• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a method for regenerating the primary energy store (1) of a brine heat pump (4), in which a preferably designed as a metallic fin heat exchanger Luftsolewärmetauscher (3) is connected in series in the primary circuit of the brine heat pump (4), in such a way that the Solepumpe (6) is operated even if the cooling circuit of the heat pump (4) is deactivated. Thus, the space requirement for the primary energy storage (1) can be reduced to a fraction of a conventional surface collector. The air-oil heat exchanger (3) is preferably operated with exclusively natural air movement.
    公开号:AT516403A4
    申请号:T8/2015
    申请日:2015-01-08
    公开日:2016-05-15
    发明作者:Josef Masswohl；Gerd Wagner；August Kerschberger
    申请人:Masswohl Josef Dipl Ing Dr Techn；
    IPC主号:
    专利说明:

    Process for the regeneration of the primary energy storage of a brine-to-water heat pump
    Background and field of the invention
    The invention relates to a method for the regeneration of the primary energy storage of a brine heat pump according to the independent claims.
    Previous state of the art
    From EP 2 246 633 A2 a method for the use of solar heat is known, in which the solar energy output can be routed to a geothermal probe in addition to a heating circuit and a hot water tank. In contrast to the method according to the invention, however, the soil surrounding the probe is regenerated exclusively by solar energy and not by the heat energy of ambient air.
    From EP 2 151 637 A2 an arrangement for the provision of domestic hot water is known in which a solar circuit with a solar collector and a consumer on the one hand, and the primary circuit of a heat pump (brine circuit) are thermally coupled via a heat exchanger on the other hand. The extent of thermal coupling is determined by a mixing valve. The arrangement allows the use of solar energy in particular when the sunlight is no longer sufficient to reach the temperature level of the consumer in the solar circuit, but the temperature level is above that of the primary circuit of the heat pump.
    From EP 1 248 055 A2 a total environmental heat source is known in which in the primary circuit of a heat pump up to the three heat sources (geothermal heat exchanger, air collector, solar absorber) are connected in series, the heat sources are each bypassed individually by a controlled by a switching valve bypass line can. Thus, under the given conditions each best heat source (or combination of heat sources) can be selected for the operation of the heat pump. In contrast to the process according to the invention, however, EP 1 248 055 A2 does not provide any circulation of the heat transfer medium - and therefore also no energy exchange between the heat sources - when the heat pump is not in operation. Furthermore, in EP 1 248 055 A2, a change-over valve is provided for each individual heat source, while in the method according to the invention only a single switching element is necessary because the ground collector is always located in the primary circuit of the heat pump.
    WO 2012/032159 A2 proposes a storage tank which uses the latent heat energy of a storage medium, in particular water. In the center of the storage tank is a first heat exchanger through which the storage tank is preferably deprived of energy by a heat pump. Two further heat exchangers, which are cast for example in the housing wall of the storage tank and surround the first heat exchanger, serve for regeneration. The heat transfer medium of the second heat exchanger is preferably a gas, in particular ambient air or sewage air, that of the third is a liquid, via which the storage tank preferably obtained from solar absorbers energy is supplied. In contrast to the method according to the invention, different heat exchangers are proposed in WO 2012/032159 A2 for the entry and withdrawal of the energy from the storage tank, which leads to a high mechanical and electrical expense.
    The present invention will now be described by way of preferred embodiments and with reference to the drawings.
    1 shows a flow chart of a heating and / or cooling system (10), on whose primary energy storage (1) the method according to the invention is applied,
    2 shows a preferred variant of the air-oil heat exchanger (3) or of a heat exchanger module (3a) in a schematic representation,
    Fig. 3 shows a preferred variant of the ground collector (2) or a collector module (2a) in a schematic representation.
    Detailed description of the embodiments
    Fig. 1 shows a flow chart of the heating and / or cooling system (10), on the primary energy storage (1), the inventive method is applied. The elementary primary circuit (8) contains the brine pump (6), the ground collector (2) and the primary heat exchanger (5) of the brine water heat pump (4). In the extended primary circuit (8a), an air-oil heat exchanger (3) is additionally contained, the latter being connected in series into the brine circuit by a switching element (9), in particular by a change-over valve. In the secondary circuit of the brine heat pump (4) a consumer (7) is included, to which the recovered heat and / or cold is released. In the event that with the same brine heat pump (4) in the warm season cold and in the cold season heat is to be generated, this must be designed as a reversible heat pump. For heat pumps of this type, a four-way valve simply swaps the evaporator and condenser in the refrigerant circuit; Usually two different expansion valves are also used for optimum adaptation to the two operating modes. However, these details are not shown in the schematic representation of the heat pump (4) in Fig. 1, because they are irrelevant to the inventive method.
    Basically, the brine heat pump (4) for each of the two main modes (heating and cooling) can be operated in three sub-modes. These are: a. Operation of the heat pump (4) with elementary primary circuit (8) (operating mode Bl) b. Operation of the heat pump (4) with extended primary circuit (8a) (mode B2), c. Operation of the brine pump (6) with the heat pump (4) and extended primary circuit (8a) deactivated (operating mode B3).
    In the operating mode Bl, the primary energy is taken exclusively from the primary energy storage (1). The heating and / or cooling system (10) can be converted into the operating mode B2, if (a) in the heating mode, the air temperature is greater than the temperature of the storage medium (31b) of the primary energy storage (1) or (b) in the cooling mode, the air temperature less represents the temperature of the storage medium (31b) of the primary energy storage (1). In operating mode B2, at least part of the primary energy is then removed from the ambient air via the air-oil heat exchanger (3), but it may also be the case that the entire primary energy requirement is taken from the ambient air and, in addition, regeneration of the primary energy store (1) occurs , This case occurs when there is a significant temperature difference between ambient air (31a) and the storage medium (31b) of the primary energy store (1). Is in the heating mode, for example, the air temperature (31 a) 10 ° C and the temperature of the storage medium (31 b) 0 ° C, and regulates the heat pump (4) the spread of the brine temperature to 4 Kelvin, could with appropriate dimensioning of Luftsolewärmetauscher (3) and earth collector (2) set the following temperature ratios: reference point 1 (30a): 1 ° C, reference point 2 (30b): 8 ° C, reference point 3 (30c): 5 ° C. The temperature difference is at Luftsolewärmetauscher (3) 8 ° C - 1 ° C = 7K, at the ground collector (2) 5 ° C - 8 ° C = -3K and 5 ° C - 1 ° C = 4K at the primary heat exchanger (5). In other words, 4/7 of the energy obtained at Luftsolewärmetauscher (3) go to the heat pump (4) and from there to the consumer (7) and 3/7 of the energy gained in the regeneration of the primary energy storage (1).
    It also becomes clear from the above example calculation that it can be advantageous to change from operating mode B1 to operating mode B2 even when the air temperature (31a) is lower than the temperature of the storage medium (31b)
    Heat pump control strategy to establish a temperature spread of 4K brine at the primary heat exchanger (5) results in a brine outlet temperature (reference point 1 (30a)) which is at least 4K lower than the temperature of the storage medium (31b). If the air temperature (31a) now lies between the temperature of the storage medium (31b) and the said brine outlet temperature (30a), in the operating mode B2 at the air-oil heat exchanger (3) there is in any case a rise in the temperature of the brine and thus a heat input, as a result Primary energy storage (1) is spared compared to operating mode Bl.
    The mode B3 is activated when the consumer (7) currently no heat or cooling demand is given, the air temperature (31a) (a) in heating but greater than the tempera ture of the storage medium (31b) in the primary energy storage (1) or ( b) is smaller than the latter in the cooling mode. By the brine flow it comes (a) in heating mode to heat absorption on Luftsolewärmetauscher (3) and heat dissipation at the ground collector or (b) in the cooling mode to a cold absorption on Luftsolewärmetauscher and a cooling discharge to the ground collector (2), whereby in both main modes regeneration of the primary energy store (1) is given.
    The storage medium of the primary energy store (1) should have a high water content, in particular during heating operation. The enormous melting enthalpy (333.5 kJ / kg) of the water ensures that the entire primary energy storage (1) can remain at a temperature level of 0 ° C (freezing / melting point water) for a long time. Thus, during periods of warm weather during the heating season (for example in Föhnwetterlagen) due to the high temperature differences between air and storage medium to large energy inputs, which do not weaken even in long periods of warm weather, because a temperature increase in the memory only after a complete melting of the Ice is possible. If the molten water remains in the primary energy store (1), the heat input is available for subsequent cold phases such as that, as a result of which even long periods of cold can be bridged at a temperature level of the storage medium of 0 ° C.
    With regard to the second main operating mode (cooling), there are large temperature differences between day and night in many regions of the world. But even in the temperate zones of Central Europe, temperatures of 35 ° C are often reached on summer days, while temperatures drop to below 20 ° C during the night. The method according to the invention now makes it possible to emit the heat accumulating during the cooling process during the day against the relatively cool storage medium of the primary energy store (1). At night, the now warm primary energy storage tank (1) is discharged via the air-oil heat exchanger (3) against the cold outside air. This anticyclical mode of operation allows considerably better numbers of jobs (EER) to be realized than would be possible with a direct release of the heat to the hot outside air of the day. For example, reversible brine heat pumps achieve "B20 / W7" operating point. (Brine: 20 ° C, water: 7 ° C) Work figures (EER) of 6.4 and more. If this value is compared with reversible air-source heat pumps, the operating data (EER) for the operating point "A35 / W7 " (Air: 35 ° C, water: 7 ° C) rarely the value of 3.30. Another advantage of the method according to the invention is that a brine is used as the heat transfer medium and not a gaseous refrigerant, as is the case with air-water heat pumps, whereby the construction and maintenance of the systems is substantially simplified. In addition, the numbers of brine water heat pumps are generally better than those of air water heat pumps.
    Fig. 2 shows a preferred variant of the Luftsolewärmetauschers (3). This consists of a plurality of metallic core tubes (11), which are thermally conductively connected to a plurality of likewise metallic lamellae (12). The lamellae (12) are preferably arranged in a normal plane of the core tube axes, wherein the core tubes (11) first in series to subsole (11b) and then parallel to a Gesamttsolekreis with two Solesammelan-
    Closures (13) are interconnected. The serial interconnection of the core tubes (11) to subsole circles (11b) is carried out by elbows, which are also referred to as hairpins (11a). The parallel connection of the sub-loop circuits (11b) to the total closed loop circuit takes place via manifolds (14). The preferred material for the fins (12) is aluminum, the preferred material for the core tubes (11), hairpins (11a) and headers (14) is aluminum or copper. Copper has the advantage that it is easy to process by soldering, aluminum must be welded, but is less expensive. Core tubes (11), fins (12), hairpins (11 a) and manifolds (14) are prefabricated in the prior art by the refrigeration industry in large numbers for evaporators and condenser, which is also favorable production costs for the Luftsolewärmetauscher (3) of the invention Procedure result.
    The Luftsolewärmetauscher (3) is designed in its preferred embodiment for operation with natural air movement. This saves the use of fans and prevents noise emissions. The smaller area-specific power is easily compensated by a larger area. To prevent the risk of a continuous icing of the slats in the heating mode, the slats (12) are spaced at 5 mm. In general, the risk of icing up is greatly reduced anyway, because at low temperatures the air-oil heat exchanger (3) is not integrated in the primary circuit of the heat pump (4) at all.
    In a preferred embodiment of the Luftsolewärmetauschers (3) this is also modular, with the total heat exchanger preferably from the hydraulic parallel circuit of the collector modules (3a) composed. This ensures easy deployment of the system. A collector module (3a) preferably has dimensions of about 2 m x 1 m (length x height) and then weighs about 30 kg in an aluminum version. So it is still easy to handle, in an emergency by a single man. The slat width or the module depth is about 50 mm. An even greater lamella width would no longer develop a decisive increase in performance with an assumed frontal speed of the air of about 0.15 m / s (natural air movement) and the above-mentioned spacing of the lamellae. Under the assumptions made, the air-oil heat exchanger (3) can be assumed to have a specific power of about 140 watts per square meter and degrees Kelvin of mean temperature difference between brine and air. This value can also be verified well in practice. He already takes into account that in the open air there is practically never complete calm, and the natural air movement enhances the heat exchange between air and brine. On the other hand, if the air-oil heat exchanger really is "in the wind", specific capacities of 500 W / (m2 * K) are also possible (front air loss of the air: 1.0 m / s).
    Fig. 3 shows a preferred variant of the ground collector (2) or a collector module (2a). As with the air-oil heat exchanger (3), the earth collector (2) is preferably formed by the hydraulic parallel connection of individual collector modules (2a). A collector module (2a) is designed as a tube heat exchanger, wherein a PE tube (15) is laid helically in a horizontal plane so that the tube turns in a first, lower layer of a connection point (16) with the two brine connections (17 ) and return to this in a second, upper layer.
    A sustained high water content in the storage medium of the primary energy store (1) is preferably ensured by the following two variants: a. If the soil consists of soils that can hold a high water content against gravity (adhesively bound adhesive water and closed micro-cavities), the ground collector can be inserted directly into the soil. For example, clay or clay soils can easily hold 0.25 liters of water and more per cubic decimeter. If such floors are present, in an application of the method according to the invention
    Pipes of the earth collector (2) are laid so tightly that results in withdrawal rates of 100 W / m2 and more. Usually, in a surface collector, a floor, depending on the type of soil, not more than 10 - 35 W / m2 withdrawn, because the soil otherwise thermally exhausted during the heating period or can no longer completely regenerate between the heating periods. Due to the thermal regeneration of the soil within the heating season, the withdrawal rate can be chosen much larger. As a rule of thumb, for temperate climates with not more than 4,000 degree days per annum (according to VDI 3807, eg Vienna: 3,235 Kd / a, Berlin: 3,606 Kd / a, Munich: 3,809 Kd / a), the area required for the collector to one quarter Conventional surface collector can be reduced if, for an annual heating demand of 2,500 kWh in each case one square meter Luftsolewärmetauscher (3) is provided in the above-mentioned embodiment. For example, if a building has an annual heating demand of 10,000 kWh, and if a surface area requirement of 240m2 has been calculated for a conventional area collector, the space requirement can be reduced to 60m2 if the air solar heat exchanger (3) has an area of 4m2. Of course, only the area required and not the tube length of the collector can be reduced. The latter now preferably has to be concentrated in the variant proposed in FIG. 3 onto the smaller area. The reduction of the collector area to 1/4 the size of a conventional surface collector means that there is a turnover rate of the energy contained in the primary storage of 4, based on a heating period. At a reference plant (3,340 Kd / a), a turn over frequency of 10 (but for a gravel / water reservoir) was successfully tested, so you should be on the safe side with the design proposed above. b. In sandy or gravel soils, a high water content of the primary energy storage (1) can be ensured by introducing a waterproof film into the soil. As a filler, a round gravel is preferably used, because this does not violate the PE pipes (15) of the ground collector (2) or the film. This variant also has the advantage that excess storage water in the removal of heat (and the associated freezing process) can be easily pushed up and derived there defined. This results in no soil elevations, which makes this variant is particularly suitable for sealed surfaces.
    A further preferred embodiment of the method according to the invention relates to the fact that the switching member (9) for the integration of the Luftsolewärmetauschers (3) in the primary circuit of the brine heat pump (4) is done manually. This is particularly useful for existing systems, if it turns out that the area of the surface collector was chosen too low and an additional regeneration outside the heating period is desired. The heating and regeneration periods can also overlap; In Germany, for example, the months April to October offer continuous activation of the air-oil heat exchanger (3) due to the still very positive average temperatures. By the manual operation of the switching element (9), the electrical control of an existing system requires no modification.
    The performance of a regeneration outside the heating period will now be demonstrated by means of a calculation example: If at the end of the heating season, a large part of the soil around the PE pipes of the collector iced, it can be assumed that the temperature of the storage medium practically over the entire regeneration period 0 ° C remains. (If the ice melted completely earlier, then one may well enjoy this circumstance!) If it is further assumed that at a for this application very small (in terms of heat transfer and in relation to the earth collector (2) ) dimensioned Luftsolewärmetauscher (3) de facto the entire temperature rise of the brine in the earth collector (2) can be harvested again, it is calculated over the assumed regeneration period of 7 months (April to October), exner average air temperature of 14 ° C in this period ( Germany, average 2001-2013) and a specific performance of the air-fluid heat exchanger of 140 W / (m2 * K) a heat input of 14 K * 210 d / a * 24 h / d * 0.14 kW / (m2 * K) = 10,580 kWh / (m2 * a). This is about seven times (!) The average annual solar irradiation in Germany [1,400 kWh / (m2 * a)]. With regard to the regeneration of a low-temperature storage medium, the air-oil heat exchanger (3) proposed in the method according to the invention is therefore far superior to a solar collector, which opens up an interesting point of view, in particular with regard to the proposals of EP 2 246 633 A2 and EP 2 151 637 A2.
    Reference sign to position 1 Primary energy storage 2 Ground collector 2a Collector module 3 Air solar heat exchanger 3a Heat exchanger module 4 Brine heat pump 5 Primary heat exchanger 6 Brine pump 7 Consumers 8 Elementary primary circuit 8a Extended primary circuit 9 Changeover element 10 Heating / cooling system 11 Core tube 11a Hairpin 11b Subsole circle 12 Slat 13 Solesammelanschluss 14 Collector pipe 15 Polyethylene pipe (PE Tube) 16 Junction 17 Brine collector 30a Reference point 1: Brine temperature Heat pump outlet 30b Reference point 2: brine temperature Exit air solar heat exchanger 30c Reference point 3: Brine temperature Exit earth collector 31a Reference point 4: Ambient air temperature 31b Reference point 5: Temperature Storage medium
    权利要求:
    Claims (9)
    [1]
    1. A method for regenerating the primary energy storage (1) of a heating and / or cooling system (10), consisting of (a) a brine heat pump (4) with a connected to her heat and / or refrigeration consumer (7), (b) a primary energy storage device (1) having a ground collector (2), (c) a brine pump (6) for transporting a heat transfer medium (brine) through the primary circuit (8), characterized in that in at least one operating mode by means of a changeover element (9) additionally Air solar heat exchanger (3) is connected in series in the primary circuit (8), and a. in the event that the brine heat pump (4) is configured to deliver heat to the consumer (7), the brine pump (6) is activated even if the brine circuit of the brine heat pump (4) is deactivated, if the air temperature (31a) is greater than Represents temperature of the storage medium (31b) in the primary energy storage (1), and / or b. for when the brine heat pump (4) is configured to deliver refrigeration to the consumer (7), the brine pump (6) is activated even with the brine circuit heat pump (4) deactivated, when the air temperature (31a) is less than represents the temperature of the storage medium (31b) in the primary energy storage (1).
    [2]
    2. The method according to claim 1 or one of the following, characterized in that the Luftsolewärmetauscher (3) (or a module (3a) of a modular Luftsolewärmetauschers (3)) by a plurality of metallic core tubes (11) thermally conductively connected to a plurality of also metallic lamellae (12) is formed, wherein the lamellae (12) are preferably arranged in a normal plane of the core tube axes and the core tubes (11) are connected in parallel and / or series to a brine circuit with at least two brine collector connections (13).
    [3]
    3. The method according to claim 1 or one of the following, characterized in that the Luftsolewärmetauscher (3) is designed for operation with only natural air movement.
    [4]
    4. The method according to claim 1 or one of the following, characterized in that the Erdkollektor (2) or a module (2a) of a modular Erdkollektors (2) from a spirally laid in a horizontal plane PE pipe (15) is formed, wherein the pipe turns in a first position of a connection point (16) with the two brine connections (17) remove and lead back to this in a second position.
    [5]
    5. The method according to claim 1 or one of the following, characterized in that the storage medium of the primary energy storage (1) is formed by the soil, wherein the soil is such that it holds at least 0.25 liters of water per cubic decimeter of soil against gravity can, as is especially given in loam or clay soils.
    [6]
    6. The method according to claim 1 or one of the following, characterized in that the ground collector (2) of the primary energy storage (1) is dimensioned so that the heat and / or cold extraction power is at least 50 watts per square meter collector area.
    [7]
    7. The method according to claim 1 or one of the following, characterized in that the primary energy storage (1) is formed by a filled with water gravel storage, wherein the gravel storage is sealed by a waterproof shell against the soil.
    [8]
    8. The method according to claim 1 or one of the following, characterized in that the primary energy storage (1) is designed as a latent heat storage with the storage medium water.
    [9]
    9. The method according to claim 1 or one of the following, characterized in that the switching member (9) in particular with regard to a regeneration of the primary energy storage (1) outside or predominantly outside the heating period is designed for manual operation.
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    WO2016109861A2|2016-07-14|
    EP3183513A2|2017-06-28|
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    DE102013012116A1|2013-07-17|2014-04-03|Michael Bauer|Heating system for e.g. buildings, has energy collectors absorbing heat of standing or running or waste water, and heat exchanger units arranged parallel or downstream to heat pump by heat carrier supply and receiving surrounding air heat|EP3460340B1|2017-09-25|2021-05-26|ATF Anwendungszentrum für Technik und Forschung UG |Method for providing heat, heat recovery system and heat provision unit|
    法律状态:
    2020-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20200108 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA8/2015A|AT516403B1|2015-01-08|2015-01-08|Process for the regeneration of the primary energy storage of a brine water heat pump|ATA8/2015A| AT516403B1|2015-01-08|2015-01-08|Process for the regeneration of the primary energy storage of a brine water heat pump|
    PCT/AT2015/000163| WO2016109861A2|2015-01-08|2015-12-23|Method for the regeneration of the primary energy store of a brine water heat pump|
    EP15831039.1A| EP3183513A2|2015-01-08|2015-12-23|Method for the regeneration of the primary energy store of a brine water heat pump|
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