner is adjus¬ table between an extreme position in which substantially the whole medium flow from a first inlet (15,85) is directed to the evaporator (11,41,71,81) and from a second inlet (16,86) to the condenser (12,42,72,82), and another extreme position in which substantially the whole medium flow from the first inlet (15,85) is directed to the condenser (12,42,72,82) and from the second inlet (16,86) to the evaporator (11,41,71,- 81) . 4. Apparatus according to claim 3, c h a r a c t e r i z e d in that the separating damper blade (70) at least on one main surface is provided with a relatively narrow guide plate (79A,79B) arranged approx¬ imately at a right angle to the main surface concerned and extending obliquely in general from one side egde to another on the separating damper blade (70) . 5. Apparatus according to anyone of claim 1-4, adapted for a medium in the form of air, c h a r a c t e r i z e d in that at least one inlet (85,86) has an associated reversible fan (87,88) as known per se, for selectively controlling the air flow direction in relation to the distribution chamber (84) . 6. Apparatus according to claim 1 or 5, c h a r a c t e r i z e d in that the medium flow into the distribution chamber (84) takes place through the evaporator (92) and the condenser (91) , and that there are provided two substantially mutually opposite outlets (95,96). 7. Apparatus according to claim 6, c h a r a c t e r i z e d in that one and the same driving device (97) through branched ducts (97A,97B,97C) serves to deliver one portion (97C) of the medium flow to the evapora- tor (92) and another portion (97B) of the medium flow to the condenser (91) . 8. Apparatus according to claim 6 or 7, intended for a medium in the form of air, c h a r a c t e r i z e d in that the evaporator (92) is located generally above the distribution chamber (94) , that the separating damper blade (90) in both its extreme pos¬ itions is adapted to have a downward slope in the direction towards one of the two opposite edge portions of the separatr ing damper blade (90) , and that the generally downwardly facing main surface of the separating damper blade is pro¬ vided with a heat insulating coating (100) so that condensa¬ tion water being collected and lead on the upper side of the separating damper blade (90) will not to any undesired degree be subjected to heat influence from the opposite side of the separating damper blade. 9. Apparatus according to claim 8, c h a r a c t e r i z e d by at least one collecting gutter (101,102) for condensation water being collected and lead on the separating damper blade (90) , with the collecting gut- ter(s) being positioned in relation to one or both of the two opposite edge portions of the separating damper blade (90) in respective lower extreme positions respectly thereof, and that the heat insulating coating (100) consists of a somewhat hygroscopic material and in at least one of said extreme positions is adapted to contact the collecting gutter (101,102) so that the coating (100) is moistened by condensa¬ tion water in the gutter, and that a main surface of the coating (100) is substantially exposed to the air flow from the condenser (91) , with a resulting evaporation of condens- ation water from the coating (100) . 10. Apparatus according to claim 9, c h a r a c t e r i z e d in that a discharge pipe (101A) from one collecting gutter (101) is lead to a container or water jacket (105) being in good heat contact with a portion of a pipe connection (93W) in the heat pump circuit between the condenser (91) and said throttle means (93X) , so that condensation water in the container (105) will cool the circulating medium in the heat pump circuit at said portion. AMENDED CLAIMS [received by the Internationl Bureau on 17 August 1993 (17.08.93); original claim 1 amended; other claims unchanged (4 pages)] 1. Apparatus for the heating or cooling of a gaseous or liquid medium, comprising a heat pump circuit with a compressor, condenser (11,41,71,81,91), throttle means (93X) and evaporator (12 ,42 ,62 ,72,82) , and urther comprising at least one driving device (7,8,17,18,47,48,77,78,87,88,97) for the flow of the medium, and a distribution chamber (4,14A,14B,44A,44B,74,84,94) adapted to communicate with the condenser and the evaporator as well as with an inlet (5,6,15,16,45,85) or outlet (86,95,96) for the medium to or from the distribution chamber, and provided with adjustable damper blade means (10,40,70,80,90) for the flow of the medium in the distribution chamber, c h a r a c t e r i z e d in - that the condenser (11,41,71,81,91) and the evaporator (12,42,72,82,92) form two substantially mutually opposite main confining surfaces (1A,2A,41A,42A) of the distribution Chamber (4,14A,14B,44A,44B,74,84,94) , - that the inlet (5,6,15,16,45,85,86) or outlet (95,96) of the distribution chamber is directed substantially in paral¬ lel to said main confining surfaces (1A,2A,41A,42A,71A,72A) , and - that said damper blade means is a unitary, pivotable damper blade (10,40,70,80,90) having two oppositely located edge portions (75A,75B) which in the two extreme positions of the damper blade are adapted to substantially directly engage marginal portions of the respective main confining surfaces (71A,72A) . 2. Apparatus according to claim 1 wherein the medium flow out of the distribution chamber takes place through the evaporator (42) and the condenser (41), c h a r a c t e r i z e d in that a first and a second inlet (47P,48P) to the distribution chamber (44A/44B) are directed at an inclination towards each other at an angle smaller than 180° so that mixing of two associated medium flows to a large extent takes place centrally in the distribution chamber (44A/44B) when the damper blade (40) is set in an inter¬ mediate position. 3. Apparatus according to claim 1 or 2, wherein the medium flow out of the distribution chamber takes place through the evaporator (42) and the condenser (41) , c h a r a c t e r i z e d in that the damper blade (- 10,40,70,80) preferably in a stepless manner is adjustable between an extreme position in which substantially the whole medium flow from a first inlet (15,85) is directed to the evaporator (11,41,71,81) and from a second inlet (16,86) to the condenser (12,42,72,82), and another extreme position in which substantially the whole medium flow from the first inlet (15,85) is directed to the condenser (12,42,72,82) and from the second inlet (16,86) to the evaporator (11,41,71,- 81) . 4. Apparatus according to claim 3, c h a r a c t e r i z e d in that the damper blade (70) at least on one main surface is provided with a relatively narrow guide plate (79A,79B) arranged approximately at a right angle to the main surface concerned and extending obliquely in general from one side egde to another on the damper blade (70) . 5. Apparatus according to anyone of claim 1-4, adapted for a medium in the form of air, c h a r a c t e r i z e d in that at least one inlet (85,86) has an associated reversible fan (87,88) as known per se, for selectively controlling the air flow direction in relation to the distribution chamber (84) . 6. Apparatus according to claim 1 or 5, c h a r a c t e r i z e d in that the medium flow into the distribution chamber (84) takes place through the evaporator (92) and the condenser (91), and that there are provided two substantially mutually opposite outlets (95,96). 7. Apparatus according to claim 6, c h a r a c t e r i z e d in that one and the same driving device (97) through branched ducts (97A,97B,97C) serves to deliver one portion (97C) of the medium flow to the evapora- tor (92) and another portion (97B) of the medium flow to the condenser (91) . 8. Apparatus according to claim 6 or 7, intended for a medium in the form of air, c h a r a c t e r i z e d in that the evaporator (92) is located generally above the distribution chamber (94) , that the damper blade (90) in both its extreme positions is adapted to have a downward slope in the direction towards on of the two opposite edge portions of the damper blade (90) , and that the generally downwardly facing main surface of the damper blade is provided with a heat insulating coating (100) so that condensation water being collected and lead on the upper side of the damper blade (90) will not to any undesire degree be subjected to heat influence from the opposite side of the damper blade. 9. Apparatus according to claim 8, c h a r a c t e r i z e d by at least one collecting gutter (101,102) for condensation water being collected and lead on the damper blade (90) , with the collecting gutter(s) being positioned in relation to one or both of the two opposite edge portions of the damper blade (90) in respective lower extreme positions respectly thereof, and that the heat insu¬ lating coating (100) consists of a somewhat hygroscopic material and in at least one of said extreme positions is adapted to contact the collecting gutter (101,102) so that the coating (100) is moistened by condensa tion water in the gutter, and that a main surface of the coating (100) is substantially exposed to the air flow from the condenser (91) , with a resulting evaporation of condens¬ ation water from the coating (100) . 10. Apparatus according to claim 9, c h a r a c t e r i z e d in that a discharge pipe (101A) from one collecting gutter (101) is lead to a container or water jacket (105) being in good heat contact with a portion of a pipe connection (93W) in the heat pump circuit between the condenser (91) and said throttle means (93X) , so that condensation water in the container (105) will cool the circulating medium in the heat pump circuit at said portion. STATEMENT UNDER ARTICLE19 In the enclosed amended claims 1-10, claim 1 has been amended so as to take into account the documents cited in the international search report, in particular US 3,995,446. Thus, in the preamble of amended claim 1 adjustable damper blade means are recited. Moreover, in all the claims the term "separating damper blade" has been amended to "damper blade". Apart from this amended wording, claims 2-10 have been maintained without change.

Inventors: SAKKI ARNFINN, SAKKI, ARNFINN
Applicants: SAKKI ARNFINN, SAKKI, ARNFINN
Application year: 1993
Main classification: F24F12
IPC codes: F24F1, F25B47