[go: up one dir, main page]

US20110259029A1 - Air conditioning system for a building - Google Patents

Air conditioning system for a building Download PDF

Info

Publication number
US20110259029A1
US20110259029A1 US13/095,183 US201113095183A US2011259029A1 US 20110259029 A1 US20110259029 A1 US 20110259029A1 US 201113095183 A US201113095183 A US 201113095183A US 2011259029 A1 US2011259029 A1 US 2011259029A1
Authority
US
United States
Prior art keywords
heat
air
conditioning system
air conditioning
heat pump
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.)
Abandoned
Application number
US13/095,183
Other languages
English (en)
Inventor
Roland Burk
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Assigned to BEHR GMBH & CO. KG reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BURK, ROLAND
Publication of US20110259029A1 publication Critical patent/US20110259029A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
    • F25B17/083—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt with two or more boiler-sorbers operating alternately
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2315/00—Sorption refrigeration cycles or details thereof
    • F25B2315/007—Parallel systems therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/272—Solar heating or cooling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the invention relates to an air conditioning system for a building.
  • WO 2007/068481 A1 which corresponds to U.S. Publication No. 2009000327, describes a heat pump according to the adsorber/desorber principle, wherein a heat-transporting fluid can flow around a stack of hollow elements, each containing a working medium, on an adsorption/desorption side of the hollow elements via a plurality of flow paths.
  • the flow paths are alternately cyclically interconnected by a pair of two rotary valves, wherein the large number of separate flow paths improves the overall efficiency of the heat pump.
  • a second fluid for example air
  • An air conditioning system according to the invention is based on such a heat pump, wherein depending on the requirements of the invention, reference is made to the detailed explanations of the heat pump.
  • heat pumps have been considered as central large-scale plants for building air conditioning, wherein the heat pump should be disposed centrally, for example in a basement or beneath the roof of a building, and heated or cooled water is conducted via a line network to different heating or cooling sites of a building.
  • the heat pump can be provided in a manner similar to a facade or window air conditioner.
  • the heat pump will then typically condition only one room, or a few rooms, and the output and size thereof are dimensioned accordingly.
  • At least two locally disposed heat pumps are provided. These local heat pumps can be connected to a fluid line system of the building, similar to a radiator.
  • a fluid line system of the building similar to a radiator.
  • the fluid line system can notably be a liquid line system.
  • the locally disposed heat pump is designed for a cooling power of no more than 10 kilowatts, and more particularly no more than 5 kilowatts, in the normal operating mode.
  • an air conditioning unit is made possible that is flexible to install and, in particular, can also be retrofitted and that is sufficiently dimensioned for individual rooms of average size.
  • the heat sink can be designed as a heat exchanger through which air flows.
  • the heat exchanger is designed as an integrated unit comprising the locally disposed heat pump.
  • the heat pump can be connected to a dual-line system of the building, whereby the installation complexity and costs are reduced.
  • the locally disposed heat pump can be disposed in an outside wall region of the building, wherein at least one outside wall breakthrough connected to the heat pump enables air exchange with a room of the building.
  • This arrangement has the advantage that circulating air and/or outside air can be fed selectively, or in a mixable manner, for example as circulating, mixed or fresh air, to the conditioned region.
  • the heat pump comprises an adjustable mixing member, wherein at least an air current of the group including outside air, building air or conditioned feed air can be mixed with another air current of the group and divided in a complementary fashion to an evaporation zone and a condensation zone of the heat pump.
  • the mixing member is disposed on the inlet side of the heat pump.
  • the term ‘circulating air’ within the context of the present invention, shall generally be understood to mean building air that is withdrawn from the building. Depending on the particular use, this circulating air/building air can then be recirculated to the building or dissipated to the outside.
  • the fluid is connected to the heat pump by way of a dual-line system.
  • the dual-line system will generally lead to either a heat source or heat sink, wherein the respectively other component is provided locally or decentralized in the region of the heat pump, for example in the form of a recooling unit operated by outside air.
  • the fluid is connected to the heat pump by way of a triple-line system, wherein one of the lines leads to the heat source and another one of the lines leads to the heat sink, and wherein a third line forms a mean temperature return of the heat pump.
  • the flow direction of the fluid runs preferably from the heat source to the heat pump and from the heat sink to the heat pump, wherein the fluid flow in the mean temperature return leads away from the heat pump.
  • the third line is connected by way of a branch to the heat source and the heat sink.
  • the heat pump is spatially separated from both the heat source and the heat sink, which further reduces the size and makes the system more effective.
  • a fourth line may be provided, which likewise forms a mean temperature return of the heat pump, wherein in particular the third line is connected to the heat source and the fourth line is connected to the heat sink.
  • the different temperature levels of the returns to the heat source and to the heat sink are taken into consideration, which develop with optimized internal heat recovery of the heat pump, whereby slightly higher thermal ratios can be achieved.
  • the thermal ratio of a thermally driven heat pump is the quotient of useful heating or cooling power and the required drive thermal output, and therefore constitutes a measure of the efficiency.
  • At least the third line can be connected to a mean temperature heat accumulator.
  • the centrally developing adsorption heat can be utilized, which is dissipated via the hot or mean-temperature return of the heat pump.
  • a mean temperature heat accumulator within this meaning can be any thermodynamically expedient storage or transfer of this heat volume. In particular, it can be designed as at least one of the group of process water accumulator, hot water accumulator or low-temperature heater.
  • a low-temperature heater shall generally be understood to mean any type of component activation of the building, for example floor or wall surface heater.
  • the heat pump can be designed so that it has both a cooling operating mode for cooling air that is fed to the building and a heating operating mode for heating air that is fed to the building.
  • a heating operating mode shall preferably be understood to mean that not only energy of the heat source is delivered to the building, but that in fact additional heat pumping takes place to improve the utilization of energy.
  • air is conducted to the outside, which has been cooled by the heat pump driven by the heat source/heat sink to below the outside temperature. The amount of heat withdrawn from the outside air is then additionally available for heating the building.
  • the portion incurred as adsorption heat is transferred via the fluid circuit to the heat accumulator or the heat consumer of the building, and the portion incurred as condensation heat is transferred to the useful air of the building, while the evaporation heat is withdrawn from the air current delivered to the outside air.
  • this corresponds to exhaust air/supply air heat recovery with a concurrent temperature increase due to the heat pump effect.
  • a portion of the hollow elements around which air flows is provided with a water-storing device.
  • condensation water that precipitates from the cooled air during an evaporator operation of the hollow element can be stored distributed in an areal manner, so that it evaporates again in the subsequent internal, and heat-emitting, condensation operation of the same respective hollow element and can be emitted to the air.
  • the condensation water precipitated from the air is conducted as steam to the outside or emitted to the outside air.
  • an enthalpy transfer medium is formed for the condensation water formed when the useful air cools, by which an enthalpy exchange can be achieved between the supply air and exhaust air from the room to be conditioned.
  • the water-storing device is designed as a rib member having capillary structures and/or as a hydrophilic coating.
  • conventional louvered corrugated fins are suited to retain condensation water in a capillary manner in the fine louver slits, which were originally provided in heat exchangers to cause better turbulence of the air current.
  • a possible embodiment would therefore be to provide conventional louvered fins in the gap between adjoining hollow elements through which air flows, whereby at the same time the heat transfer between the air and the hollow elements is improved.
  • an air filter can be designed on the heat pump for filtering outside air and/or circulating air, so that pollen, dust and the like are easily filtered out.
  • the heat sink of an air conditioning system can have any arbitrary design, preferably, for example, as at least one of the group including a heat exchanger through which air flows, body of flowing water, wet cooling tower or geothermal probe.
  • the heat source can have any arbitrary design, and in a particularly preferred embodiment it is designed as at least one of the group including a solar thermal system, district heating connection, boiler or co-generation plant.
  • the heat sink and/or the heat source can be switched or connected, depending on the heating or cooling operating mode.
  • the local heat pump comprises at least one integrated pump for delivering the fluid.
  • each heat pump can branch off an individual amount of fluid, without impairing the operation of the other heat pumps.
  • This is preferably supported in that the pressure differential of the central feed lines coming from the heat source and heat sink and leading to the heat pumps is regulated by means of central pumps in relation to the return.
  • the heat pump has an electronic controller, wherein in particular a rotational speed of the rotary valve and a volume flow of the fluid can be controlled in an actuatable manner.
  • the volume flow and rotational speed are notably linked by a fixed characteristic curve.
  • electronic control is particularly suited because optimizing the efficiency under changing operating conditions is key here.
  • At least a fluid-side part of the heat pump comprises exactly only one rotary valve.
  • the exactly one rotary valve alternately interconnects at least 4, and more particularly at least 6, separate flow paths.
  • the document WO 2007/068481 A1 describes in detail only heat pumps that have pairs of two opposing rotary valves, respectively, both on the fluid side and on the air side.
  • exactly only one rotary valve is required at least on the fluid side, with the overall function being analogous otherwise.
  • FIG. 1 shows a first embodiment of an air conditioning system according to the invention.
  • FIG. 2 shows a detailed view of a heat pump of the embodiment of FIG. 1 .
  • FIG. 3 shows a schematic illustration of an air-side part of the heat pump of FIG. 2 in a cooling operation.
  • FIG. 4 shows a second embodiment of an air conditioning system according to the invention.
  • FIG. 5 shows a detailed view of a heat pump of the embodiment of FIG. 4 .
  • FIG. 6 shows a schematic illustration of an air-side part of the heat pump of FIG. 5 in a heating operation.
  • FIG. 7 shows a schematic longitudinal section of the heat pump of FIG. 5 or FIG. 2 .
  • FIG. 8 shows a schematic cross-section of the heat pump of FIG. 5 or FIG. 2 in the outlet plane.
  • FIG. 9 shows a schematic cross-section of the heat pump of FIG. 5 or FIG. 2 in the inlet plane.
  • FIG. 10 shows a variant of a rotary valve for a heat pump that is suited for all embodiments.
  • FIG. 11 shows a map projection of the rotary valve of FIG. 1 in a first position.
  • FIG. 12 shows the rotary valve of FIG. 11 in a second position.
  • FIG. 13 shows a detailed longitudinal section of the rotary valve of FIGS. 11 and 12 .
  • 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 map projection of a modified embodiment of the 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 disposed in a building, which in the present example takes on the form of a solar thermal system, comprising a solar collector 1 a and a heat accumulator 1 b (for example insulated fluid tank), and a plurality of heat pumps 2 disposed locally in the building.
  • the heat pumps 2 which are provided, for example, on broken-through outside walls, each have an integrated local heat sink 3 in the form of an air-cooled recooling unit.
  • This recooling unit integrated in the local units 2 comprises a heat exchanger 3 a through which fluid flows and a blower fan 3 b for efficiently dissipating the heat to the outside air ( FIG. 2 ).
  • the description of the operation of the air conditioning system in all embodiments relates to a cooling mode, in which cooled air is conducted through the building.
  • the fluid which in the present case is a water/glycol mixture, is connected by way of a dual-line system 4 , which has a first line 4 a leading from the heat source and a second line 4 b leading back to the heat source, to the heat pumps, which are connected to the line system 4 in parallel to each other.
  • a circulating pump 5 applies a pressure to the line system 4 , wherein each of the heat pumps 2 connected in parallel additionally comprises a dedicated feed pump 6 (see FIG. 2 ).
  • a fluid volume flow can be individually set for each heat pump 2 , without the volume flow being influenced by the operation of the other heat pumps.
  • the local heat pumps 2 are each dimensioned such that they produce a cooling power between 1 kW and 5 kW in a typical cooling operating mode. With respect to the design thereof, they correspond to a heat pump according to WO 2007/068481 A1 or a heat pump that is modified in this respect, comprising 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 local heat pumps 2 shown in detail in FIG. 2 comprise a region 7 on the air side or through which air flows and a region 8 through which fluid flows, or a regenerative adsorption model, in which the adsorption/desorption process takes place.
  • the two regions 7 , 8 are in fluid connection with each other via closed hollow elements (not shown), wherein in the hollow elements methanol as the working medium is displaced between an adsorber side comprising activated carbon as the adsorption component and an evaporator/condenser side comprising capillary component for receiving a liquid phase of the working component (see WO 2007/068481).
  • the fluid lines of the heat pumps cross over the air-side region 7 only for illustration purposes, but have no direct thermal exchange with the same.
  • the air-side region is divided into an evaporator region 9 and a condenser region 10 .
  • circulating air (building air) L 1 and/or outside air L 2 is fed for conditioning via two fans 11 , 12 to the region 7 .
  • an air current L 3 is dissipated to the outside (exhaust air) and another air current L 4 (useful air), which is conditioned if desired, is fed to the building.
  • the air currents L 1 out of the building and L 4 into the building are conducted locally via wall or ceiling breakthroughs (see for example FIGS. 7 to 9 ), and the heat pumps 2 are disposed on the building facade or the building roof.
  • the heat pumps are preferably disposed on the outside or integrated in the brickwork or the facade insulation.
  • FIG. 3 is a schematic illustration of the individual air currents L 1 -L 4 and the interconnection thereof in the air-conducting region in two operating modes.
  • An electromechanically adjustable mixing member 15 by which the fed circulating air L 1 and outside air L 2 can be mixed, is disposed on the inlet side of the air-conducting region 7 .
  • a first extreme of the setting is selected, wherein only outside air flows through the evaporator 11 and only circulating air flows through the condenser 10 .
  • the condensation that develops is generally particularly high because of the higher humidity of the outside air.
  • FIG. 3 is a schematic illustration of the individual air currents L 1 -L 4 and the interconnection thereof in the air-conducting region in two operating modes.
  • An electromechanically adjustable mixing member 15 by which the fed circulating air L 1 and outside air L 2 can be mixed, is disposed on the inlet side of the air-conducting region 7 .
  • a first extreme of the setting is selected, wherein only outside air flows through the
  • the opposite extreme operating mode is selected, wherein only circulating air L 1 is conducted over the cold evaporator region 9 and only outside air L 2 is conducted over the hot condenser region 10 .
  • this operating mode generally particularly effective cooling of the building air is achieved, but no air renewal by outside air.
  • the hollow elements of the heat pump 2 are provided on the air side with a water-storing device, in the present case are soldered-on louvered corrugated fins (not shown). Because during a complete cycle, which typically lasts approximately 10 minutes, the hollow elements undergo an evaporator mode and a condenser mode, in the first case condensation water is deposited from the conditioned air and is held in a capillary manner by the louvered fins, whereupon in the condensation mode the hollow elements are dried again by means of the dissipated air. Depending on the design, the entire cycle may also take up to 20 minutes or longer.
  • the second embodiment of the invention shown in FIGS. 4 to 6 has the following differences as compared to the first example: the heat pumps 2 are connected by way of a triple-line system comprising three lines 4 a, 4 b and 4 c; and the heat sink 3 is not disposed in each case locally on the heat pumps 2 , but centrally in or on the building. Accordingly, only a single large heat exchanger 3 a comprising a fan 3 b is present, which is likewise connected to the triple-line system. Instead of a heat exchanger 3 a comprising a fan 3 b, heat dissipation could also take place via a body of flowing water, wet cooling tower, geothermal probe or the like.
  • the heat pump 2 is connected to the triple-line system such that both a hot fluid line 4 a leads from the heat source 1 and a cold fluid line 4 c leads from the heat sink to the heat pump, wherein accordingly an additional circulating pump 5 ′ is provided in the line 4 c.
  • a mean temperature line 4 b leads away from the adsorption module 8 and opens via a T-piece 13 , respectively, into a common return line, wherein a first branch 4 d leads back to the heat source and a second branch 4 e leads back to the heat sink.
  • the heat pump 2 comprises two separate feed pumps 6 , 6 ′, by means of which an adsorption-side fluid flow 8 b and a desorption-side fluid flow 8 a of the adsorption module 8 are delivered separately.
  • the volume flows 8 a, 8 b may be different. Downstream of the two pumps 6 , 6 ′, the flows 8 a, 8 b unite to form a flow that opens into the returning mean temperature line 4 b (see FIG. 5 ). Because of the distributing branch 13 in the triple-line system, any arbitrary ratio of fluid flows 8 a, 8 b can be set in relation to each other for each heat pump 2 .
  • FIG. 4 additionally schematically shows an inside building wall 14 , which is intended to symbolize the separation of two rooms inside a building with respect to climate control.
  • the returning mean temperature line 4 b can lead through built-in or subsequently added wall surface heaters, floors or generally parts of the concrete core of the building, at least in a heating operation of the heat pumps. In this way, the amount of heat contained in the recirculated fluid is also used for heating and storage purposes, whereby the overall efficiency of the system is improved.
  • the return line can also be connected to a process water accumulator, a swimming pool or the like, for which in general heating is desired even in the summer or during a cooling operation of the heat pumps 2 .
  • FIG. 6 shows the air-side region comprising the mixing member 15 analogous to FIG. 3 , however with the heat pump being in heating mode.
  • the control In the top view, the control is set to the extreme where only heated circulating air is fed. In the bottom view, the control is set to the extreme where only heated outside air is fed.
  • heating operation is also possible in the first embodiment using local heat sinks.
  • an adjustable air by-pass must be provided, so that in the heating operation the useful air is conducted over the heat exchanger 3 a of the recooling unit 3 .
  • FIGS. 7 to 9 show schematically 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 to that of WO 2007/068. It comprises two cooperating rotary valves 2 a, 2 b in the adsorption/desorption region 8 and two cooperating rotary valves 2 c, 2 d in the air conducting region 7 . Additionally shown are breakthroughs 16 , 19 in a facade 17 of the building, wherein the lower breakthrough 19 conducts circulating air L 1 to the heat pump and the top breakthrough 16 conducts useful air into the building.
  • an air filter 18 is shown, which filters particles and/or harmful substances out of the outside air L 2 that is fed.
  • a quadruple-line system is provided to improve the efficiency. Contrary to the triple-line system, separate returning lines are provided instead of a collecting line 4 b. The colder discharge from the adsorption module 8 is recirculated to the heat sink and the warmer discharge is recirculated to the heat source.
  • FIG. 10 shows the switching design of a rotary valve 100 according to an embodiment of a heat pump that deviates from WO 2007/068481 A1 as a 2-D diagram for the case of the quadruple-line system, wherein the heat sink 118 and the heat source 120 are connected via two lines 128 and 129 , respectively, to the heat pump.
  • the rotary valve that is shown replaces the two rotary valves disposed opposite of each other on the adsorber/desorber side, so that at least on this side only a single rotary valve is provided.
  • the rotary valve 100 comprises a plurality of inlets 101 to 112 and outlets 201 to 212 , which can be individually associated with the inlets 101 to 112 via connecting lines 126 or 128 and 129 .
  • the inlets and outlets are connected, for example, to thermally active modules (adsorber/desorber hollow elements) 301 to 312 .
  • the rotary valves 100 comprises a switching member 114 , which in turn comprises a rotary body 115 , which can be rotated as indicated by an arrow 116 .
  • a first heat exchanger in the form of a cooler 118 is shown in the rotary body 115 , with a pump 119 being connected downstream of the cooler.
  • a second heat exchanger is configured as a heater 120 .
  • the rotary valve 100 shown in FIG. 10 is used to control the flow of a heat transfer fluid through twelve thermally active modules.
  • a heat transfer fluid can flow serially through the twelve thermally active modules 301 to 312 .
  • the heat source, notably the heater 120 , and the heat sink, notably the recooling unit 118 are connected between each of the modules, respectively.
  • the function of the rotary valve 100 is to incrementally shift the site of interconnection of the heater 120 and the recooling unit 118 , without having to rotate them as well, as it would be required with a direct implementation of the schematic circuit. Deviating from the illustration of FIG. 10 , the cooler 118 , the pump 119 and the heater 120 are therefore disposed outside of the rotary valve 100 in a stationary manner in the following figures of an exemplary design implementation.
  • FIGS. 11 and 12 show the rotary valve 100 of FIG. 10 first in a schematic map projection.
  • the rotary valve 100 comprises twelve inlets 101 to 112 , which are also referred to as entrances and combined to form an inlet region 81 .
  • the rotary valve 100 comprises twelve outlets 201 to 212 , which are also referred to as exits and combined to form an outlet region 82 .
  • the switching member 114 which comprises the rotary body 115
  • the inlets 101 to 112 can be connected in a variety of ways to the outlets 201 to 212 when the rotary body 115 rotates in the direction of the arrow 116 .
  • the cooler 118 and the heater 120 are disposed outside of a housing 125 .
  • Each of the inlets 101 to 112 and each outlet 201 to 212 are associated with an opening in an end face of the housing 125 , which substantially has the shape of a hollow circular cylinder.
  • the inlets and outlets open into the end faces of the housing 125 .
  • Each opening in the housing 125 can be associated with an opening in the rotary body 115 . Because of these associations, each of the inlets 101 to 112 can be connected in a defined manner to the related outlet 201 to 212 .
  • each of the inlets 102 to 106 and 108 to 112 is connected via a through-channel 126 to the related outlets 202 to 206 and 208 to 212 .
  • the through-channels 126 extend in a linear fashion through the rotary body 115 .
  • the inlets 101 and 107 are connected to the related outlet 201 , 207 , respectively, via interrupted connecting channels 128 , 128 .
  • the connecting channels 128 , 128 are divided by means of separating walls or the like into sub-channels 128 a , 128 b or 129 a, 128 b such that they force a flow diversion over the cooler 118 or the heater 120 .
  • four annular chambers 131 to 134 are provided inside the housing 125 , which in the map projections of FIGS. 11 and 12 are shown as straight channels.
  • the inlet 101 is connected via the interrupted connecting channel 129 to the annular chamber 133 , which in turn is connected to the heater 120 .
  • the heater 120 is connected via the annular chamber 134 to the outlet 201 .
  • the inlet 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 to the outlet 207 .
  • the through-channels 126 and the interrupted connecting channels 128 , 129 are associated with other inlets and outlets. This displacement preferably takes place incrementally, so that the rotary body 115 always come to a stop when the mouth openings of the channels 126 , 128 , 129 provided in the rotary body 115 cover the corresponding openings in the housing 125 .
  • FIG. 12 shows the rotary body 114 rotated by one increment in relation to the illustration of FIG. 11 .
  • the inlet 102 is connected via the heater 120 to the related outlet 202 .
  • the inlet 108 is connected via the cooler 118 to the related outlet 208 .
  • the remaining inlets 101 , 103 to 107 , 109 to 112 are connected via the through-channels 126 directly to the related outlets 201 , 203 to 207 , 209 to 212 .
  • FIGS. 13 to 15 show the rotary valve 100 , which in FIGS. 11 and 12 is shown in a simplified illustration, in slightly more detail.
  • the rotary body 115 is rotatably driven using a mounted drive shaft 150 that is sealed with respect to the surroundings.
  • two ceramic sealing plates 151 , 152 are provided at each end face of the housing 125 .
  • the ceramic sealing plate 151 is fixedly associated with the housing 125 .
  • the ceramic sealing plate 152 is associated with the rotary body 115 and rotates with the same relative to the ceramic sealing plate 151 and the housing 125 .
  • the two plate pairs can be elastically preloaded with respect to each other by way of a spring device (not shown).
  • annular chambers or annular spaces 131 to 134 are connected via a radial opening 141 to 144 to the related connecting channel 128 , 129 .
  • the radial openings 141 to 144 constitute a radial through-window, which creates a fluid connection between the annular chambers 131 to 134 and the radially inwardly disposed axial connecting channels 128 , 128 , which contrary to all other connecting channels 126 are divided by at least one dividing wall 128 c or 129 c into two sub-channels 128 a and 128 b, or 129 a and 129 b.
  • the association between the sub-channels 128 a, 128 b or 129 a, 129 b and the annular chambers 131 to 134 is preferably selected so that in each case two adjoining annular chambers 131 , 132 and 133 , 134 are connected to corresponding, which is to say mutually aligned, inlets 101 ; 107 and outlets 201 ; 207 .
  • one fluid path always leads through the heater 120 and another of the total of twelve available fluid paths leads through the cooler or recooling unit 118 , depending on the position or rotation of the rotary body 115 .
  • the fluid travels from the inlet 101 via the radial opening 143 and the annular chamber 133 to the heater 120 , as is indicated by an arrow 121 .
  • Another arrow 122 indicates that the fluid travels from the heater 120 via the annular chamber 134 and the radial opening 144 to the outlet 201 .
  • the fluid travels from the inlet 107 via the radial opening 141 and the annular chamber 131 to the cooler 118 , as is indicated by an arrow 123 .
  • Another arrow 124 indicates that the fluid travels from the cooler 118 via the annular chamber 132 and the radial opening 142 to the outlet 207 .
  • FIGS. 14 and 15 show two sections of the rotary valve 100 of FIG. 13 .
  • arrows 161 and 162 indicate how the fluid travels from the heater 120 to the radial opening 144 .
  • additional arrows 163 , 164 indicate how the fluid travels from the cooler 118 to the radial opening 142 .
  • the sections show the rotary body 115 divided into 12 axial chambers, which are preferably made of plastic injection molded elements and positively stacked on a common shaft 150 .
  • the reference numerals 128 and 129 denote the through-channels, which are each divided by means of separating walls 128 c or 129 c into two sub-channels 128 a, 128 b or 129 a, 129 b.
  • the rotary body 115 in a first embodiment shown here comprises only interrupted through-channels in the manner of reference numerals 128 and 129 , which in each case are again divided by separating walls 128 c and 129 c into sub-channels 128 a, 128 b or 129 a, 129 b and comprise radial through-windows to the annual chambers 131 to 134 , which in turn are connected in pairs to two heat transfer units, which here are identified as “ heat sink” and “recooling unit”.
  • FIG. 17 shows the rotary valve in the next position.
  • This modified embodiment enables an association of thermally active modules 301 to 312 that is dependent on the switch position of the rotary valve with at least two separate fluid circuits driven by dedicated feed devices, with the associated modules experiencing parallel flow inside these fluid circuits.
  • a plurality of radial through-windows are required, which each establish a flow connection into a common of the total of four required annular chambers.
  • the separating walls within a group of through-channels can be eliminated in the rotary body, whereby then each annular chamber only requires one large radial through-window, which is not shown in the illustration here in detail.
  • the respectively last channel of a group of parallel channels comprises no radial breakthrough to an annular chamber, whereby flow is suppressed. In this way, no flow takes place through the connected modules. This can have advantages during the process changes between condensation and evaporation phases, which entail intermediate temperatures that cannot be used further.
  • the two embodiments according to FIG. 11 , 12 or 16 , 17 represent only two examples of the division of the through-channels in keeping with the categories 126 , 128 and 129 . Other divisions of the through-channels to these categories are of course possible and useful for particular applications.
  • the advantages of the rotary valve 100 include the following: high integration of switch functions replaces two conventional rotary valves; reduced complexity for drive and control; compact, material-saving design; simple, cost-effective to produce, for example from plastic injection molded parts; easy-to-implement, low-wear surface seal using ceramic disks or ceramic plates 151 , 152 ; short flow paths with low heat exchange between the individual flow paths; low friction and required driving torque; and low by-pass losses.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
US13/095,183 2008-10-28 2011-04-27 Air conditioning system for a building Abandoned US20110259029A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008053554A DE102008053554A1 (de) 2008-10-28 2008-10-28 Klimasystem für ein Gebäude
DEDE102008053554.0 2008-10-28
PCT/EP2009/063794 WO2010049325A2 (de) 2008-10-28 2009-10-21 Klimasystem für ein gebäude

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/063794 Continuation WO2010049325A2 (de) 2008-10-28 2009-10-21 Klimasystem für ein gebäude

Publications (1)

Publication Number Publication Date
US20110259029A1 true US20110259029A1 (en) 2011-10-27

Family

ID=41479330

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/095,183 Abandoned US20110259029A1 (en) 2008-10-28 2011-04-27 Air conditioning system for a building

Country Status (6)

Country Link
US (1) US20110259029A1 (de)
EP (1) EP2352956A2 (de)
CN (1) CN102197268B (de)
BR (1) BRPI0920086A2 (de)
DE (1) DE102008053554A1 (de)
WO (1) WO2010049325A2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH707175A1 (de) * 2012-11-13 2014-05-15 Bs2 Ag Ventil zur Umschaltung der Wärmeströme einer Wärmepumpe.
US9848586B2 (en) * 2014-01-16 2017-12-26 GeoSolarHeat System and method for environmental control

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010007033A1 (de) * 2010-02-10 2012-12-27 Sabine Ludewig Parallelschaltung von Wärmepumpen im Gegenstrom zur Ausnutzung minimaler Temperaturgefälle zwischen den einzelnen Wärmepumpen
JP5861726B2 (ja) * 2014-02-03 2016-02-16 ダイキン工業株式会社 空気調和システム
CN104746910B (zh) * 2015-03-27 2016-11-23 吉首大学 一种热回收低能耗除雾游泳馆
FR3038366B1 (fr) * 2015-07-03 2019-08-30 Bull Sas Systeme de climatisation d'un batiment
CN113390201A (zh) * 2020-12-23 2021-09-14 荏原冷热系统（中国）有限公司 一种热泵机组
DE102023000478A1 (de) 2023-02-13 2024-08-14 shoch3 GmbH SolarShift-Modul

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3602006A (en) * 1969-09-15 1971-08-31 Westinghouse Electric Corp Room air conditioner
US5471852A (en) * 1991-07-05 1995-12-05 Meckler; Milton Polymer enhanced glycol desiccant heat-pipe air dehumidifier preconditioning system
JPH08159598A (ja) * 1994-12-01 1996-06-21 Zexel Corp 吸着式冷暖房装置
US20020092315A1 (en) * 2000-07-21 2002-07-18 Masaaki Tanaka Cooling system of heat emitters
US6442951B1 (en) * 1998-06-30 2002-09-03 Ebara Corporation Heat exchanger, heat pump, dehumidifier, and dehumidifying method
US20060130652A1 (en) * 2003-04-01 2006-06-22 Mitsubishi Chemical Corporation Adsorbent for adsorption heat pump, adsorbent for humidity-control air conditioner, adsorption heat pump and humidity-control air conditioner

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH635415A5 (de) * 1978-09-13 1983-03-31 Sulzer Ag Absorptions-waermepumpenanlage.
US4199952A (en) * 1978-10-10 1980-04-29 Owens-Illinois, Inc. Modular solar powered heat pump
GR73999B (de) * 1980-02-04 1984-06-06 Ego Elektro Blanc & Fischer
JP3341516B2 (ja) * 1994-09-19 2002-11-05 株式会社デンソー 吸着式冷凍機
DE19834696A1 (de) * 1998-07-31 2000-02-10 Ufe Solar Gmbh Chemische Wärmepumpe, Sorptionsreaktor für eine chemische Wärmepumpe und Verfahren zur Wärmebedarfsdeckung und Klimatisierung von Gebäuden mittels einer chemischen Wärmepumpe
JP4096646B2 (ja) * 2002-07-09 2008-06-04 株式会社デンソー 冷却システム
DE10325933A1 (de) * 2003-06-07 2004-12-23 Entex Energy Ltd. Diffusionsabsorptionsanlage
WO2007000068A1 (en) 2005-06-29 2007-01-04 Eth Zurich Manufacturing process for catalytic active material
EP1920196B1 (de) * 2005-08-24 2015-02-11 NuAire Limited Luftbehandlungsvorrichtung
WO2007068481A1 (de) 2005-12-14 2007-06-21 Behr Gmbh & Co. Kg Wärmepumpe
DE102006043715A1 (de) * 2006-09-18 2008-03-27 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Adsorptionswärmepumpe mit Wärmespeicher
WO2008155543A2 (en) * 2007-06-18 2008-12-24 Thermal Energy Systems Ltd Heat pump
WO2009103325A2 (de) * 2008-02-22 2009-08-27 Behr Gmbh & Co. Kg Rotationsventil und wärmepumpe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3602006A (en) * 1969-09-15 1971-08-31 Westinghouse Electric Corp Room air conditioner
US5471852A (en) * 1991-07-05 1995-12-05 Meckler; Milton Polymer enhanced glycol desiccant heat-pipe air dehumidifier preconditioning system
JPH08159598A (ja) * 1994-12-01 1996-06-21 Zexel Corp 吸着式冷暖房装置
US6442951B1 (en) * 1998-06-30 2002-09-03 Ebara Corporation Heat exchanger, heat pump, dehumidifier, and dehumidifying method
US20020092315A1 (en) * 2000-07-21 2002-07-18 Masaaki Tanaka Cooling system of heat emitters
US20060130652A1 (en) * 2003-04-01 2006-06-22 Mitsubishi Chemical Corporation Adsorbent for adsorption heat pump, adsorbent for humidity-control air conditioner, adsorption heat pump and humidity-control air conditioner

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH707175A1 (de) * 2012-11-13 2014-05-15 Bs2 Ag Ventil zur Umschaltung der Wärmeströme einer Wärmepumpe.
US9848586B2 (en) * 2014-01-16 2017-12-26 GeoSolarHeat System and method for environmental control
US10321665B2 (en) * 2014-01-16 2019-06-18 Agrieosip Llc System for controlled heating and ventilation of livestock structures

Also Published As

Publication number Publication date
WO2010049325A3 (de) 2010-07-01
BRPI0920086A2 (pt) 2015-12-08
CN102197268B (zh) 2014-01-01
WO2010049325A2 (de) 2010-05-06
CN102197268A (zh) 2011-09-21
EP2352956A2 (de) 2011-08-10
DE102008053554A1 (de) 2010-04-29

Similar Documents

Publication Publication Date Title
US20110259029A1 (en) Air conditioning system for a building
AU2006301121B2 (en) Phase change material heat exchanger
US11525600B2 (en) Air conditioning system and control method thereof
CN101384859B (zh) 冷却及通风装置
CN104075391B (zh) 空气调节装置
US20140083648A1 (en) Dedicated outdoor air system with pre-heating and method for same
JP2008215795A (ja) 可動式熱交換方式とそれを応用した、エアーコンディショナー、貯湯器、扇風機、その他熱交換器、熱の交換方式
US20070209780A1 (en) Combined Fluid-Air Evaporator And Novel Switching Concept For A Heat Pump In A Ventilating Apparatus
EP2997314A1 (de) Dediziertes aussenluftsystem mit vorwärmung und verfahren dafür
KR101824145B1 (ko) 환기장치
KR20130013585A (ko) 열회수형 환기 기능을 갖는 히트펌프 냉난방기
RU2375640C2 (ru) Оборудование для охлаждения и нагрева помещений в зданиях
Abdelgaied et al. Performance improvement of solar-assisted air-conditioning systems by using an innovative configuration of a desiccant dehumidifier and thermal recovery unit
KR20120021519A (ko) 저온수를 이용한 냉난방 및 발전시스템
WO1996027767A1 (en) Arrangement in connection with an air conditioning unit comprising heat recovery means and means for introducing additional heating and cooling
CN1117249C (zh) 空调机
WO2011133027A1 (en) Heat exchanger
Babota Mechanical ventilation systems with heat recovery for refurbishment projects and new buildings
CN213747110U (zh) 空调系统
CN111660754B (zh) 热管理装置及其控制方法和具有其的车辆
JP2006145092A (ja) 空調システム及び建物
FI102320B (fi) Menetelmä ja sovitelma lämmön siirtämiseksi
CN112325406A (zh) 空调系统
KR100426352B1 (ko) 에너지회수용 일체형 냉난방장치
JP2024051877A (ja) 空調装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: BEHR GMBH & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BURK, ROLAND;REEL/FRAME:026570/0929

Effective date: 20110502

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION