WO2010049325A2

WO2010049325A2 - Air conditioning system for a building

Info

Publication number: WO2010049325A2
Application number: PCT/EP2009/063794
Authority: WO
Inventors: Roland Burk
Original assignee: Behr Gmbh & Co. Kg
Priority date: 2008-10-28
Filing date: 2009-10-21
Publication date: 2010-05-06
Also published as: CN102197268A; US20110259029A1; WO2010049325A3; EP2352956A2; DE102008053554A1; CN102197268B; BRPI0920086A2

Abstract

The invention relates to an air conditioning system for a building, comprising a heat sink (3), a heat source (1) and a heat pump (2), the heat pump (2) having a plurality of hollow elements especially comprising an adsorption agent. A heat-transporting fluid for heat exchange with the heat source (1) and/or the heat sink (3) can be distributed in a variable manner between a plurality of flow paths associated with the hollow elements, by means of a rotary valve (2a, 2b, 100), whereby the hollow elements are brought into thermal contact with the fluid at a variable temperature. Air in the building can be conditioned by means of the hollow elements by a temperature difference between the heat source (1) and the heat sink (3). The heat pump is designed as a decentrally arranged structural unit spatially separated from at least either the heat source (1) or heat sink (3).

Description

BEHR GmbH & Co. KG Mauserstrasse 3, 70469 Stuttgart

Air conditioning system for a building

The invention relates to a climate system for a building according to the preamble of claim 1.

WO 2007/068481 A1 describes a heat pump according to the adsorber / desorber principle, in which a stack of hollow elements each containing a working medium on an adsorption / desorption side of the hollow elements can be flowed through a plurality of flow paths by a heat-transporting fluid. The flow paths are alternately cyclically interconnected by a pair of two rotary valves, the large number of separate flow paths improving overall heat pump efficiency. On an opposite evaporation / condensation side of the hollow elements, these are surrounded by a second fluid, for example air, which is likewise guided alternately over the hollow elements by a pair of two rotary valves. Such a heat pump is based on a climate system according to the invention, while reference is made to detail embodiments of the heat pump, depending on the requirements of the invention.

So far, such heat pumps were contemplated due to their complex design as a central large-scale systems for air conditioning buildings, the heat pump centrally, for example, in a basement or under the roof of the building is to be arranged and heated or cooled water is conducted via a pipeline network to different heating or cooling points of a building.

It is the object of the invention to specify an air conditioning system for a building, which is designed to be small in size, in particular retrofittable, and can be used as needed.

This object is achieved for an aforementioned climate system according to the invention with the characterizing features of claim 1. By training as a decentralized unit, the heat pump can be provided similar to, for example, a facade or window air conditioner. The heat pump usually only conditions one or a few rooms and is dimensioned accordingly in terms of performance and size.

In a particularly preferred embodiment, at least two decentralized heat pumps are provided. For example, these decentralized heat pumps may be connected to a fluid management system of the building, similar to a radiator. In the case of retrofits, existing pipelines of a heating system may also be used for this or they may be embedded in the external façade insulation as part of an energy-saving refurbishment measure. The fluid-line system may in particular be a liquid-line system.

In a preferred detailed design, the decentralized heat pump is designed for a cooling capacity of not more than 10 kilowatts, in particular not more than 5 kilowatts, in normal operating mode. As a result, a flexibly installable, in particular retrofittable air conditioning unit is made possible, which is sufficiently dimensioned in particular for individual rooms of average size.

In one possible embodiment of the invention, the heat sink is designed as a heat exchanger through which air flows. In a possible detail design of the heat exchanger is designed as an integrated unit with the decentralized arranged heat pump. In such a design can be Connect the heat pump to a two-wire system of the building, reducing the cost and expense of an installation.

In a generally preferred embodiment, the decentralized heat pump is arranged in an outer wall area of the building, wherein at least one outer wall opening connected to the heat pump allows an exchange of air with a room of the building. This arrangement has the advantage that recirculated air and / or outside air can be supplied to the conditioned area selectively or else mixable, thus for example as recirculation, mixing or fresh air. Particularly preferably, the heat pump comprises an adjustable mixing element, wherein at least one air stream from the group outside air, building air or conditioned feed air is miscible with another air stream from the group and complementary to a vaporization zone and a condensation zone of the heat pump is divisible. In this way, on the one hand air temperature, humidity and Lufterneuerungsrate in the room can be easily influenced and further optimize the operation and efficiency of the heat pump and on the other hand realize a Zuluft- / exhaust air heat recovery. In an advantageous detailed design, the mixing element is arranged on the input side of the heat pump. The term circulating air in the sense of the present invention is generally to be understood as building air that is taken from the building. After each use of this recirculation / building air can then be supplied to the building again or be discharged to the outside.

In a particularly simple and inexpensive installation of the air conditioning system, the fluid is connected via a two-wire system to the heat pump. In this case, the two-wire system will generally lead to one of the two, heat source or heat sink, the other one being provided locally or decentrally in the region of the heat pump, for example in the form of an outside-air driven recooler.

In alternative and depending on the requirements preferred embodiment is

Fluid connected at least via a three-wire system to the heat pump, wherein one of the conductors to the heat source and another of the conductors to the Heat sink leads and wherein a third conductor forms a medium temperature return of the heat pump. The direction of flow of the fluid preferably extends from the heat source to the heat pump and from the heat sink to the heat pump, with the fluid flow in the center temperature return leading away from that of the heat pump. In a preferred detailed design, the third conductor is connected via a branch to the heat source and the heat sink. Further preferably, a spatial separation of the heat pump is provided by both the heat source and the heat sink, which further reduces the size and makes the system more effective. In addition, this can be easily converted from a cooling operation to a heating operation of the heat pump. To optimize the efficiency of the heat pump can also be provided that a fourth conductor is provided, which also forms a central temperature return of the heat pump, in particular, the third conductor is connected to the heat source and the fourth conductor to the heat sink. As a result, the different temperature level of the returns to the heat source and the heat sink is taken into account, which adjust with optimized internal heat recovery of the heat pump, which can be achieved with slightly higher heat conditions. The heat ratio of a thermally driven heat pump is the quotient of Nutzwärme- or cooling capacity and the required drive heat output and is thus a measure of its efficiency.

In a preferred embodiment with at least three conductors, it is provided that at least the third conductor can be connected to a medium-temperature heat store. Thus, the centrally occurring heat of adsorption can be used, which is dissipated via the warm or medium-temperature return of the heat pump. A medium-temperature heat storage in this sense can be any thermodynamically meaningful storage or transfer of this amount of heat. In particular, it may be designed as at least one of the group of water heater, hot water tank or low-temperature heating. Under low-temperature heating is in general any type of component activation of the building to understand, for example, floor or wall surface heating. More generally, the heat pump is preferably configured to have both a cooling mode for cooling air supplied to the building and a heating mode for heating air supplied to the building. The heating mode is to be understood as meaning that not only is the energy of the heat source discharged into the building, but in fact an additional heat pumping takes place to improve the use of energy. As a result, in such an operation, for example, air is led to the outside, which was cooled by the heat pump below the outside temperature by means of the drive through the heat source / heat sink. The amount of heat extracted from the outside air is additionally available according to the building heating.

In a preferred embodiment and operating mode, the heat accumulating as Adsorptionswärme part is transferred via the liquid circuit to the heat storage or the heat consumer of the building and incurred as condensation heat part of the useful air of the building, while the heat of evaporation is removed from the air stream discharged to the outside air. When using building air as a heat transfer medium, this corresponds to an exhaust air supply air heat recovery with simultaneous increase in temperature by the heat pump effect.

In a particularly preferred embodiment of the invention, an air-flow part of the hollow elements is provided with a water-storing means. As a result, condensation water which precipitates out of the cooled air during an evaporator operation of the hollow element can be stored so that it evaporates again in the subsequent inside and thus heat-emitting condensation operation of the same respective hollow element and can thus be released into the air. In the usual operating mode, the condensed water that has precipitated out of the air is led outwards as steam or released to the outside air. Overall, an enthalpy transformer is thereby formed for the condensation water formed during the cooling of the useful air, with which an enthalpy exchange between supply air and exhaust air from the room to be conditioned can be realized. In addition, there is the considerable advantage that at no point on the air-side heat pump is a quantity of water over a longer period of time. collects space, which prevents the formation of microorganisms or their odorous metabolic products. Typical cycle times of such a heat pump are 10 minutes, so that the air-flow area of a hollow element of the invention in simple terms alternately 5 minutes wet and 5 minutes dry.

In a simple and preferred detailed design, the water-storing agent is designed as a rib member having capillary structures and / or as a hydrophilic coating. For example, conventional gill corrugated fins are capable of capping condensed water in the fine gill slots originally intended to better swirl the air flow in heat exchangers. A possible embodiment would therefore be to provide conventional gill ribs in the air-flowed spa between adjacent hollow elements, whereby at the same time the heat transfer between the air and the hollow elements is improved.

In a preferred embodiment, an air filter for filtering outside air and / or circulating air is formed on the heat pump, so that pollen, dust u.a. be easily filtered out.

In general, the heat sink of a climate system according to the invention may be of any desired design, preferably, for example, as at least one of the group of air-flow heat exchangers, flowing waters, wet cooling tower or ground probe. Likewise, the heat source can be designed as desired, particularly preferably as at least one of the group solar thermal system, Femwärmeanschluss, boilers or combined heat and power plant.

In a preferred embodiment, the heat sink and / or the heat source can be switched on or off depending on the heating or cooling mode.

In a preferred embodiment of the invention, the decentral heat pump has at least one integrated pump for conveying the fluid. Thus, with a parallel connection of multiple heat pumps on a fluid conductor system of the building, each heat pump an individual amount branch off of fluid without affecting other heat pumps in their operation. This is preferably supported by the fact that coming from the heat source and the heat sink leading to the heat pump central supply lines by means of central pumps in relation to the return pressure differential pressure-controlled.

In general, particularly preferably, the heat pump has an electronic control, wherein in particular a rotational speed of the rotary valve and a volume flow of the fluid can be controllably controlled. In particular, the volume flow and the rotational speed are related via a fixed characteristic curve. Especially in one of the invention of the underlying heat pump electronic control is particularly suitable, since it depends particularly on the optimization of the efficiency under changing operating conditions.

In a further particularly preferred embodiment of the invention, it is provided that at least one fluid-side part of the heat pump has only exactly one rotary valve. As a result, the size, number of moving components and production costs of a heat pump can be reduced. To improve the efficiency of at least 4, in particular at least 6 separate flow paths are alternately connected by the exactly one rotary valve. The document WO 2007/068481 A1 describes in detail only heat pumps which have pairs of two opposite rotary valves both on the fluid side and on the air side. In addition, an embodiment is given below, in which at least the fluid side, only one rotary valve is needed with otherwise analogous overall function.

Further advantages and features of the invention will become apparent from the embodiments described below and from the dependent claims.

Hereinafter, several preferred embodiments of the invention will be described and explained in more detail with reference to the accompanying drawings. Fig. 1 shows a first embodiment of an inventive

Climate system.

Fig. 2 shows a detailed view of a heat pump of the embodiment of Fig. 1. Fig. 3 shows a schematic representation of an air-side part of

Heat pump of Fig. 2 in a cooling operation. Fig. 4 shows a second embodiment of an inventive

Climate system.

5 shows a detailed representation of a heat pump of the exemplary embodiment from FIG. 4.

Fig. 6 shows a schematic representation of an air-side part of

Heat pump of Fig. 5 in a heating operation. FIG. 7 shows a schematic longitudinal section through the heat pump from FIG. 5 or also FIG. 2. FIG. 8 shows a schematic cross section through the heat pump from FIG. 5 or also FIG. 2 in the outlet plane. FIG. 9 shows a schematic cross section through the heat pump from FIG. 5 or also FIG. 2 in the inlet plane.

FIG. 10 shows a variant of a rotary valve for a heat pump which is suitable for all embodiments.

Fig. 11 shows a development of the rotary valve of Fig. 10 in a first position.

Fig. 12 shows the rotary valve of Fig. 11 in a second position. FIG. 13 shows a detailed illustration of the rotary valve from FIGS. 11 and 12 in longitudinal section.

Fig. 14 shows the view of a section along the line XXIX-XXIX in

Fig. 13. Fig. 15 shows the view of a section along the line XXX-XXX in FIG.

13. FIG. 16 shows a development of a modified embodiment of the invention

Rotary valve of FIG. 11 in a first position. Fig. 17 shows the rotary valve of Fig. 16 in a second position.

The air conditioning system according to FIG. 1 comprises a heat source 1 arranged in a building, in the present case in the form of a solar thermal system with one Solar collector 1a and a heat storage 1 b (eg insulated fluid tank) and a plurality of decentralized in the building arranged heat pumps 2. The attached, for example, in broken outer walls heat pumps 2 each have an integrated decentralized heat sink 3 in the form of an air-cooled recooler. This recooler integrated into the decentralized units 2 comprises a fluid-flowed heat exchanger 3a and a blower fan 3b for efficient removal of the heat to the outside air (FIG. 2). Unless otherwise noted, the description of the operation of the air conditioning system in all embodiments basically relates to a cooling mode in which cooled air is introduced into the building.

The fluid, which in the present case is a water-glycol mixture, is connected via a two-pipe system 4 to a first conductor 4a leading from the heat source and a second conductor 4b returning to the heat source to the heat pumps are connected parallel to each other to the conductor system 4. A circulating pump 5 pressurizes the conductor system 4 with a pressure, but each of the heat pumps 2 connected in parallel also has its own delivery pump 6 (see FIG. 2). In this way, a fluid volume flow can be set individually for each heat pump 2, without this being influenced by the operation of the other heat pumps.

The decentralized heat pumps 2 are each dimensioned so that they provide a cooling capacity between 1 kW and 5 kW in a typical cooling mode. They correspond in their design to a heat pump according to WO 2007/068481 A1 or else a heat pump modified for this purpose with only a single fluid-side rotary valve. Such a rotary valve is described below by way of example and shown schematically in FIGS. 10 to 17.

The decentralized heat pumps 2 shown in detail in FIG. 2 comprise not only the aforementioned feed pump 6 but also an air-side or air-flow 7 and a flow-through area 8 or a regenerative adsorption module in which the adsorption / desorption process takes place. The The regions 7, 8 are in fluid communication via closed hollow elements (not shown), in which hollow elements methanol is displaced as working medium between an adsorber side with activated carbon as adsorbent and an evaporator / condenser side with capillary means for receiving a liquid phase of the working medium (see WO 2007/068481). The fluid lines of the heat pump overlap the air-side area 7 only for the sake of illustration, but are not in direct thermal exchange with this.

Depending on the current mode of operation of the individual hollow elements, the air-side region is subdivided into an evaporator region 9 and a condenser region 10. Via two fans 11, 12, circulating air (building air) L1 and / or fresh air L2 is supplied to region 7 for conditioning depending on requirements and operating conditions. On the output side of the region 7, an air flow L3 is discharged to the outside (exhaust air) and another, desired conditioned air flow L4 (useful air) supplied to the building.

The air flows L1 out of the building and L4 into the building are guided locally via wall or ceiling openings (see, for example, FIGS. 7 to 9), and the heat pumps 2 are arranged on the building facade or also on the building roof. Preferably, the heat pumps are attached to the outside or integrated into the masonry or facade insulation.

Fig. 3 shows a schematic representation of the individual air streams L1-L4 and their interconnection in the air-conducting area in two modes. On the input side of the air-conducting area 7, an electromechanically adjustable mixing element 15 is arranged, can be mixed by the supplied circulating air L1 and outside air L2. In the upper illustration, a first extreme of the setting is selected, in which the evaporator 11 is only flowed through by outside air and the condenser 10 exclusively by circulating air. In this mode, a particularly large condensation usually occurs due to the higher humidity of the outside air. In the lower illustration of FIG. 3, the opposite extreme mode is selected, in which exclusively circulating air L1 is led over the cold evaporator region 9 and only outside air L2 over the hot condenser area 10. In this mode, most effective cooling of the building air is achieved, but no air renewal by outside air.

It is understood that all mixing ratios between the extreme settings described above are adjustable depending on requirements.

To improve the efficiency and to suppress micro-organisms, the hollow elements of the heat pump 2 are provided on the air side with a water-storing agent, in the present case in the form of soldered gill corrugated fins (not shown). In the first case, since the hollow elements each undergo an evaporator and condenser mode within a total cycle, which typically lasts about 10 minutes, condensation water from the conditioned air initially accumulates and is held capillary by the gill ribs, whereupon, in the condensation mode, the hollow elements are recirculated by means of the continued air be dried. Depending on the configuration, the total cycle can take up to 20 minutes or more.

In the second exemplary embodiment of the invention illustrated in FIGS. 4 to 6, the following differences from the first example are present:

-The heat pumps 2 are connected via a three-wire system with three lines 4a, 4b and 4c.

The heat sink 3 is not arranged in each case decentralized to the heat pumps 2, but centrally in or on the building. Accordingly, there is only a single large heat exchanger 3a with fan 3b, which is also connected to the three-wire system. Instead of a heat exchanger 3a with fan 3b could also be a heat dissipation via a running water, wet cooling tower, geothermal probe or the like.

The connection of the heat pump 2 to the three-wire system is such that both a hot fluid line 4a from the heat source 1 and a cold fluid line 4c lead from the heat sink to the heat pump, wherein according to an additional circulation pump 5 'is provided in the conduit 4c. A middle temperature line 4b continues from the adsorption module 8 and flows via a respective T-piece 13 in a common return line, wherein a first branch 4d leads back to the heat source and a second branch 4e back to the heat sink.

The heat pump 2 comprises two separate feed pumps 6, 6 ', by means of which in each case an adsorption-side fluid flow 8b and a desorption-side fluid flow 8a of the adsorption module 8 are conveyed separately. The volumetric flows 8a, 8b may vary considerably depending on the operating conditions. Downstream of the two pumps 6, 6 ', the streams 8a, 8b combine to form a stream which opens into the returning center temperature line 4b (see FIG. 5). Due to the distributing branch 13 in the three-pipe system, any desired ratio of leading fluid streams 8a, 8b to each other can be set for each heat pump 2.

In Fig. 4 also schematically an inner building wall 14 is shown, which is intended to symbolize the climatic separation of two rooms within a building. In general, recessed or retrofitted wall surface heaters, floors or in general parts of the concrete core of the building can be flowed through by at least one heating operation of the heat pump from the returning medium temperature line 4b. In this way, the amount of heat contained in the recycled fluid is used for heating and storage purposes, whereby the overall efficiency of the system is improved. Alternatively or additionally, the return line can also be connected to a hot water tank, a swimming pool or the like, for which heating in the summer or during a cooling operation of the heat pumps 2 is generally desired.

Fig. 6 shows the air-side region with the mixing member 15 analogous to FIG. 3, wherein the heat pump is in a heating mode. In the upper illustration, the regulation is extremal with the exclusive supply of heated circulating air. In the lower illustration, the control is extreme with the exclusive supply of heated outside air. It should be noted that in the first embodiment with decentralized heat sinks a heating operation is possible. In this case, an adjustable air diversion is provided, so that in the heating operation, the useful air is passed through the heat exchanger 3a of the recooler 3.

The drawings Fig. 7 to Fig. 9 schematically show the installation situation of the heat pump 2 according to any one of the above embodiments on a facade of the building. The present heat pump corresponds in its design to WO 2007/068. It also has two cooperating rotary valves 2a, 2b in the adsorption / desorption 8 and two cooperating rotary valves 2c, 2d in the air duct 7. Also shown are openings 16, 19 of a facade 17 of the building, the lower opening 19 circulating air L1 leads to the heat pump and the upper opening 16 carries useful air into the building. Furthermore, an air filter 18 is shown, are filtered by the particles and / or pollutants from the supplied outside air L2.

In a further, not shown embodiment, a four-wire system is provided to improve the efficiency. In contrast to the three-wire system, there are separate return lines instead of a bus 4b. The colder exit from the adsorption module 8 is thereby returned to the heat sink and the warmer exit to the heat source.

In Fig. 10, the switching task of a rotary valve 100 is shown according to a deviating from WO 2007/068481 A1 embodiment of a heat pump as a 2-D scheme for the case of the four-wire system, in which the heat sink 118 and the heat source 120 via two conductors 128th or 129 is connected to the heat pump. In this case, the illustrated rotary valve replaces the two rotary valves arranged opposite one another on the adsorber / desorber side, so that only a single rotary valve is provided at least on this side. The rotary valve 100 comprises a plurality of feeders 101 to 112 and discharges 201 to 212, which can be individually assigned to the feeders 101 to 112 via connecting lines 126 or 128 and 129. The additions and removals are z. B. with thermally active modules (adsorber / desorber hollow elements) 301 to 312 connected. The rotary valve 100 comprises a switching member 114, which in turn comprises a rotary body 115, which, as indicated by an arrow 116, is rotatable. In the rotary body 115, a first heat exchanger in the form of a cooler 118 is shown, to which a pump 119 is connected downstream. A second heat exchanger is designed as a heater 120.

The rotary valve 100 shown in FIG. 10 serves to control the flow of twelve thermally active modules with a heat transfer fluid. With the rotary valve 100 shown in FIG. 10, the twelve thermally active modules 301 to 312 can be flowed through serially by a heat transfer fluid. Between each two of the modules, the heat source, in particular the heater 120, and the heat sink, in particular the recooler 118, connected. The purpose of the rotary valve 100 is to gradually shift the location of the interposition of the heater 120 and the recooler 118 without having to co-rotate them, as would be required if the schematic circuit were implemented directly. Notwithstanding the representation of FIG. 10, the radiator 118, the pump 119 and the heater 120 are therefore arranged in a stationary manner outside the rotary valve 100 in the following figures of an exemplary design implementation.

11 and 12, the rotary valve 100 of FIG. 10 is initially shown in a schematic development. The rotary valve 100 comprises twelve feeders 101 to 112, which are also referred to as inputs and are combined to form a feed region 81. Analogously, the rotary valve 100 comprises twelve discharges 201 to 212, which are also referred to as outputs and are combined to form a discharge region 82. The feeders 101 to 112 can be connected in a different manner to the drains 201 to 212 by means of the switching element 114, which comprises the rotary body 115, when the rotary body 115 in the direction of arrow 116 rotates. In FIGS. 11 and 12, the radiator 118 and the heater 120 are disposed outside of a housing 125.

Each supply 101 to 112 and each discharge 201 to 212 is associated with an opening in an end face of the housing 125, which has substantially the shape of a hollow circular cylinder. The feeds and discharges open into the end faces of the housing 125. Each opening in the housing 125 is an opening in the rotary body 115 can be assigned. Through these assignments, each of the feeders 101 to 112 can be connected to the associated discharge 201 to 212 in a defined manner. In the embodiment shown in FIG. 11, the feeders 102 to 106 and 108 to 112 are each connected via a through-passage 126 to the associated outlets 202 to 206 and 208 to 212. The through-channels 126 extend in a straight line through the rotary body 115.

The feeders 101 and 107 are connected via interrupted connecting channels 128, 129 respectively to the associated discharge 201, 207. The connection channels 128, 129 are subdivided by means of dividing walls or the like into subchannels 128a, 128b or 129a, 129b such that they force a flow diversion via the radiator 118 or the heater 120. For this purpose, four annular chambers 131 to 134 are provided within the housing 125, which are shown in the development of FIGS. 11 and 12 as straight channels. The supply 101 is connected via the interrupted connection channel 129 with the annular chamber 133, which in turn is connected to the heater 120.

The heater 120 is connected via the annular chamber 134 with the discharge 201. Analogously, the feed 107 is connected via the annular chamber 131 to the cooler 118, which in turn is connected via the annular chamber 132 and the interrupted connecting channel 128 with the discharge 207. By rotation of the rotary body 115 in the direction of the arrow 116, the through channels 126 and the broken connection channels 128, 129 are assigned to other feeders and discharges. This displacement preferably takes place in steps such that the rotational body 115 always comes to a halt when the mouth openings of the channels 126, 128, 129 provided in the rotary body 115 overlap with the corresponding openings in the housing 125.

In FIG. 12, the rotational body 114 is rotated by one step with respect to the illustration of FIG. 11. In Fig. 12, the feeder 102 is connected to the associated discharge 202 via the heater 120. Analogously, the feed 108 is connected via the cooler 118 with the associated discharge 208. The remaining feeds 101, 103 to 107, 109 to 112 are connected via the through-channels 126 directly to the associated outlets 201, 203 to 207, 209 to 212.

In FIGS. 13 to 15, the rotary valve 100 shown in simplified form in FIGS. 11 and 12 is shown in somewhat greater detail. In the longitudinally sectioned cylindrical housing 125, the rotary body 115 is rotatably driven by means of a mounted drive shaft 150 which is sealed to the environment. For the axial mounting of the rotary body 115, two ceramic sealing plates 151, 152 are provided on each end face of the housing 125. The ceramic sealing plate 151 is fixedly assigned to the housing 125. The ceramic sealing plate 152 is associated with the rotary body 115 and rotates with this relative to the ceramic sealing plate 151 and the housing 125. The two plate pairs can be resiliently biased against each other via a (not shown) spring means.

Four annular chambers or annular spaces 131 to 134 are in each case via a radial opening 141 to 144 with the associated connecting channel 128, 129 in connection. The radial openings 141 to 144 constitute a radial through-opening window which creates a fluid connection between the annular chambers 131-134 and the radially inner axial connection channels 128, 129 which, in contrast to all other connection channels 126, are provided by at least one partition wall 128c 129c are divided into two subchannels 128a and 128b and 129a and 129b, respectively. The assignment between the subchannels 128a, 128b or 129a, 129b and the annular chambers 131 to 134 are preferably selected so that each two adjacent ring chambers 131, 132 and 133, 134 with corresponding, so aligned feeds 101; 107 and discharges 201; 207 are connected. Thereby, depending on the position or rotation of the rotary body 115, always a fluid path through the heater 120 and another of the total of twelve existing fluid paths through the cooler or recooler 118 out.

In Fig. 13, the fluid passes from the supply 101 via the radial opening 143 and the annular chamber 133 to the heater 120, as indicated by an arrow 121. By a further arrow 122 is indicated that the fluid passes from the heater 120 via the annular chamber 134 and the radial opening 144 to the discharge 201. Similarly, the fluid passes from the supply 107 via the radial opening 141 and the annular chamber 131 in the radiator 118, as indicated by an arrow 123. By a further arrow 124 is indicated that the fluid passes from the radiator 118 via the annular chamber 132 and the radial opening 142 to the discharge 207.

In Fig. 13 it can be seen that the rotor axis is mounted with the bearings 155, 156 in the cylindrical housing and the entire inner volume is sealed by a sealing element 154 from the environment. In addition, apart from the two preferably ceramic surface seal pairs 151, 52 only three further sealing elements 157, 158, 159 required to seal the four annular chambers 131 to 134 in the axial direction against each other.

In FIGS. 14 and 15, two sections through the rotary valve 100 of FIG. 13 are shown. In Fig. 14 is indicated by arrows 161 and 162, as the fluid passes from the heater 120 to the radial opening 144. In FIG. 15, further arrows 163, 164 indicate how the fluid passes from the cooler 118 to the radial opening 142. In addition, the sections show the rotational body 115 subdivided into 12 axial chambers, which are preferably stacked from plastic injection-molded elements on a common shaft 150 with positive locking. The reference numerals 128 and 129 designate the passageways by means of partitions 128c or 129c are subdivided into two subchannels 128a, 128b and 129a, 129b, respectively.

In the case of indirect air cooling via a likewise liquid heat carrier, the use of a slightly modified valve, the development of which is illustrated in FIGS. 16 and 17 in two positions, is advantageous for controlling the fluid circuits of the evaporation / condensation zones designated as zones B. ,

As shown in FIG. 16, in a first embodiment shown here, the rotary body 115 has only interrupted passage channels of the type of reference numerals 128 and 129, which are subdivided again by partition walls 128c and 129c into subchannels 128a, 128b and 129a, 129b and radial aperture windows to the annular spaces 131 to 134, which in turn communicate in pairs with two heat exchangers, which are referred to as "heat sink" and "recooler". In the illustrated embodiment, there are therefore no pure through-channels of the category corresponding to reference number 126.

Fig. 17 shows the rotary valve in the following position.

This modified embodiment allows a dependent of the switching position of the rotary valve assignment thermally active modules 301 to 312 to at least two separate driven with their own funding fluid circuits within which the associated modules are flowed through in parallel.

Through the respective parallel guidance of two groups of passage channels 128 and 129 in the rotary body 115, a plurality of radial aperture windows are required, which produce a flow connection in each case one common of the four required annular chambers. Preferably, the partitions within a group of passage channels can be omitted in the rotary body, which then only one large radial aperture window is required per annular chamber, which is not illustrated here in detail. In another embodiment, which is not illustrated here, the respective last channel of a group of parallel channels (eg 102/202 and 108/208) has no radial breakthrough to an annular chamber, whereby a flow is prevented. In this way, the connected modules are not flowed through. This can bring advantages in the process change between the condensation and evaporation phase, since it does not pass through any further intermediate temperatures.

The two embodiments according to FIGS. 11, 12 and 16, 17 represent only two examples of the division of the through-channels according to the categories 126, 128 and 129. Further distributions of the through-channels to these categories are of course possible and also useful for particular applications.

The rotary valve 100 has, among other things, the following advantages: High integration of switching functions replaces two conventional rotary valves; reduced effort for drive and control; compact, material-saving construction; simple, cost-effective producibility, for example made of plastic injection-molded parts; easily realizable, low-wear surface seal over ceramic discs or ceramic plates 151, 152; short flow paths with low heat exchange between the individual flow paths; low friction and required drive torque; low bypass losses.

It is understood that the individual features of the various embodiments can be usefully combined depending on the requirements. In particular, it is advantageous to remain in the direct use of air for the transmission of the evaporation and condensation heat in the solution with two communicating rotary valves according to WO 2007/068481 A1.

Claims

Patent claims

An air conditioning system for a building, comprising a heat sink (3), a heat source (1) and a heat pump (2), the heat pump (2) comprising a plurality of hollow elements comprising in particular an adsorbent, and a heat transporting and heat source (1) and / or the heat sink (3) in heat exchange fluid by means of a rotary valve (2a, 2b, 100) variably distributable to a plurality of the hollow elements associated flow paths, whereby the hollow elements with the fluid under a variable temperature in thermal Be contacted, and wherein by a temperature difference between the heat source (1) and the heat sink (3) by means of the hollow elements conditioning of the building supplyable air is effected, characterized in that the heat pump as spatially of at least one of the two

Heat source (1) or heat sink (3), separate and decentralized assembly is formed.

2. Air conditioning system according to claim 1, characterized in that at least two decentralized heat pumps (2) are provided.

3. Air conditioning system according to one of the preceding claims, characterized in that the decentralized heat pump (2) for a cooling capacity of not more than 10 kilowatts, in particular not more than 5 kilowatts, is designed in normal mode.

4. Air conditioning system according to one of the preceding claims, characterized in that the heat sink (3) as an air-flowed heat exchanger (3a, 3b) is formed.

5. Air conditioning system according to claim 4, characterized in that the heat exchanger (3a) is designed as an integrated unit with the decentralized heat pump (2).

6. Air conditioning system according to one of the preceding claims, characterized in that the decentralized heat pump (2) in an outer wall region (17) of the building is arranged, wherein at least one of the heat pump (2) connected outer wall opening (15, 16) with an air exchange a room of the building.

7. Air conditioning system according to claim 6, characterized in that the heat pump (2) comprises an adjustable mixing member (15), wherein at least one air flow from the group outside air (L2), building air (L1) or conditioned supply air (L4) with another air flow from the group is miscible.

8. Air conditioning system according to claim 7, characterized in that the mixing member (15) on the input side of the heat pump (2) is arranged.

9. Air conditioning system according to one of the preceding claims, characterized in that the fluid via a two-wire system (4) with the heat pump (2) is connected.

10. Air conditioning system according to one of claims 1 to 8, characterized in that the fluid is connected at least via a three-wire system (4) to the heat pump (2), wherein one of the conductors (4a) to the heat source (1) and a another of the conductors (4c) leads to the heat sink (3) and wherein a third conductor (4b) forms a medium temperature return of the heat pump (2).

11. Air conditioning system according to claim 11, characterized in that the third conductor (4b) via a branch (13) with the heat source (1) and the heat sink (3) is connected.

12. Air conditioning system according to one of claims 1 to 11, characterized in that the flow lines are regulated in relation to the common return line by means of a respective central pump differential pressure.

13. Air conditioning system according to claim 10 to 12, characterized in that both the heat sink (3) and the heat source (1) spatially separated from the heat pump (2) are arranged.

14. Air conditioning system according to one of claims 10 to 13, characterized in that a fourth conductor is provided, which also has a medium temperature

Forming return of the heat pump (2), wherein in particular the third conductor to the heat source (1) and the fourth conductor to the heat sink (3) is connected.

15. Air conditioning system according to one of claims 10 to 14, characterized in that at least the third conductor (4b) with a medium-temperature heat storage (14) is connectable.

16. Air conditioning system according to claim 15, characterized in that the medium-temperature heat storage as at least one of the group

Hot water tank, low temperature heating (14) or fluid channel system of a component or concrete core activation is formed.

17. Air conditioning system according to one of the preceding claims, characterized in that the heat pump (2) both a cooling mode for

Cooling of supplied air from the building and a heating mode for heating air supplied from the building has.

18. Air conditioning system according to one of the preceding claims, characterized in that a luftumströmter part of the hollow elements is provided with a water-storing means.

19. Air conditioning system according to claim 18, characterized in that the water-storing agent is designed as a rib member with capillary structures and / or as a hydrophilic coating.

20. Air conditioning system according to one of the preceding claims, characterized in that an air filter (18) for filtering outside air and / or circulating air to the heat pump (2) is formed.

21. Air conditioning system according to one of the preceding claims, characterized in that the heat sink (3) as at least one of the group of air-flow heat exchanger, flowing water, wet or hybrid cooling tower or ground probe is formed.

22. Air conditioning system according to one of the preceding claims, characterized in that the heat source (1) is designed as at least one of the group solar thermal system, Nah- or Femwärmeanschluss, boilers, combined heat and power plant or fuel cell.

23. Air conditioning system according to one of the preceding claims, characterized in that the heat pump (2) at least one integrated

Having pump (6, 6 ') for conveying the fluid.

24. Air conditioning system according to one of the preceding claims, characterized in that the heat pump comprises an electronic control, wherein in particular a mean rotational speed of

Rotary valve and a volume flow of the fluid controlled controllable.

25. Air conditioning system according to one of the preceding claims, characterized in that at least one fluid-side part of the heat pump has only exactly one rotary valve (100).

26. Air conditioning system according to claim 25, characterized in that at least 4, in particular at least 6 separate flow paths are alternately connected by the exactly one rotary valve (100).

27. Air conditioning system according to one of the preceding claims, characterized in that different heat sources and / or heat sinks can be connected via a fluid circuit with the heat pump depending on a heating or cooling mode.