DEHUMIDIFYING SYSTEM AND METHOD FOR REMOVING WATER VAPOR FROM AN AIR CHAIN

专利摘要:
system and method for efficient air dehumidification and liquid recovery with evaporative cooling. the present invention relates to systems and methods that are provided to dehumidify the air by establishing moisture gradients in one or more dehumidifying units. the water vapor from the relatively humid atmospheric air entering the dehumidifying units is extracted by the dehumidifying units without substantial condensation in vacuum volumes of low pressure water vapor. water vapor can be extracted through the water vapor permeable membranes of the dehumidifying units in vacuum volumes of low pressure water vapor extracted from the air is compressed to a slightly higher pressure, condensed and removed from the system under ambient conditions. in addition, each dehumidification unit can be associated with one or more evaporative cooling units arranged upstream and / or downstream. in one embodiment, the dehumidifying units work to reduce the humidity to temperature ratio to desired final conditions by the interactive approach of an ideal humidity ratio x temperature curve.
公开号:BR112013011749B1
申请号:R112013011749-4
申请日:2011-11-11
公开日:2020-12-15
发明作者:David E. Claridge；Charles H. Culp；Jefrey S. Haberl
申请人:The Texas A & M University System；
IPC主号:

专利说明:

Background
[0001] Dear heating, ventilation and conditioning (HVAC) systems often have dehumidification systems integrated into the cooling device to dehumidify the air being conditioned by such systems. When cooling is required in hot environments, the air being cooled and dehumidified will normally have a moisture ratio above approximately 0.009 (pounds of H2O per pounds of dry air). In these environments, HVAC systems traditionally use refrigerant compressors to reasonably cool the air and remove latent energy (ie, moisture). The air is typically cooled to about 12.78 oC (55 oF), which condenses H2O from the air until the air is about 100% saturated (ie, the relative humidity at about 100%). The temperature of 12.78 oC (55 oF) reduces the humidity ratio to about 0.009 pounds of H2O to pounds of dry air, which is the water vapor saturation point at 12.78 C, resulting in relative humidity almost 100%. When this air heats to about 23.89 ° C (75 ° F), the humidity ratio remains almost the same, and the relative humidity drops to approximately 50%. This traditional method of dehumidification requires the air to be cooled to approximately 12.78 ° C (55 ° F), and can normally achieve a coefficient of performance (COP) of approximately 3-5. Brief Description
[0002] Certain modalities communicated within the scope of this description are summarized below. These modalities should not limit the scope of the claimed invention, but, instead, these modalities should provide only a brief summary of possible forms of the invention. In fact, the invention can encompass a variety of forms that may be similar to or different from the modalities presented below.
[0003] In a first embodiment, a dehumidification system for removing water vapor from an air stream is provided. The system includes a first and a second channel separated by a membrane. The membrane is configured to facilitate the removal of water vapor from an air stream flowing through the first channel by facilitating the passage of H2O from water vapor to the second channel through preamble volumes of the membrane while substantially blocking all other components of the membrane. airflow and prevents them from passing through the membrane. The system also includes an evaporative cooling unit configured to cool the air stream. The system additionally includes a pressure boosting device configured to create a lower partial pressure of the water vapor within the second channel than in the first channel, so that H2O moves through the membrane to the second channel. The pressure increase device is also configured to increase the water vapor pressure at an outlet of the pressure increase device to a partial pressure of water vapor in a range suitable for subsequent condensation in water in liquid form.
[0004] In a second embodiment, a system includes a dehumidifying unit for removing H2O vapor from an air stream. The dehumidifying unit includes an air channel configured to receive an incoming air stream and discharge an outgoing air stream. The dehumidification unit also includes a H2O-permeable material adjacent to the air channel. The H2O permeable material is configured to selectively allow H2O of H2O vapor in the incoming air stream to pass through the H2O permeable material to a suction side of the H2O permeable material and substantially block other components in the incoming air stream and prevent them from passing through the H2O permeable material to the suction side of the H2O permeable material. The system additionally includes a pressure boosting device configured to create a lower partial pressure of H2O vapor from the H2O permeable material than the partial pressure of H2O vapor in the incoming air stream to trigger the passage of H2O from the H2O in the incoming air stream through the H2O permeable material, and to increase the pressure at an outlet of the pressure increase device to a partial pressure of H2O vapor suitable for condensation of H2O vapor on the suction side into the Liquid H2O.
[0005] In a third embodiment, a method includes receiving an air stream including H2O vapor within an air channel of a dehumidifying unit, where the air stream has a first partial pressure of H2O vapor. The method also includes cooling the air stream through and an evaporative cooling unit. The method additionally includes the suction of H2O into a H2O vapor channel of the dehumidification unit through an H2O permeable material from the dehumidification unit using a pressure differential through the H2O permeable material. The H2O vapor channel has a second H2O vapor partial pressure less than the first H2O vapor partial pressure of the air stream. Additionally, the method includes receiving H2O vapor from the H2O vapor channel in a pressure increasing device and increasing the H2O vapor pressure from the pressure increasing device to a third partial H2O vapor pressure that is greater than the second partial pressure of H2O vapor. Brief Description of Drawings
[0006] These and other characteristics, aspects, and advantages of the modalities of the present description will become better understood when the following detailed description is read with reference to the attached drawings in which similar characters represent similar parts throughout the drawings, where:
[0007] Figure 1 is a schematic diagram of an HCV system having a dehumidifying unit and one or more evaporative cooling units according to an embodiment of the present description;
[0008] Figure 2A is a perspective view of the de-sumidification unit of figure 1 having multiple parallel air channels and water vapor channels according to an embodiment of the present description;
[0009] Figure 2B is a perspective view of the de-sumidification unit of figure 1 having a single air channel located within a single water vapor channel according to an embodiment of the present description;
[00010] Figure 3 is a plan view of an air channel and adjacent water vapor channels of the dehumidifying unit of figures 1, 2a and 2b according to an embodiment of the present description;
[00011] Figure 4 is a perspective view of a separation module formed using a membrane that can be used as a water vapor channel for the dehumidification unit of figures 1 to 3 according to one embodiment of the present description;
[00012] Figure 5 is a psychrometric graph of the temperature and humidity ratio of the humid air flowing through the dehumidification unit of figures 1 to 3, according to one embodiment of the present description;
[00013] Figure 6 is a schematic diagram of the HVAC system and the dehumidification unit and one or more evaporative cooling units of figure 1 having a vacuum pump for removing non-condensable components from the water vapor in the extraction chamber. steam from the dehumidifying unit according to an embodiment of the present description;
[00014] Figure 7 is a schematic diagram of the HVAC system and the dehumidifying unit and one or more evaporative cooling units of figure 6 having a control system to control various operating conditions of the HVAC system and the dehumidifying unit accordingly. with an embodiment of the present description;
[00015] Figure 8 is a schematic diagram of an HVAC system having an evaporative cooling unit arranged upstream of the dehumidification unit according to an embodiment of the present description;
[00016] Figure 9A is a psychrometric graph of the temperature and humidity ratio of the air flowing through a direct evaporative cooling unit and the dehumidifying unit of figure 8 according to an embodiment of the present description;
[00017] Figure 9B is a psychrometric graph of the temperature and humidity ratio of the air flowing through an indirect evaporative cooling unit and the dehumidification unit of figure 8 according to one embodiment of the present description;
[00018] Figure 10 is a schematic diagram of an HVAC system having the evaporative cooling unit arranged downstream of the dehumidification unit according to an embodiment of the present description;
[00019] Figure 11A is a psychrometric graph of the temperature and the humidity ratio of the air flowing through the dehumidification unit and a direct evaporative cooling unit of figure 10 according to an embodiment of the present description;
[00020] Figure 11B is a psychrometric graph of the temperature and humidity ratio of the air flowing through the dehumidification unit and an indirect evaporative cooling unit of figure 10 according to an embodiment of the present description;
[00021] Figure 12A is a psychrometric graph of the air temperature and humidity ratio flowing through a plurality of dehumidifying units and a plurality of direct evaporative cooling units according to an embodiment of the present description; and
[00022] Figure 12B is a psychrometric graph of the temperature and humidity ratio of the air flowing through a plurality of dehumidifying units and a plurality of direct evaporative cooling units according to an embodiment of the present description. Detailed Description of Specific Modalities
[00023] The specific modalities of this description will be described here. In an effort to provide a concise description of these modalities, all features of an actual implementation may not be described in the specification. It should be appreciated that in the development of any real implementation like this, as in any engineering project or design, a number of specific implementation decisions must be made to achieve the specific objectives of the designers, such as compliance with system and business-related restrictions , which can vary from one implementation to another. In addition, it must be appreciated that such a development effort must be complex and time-consuming, but, nevertheless, it is a routine resumption of design, manufacturing for those skilled in the art with the benefit of this description.
[00024] When introducing elements of various modalities of the present invention, the articles "one", "one", "o", "a" a and "said", "said" must mean that there are one or more of the elements. The terms "comprising", "including", and "possessing" must be inclusive and mean that there may be additional elements in addition to the elements listed.
[00025] The present matter described here refers to dehumidification systems and, more specifically, to systems and methods capable of dehumidifying the air without initial condensation by establishing a moisture gradient in a dehumidification unit. In one embodiment, a water vapor permeable material (ie, a water vapor permeable membrane) is used along at least one boundary separating an air channel from a secondary channel or chamber to facilitate the removal of water vapor. water from the air that passes through the air channel. The secondary channel or chamber separated from the air channel by the water vapor permeable material can receive water vapor extracted from the air channel through the water vapor permeable material.
[00026] In certain embodiments, the dehumidifying unit can be used in conjunction with one or more evaporative cooling units. For example, in certain embodiments, an evaporative cooling unit can be arranged upstream of the dehumidifying unit. , with the air expelled from the evaporative cooling unit directed into an inlet of the dehumidifying unit. Conversely, in other embodiments, the dehumidifying unit can be arranged upstream of the evaporative cooling unit, with the air expelled. from the dehumidifying unit directed into an inlet of the evaporative cooling unit. In fact, in other embodiments, multiple dehumidifying units can be used with multiple evaporative cooling units arranged between the dehumidifying units. Using multiple dehumidification units and multiple evaporative cooling units, a "serrated" progression is possible in a psychometric graph from initial conditions of the temperature and humidity ratio of the inlet air to the desired final conditions of air ratio. temperature and humidity of the outlet air. In other words, each of the dehumidifying units successively dehumidifies the air at a substantially constant temperature, while each of the evaporative cooling units successively cools (and humidifies, in the case of direct evaporative cooling) the air until the final conditions desired temperature and humidity ratio are achieved.
[00027] In operation, the water vapor permeable material allows the flow of H2O (which can refer to H2O as water molecules, gaseous water vapor, water in liquid form, adsorbed / desorbed water molecules, water molecules absorbed / desorbed water, or combinations thereof) through water vapor permeable material from the air channel to the secondary channel or chamber, while substantially blocking the flow of other air components flowing through the air channel preventing them from passing through water vapor permeable material. As such, the water vapor permeable material reduces the moisture in the air flowing through the air channel by basically removing only water vapor from the air. Correspondingly, the channel or secondary chamber is basically filled with water vapor. It should be noted that the passage of H2O through the water vapor permeable material can be facilitated by a pressure differential. In fact, a lower partial pressure of water vapor (that is, a partial pressure lower than the partial pressure of water vapor in the air channel) can be created in the secondary channel or chamber to further facilitate the passage of H2O through the material. permeable to water vapor. Accordingly, the side of the water vapor permeable material opposite the air channel can be referred to as the suction side of the water vapor permeable material.
[00028] Once H2O has passed through the water vapor permeable material, a vacuum pump is used to increase the partial pressure of the water vapor on the suction side of the water vapor permeable material to a minimum saturation pressure necessary to allow water vapor to condense through a condenser. that is, the vacuum pump compresses the water vapor to a pressure in a range suitable for condensing water vapor into liquid water (for example, a range of approximately 1.72 to 7.58 kPa abs (0, 25 - 1.1 psia), with the highest value applying to the modalities using multiple de-demidification units in series), depending on the desired conditions for condensation. The condenser then condenses the water vapor into a liquid state, and the resulting liquid water is then pressurized to approximately atmospheric pressure, so that liquid water can be rejected under ambient atmospheric conditions. By condensing water vapor into a liquid state before expelling it, certain efficiencies are provided. For example, pressurizing water in liquid to atmospheric pressure requires less energy than pressurizing water vapor at atmospheric pressure. It should also be noted that the dehumidification unit described here generally uses significantly less energy than systems conventional.
[00029] While the modalities described here are basically presented as allowing the removal of water vapor from the air, other modalities may allow the removal of other H2O components from the air. For example, in certain embodiments, instead of a water vapor permeable material, an H2O permeable material can be used. As such, the H2O permeable material can allow the flow of one, all or any combination of H2O components (ie, water molecules, gaseous water vapor, liquid water, adsorbed / desorbed water molecules, molecules of absorbed / desorbed water and so on) through the H2O permeable material from the air channel to the secondary channel or chamber, while substantially blocking the flow of other components of the air flowing through the air channel preventing them from passing through the permeable material to H2O. In other words, the described modalities are not limited to the removal of water vapor from the air, but, instead, to the removal of H2O (that is, in any of its states) from the air. However, for the sake of brevity, the modalities described here are basically focused on removing water vapor from the air.
[00030] Figure 1 is a schematic diagram of an HVAC system 8 having a dehumidifying unit 10 and one or more evaporative cooling units 12 according to an embodiment of the present description. As illustrated, in certain embodiments, the dehumidifying unit 10 can receive inlet air 14A having a relatively high humidity from a first evaporative cooling unit 12 on one inlet side of the dehumidifying unit 10. Additionally, in certain embodiments, the dehumidifying unit 10 can expel the outlet air 14B having relatively low humidity into a second evaporative cooling unit 12 positioned on one outlet side of the dehumidifying unit 10. Aspects of the evaporative cooling units 12 and their positioning in the HVAC 8 system will be discussed in more detail here. In particular, while figure 1 illustrates the evaporative cooling units 12 on the inlet and outlet side of the dehumidifying unit 10, in other embodiments, the HVAC system 8 can include only one evaporative cooling unit 12 a upstream of the dehumidifying unit 10, or just an evaporative cooling unit 12 downstream from the dehumidifying unit 10. Additionally, in more complex arrangements, the multiple dehumidifying units 10 can be used with multiple evaporative cooling units 12.
[00031] The dehumidifying unit 10 can include one or more air channels 16 through which air 14 (i.e., inlet air 14A and outlet air 14B) flows. In addition, the dehumidifying unit 10 may include one or more water vapor channels 18 adjacent to one or more air channels 16. As shown in figure 1, air 14 does not flow through water vapor channels 18. Instead In addition, the modalities described here allow the passage of water vapor from the air 14 in the air channels 16 to the water vapor channels 18, thus dehumidifying the air 14 and accumulating the water vapor in the water vapor channels 18 In particular, water vapor from air 14 in air channels 16 can flow through an interface 20 (i.e., a shield or membrane) between adjacent air channels 16 and water vapor channels 18, while other components (eg nitrogen, oxygen, carbon dioxide and so on) of air 14 are blocked and prevented from flowing through interface 20. In general, water vapor channels 18 are sealed to create the low pressure that pulls water vapor from the air 14 into the air channels 16 through the interfaces 20 as H2O (that is, as water molecules, gaseous water vapor, liquid water, adsorbed / desorbed water molecules, absorbed / desorbed water molecules, and so on, through interfaces 20).
[00032] As such, a moisture gradient is established between the air channels 16 and the adjacent water vapor channels 18. The moisture gradient is generated by a pressure gradient between the air channels 16 and the steam channels. adjacent water flows 18. In particular, the partial pressure of the water vapor in the water vapor channels 18 is maintained at a lower level than the partial pressure of the water vapor in the air channels 16, so that the water vapor in the air 14 flowing through the air channels 16 tent towards the suction side (i.e., the water vapor channels 18 having a lower partial pressure of the water vapor) of the interfaces 20.
[00033] Air components other than H2O can be substantially blocked and prevented from passing through interfaces 20 in accordance with the present modalities. In other words, in certain embodiments, approximately 95% or more, approximately 96% or more, approximately 97% or more, approximately 98% or more, or approximately 99% or more of the air components 14 in addition to H2O (for example, nitrogen, oxygen, carbon dioxide and so on) can be blocked and prevented from passing through interfaces 20. When compared to an ideal interface 20 that blocks 100% of the components in addition to H2O, an interface 20 that blocks 99.5% of components other than H2O will suffer a reduction in efficiency of approximately 2 to 4%. As such, components in addition to H2O can be periodically purged to minimize these adverse effects on efficiency.
[00034] Figure 2A is a perspective view of the dehumidifying unit 10 of figure 1 having multiple parallel air channels 16 and water vapor channels 18 according to an embodiment of the present description. In the embodiment illustrated in Figure 2A, the air channels 16 and the water vapor channels 18 are generally straight channels, which provide a substantial amount of surface area of the interfaces 20 between the adjacent air channels 16 and the water vapor channels. water 18. Additionally, generally straight channels 16, 18 allow water vapor 26A to be removed along the path of air channels 16 before air 14 leaves air channels 16. In other words, incoming air relatively humid 14A (for example, air with a dew point of 12.78 oC (55 oF) or more so that the air is suitable for air conditioning) passes directly through the air channels 16 and exits as an exhaust air relatively dry 14B since moisture has been removed as the air 14 passes through the atmospheric pressure side of the interfaces 20 (i.e., the interface side 20 in the air channels 16). In a mode where a single unit is dehumidifying at a saturation pressure of 15.56 oC (60oF) or less, the suction side of interfaces 20 (that is, the interface side 20 in water vapor channels 18) will be generally maintained at a partial pressure of water vapor which is less than the partial pressure of water vapor on the atmospheric pressure side of the interfaces 20.
[00035] As illustrated in figure 2A, each of the water vapor channels 18 is connected to a water vapor channel outlet 22 through which the water vapor in the water vapor channels 18 is removed. As shown in figure 2A, in certain embodiments, the water vapor channel outlets 22 can be connected through a water vapor outlet pipe 24, where water vapor 26A from all water vapor channels 18 is combined in a single volume of water vapor vacuum 28, such as a tube or chamber. Other configurations of air channels 16 and water vapor channels 18 can also be implemented. As another example, figure 2B is a perspective view of the dehumidification unit 10 of figure 1 having a single air channel 16 located within a single water vapor channel 18 according to an embodiment of the present description. As illustrated, the air channel 16 can be a cylindrical air channel located within a larger concentric cylindrical water vapor channel 18. The modalities illustrated in figures 2A and 2B are merely illustrative and should not be limiting.
[00036] Figure 3 is a plan view of an air channel 16 and adjacent water vapor channels 18 of the dehumidifying unit 10 of figures 1, 2A and 2B according to an embodiment of the present description. In figure 3, a presentation of water vapor 26 is exaggerated for purposes of illustration. In particular, water vapor 26 from air 14 is illustrated flowing through interfaces 20 between air channel 16 and adjacent water vapor channels 18 as H2O (i.e., as water molecules, gaseous water vapor, water in liquid state, adsorbed / desorbed water molecules, absorbed / desorbed water molecules, and so on, through interfaces 20). Conversely, other components 30 (for example, nitrogen, oxygen, carbon dioxide and so on) of air 14 are illustrated as being blocked and prevented from flowing through interfaces 20 between air channel 16 and water vapor channels. adjacent 18.
[00037] In certain embodiments, interfaces 20 may include membranes that are permeable to water vapor and allow the flow of H2O to pass through the permeable volumes of the membranes while blocking the flow of other components 30. Again, it should be noted that when H2O passes through interfaces 20, it can actually pass as one, all or any combination of water states (for example, as water vapor, liquid water, adsorbed / desorbed water molecules, absorbed water molecules / desorbed, and so on) through interfaces 20. For example, in one embodiment, interfaces 20 can adsorb / desorb water molecules. In another example, interfaces 20 can adsorb / desorb water molecules and allow water vapor to pass through. In other embodiments, interfaces 20 can facilitate the passage of water in other combinations of states. The interfaces 20 extend along the air flow path 14. As such, water vapor 26 is continuously removed from one side of the interface 20 as the relatively wet inlet air 14A flows through the air channel 16. Therefore, dehumidification of the air 14 flowing through the air channel 16 is accomplished by separating the water vapor 26 from other components 30 of the air 14 incrementally as it progresses along the flow path of the air channel 16 and continuously contacts the interfaces 20 adjacent to the air channel 16 from the air inlet location 14A to the air outlet location 14B.
[00038] In certain embodiments, the water vapor channels 18 are evacuated prior to the use of the dehumidifying unit 10, so that a lower partial pressure of the water vapor 26 (i.e., a partial pressure lower than the partial pressure of the steam) water in the air channels 16) is created in the water vapor channels 18. For example, the partial pressure of the water vapor 26 in the water vapor channels 18 can be in the range of approximately 0.69 - 1.72 KPa abs (0.10-0.25 psia) during normal operation, which corresponds to dehumidification at a saturation pressure of 15.56 ° C 60oF or below. In this example, an initial condition in the range of 0.07 kPa abs (0.01 psia) can be used to remove non-condensing elements, whereas the partial pressure of water vapor in the air channels 16 may be in the range approximately 1.38 - 6.89 kPa abs (0.2-1.0 psia). However, at certain times, the pressure differential between the partial pressure of the water vapor in the water vapor channels 18 and the air channels 16 can be as low as (or less) than 0.07 kPa abs (0, 01 psia). The lower partial pressure of the water vapor in the water vapor channels 18 further facilitates the flow of water vapor 26 from the air channels 16 to the water vapor channels 18 as the air 14 flowing through the air channels 16 is at local atmospheric pressure (ie, approximately 101.4 kPa abs (14.7 psia) at sea level). Since the partial pressure of the water vapor in the air 14 in the air channels 16 is greater than the partial pressure of the water vapor 26 in the water vapor channels 18, a pressure gradient is created from the air channels 16 for water vapor channels 18. As previously described, interfaces 20 between adjacent air channels 16 and water vapor channels 18 provide protection, and allow substantially only water vapor 26 to flow from air 14 into air channels 16 into water vapor channels 18. As such, air 14 flowing through air channels 16 will generally reduce in moisture from inlet air 14A to outlet air 14B.
[00039] The use of water vapor permeable membranes as the interfaces 20 between air channels 16 and water vapor channels 18 has many advantages. In particular, in some embodiments, no additional energy is needed to generate the moisture gradient from air channels 16 to water vapor channels 18. Additionally, in some embodiments, no regeneration is involved and no environmental emissions (for example , solids, liquids or gases) is generated. In fact, according to one embodiment, the separation of water vapor 26 from the other components 30 of air 14 through water-permeable membranes (i.e., interfaces 20) can be performed at energy efficiencies much greater than technology compressor used to condense water directly from the air stream.
[00040] Since water vapor permeable membranes are highly permeable to water vapor, the operating costs of the dehumidifying unit 10 can be minimized since the air 14 flowing through the air channels 16 does not need to be significantly pressurized to facilitate the passage of H2O through interfaces 20. Water vapor permeable membranes are also highly selective for permeation of water vapor from air 14. In other words, water vapor permeable membranes are very efficient in preventing from the entry of components 30 of air 14 in addition to water vapor in water vapor channels 18. This is advantageous since H2O passes through interfaces 20 due to a pressure gradient (ie due to lower partial pressures of steam of water in the water vapor channels 18) and any permeation or leakage of air 14 into the water vapor channels 18 will increase the energy consumption of the vacuum pump used to evacuate the water vapor channels 18. In addition, water vapor permeable membranes are robust enough to be resistant to air contamination, biological degradation, and mechanical erosion of air channels 16 and water vapor channels 18. Permeable membranes water vapor can also be resistant to bacteria fixation and growth in hot and humid air environments according to one modality.
[00041] An example of a material used for water vapor permeable membranes (ie interfaces 20) is zeolite supported on thin porous metal sheets. In particular, in certain embodiments, a dense, ultrafine zeolite membrane film (for example, less than approximately 2 Dm) can be deposited on a porous metal sheet 50 Dm thick. The resulting membrane sheets can be packaged in a membrane separation module to be used in the dehumidification unit 10. Figure 4 is a perspective view of a separation module 32 formed using a membrane that can be used as a water vapor channel 18 of the dehumidifying unit 10 of figures 1 to 3 according to an embodiment of the present description. Two membrane sheets 34, 36 can be folded and fixed together in a generally rectangular shape with a channel for water vapor having a width of approximately 5 mm wmsm. The separation module 32 can be positioned inside the dehumidifying unit 10 so that the membrane coating surface is exposed to air 14. The thinness of the metal backing sheet reduces the weight and cost of the raw metallic material and also minimizes the resistance to H2O diffusing through the water vapor-permeable membrane film deposited on membrane sheets 34, 36. The metallic nature of sheets 34, 36 provides mechanical strength and flexibility for packaging so that the separation module 32 can support a pressure gradient of more than approximately 413.7 kPa (60 psi) (ie, approximately 4 times the atmospheric pressure).
[00042] The separation of water vapor from other components 30 of air 14 can create a permeation flow of water vapor of approximately 1.0 kg / m2 / h (for example, in a range of approximately 0.5 to 2 , 0 kg / m2 / h), and a water vapor to air selectivity range of approximately 5-200 +. As such, the efficiency of the dehumidifying unit 12 is relatively high compared to other conventional dehumidification techniques at a relatively low cost of production. As an example, approximately 7 to 10 m2 of membrane area of interfaces 20 may be required to dehumidify 1 ton of air cooling load under ambient conditions. In order to handle such an air cooling load, in certain modalities, from 17 to 20 separation modules 32 having an hmsm height of approximately 450 mm, an Imsm length of approximately 450 mm, and a wmsm width of approximately 5 mm can be used. These separation modules 32 can be mounted side by side on the dehumidifying unit 10, leaving approximately 2 mm of space between the separation modules 32. These spaces define the air channels 16 through which the air 14 flows. example are merely illustrative and should not be limiting.
[00043] Figure 5 is a psychrometric graph 38 of the temperature and humidity ratio of the humid air 14 flowing through the dehumidification unit 12 of figures 1 to 3 according to an embodiment of the present description. In particular, the geometric axis x 40 of the psychrometric graph 38 corresponds to the temperature of the air 14 flowing through the air channels 16 of figure 1, the geometric axis y 42 of the psychometric graph 38 corresponds to the humidity ratio of the air 14 flowing through of air channels 16, and curve 44 represents the water vapor saturation curve of air 14 flowing through air channels 16. As illustrated by line 46, as water vapor is removed from air 14 flowing through air channels 16, the humidity ratio of the outgoing air 14B (i.e., point 48) of the dehumidifying unit 12 of figures 1 to 3 is less than the humidity ratio of the incoming air 14A (that is, point 50 ) inside the dehumidifying unit 12 of figures 1 to 3, while the temperature of the outlet air 14B and the inlet air 14A are substantially the same.
[00044] Returning now to figure 1, as previously described, a lower partial pressure of the water vapor 26 (i.e., a partial pressure lower than the partial pressure of the water vapor in the air channels 16) is created in the air channels water vapor 18 from the dehumidification unit 10 to further facilitate the passage of H2O through the interfaces 20 of the air channels 16 to the water vapor channels 18. In certain embodiments, the water vapor channels 18 can be initially evacuated using a vacuum pump 52. In particular, the vacuum pump 52 can evacuate the water vapor channels 18 and the water vapor vacuum volume 28, in addition to the water vapor outlets 22 and the steam pipe of water 24 of figure 2A. However, in other embodiments, a pump separate from the vacuum pump 52 can be used to evacuate the water vapor channels 18, the water vapor vacuum volume 28, the water vapor outlets 22 and the steam pipe of water 24. As illustrated in figure 1, water vapor 26 removed from the air 14 in the dehumidifying unit 10 can be distinguished between water vapor 26A in the water vapor vacuum volume 28 (that is, the suction pump 52) and water vapor 26B expelled from an exhaust side (i.e., an outlet) of vacuum pump 52 (i.e. water vapor 26B distributed to a condensing unit). In general, the water vapor 26B expelled from the vacuum pump 52 will have a slightly higher pressure and a higher temperature than the water vapor 26A in the water vapor vacuum volume 28. The vacuum pump 52 can be a compressor or any other suitable pressure increasing device capable of maintaining a lower pressure on the suction side of the vacuum pump 52 than the partial pressure of the water vapor in the humid air 14.
[00045] For example, the lower partial pressure of water vapor 26A maintained in the water vapor vacuum volume 28 may be in the range of approximately 1.03 to 1.72 kPa abs (0.15-0.25 psia) , which corresponds to saturation temperatures of approximately 7.2 to 15.6oC (45 to 60oF) with water vapor 26A typically in the range of approximately 18.3 to 23.9oC (65 to 75oF). However, in other embodiments, water vapor 26A in the water vapor vacuum volume 28 can be maintained at a partial water vapor pressure in the range of approximately 0.069 to 0.172 kPa abs (0.01-0.025 psia) and a temperature in the range of approximately 12.78oC (55oF) to the highest ambient air temperature. A specific modality can be designed to reduce the partial pressure in the water vapor vacuum volume 28 to the 0.069 kPa abs (0.01 psia) range to increase the water vapor removal capacity from the air 14 to allow a evaporative cooler process the entire air conditioning load when atmospheric conditions allow this mode of operation.
[00046] In certain embodiments, the vacuum pump 52 is a low pressure pump configured to reduce the water vapor pressure 26A in the water vapor vacuum volume 28 to a partial pressure lower than the water vapor partial pressure in the atmospheric side of interfaces 20 (i.e., partial pressure of air 14 in air channels 16). On the exhaust side of the vacuum pump 52, the partial pressure of water vapor 26B was increased enough to facilitate condensation of water vapor (i.e., in a condensing unit 54). In fact, the vacuum pump 52 is configured to increase the pressure so that the water vapor 26B in the condensing unit 54 is at a pressure close to a minimum saturation pressure in the condensing unit 54.
[00047] As an example, when in operation, air 14 can enter the system at a partial water vapor pressure of 2.21 kPa abs (0.32 psia), which corresponds to a moisture ratio of 0.014 pounds of H2O per pound of dry air. The system can be configured to remove 0.005 pounds of H2O per pound of dry air from air 14. Pressure differentials through interfaces 20 can be used to create a flow of H2O through interfaces 20. For example, partial vapor pressure of water in the water vapor vacuum volume 28 can be determined to approximately 0.69 kPa abs (0.1 psia). The pressure of the water vapor 26B is increased by the vacuum pump 52 in a basically adiabatic process, and as the pressure of the water vapor 26B increases, the temperature also increases (in contrast to the relatively negligible temperature differential across the interfaces 20). As such, if, for example, the water vapor pressure 26B is increased in the vacuum pump 52 by 2.2 kPa (0.32 psi) (ie, approximately 2.76 kPa abs (0.4 psia), condensing unit 54 is then able to condense water vapor 26B at a temperature of approximately 22.2 to 22.8 ° C (72 to 73oF), and the temperature of water vapor 26B will be increased to a substantially higher temperature than the condenser temperature. The system can continuously monitor the pressure and temperature conditions of both the upstream water vapor 26A and the downstream water vapor 26B to ensure that the 26B water vapor is expelled from the vacuum pump 52 has a partial pressure of water vapor high enough to facilitate condensation in the condensing unit 54. It should be noted that the pressure and temperature values presented in this situation are merely illustrative and should not be limiting.
[00048] It is noted that as the pressure difference of water vapor 26A entering the vacuum pump 52 to water vapor 26B leaving the vacuum pump 52 increases, the efficiency of the dehumidifying unit 10 decreases. For example, in a preferred embodiment, the vacuum pump 32 will be configured to adjust the water vapor pressure 26B in the condensing unit 54 just above the saturation pressure at the lowest ambient temperature of the cooling medium (ie, air or water) used by condensing unit 54 to condense water vapor 26B. In another embodiment, the temperature of the water vapor 26B can be used to control the pressure in the condensing unit 54. The temperature of the water vapor 26B expelled from the vacuum pump 52 can be substantially higher than the humid air 14A (for example , this temperature can reach 93.3 ° C (200oF) or above depending on a variety of factors). Since the vacuum pump 52 only increases the water vapor pressure 26B to a point where condensation of the water vapor 26B is facilitated (that is, approximately the saturation pressure), the energy requirements of the vacuum pump 52 as relatively small, thus obtaining a high efficiency of the dehumidification unit 10.
[00049] Since the water vapor 26B has been slightly pressurized (i.e., compressed) by the vacuum pump 52, the water vapor 26B is directed into the condensing unit 54, where the water vapor 26B is condensed into a liquid state. In certain embodiments, the condensing unit 54 may include a condensing coil 56, a tube-type condenser, a flat plate-type condenser, or any other system suitable for causing a temperature below the dew point of water vapor 26B. Condenser unit 54 can be air-cooled or water-cooled. For example, in certain embodiments, condenser unit 54 can be cooled by ambient air or water from a cooling tower. As such, the operating costs of the condensing unit 54 can be relatively low, as both ambient air and water from the cooling tower exist in relatively unlimited supplies.
[00050] Once the water vapor 26B has been condensed into a liquid state, in certain embodiments, the liquid water from the condensing unit 54 can be directed into a reservoir 58 for the temporary storage of saturated steam and water in the state liquid. However, in other embodiments, no reservoir 58 can be used. In any case, the liquid water from the condensing unit 54 can be directed to a liquid pump 60 (ie, a water transport device), within which the liquid water pressure from the condensing unit condensation 54 is increased to approximately atmospheric pressure (ie approximately 101.35 kPa abs (14.7 psia) so that liquid water can be discarded under ambient conditions. As such, liquid pump 60 can be sized as enough to increase the liquid water pressure from the condensing unit 54 to near atmospheric pressure, therefore the operating costs of the liquid pump 60 can be relatively low. Additionally, the liquid water of the liquid pump 60 may be at a slightly elevated temperature due to the increase in liquid water pressure. As such, in certain embodiments, heated liquid water can be transported for use as a domestic hot water, further increasing the efficiency of the system by recapture the heat transferred into the liquid water.
[00051] Although the interfaces 20 between air channels 16 and water vapor channels 18 as previously described generally allow only H2O to pass from air channels 16 to water vapor channels 18, in certain modalities, quantities very small (eg less than 1% oxygen (O2), nitrogen (N2), or other non-condensable components) from other components 30 of air 14 can pass through interfaces 20 from air channels 16 to channels water vapor 18. Over time, the amount of other components 30 can accumulate in water vapor channels 18 (in addition to the water vapor vacuum volume 28, water vapor outlets 22, and water vapor tubing). water 24 of figure 2A). In general, these other components 30 are non-condensable in the condenser temperature ranges used in the condensing unit 54. As such, components 30 can adversely affect the performance of the vacuum pump 52 and all other equipment downstream of the vacuum pump. vacuum 52 (in particular, in condensing unit 54).
[00052] Accordingly, in certain embodiments, a second vacuum pump can be used to periodically purge the other components 30 from the water vapor vacuum volume 28. Figure 6 is a schematic diagram of the HVAC system 8 and the dehumidifying unit 10 and one or more evaporative cooling units 12 of figure 1 having a vacuum pump 62 for removing non-condensable components 30 from water vapor 26A in the water vapor vacuum volume 28 of dehumidifying unit 10 according to an embodiment of the present description. The vacuum pump 62 may, in certain embodiments, be the same pump used to evacuate the water vapor vacuum volume 28 (in addition to the water vapor channels 18, the water vapor outlets 22 and the steam pipe 24) to create the lower partial pressure of the water vapor previously described which facilitates the passage of H2O through the interfaces 20 of the air channels 16 to the water vapor channels 18. However, in other embodiments, the water pump vacuum 62 may be different from the pump used to evacuate the water vapor vacuum volume 28 to create the lower partial pressure of the water vapor.
[00053] The dehumidification unit 10 described here can also be controlled between various operating states, and modulated based on the operating conditions of the dehumidification unit 10. For example, figure 7 is a schematic diagram of the HVAC system 8 and the dehumidification unit. dehumidification 10 and one or more evaporative cooling units 12 of figure 6 having a control system 64 to control various operating conditions of the HVAC system 8 and dehumidification unit 10 and one or more evaporative cooling units 12 according to a modality of the present description. The control system 64 may include one or more processors 66, for example, one or more "general purpose" microprocessors, one or more special purpose microprocessors and / or ASIC (application specific integrated circuit), or some combination of such processing components. Processors 66 can use input and output (I / O) devices 68 to, for example, receive signals from and output control signals to the components of dehumidification unit 10 (i.e., vacuum pumps 52, 62 , condensing unit 54, reservoir 58, liquid pump 60, other equipment such as a fan blowing inlet air 14A through dehumidifying unit 10, sensors configured to generate signals related to inlet and outlet air characteristics 14A, 14B, and so on) and one or more evaporative cooling units 12. Processors 66 can consider these signals as inputs and calculate how to control the functionality of these dehumidification unit components 10 and one or more evaporative cooling units 12 to cool the air 14 more efficiently while also removing water vapor 26 from the air 14 flowing through the dehumidifying unit 10. The control system l and 64 can also include a non-transitory computer-readable medium (i.e., a memory 70) which, for example, can store instructions or data to be processed by one or more processors 66 of the control system 64.
[00054] For example, the control system 64 can be configured to control the rate of removal of the non-condensable components 30 of the water vapor 26A from the water vapor vacuum volume 28 of the dehumidifying unit 10 by turning on or off the vacuum pump 62, or by modulating the rate at which vacuum pump 62 removes non-condensable components 30 from water vapor 26A. More specifically, in certain embodiments, the control system 64 can receive signals from a sensor in the water vapor vacuum volume 28 which detects when many non-condensable components 30 are present in the water vapor 26A contained in the water vapor vacuum volume. water 28. This process of removing non-condensable components will operate cyclically. In "normal" operation to remove water vapor 26 from air 14, vacuum pump 62 will not be in operation. As the non-condensable components 30 accumulate in the water vapor vacuum volume 28, the internal pressure in the water vapor vacuum volume 28 will eventually reach a set point. At that time, vacuum pump 62 will turn on and remove all components (ie, both non-condensable components 30 in addition to H2O including water vapor) until the internal pressure in the water vapor vacuum volume 28 reaches another point (for example, lower than the initial vacuum pressure). Then, the vacuum pump 62 shuts down and the dehumidifying unit 10 returns to normal operating mode. The set points can be predetermined or determined dynamically. A preferred method will need to have the vacuum pump 62 only operating in the purge mode. intermittent.
[00055] Another example of the type of control that can be performed by the control system 64 is the modulation of the lower partial pressure of the water vapor 26A in the water vapor vacuum volume 28 (in addition to the water vapor channels 18, outlets steam water 22, and water steam tubing 24) to modify the water vapor removal capacity and efficiency ratio of the dehumidification unit 10. For example, the control system 64 can receive signals from the pressure sensors in the water vapor vacuum volume 28, water vapor channels 18, o = water vapor outlets 22, and / or water vapor pipe 24, in addition to signals generated by the sensors referring to the characteristic ( for example, temperature, pressure, flow rate, relative humidity and so on) of the inlet and outlet air 14A, 14B, among other things. Control system 64 can use this information to determine how to modulate the lower partial pressure of water vapor 26A (for example, with respect to the partial pressure of water vapor in air 14 flowing through air channels 16) to increase or decrease the rate of removal of water vapor 26 from air channels 16 to water vapor channels 18 through interfaces 20.
[00056] For example, if greater removal of water vapor is desired, the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 can be reduced and, conversely, if less water vapor removal is desired, the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 can be increased. In addition, in certain embodiments, the amount of dehumidification (ie, removal of water vapor) can be recycled to improve the efficiency of the dehumidifying unit 10. More specifically, under certain operating conditions, the dehumidifying unit 10 can function more efficiently at higher rates of water vapor removal. As such, in certain embodiments, the dehumidifying unit 10 can be recycled to remove a maximum amount of water vapor from the air 14 for a while, then to remove relatively no water vapor from the air 14 for a while, then to remove a maximum amount of water vapor from the air 14 for a while, and so on. In other words, the dehumidifying unit 10 can be operated with full water vapor removal capacity for periods of time alternating with other periods of time where no water vapor is removed. In addition, the control system 64 can be configured to control the startup and shutdown sequencing of the dehumidifying unit 10.
[00057] Dehumidification unit 10 and evaporative cooling units 12 can be designed and operated in many of the various modes and operating conditions. In general, the dehumidifying unit 10 will be operated with a water vapor vacuum volume 28 (in addition to water vapor channels 18, water vapor outlets 22, and water vapor piping 24) at a partial vapor pressure of water below the partial pressure of water vapor from the air 14 flowing through the steam channels 18, the water vapor outlets 22, and the water vapor pipe 24 at a partial pressure of water vapor below the partial pressure of water vapor from air 14 flowing through air channels 16. In certain embodiments, the dehumidifying unit 10 and evaporative cooling units 12 can be optimized for use with the dedicated external air system (DOAS), where air 14 it can have a temperature in the range of approximately 12.78 ° C to 37.78 ° C, and a relative humidity in the range of approximately 55 to 100%. In other embodiments, the dehumidifying unit 10 and evaporative cooling units 12 can be optimized for residential use for recirculated air having a temperature in the range of approximately 21.11 to 29.44 C, and a relative humidity in the range of approximately 55 to 65%. Similarly, in certain embodiments, the dehumidifying unit 10 and evaporative cooling units 12 can be optimized to dehumidify the external air in recirculated air systems in commercial buildings, which dehumidifies the incoming air 14A having a temperature in the range from approximately 12.78 to 43.33 ° C, and a relative humidity in the range of approximately 55 to 100%. The outlet air 14B has less humidity and about the same temperature as the inlet air 14A, unless cooling is performed on the outlet air 14B.
[00058] The dehumidification unit 10 described here requires less operating energy than conventional dehumidification systems due to the relatively low pressures that are required to dehumidify the air 14A. This is due at least in part to the ability of interfaces 20 (i.e., water vapor permeable membranes) to remove water vapor 26 from air 14 efficiently without requiring excessive pressure to force water vapor 26 through the interfaces 20. For example, in one embodiment, the minimum energy required to operate the dehumidifying unit 10 includes only the fan energy necessary to move the air 14 through the dehumidifying unit 10, the compression energy of the vacuum pump 52 to compress water vapor 26 to approximately saturation pressure (for example, to approximately 6.89 kPa abs * (1.0 psia), or to a saturation pressure that corresponds to a determined condensation temperature, for example example, approximately 37.78 ° C (100oF), the pumping and / or fan energy of the condensing unit 54 (for example, depending on whether water from the cooling tower or ambient air is used as a cooling medium) , the en pumping lift of the liquid pump 60 to reject the liquid water from the condensing unit 54 under ambient conditions, and the power of the vacuum pump 62 to purge the non-condensable components 30 that leak into the vacuum volume of vapor water 28 from dehumidification unit 10. As such, the only relative main energy component required to operate dehumidification unit 10 is the compression energy of vacuum pump 52 to compress water vapor 26 to approximately saturation pressure ( for example, only for approximately 0.07 bar, or for a saturation pressure that corresponds to a certain condensing temperature, for example, approximately 37.78 ° C (100oF). As mentioned earlier, this energy is relatively low and therefore the operation of the dehumidification unit 10 is relatively inexpensive as opposed to conventional refrigeration compression dehumidification systems. Furthermore, the calculations for a modality indicate that the dehumidification unit 10 has a performance coefficient (COP) at least twice (or even five times, depending on operational conditions) than these conventional dehumidification systems. In addition, the dehumidifying unit 10 allows dehumidification of the air without reducing the temperature of the air below the temperature at which the air is needed, and is often done in conventional dehumidification systems.
[00059] In certain embodiments, as previously indicated, the dehumidification unit 10 described in relation to figures 1 to 7, can be used in conjunction with one or more evaporative cooling units 12. For example, figure 8 is a diagram schematic of an HVAC system 72 having an evaporative cooling unit 74 arranged upstream of the dehumidifying unit 10 according to an embodiment of the present description. The HVAC 72 system in figure 8 generally works the same as the HVAC 8 system in figures 1, 6 and 7. However, as shown in figure 8, the HVAC 72 system specifically includes the evaporative cooling unit 74 arranged upstream of the cooling unit. Dehumidification 10. In this way, the HVAC 72 system first receives the relatively humid inlet air 14A in the evaporative cooling unit 74, instead of the dehumidification unit 10. The evaporative cooling unit 74 reduces the air temperature of relatively humid inlet 14A and expels the cooler (but still relatively humid) air 14B, which is directed into the dehumidifying unit 10 through a duct 76. As previously described, the cooler (but still relatively humid) air 14B is then dehumidified in the dehumidification unit 10 and expelled as relatively dry air 14C into the conditioned space.
[00060] The evaporative cooling unit 74 of figure 8 can be a direct evaporative cooling unit or an indirect evaporative cooling unit. In other words, when the evaporative cooling unit 74 uses direct evaporative cooling techniques, a relatively cold and wet medium 78 (e.g., relatively slow water) is added directly to the relatively humid inlet air 14A. However, when the evaporative cooling unit 74 uses indirect evaporative cooling techniques, the relatively humid air 14A can, for example, flow through one side of a heat exchanger plate while the relatively cold and wet medium 78 flows through the other side of the heat exchanger plate. In other words, in general terms, part of the relatively cold humidity of the relatively cold and wet medium 78 is indirectly added to the relatively humid air 14A. Whether direct or indirect evaporative cooling techniques are used in the evaporative cooling unit 74 and affect the rate of moisture removal and temperature reduction of the air 14 flowing through the HVAC 72 system in figure 8. In general, however , the evaporative cooling unit 74 of figure 8 initially cools to r 14 to a temperature as low as possible for the particular application, and the dehumidifying unit 10 reduces the humidity ratio at approximately constant temperature.
[00061] As illustrated, many of the components of the HVAC 72 system in figure 8 can be considered identical to the components of the HVAC 8 system in figures 1, 6 and 7. For example, as previously described, the HVAC 72 system in figure 8 includes the condensing unit 54 which receives water vapor 26B having a partial pressure high enough to facilitate condensation, as previously described. In certain embodiments, the HVAC system 72 of figure 8 may also include the reservoir 58 for the temporary storage of saturated steam and liquid water. However, as previously described, in other embodiments, no reservoir can be used. In any case, the liquid water of the condensing unit 54 can be directed into the liquid pump 60, within which the pressure of the liquid water of the condensing unit 54 is increased to approximately the atmospheric pressure ( that is, approximately 101.35 kPa abs * (14.7 psia) so that liquid water can be discarded under ambient conditions.
[00062] Additionally, the control system 64 of figure 7 can also be used in the HVAC 72 system of figure 8 to control the operation of the HVAC 72 system in a similar way to that previously described with respect to figure 7. For example, as described previously, the control system 64 can be configured to control the rate of removal of non-condensable components 30 from the water vapor 26A in the water vapor vacuum volume 28 by turning the vacuum pump 52 (or separate vacuum pump 62 on or off) ), or by modulating the rate at which vacuum pump 52 (or separate vacuum pump 62) removes non-condensable components 30. More specifically, in certain embodiments, control system 64 can receive signals from sensors in the vacuum volume water vapor 28 which detects when many non-condensable components 30 are present in water vapor 26A contained in the water vapor vacuum volume 28.
[00063] Additionally, the control system 64 can modulate the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 to modify the water vapor removal capacity and the efficiency ratio of the dehumidification unit 10 For example, the control system 64 can receive signals from the pressure sensors in the water vapor vacuum volume 28, water vapor channels 18, as well as signals generated by the sensors regarding the characteristics (for example, temperature, pressure, flow rate, relative humidity and so on) of the air 14 in the evaporative cooling unit 74, the dehumidifying unit 10, or both, among other things.
[00064] The control system 64 can use this information to determine how to modulate the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 to increase or reduce the rate of water vapor removal 26 from the water channels. air 16 to the water vapor channels 18 through the interfaces 20 of the dehumidification unit 10 as H2O (ie water molecules, gaseous water vapor, liquid water, adsorbed / desorbed water molecules, water molecules absorbed / desorbed water, and so on, through interfaces 20). For example, if greater water vapor removal is desired, the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 may be reduced and, conversely, if less water vapor removal is desired, the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 can be increased. In addition, as described above, the amount of dehumidification (i.e., removal of water vapor) can be recycled to improve the efficiency of the dehumidifying unit 10. More specifically, under certain operating conditions, the dehumidifying unit 10 can operate more efficiently. at higher rates of water vapor removal. As such, in certain embodiments, the dehumidifying unit 10 can be recycled to remove a maximum amount of water vapor from the air 14 for a while, then to remove relatively no water vapor from the air 14 for a time, then to remove a maximum amount of water vapor from the air 14 for a while, and so on. In other words, the dehumidifying unit 10 can be operated with full water vapor removal capability for periods of time alternating with other periods of time where no water vapor is removed.
[00065] Additionally, the control system 64 can also be configured to control the operation of the evaporative cooling unit 74. For example, the control system 64 can selectively modulate how much evaporative cooling (direct or indirect) occurs in the cooling unit. evaporative cooling 74. As an example, the valves can be operated to control the flow rate of the relatively cold and wet medium 78 through the evaporative cooling unit 74, thus directly affecting the amount of evaporative cooling (direct or indirect) in the evaporative cooling unit 74. In addition, the operation of the evaporative cooling unit 74 and the dehumidifying unit 10 can be controlled simultaneously. In addition, the control system 64 can be configured to control the startup and shutdown sequencing of the evaporative cooling unit 74 and the dehumidifying unit 10.
[00066] Figures 9A and 9B are psychrometric graphs 80, 82 of the air temperature and humidity ratio 14 flowing through the evaporative cooling unit 74 and the dehumidifying unit 10 of figure 8 according to an embodiment of the present description. More specifically, figure 9A is the psychrometric graph 80 of the air temperature and humidity ratio 14 flowing through an evaporative cooling unit 74 and dehumidification unit 10 of figure 8 according to an embodiment of the present description, and figure 9B is a psychrometric graph 82 of the air temperature and humidity ratio 14 flowing through an indirect evaporative cooling unit 74 and the dehumidifying unit 10 of figure 8 according to an embodiment of the present description. In particular, in each graph 80, 82, the geometric axis x 84 corresponds to the temperature of the air 14 flowing through the evaporative cooling unit 74 and the dehumidifying unit 10 in figure 8, the geometric axis y 86 corresponds to the humidity ratio. of the air 14 flowing through the evaporative cooling unit 74 and the dehumidifying unit 10 of figure 8, and curve 88 represents the water vapor saturation curve for a given relative humidity of air 14 flowing through the air unit. evaporative cooling 74 and dehumidifying unit 10 in figure 8.
[00067] As illustrated by line 90 in figure 9A, since the relatively cold and wet medium 78 is directly introduced into the air 14 flowing through the direct evaporative cooling unit 74, the air humidity ratio 14B (ie point 92) leaving the direct evaporative cooling unit 74 is substantially greater than the moisture ratio of the incoming air 14A (ie, point 94) entering the direct evaporating cooling unit 74. However, the temperature of the air 14B (ie, point 92) out of the direct evaporative cooling unit 74 is substantially lower than the temperature of the inlet air 14A (ie point 94) that enters the evaporative cooling unit 74. As illustrated in line 96 of figure 9A, since water vapor 26 is removed from the air 14B flowing through the dehumidifying unit 10, the moisture ratio of the outgoing air 14C (i.e., point 98) from the dehumidifying unit 10 is less than the air humidity ratio 14B (i.e., point 92) into the dehumidifying unit 10, while the temperature of the outlet air 14C and the air 14B are substantially the same. In fact, the direct evaporative cooling unit 74 moistens and cools the air 14, while the dehumidifying unit 10 subsequently dehumidifies the air 14 at a substantially constant temperature.
[00068] As illustrated by line 100 in figure 9B, since the relatively cold and wet medium 78 indirectly cools the air 14 flowing through the indirect evaporative cooling unit 74, the air humidity ratio 14B (ie, point 102) out of the indirect evaporative cooling unit 74 is substantially equal to the moisture ratio of the incoming air 14A (i.e., point 104) into the indirect evaporative cooling unit 74. However, the air temperature 14B (i.e., point 102) out of the indirect evaporative cooling unit 74 is substantially lower than the inlet air temperature 14A (i.e. point 104) into the indirect evaporative cooling unit 74. As illustrated along line 106 of figure 9B, since water vapor 26 is removed from the air 14B flowing through the dehumidifying unit 10, the moisture ratio of the outlet air 14C (i.e., point 108) from the dehumidifying unit 10 is less than r moisture content of the air 14B (i.e., point 102) into the dehumidifying unit 10, while the temperature of the outlet air 14C and the air 14B are substantially the same. In fact, the indirect evaporative cooling unit 74 cools (without significantly humidifying) the air 14, while the dehumidifying unit 10 subsequently dehumidifies the air 14 at substantially constant temperature.
[00069] As previously described, the control system 64 of figure 8 can be configured to control the operation of the evaporative cooling unit 74 and the dehumidification unit 10. For example, the control system 64 can be configured to adjust where points 92, 94, 98, and points 102, 104, 108 of air 14 are found in psychrometric graphs 80, 82 of figures 9A and 9B when direct and indirect evaporation cooling techniques, respectively, are used in the cooling unit by evaporation 74 of figure 8.
[00070] Figure 10 is a schematic diagram of an HVAC system 110 having evaporative cooling unit 74 disposed downstream of dehumidification unit 10 according to an embodiment of the present description. The HVAC 110 system in figure 10 generally works the same as the HVAC system 8 in figures 1, 6 and 7 and HVAC 72 in figure 8. However, as illustrated in figure 10, the HVAC 110 system first receives the relatively humid inlet air. 14A in dehumidification unit 10. As previously described, the relatively humid inlet air 14A is first dehumidified in dehumidification unit 10 and expelled as relatively dry air 14B into the duct 76. The evaporative cooling unit 74 then reduces the dry air temperature 14B and expels the cooler dry air 14C into the conditioned space.
[00071] As previously described with reference to figure 8, the evaporative cooling unit 74 of figure 10 can be a direct evaporative cooling unit or an indirect evaporative cooling unit. In other words, when the evaporative cooling unit 74 uses direct evaporative cooling techniques, the relatively cold and wet medium 78 (for example, relatively cold water) is directly added to the relatively dry air 14B in duct 76. However, when the evaporative cooling unit 74 uses indirect evaporation cooling techniques, the relatively dry air 14B can, for example, flow through one side of a heat exchanger plate while the relatively cold and wet medium 78 flows through the other side of the heat exchanger plate. In other words, in general terms, part of the relatively cold humidity of the relatively cold and wet medium 78 is indirectly added to the relatively dry air 14B in the duct 76. Whether direct or indirect evaporative cooling techniques are used in the evaporative cooling unit 74 and affect the rate of moisture removal and temperature reduction of the air 14 flowing through the HVAC system 110 of figure 10. In general, however, the dehumidification unit 10 initially reduces the humidity ratio to approximately constant temperature, and the evaporative cooling unit 74 cools the air 14 to as low a temperature as possible for the particular application.
[00072] As illustrated, many of the components of the HVAC system 110 in figure 10 can be considered identical to the components of the HVAC system 8 in figures 1, 6 and 7 and the HVAC system 72 in figure 8. For example, as previously described, the The HVAC system 110 of Figure 10 includes a condensing unit 54 that receives water vapor 26B having a partial pressure sufficient to facilitate condensation, as previously described. In certain embodiments, the HVAC 110 system of figure 10 may also include reservoir 58 for the temporary storage of saturated steam and liquid water. However, as previously described, in other modalities, no reservoir was used. In any case, the liquid water of the condensing unit 54 can be directed into the liquid pump 60, within which the pressure of the liquid water of the condensing unit 54 is increased to approximately atmospheric pressure (i.e. approximately 101.35 kpa abs * (14.7 psia) so that liquid water can be discarded under ambient conditions.
[00073] Additionally, the control system 64 of figures 7 and 8 can also be used in the HVAC 110 system of figure 10 to control the operation of the HVAC 110 system in a similar way to that previously described with respect to figures 7 and 8. For example , as previously described, the control system 64 can be configured to control the rate of removal of non-condensable components 30 from the water vapor 26A in the water vapor vacuum volume 28 by turning the vacuum pump 52 (or separate vacuum 62), by modulating the rate at which vacuum pump 52 (or separate vacuum pump 62) removes non-condensable components 30. More specifically, in certain embodiments, control system 64 can receive signals from sensors in the volume water vapor vacuum 28 which detects when many non-condensable components 30 are present in water vapor 26A contained in the water vapor vacuum volume 28.
[00074] Additionally, the control system 64 can modulate the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 to modify the water vapor removal capacity and efficiency ratio of the dehumidification unit 10. For example, the control system 64 can receive signals from the pressure sensors in the water vapor vacuum volume 28, water vapor channels 18, in addition to signals generated by the sensors regarding the characteristics (eg temperature, pressure, rate flow, relative humidity and so on) of air 14 in dehumidifying unit 10, evaporative cooling unit 74, or both, among other things.
[00075] Control system 64 can use this information to determine how to modulate the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 to increase or decrease the rate of water vapor removal 26 from the air channels 16 to water vapor channels 18 through interfaces 20 of the dehumidifying unit 10 as H2O (ie atomic water, gaseous water vapor, liquid water, and so on, adsorbed or absorbed through interfaces 20). For example, if more water vapor removal is desired, the lower partial pressure of water vapor 26A in the water vapor vacuum volume 28 can be reduced and, conversely, if less water vapor removal is desired, the pressure lower partial of water vapor 26A in the water vapor vacuum volume 28 can be increased. In addition, as described above, the amount of dehumidification (i.e., removal of water vapor) can be recycled to improve the efficiency of the dehumidifying unit 10. More specifically, under certain operational conditions, the dehumidifying unit 10 can function in a way more efficient at higher rates of water vapor removal. As such, in certain embodiments, the dehumidifying unit 10 can be recycled to remove a maximum amount of water vapor from the air 14 for a while, then to remove relatively no water vapor from the air 14 for a time, then to remove a maximum amount of water vapor from the air 14 for a while, and so on. In other words, the dehumidifying unit 10 can be operated with a total water vapor removal capability for periods of time alternating with other periods of time where no water vapor is removed.
[00076] Additionally, the control system 64 can also be configured to control the operation of the evaporative cooling unit 74. For example, the control system 64 can selectively modulate how much evaporative cooling (direct or indirect) occurs in the cooling unit. evaporative cooling 74. As an example, the valves can be operated to control the flow rate of the relatively river and wet medium 78 through the evaporative cooling unit 74, thus directly affecting the amount of evaporative cooling (direct or indirect) ) in the evaporative cooling unit 74. In addition, the operation of the dehumidifying unit 10 and the evaporative cooling unit 74 can be controlled simultaneously. In addition, the control system 64 can be configured to control the startup and shutdown sequencing of the dehumidifying unit 10 and evaporative cooling unit 74.
[00077] Figures 11A and 11B are psychrometric graphs 112, 114 of the air temperature and humidity ratio 14 flowing through a dehumidification unit 10 and the evaporative cooling unit 74 of figure 10 according to an embodiment of the present description. . More specifically, figure 11A is the psychrometric graph 112 of the temperature and air humidity ratio 14 flowing through the dehumidification unit 10 and a direct evaporative cooling unit 74 of figure 10 according to an embodiment of the present description, and the figure 11B is the psychrometric graph 114 of the air temperature and humidity ratio 14 flowing through the dehumidification unit 10 and an indirect evaporative cooling unit 74 of figure 10 according to an embodiment of the present description. In particular, as previously described with reference to figures 9A and 9B, the geometric axis x 84 corresponds to the air temperature 14 flowing through the dehumidifying unit 10 and the evaporative cooling unit 74 of figure 10, the geometric axis y 86 corresponds to the humidity ratio of the air 14 flowing through the dehumidifying unit 10 and the evaporative cooling unit 74 of figure 10, and curve 88 represents the water vapor saturation curve for a given relative humidity of the air 14 flowing through the dehumidification unit 10 and evaporative cooling unit 74 in figure 10.
[00078] As illustrated by line 116 in figure 11A, since water vapor 26 is removed from the relatively humid inlet air 14A flowing through the dehumidifying unit 10, the relative humidity ratio of the relatively dry air 14B (ie point 118) from the dehumidifying unit 10 is less than the humidity ratio of the relatively humid inlet air 14A (i.e., point 120) into the dehumidifying unit 10, while the temperature of the relatively dry air 14B and the inlet air relatively wet 14A are substantially the same. As illustrated by line 122 of figure 11A, since the relatively cold and wet medium 78 is directly introduced into the relatively dry air 14B that flows through the direct evaporative cooling unit 74, the moisture ratio of the outgoing air 14C (ie ie, point 124) from the direct evaporative cooling unit 74 is substantially greater than the humidity ratio of the relatively dry air 14B (i.e. point 118) into the direct evaporative cooling unit 74. However, the temperature of the outlet air 14C (i.e., point 124) of the direct evaporative cooling unit 74 is substantially lower than the temperature of the relatively dry air 14B (i.e., point 118) within the evaporative cooling unit direct 74. In fact, the dehumidifying unit 10 dehumidifies the air 14 substantially at constant temperature, while the direct evaporative cooling unit 74 subsequently humidifies and cools the air 14.
[00079] As illustrated by line 126 in figure 11B, since water vapor 26 is removed from the relatively humid inlet air 14A flowing through the dehumidifying unit 10, the relatively dry air humidity ratio 14B (ie point 128) of the dehumidifying unit 10 is less than the humidity ratio of the relatively humid inlet air 14A (i.e., point 130) into the dehumidifying unit 10, while the temperature of the relatively dry air 14B and the relatively wet inlet 14A are substantially the same. As illustrated by line 132 of figure 11B, since the relatively cold and wet medium 78 indirectly cools the relatively dry air 14B flowing through the indirect evaporation cooling unit 74, the moisture ratio of the outgoing air 14C (ie, point 134) of the indirect evaporative cooling unit 74 is substantially equal to the humidity ratio of the relatively dry air 14B (i.e., point 128) into the indirect evaporative cooling unit 74. However, the air temperature of outlet 14C (i.e., point 134) from the indirect evaporative cooling unit 74 is substantially lower than the temperature of the relatively dry air 14B (i.e., point 128) into the indirect evaporative cooling unit 74. In fact, the dehumidifying unit 10 dehumidifies the air 14 substantially at a constant temperature, while the indirect evaporative cooling unit 74 cools (without substantial wetting) the air 14.
[00080] As previously described, the control system 64 of figure 10 can be configured to control the operation of the dehumidification unit 10 and the evaporative cooling unit 74. For example, the control system 64 can be configured to adjust where points 118, 120, 124 and points 128, 130, 134 of air 14 are found in psychrometric graphs 112, 114 of figures 11A and 11B when the direct and indirect evaporation cooling techniques, respectively, are used in the cooling unit by evaporation 74 of figure 10.
[00081] The modalities of HVAC systems 72, 110 of figures 8 and 10 are not the only ways in which dehumidification units 10 can be combined with evaporative cooling units 74. More specifically, whereas figures 8 and 10 illustrate the use of a single dehumidifying unit 10 and a single evaporative cooling unit 4 in series with each other, in other embodiments, any number of dehumidifying units 10 and evaporative cooling units 74 can be used. be used in series with each other. For example, figure 1 illustrates the dehumidifying unit 10 having evaporative cooling units arranged on both sides (that is, both upstream and downstream) of the dehumidifying unit 10. As another example, in one embodiment, a first dehumidifying unit 10 can be followed by a first evaporative cooling unit 74, which is, in turn, followed by a second dehumidifying unit 10, which is in turn followed by a second cooling unit by 74 evaporation, and so on. However, any number of dehumidifying units 10 and evaporative cooling units 74 can actually be used in series with one another, where the air 14 leaving each unit 10, 74 is directed to the next downstream unit 10 , 74 in the series (except for the last unit 10, 74 in the series, from which air 14 is expelled into the conditioned space). In other words, the air 14 leaving each dehumidifying unit 10 in series is directed into an evaporative cooling unit downstream 74 (or to the conditioned space, if it is the last unit in the series) and the air 14 that exits each evaporative cooling unit 74 in the series is directed to a dehumidifying unit downstream 10 (or to the conditioned space, if it is the last unit in the series). As such, the air temperature 14 can be successively reduced in each evaporative cooling unit 74 between the dehumidifying units 10 in the series, and the humidity ratio of the air 14 can be successively reduced in each dehumidifying unit 10 between the units. evaporative cooling unit 74 in the series. This process can be continued within any number of dehumidifying units 10 and evaporative cooling units 74 until the desired final temperature and humidity ratio conditions of air 14 are achieved.
[00082] Figures 12A and 12B are psychrometric graphs 136, 138 of temperature and air humidity ratio 14 flowing through a plurality of dehumidifying units 10 and a plurality of evaporative cooling units 74 according to one embodiment of the present. description. More specifically, Figure 12A is a psychrometric graph 136 of the air temperature and humidity ratio 14 flowing through a plurality of dehumidifying units 10 and a plurality of direct evaporative cooling units 74 according to an embodiment of the present description, and Figure 12B is a psychrometric graph 138 of the air temperature and humidity ratio 14 flowing through a plurality of dehumidifying units 10 and a plurality of indirect evaporative cooling units 74 according to an embodiment of the present description. In particular, in each graph 136, 138, the geometric axis 84 corresponds to the air temperature 14 flowing through the plurality of dehumidifying units 10 and the plurality of evaporative cooling units 74, the geometric axis y 86 corresponds to the humidity ratio of air 14 flowing through the plurality of dehumidifying units 10 and plurality of evaporative cooling units 74, and curve 88 represents the water vapor saturation curve for a given relative humidity of air 14 flowing through the plurality of units of evaporation. dehumidification 10 and plurality of evaporative cooling units 74.
[00083] As illustrated by lines 140 in figure 12A, since water vapor 26 is removed from the relatively humid air 14 flowing through each of the plurality of dehumidifying units 10, the humidity ratio of the air 14 decreases substantially while the air temperature 14 remains substantially the same in each of the plurality of dehumidifying units 10. As illustrated by lines 142 in figure 12A, since the relatively cold and wet medium 78 is directly introduced into the relatively dry air 14 flowing through of each of the direct evaporative cooling units 74, the air humidity ratio 14 increases while the air temperature 14 decreases substantially in each of the plurality of direct evaporative cooling units 74. In other words, each of the the plurality of dehumidifying units 10 successively dehumidifies the air 14 at substantially constant temperature, while each of the pl urality of direct evaporative cooling units 74 humectively successively and cool the air 14 until the desired final conditions of temperature and humidity ratio are reached. More specifically, as illustrated in figure 12A, lines 140, 142 generally form a "step function" progression from the initial temperature and humidity ratio conditions of the inlet air 14 (i.e. point 144) to the final conditions of outlet air temperature and humidity ratio 14 (ie point 146).
[00084] As illustrated by lines 148 in figure 12B, since water vapor 26 is removed from the relatively humid air 14 flowing through each of the plurality of dehumidifying units 10, the humidity ratio donates 14 decreases substantially while the air temperature 14 remains substantially the same in each of the plurality of dehumidifying units 10. As illustrated by lines 150 in figure 12B, since the relatively cold and wet medium 78 interacts indirectly with the relatively dry air 14 flowing through of each of the indirect evaporation cooling units 74, the air humidity ratio 14 remains substantially the same while the air temperature 14 decreases substantially in each of the plurality of indirect evaporation cooling units 74. In other words , each of the plurality of dehumidifying units 10 successively dehumidifies air 14 at substantially constant temperature , while each of the plurality of indirect evaporation cooling units 74 successively cools the air 14 at a substantially constant humidity ratio until the desired final temperature and humidity ratio conditions are achieved. More specifically, as illustrated in figure 12B, lines 148, 150 generally form a "serrated" progression from the initial conditions of the temperature and humidity ratio of the inlet air 14 (ie, point 152) to the final conditions of the ratio temperature and humidity of the outlet air 14 (ie point 154).
[00085] Since evaporative cooling units 74 are used between dehumidification units 10, each dehumidification unit 10 will receive air 14 which is cooler and at a lower partial pressure of water vapor than dehumidification units. - upstream sumidification 10. As such, each of the dehumidification units 10 will operate substantially under different operating conditions. Accordingly, the control system 64 can be used to modulate the operational parameters (for example, the partial pressures of the water vapor in the water vapor vacuum volumes 28, among other things) of the dehumidifying units 10 to take into account variations between dehumidifying units 10. Similarly, since dehumidifying units 10 are used between evaporative cooling units 74, each evaporative cooling unit 74 will also receive air 14 which is cooler and in a lower partial pressure of water vapor than upstream evaporative cooling units 74. As such, each of the evaporative cooling units 74 will also operate under substantially different operating conditions. Accordingly, the control system 64 can also be used to modulate the operational parameters (for example, the flow rates of the relatively cold and wet medium 78, among other things) of the evaporative cooling units 74 to take into account variations between evaporative cooling units 74. In addition, the control system 64 can also simultaneously coordinate the operation of the plurality of dehumidifying units 10 and the plurality of evaporative cooling units 74 to account for variations.
[00086] Evaporative cooling units 74 of figures 8 and 10 are not only used to reduce the temperature of the air 14, but also serve to clean the air 14, for example, by passing the air 14 through a narrow, fibrous air . In addition, dehumidification units 10 and evaporative cooling units 14 can be operated at variable speeds or fixed speeds for optimal operation between the initial temperature different from the humidity conditions (ie, operational points 144 and 152 in figures 12A and 12B, respectively) and the final temperature and humidity conditions (that is, operating points 146 and 154 in figures 12A and 12B, respectively. Additionally, evaporative cooling units 74 are relatively low energy units, thus minimizing costs general operating conditions.
[00087] While the present description may be susceptible to various modifications and alternative forms, specific modalities have been illustrated by way of example in the drawings and tables and have been described in detail here. However, it must be understood that the modalities should not be limited to the particular forms described. Instead, the description should cover all modifications, equivalences, and alternatives that are within the spirit and scope of the description as defined by the claims in the appendix below. In addition, although individual modalities are discussed here, the description must cover all combinations of these modalities.

权利要求:
Claims (21)
[0001]
1. Dehumidification system for removing water vapor from an air stream, characterized by the fact that it comprises: a first and a second channel separated by a membrane, where the membrane is configured to facilitate the removal of water vapor from a airflow flowing through the first channel facilitating the passage of H2O from the water vapor to the second channel through the permeable membrane volumes while substantially blocking the passage of all other components of the airflow through the membrane; a first evaporative cooling unit configured to cool the air stream downstream of the membrane; a second evaporative cooling unit configured to cool the air stream upstream of the membrane; a pressure increase device configured to create a lower partial pressure of water vapor within the second channel than in the first channel, so that H2O moves through the membrane to the second channel, where the pressure increase device is also configured to increase the water vapor pressure at an outlet of the pressure increasing device to a partial pressure of the water vapor in a range suitable for subsequent condensation in liquid water, and a controller configured to control the operations of the dehumidification system , where the controller is configured to control the pressure increase device to increase the water vapor pressure at an outlet of the pressure increase device at a partial water vapor pressure close to a water vapor saturation pressure minimum in a condensing device suitable for subsequent condensation in liquid water.
[0002]
2. System according to claim 1, characterized by the fact that the controller is configured to control a first evaporative cooling phase provided by the first evaporative cooler, a first dehumidification phase provided by the membrane, and a second evaporative cooling phase provided by the second evaporative cooler during operations.
[0003]
3. System according to claim 2, characterized by the fact that the controller is configured to control the operations of the dehumidification system in order to result in a psychrometric graph control of a temperature and humidity ratio of the flowing air stream across the membrane, the psychometric plot control comprising a first angled line resulting from the first evaporative cooling phase and a first descending line resulting from the first dehumidification phase.
[0004]
4. System according to claim 1, characterized by the fact that it comprises a condensing device configured to receive water vapor from the pressure increase device and to condense the water vapor to liquid water.
[0005]
5. System according to claim 4, characterized by the fact that it comprises a water transport device configured to transport liquid water from the condensation device.
[0006]
6. System according to claim 1, characterized by the fact that the membrane comprises zeolite.
[0007]
7. System characterized by the fact that it comprises: a dehumidifying unit to remove the H2O vapor from an air stream comprising: an air channel configured to receive an incoming air stream and discharge an outgoing air stream ; and an H2O permeable material adjacent to the air channel, where the H2O permeable material is configured to selectively allow H2O passage of H2O vapor in the incoming air stream through the H2O permeable material to a suction side of the material permeable to H2O and substantially block the passage of other components in the incoming air stream through the H2O permeable material to the suction side of the H2O permeable material; an evaporative cooling unit configured to cool the air stream; a pressure boosting device configured to create a lower partial pressure of H2O vapor on the suction side of the H2O permeable material than the partial pressure of H2O vapor in the incoming air stream to trigger the passage of H2O from the H2O in the incoming air stream through the H2O permeable material, and to increase the pressure at an outlet of the pressure increasing device to a partial pressure of H2O vapor suitable for condensing the H2O vapor into liquid H2O; and a controller configured to control a first dehumidification phase provided by the H2O-permeable material during operations, wherein the controller is configured to control the pressure increase device to increase the H2O vapor pressure at an output of the increase device pressure at a partial H2O vapor pressure close to a minimum H2O vapor saturation pressure in a condensing device suitable for subsequent condensation into liquid H2O.
[0008]
8. System according to claim 7, characterized by the fact that it comprises a second evaporative cooling unit arranged upstream of the dehumidification unit.
[0009]
9. System, according to claim 7, characterized by the fact that the controller is configured to control a first evaporative cooling phase provided by the first evaporative cooler, and the first dehumidification phase provided by the H2O permeable material during operations in order to result in a psychrometric graph control of a temperature and humidity ratio of the air stream flowing through the membrane, the psychrometric graph control comprising a first angled line resulting from the first evaporative cooling phase and a first descending line resulting from the first dehumidification phase.
[0010]
10. System according to claim 7, characterized by the fact that it comprises a condensing device configured to receive H2O steam from the outlet of the pressure increasing device, and to condense the H2O vapor into liquid H2O.
[0011]
11. System according to claim 10, characterized by the fact that it comprises a liquid pump configured to transport the liquid H2O of the condensing device.
[0012]
12. System according to claim 7, characterized by the fact that the H2O permeable material comprises an H2O permeable membrane.
[0013]
13. System according to claim 7, characterized by the fact that the H2O permeable material comprises zeolite.
[0014]
14. The system according to claim 7, characterized by the fact that the dehumidifying unit is a variable speed dehumidifying unit, and the evaporative cooling unit is a variable speed evaporative cooling unit.
[0015]
15. Method characterized by the fact that it comprises the steps of: receiving an air stream including H2O vapor within an air channel of a dehumidification unit, in which the air stream has a first partial pressure of H2O vapor; cool the air stream through an evaporative cooling unit; suck H2O into a H2O vapor channel of the dehumidification unit through a H2O permeable material from the dehumidification unit using a pressure differential through the H2O permeable material, where the H2O permeable material comprises zeolite and the H2O vapor has a second partial pressure of H2O vapor lower than the first partial pressure of H2O vapor in the air stream; and receiving H2O vapor from the H2O vapor channel within the pressure increasing device and increasing the pressure of the H2O vapor from the pressure increasing device to a third partial pressure of H2O vapor which is greater than the second partial pressure of H2O vapor; and continuously monitor the pressure and temperature conditions of the H2O vapor upstream of the H2O vapor and pressure increase device downstream of the pressure increase device to ensure that the third partial pressure of the H2O vapor is close to a pressure of minimum vapor and H2O saturation in the condensing device and is suitable for subsequent condensation into liquid H2O.
[0016]
16. Method according to claim 15, characterized by the fact that it comprises the step of cooling the air stream through the evaporative cooling unit before directing the air stream into the dehumidifying unit.
[0017]
17. Method, according to claim 15, characterized by the fact that it comprises the step of cooling the air stream through the evaporative cooling unit after receiving the air stream from the dehumidifying unit.
[0018]
18. Method according to claim 15, characterized by the fact that it comprises the step of cooling the air stream through a first evaporative cooling unit before directing the air stream into the dehumidifying unit, and cooling the air flow through a second evaporative cooling unit after receiving the air flow from the dehumidifying unit.
[0019]
19. Method according to claim 15, characterized by the fact that it comprises the step of receiving H2O vapor from the pressure increasing device in a condensing device and condensing the H2O vapor into liquid H2O.
[0020]
20. Method, according to claim 19, characterized by the fact that the air stream has a first partial pressure of H2O vapor in a range of approximately 1.38 to 6.89 kPa abs (0.2 to 1, 0 psia), the second partial pressure of H2O vapor being in a range of approximately 0.69 to 6.89 kPa abs (0.1 to 1.0 psia), and the third partial pressure of H2O vapor being in a range approximately 1.72 to 7.58 kPa abs (0.25 to 1.1 psia).
[0021]
21. System according to claim 3, characterized by the fact that the control of the psychrometric graph comprises a second angled line resulting from the second phase of evaporative cooling.

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同族专利:

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公开号 | 公开日

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WO2012065132A3|2012-08-16|

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EP2638332A2|2013-09-18|

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ES2666769T3|2018-05-07|

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JP2014500793A|2014-01-16|

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WO2012065132A2|2012-05-18|

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EP2638332B1|2018-03-21|

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BR112013011749A2|2017-09-26|

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KR20130103575A|2013-09-23|

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KR101939417B1|2019-01-16|

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EP2638332A4|2014-05-14|

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JP6042341B2|2016-12-14|

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CN103282724A|2013-09-04|

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US8685142B2|2014-04-01|

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US20120117987A1|2012-05-17|

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法律状态:
2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

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2019-12-03| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

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2020-09-24| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2020-12-15| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 11/11/2011, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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US12/945,735|2010-11-12|

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US12/945,735|US8685142B2|2010-11-12|2010-11-12|System and method for efficient air dehumidification and liquid recovery with evaporative cooling|

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PCT/US2011/060479|WO2012065132A2|2010-11-12|2011-11-11|System and method for efficient air dehumidification and liquid recovery with evaporative cooling|

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