Air filter device

Abstract

To enhance the flexibility, economy, power- and size-efficiency and noise reduction in air filtering and ventilation design.SOLUTION: An air filter device comprises: one or more pleated air filters where the pleated air filters are cylindrical and designed according to the relation Gu=fhPr / (2roε0.25)>0.8; and a motor for rotating the pleated air filters, where pr=(ro-ri) / ps, ro=outer radius of the cylindrical pleated filter, fh=height of the cylindrical filter, ri=inner radius of the cylindrical pleated filter, ps=distance between two adjacent pleat tops on the inner radius, and ε=ASHRAE efficiency.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] [1] This invention relates to air purification. Specifically, it relates to air filter construction, assembly and operation, and methods for reducing noise and power consumption without compromising flow rate and filter efficiency. [Background technology]

[0002] [2] Devices for improving air quality are traditionally made by feeding air through a filter. The performance of an air purifier is measured by the air flow rate (m 3 The product of these two parameters is known as the Clean Air Delivery Rate (CADR). Another important parameter is noise. Noise is generated primarily when air passes through rotating fan blades and when high-velocity air impinges on sharp edges. Equipment designs are typically optimized for fan efficiency, flow throughput, filtration or filter efficiency, manufacturing cost, space occupancy, and noise emissions. These characteristics are often in conflict, and compromises must be made. Noise is a critical parameter when equipment is operating indoors or near people, and the requirement for low noise directly conflicts with the product's filtering performance.

[0003] [3] Another important issue is that the efficiency of traditional air fan units rarely exceeds 50%, which has a serious impact on filtering power consumption and noise. Filters require frequent replacement, and there is a cost balance between the pressure buildup that increases fan power consumption to maintain flow and the cost of replacing filters. Dealing with noise is also a major issue in ventilation, and noise dampers in ventilation systems also require space.

[0004] [4] In view of this situation, the present invention provides a means for filtering a sufficient amount of air while occupying a small space, consuming little power and making little noise.

[0005] [5] The present invention reduces the conflict and allows the design of a device that consumes less power, has a higher CADR, and emits less noise than any traditional air purifier of the same size on the market.

[0006] [6] Additionally, reducing the size and noise of filter assemblies and air purification systems opens the door to new, more efficient designs of air purification devices and ventilation systems.

[0007] [7] By reducing the power consumption of filtering systems, the present invention provides an environmentally friendly alternative to those available today.

[0008] [8] By combining current air filtration and purification systems with efficient heat exchange systems, the present invention opens up even greater power savings.

[0009] [9] This invention is based on and claims priority to three earlier patent applications, which are reproduced herein in their entirety, and which are set forth at the end of this specification with the figure reference numbers renumbered by adding 1000 for the first and second priority applications and 2000 for the third priority application, and with the figure reference numbers renumbered accordingly by adding 100 and 200. Summary of the Invention

[0010]

[10] The present invention contributes to improving flexibility, economy, power and size efficiency, and noise reduction in air filtration and ventilation designs. The invention does so by providing an air purification system with one or more rotating pleated filter assemblies, optionally combined with a unique fan and heat exchanger design. Furthermore, the system can be modular, allowing for several filter units arranged in easily replaceable modules typically used in larger installations. The key principle of the invention is that air entering the rotating pleated filter assembly is simultaneously spun and propelled as it is filtered, allowing for increased flow throughput and more compact product designs. Air filtration in the present invention conserves energy, in part by consuming the energy required for filtering while energy is gained through a centrifugal force field with little turbulence loss, and in part by utilizing newly discovered fluid dynamic effects that occur during the spinning of the pleated filter. The present invention contributes to significant improvements in air filter / fan capacity, noise reduction, and many other features, potentially impacting future design strategies related to air purification and ventilation. [Brief explanation of the drawings]

[0011]

[11] In order to facilitate an understanding of the present invention and to illustrate how it may function in practice, non-limiting examples will now be described with reference to the accompanying drawings, in which:

[0012] [Figure 1] 1 shows a first embodiment of a rotary pleated filter. [Figure 2A] 1 shows a cylindrical pleated filter viewed at an oblique angle. [Figure 2B] This is the filter in Figure 2, seen from above with an enlarged view of the pleated portion. [Figure 3A] 1 shows an embodiment of a filter for sealing point mounting. [Figure 3B]3B shows a small cross-sectional portion of the view to illustrate the airflow through the filter of FIG. 3A and the pleated air filter configuration. [Figure 3C] 3B shows the assembly of FIG. 3A with an additional airflow director. [Figure 3D] 3D illustrates airflow around the filter assembly of FIG. 3C. [Figure 3E] 1 is an example of an adjustable rotary air director. [Figure 3F] 1 shows a set of radial impeller blades with a forward angle of attack. [Figure 4A] FIG. 1 shows an exploded view of a filter assembly with an axial radial fan disposed inside the filter. [Figure 4B] 4B illustrates an embodiment of the filter assembly of FIG. 4A. [Figure 4C] FIG. 4C is a perspective view of the filter assembly of FIG. 4B. [Figure 4D] 4C is a cross-section of the filter assembly of FIG. 4B. [Figure 4E] FIG. 4C is a top view of section A-A of FIG. 4B. [Figure 4F] 4B illustrates another embodiment of the filter assembly of FIG. 4A. [Figure 4G] FIG. 4F is a perspective view of the filter assembly of FIG. 4F. [Figure 4H] 4F is a cross section of the filter assembly of FIG. 4F. [Figure 4I] FIG. 10 is a side view of an outer static lamella for controlling the outflow spin field. [Figure 4J] FIG. 4I is a cross-sectional view of the outer static membrane shown in FIG. 4I. [Figure 4K] FIG. 4I is a top view of the outer static membrane shown in FIG. 4I. [Figure 5A] FIG. 1 is a cross-sectional view of the first half of a slightly conical rotary pleated filter with an external air directing foil and air channel sleeve. [Figure 5B] The same as 5A, but from a different viewing angle. [Figure 6]FIG. 1 is a cross-sectional view of a filter with an external air directing foil mounted within a casing, viewed obliquely from the upper right. [Figure 7] This is the same object as in Figure 6, seen from a different angle. [Figure 8] FIG. 1 is a cross-sectional view of a conical pleated filter with an external air directing foil. [Figure 9] 9 shows the object of FIG. 8 as seen from above. [Figure 10] 9 shows the object of FIG. 8 as seen from below. [Figure 11] 1 shows a system combining the four filter assemblies shown in FIGS. 5 to 10. [Figure 12] 1 shows a filter assembly consisting of three radially spaced filters of different diameters. [Figure 13] 1 shows a casing for a filter unit with multiple radially spaced filters including pre-spin impellers. [Figure 14] FIG. 14 is a cross-sectional top view of the filter unit of FIG. 13. [Figure 15] FIG. 14 is a detailed view of the elements of the filter assembly of FIG. 13, without showing the casing wall. [Figure 16] 1 is a cross section of a filter unit located inside a casing, including a radial fan element, air directing foils, and a motor. [Figure 17A] 4A-4K show pressure graphs on the axial-radial impeller and filter when operating in the configuration of FIGS. 4A-4K. [Figure 17B] 4 shows the Gu number values of the filters according to the present invention. [Figure 17C] 10 is a specific case study of performance CADR / L at 35 dB for various Gu for the present invention versus a typical prior art. [Figure 17D] 1 is a specific case study of performance CADR / filter cylinder volume at 35 dB for various Gu for the present invention versus a typical prior art. [Figure 18] The corridor and pillar effects of the pleated filter are shown. [Figure 19] 1 shows pleats in a cylindrical filter in the air passageway. [Figure 20A] Internal view of two pleated filter assemblies positioned in a floor-standing frame. [Figure 20B] Floor-standing assembly with inlet protective vent and static air barrier. [Figure 20C] Floor-standing assembly with inlet protective vent. [Figure 20D] Floor standing assembly with no inlet pre-filter and carbon filter, outlet vent and internal assembly as shown in Figure 20A. [Figure 21A] 10A-10C show front and side views of a single impeller embodiment discharging above a filter assembly. [Figure 21B] 21B shows a cross-sectional view of the embodiment of FIG. 21A. [Figure 21C] 21B shows an exploded view of the filter of FIG. 21A. DETAILED DESCRIPTION OF THE INVENTION

[0013]

[12] In the following description of various embodiments, reference will be made to the drawings in which like reference numerals refer to the same or corresponding elements. The drawings are not necessarily to scale. Indeed, certain features may be exaggerated in scale or shown somewhat simplified or schematic, and certain conventional elements may be omitted so as to illustrate the principles of the invention rather than cluttering the drawings with detail that does not contribute to an understanding of the principles of the invention.

[0014]

[13] Please note that, unless otherwise specified, different features or elements may be combined with each other regardless of whether they are described together as part of the same embodiment below. The combination of features or elements in the exemplary embodiments is done to facilitate understanding of the invention rather than limiting the scope of the invention to a limited set of embodiments, and alternative elements having substantially the same functionality are intended to be interchangeable to the extent shown in each embodiment. For simplicity, no attempt has been made to disclose a complete description of all possible permutations of features.

[0015]

[14] Furthermore, those skilled in the art will understand that the present invention may be practiced without many of the details contained in this detailed description. Conversely, some well-known structures or functions may not be shown or described in detail to avoid unnecessarily obscuring the relevant description of various implementations. The terms used in the specification below are intended to be interpreted in their broadest reasonable manner, even when used in connection with a detailed description of a specific implementation of the present invention.

[0016]

[15] In this specification, the terms "pleated air filter" and "pleated filter" are used as synonyms for the same filter and should generally be understood to mean the same thing unless otherwise specified.

[0017]

[16] This specification defines several sizes and relationships, and although not always explicitly stated, it should be understood that all sizes and quantities are written in SI units.

[0018]

[17] The present invention provides several aspects that can be combined into a system for improved air filtration and ventilation. The first aspect relates to the pleated filter design and the air movement it provides as it rotates about its longitudinal axis.

[0019]

[18] Furthermore, the scope of the present invention is to utilize a combination of several physical phenomena that all improve the most important characteristics of a filter assembly and its operation: low permeability, low power consumption, low noise, and high efficiency. Pleated filters are advantageous because they offer a large filter area. Radially designed pleated filters offer even larger areas due to the small footprint of such a configuration. Furthermore, it has been found that several hydrodynamic effects come into play favorably when the filter media of a pleated filter rotates.

[0020]

[19] One of these previously unreported effects is increased filter efficiency by more effectively capturing particles due to particle acceleration transverse to the flow through the pleated filter media. This effect is more significant for larger particles and therefore more effective for coarser filters.

[0021]

[20] Another of these effects is referred to herein as the "column effect," in which centrifugal force during spinning pulls the entire column of air into the outlet channel, creating a suction at the bottom of the outlet channel. Depending on the pleat detail and media permeability, a spinning pleated filter may experience more uniform pressure on the filter media, which promotes more flow through the deepest parts of the outlet channel, compared to passing air through a static filter assembly. Furthermore, higher flow rates reduce the overall pressure on the filter media, promoting smoother flow. The pressure drop in the inlet channel is not considered, but this is important to understand the overall picture. CFD analysis is used to confirm the expected effect.

[0022]

[21] In this specification, the term "gallery effect" is defined for pleated filters and is explained as follows:

[0023]

[22] In the case of a static pleated filter, air molecules entering the outlet channel perpendicularly are partially accelerated by the high-velocity core flow B, as seen in Figure 18, and then accelerated by the superpressure at the bottom of the outlet channel. Therefore, the resulting increased pressure compared to that in the parallel flow condition is assumed to be the corridor effect. This effect has been confirmed by CFD simulations. Although it is difficult to distinguish this effect from the corridor effect when the pleated filter 2 is spinning, it is assumed that in the case of a spinning pleated filter, the centrifugal force pulls / accelerates the newly supplied air molecules A along with the air column, so the air velocity in the outlet channel core may decrease somewhat for the same amount of air exiting. The corridor effect is then reduced, resulting in a more uniform velocity profile at the outlet and a reduced pressure drop in the outlet channel. Efficiency is enhanced by reduced viscous losses and kinetic energy losses in the outlet jet. The corridor effect becomes very important when the outlet channel is wide, the media permeability is low, and the filter media velocity is high.

[0024]

[23] Suction instability effect: Air leaves the rotating cylindrical pleated filter 2 with energy that causes instability. Because of the suction force associated with the rotating outlet flow 39, this suction force draws ambient air longitudinally from the outside of the pleated filter 2, from the sides toward the longitudinal center of the pleated filter. This results in the rotating air being refocused to the center by the subsequent increase in suction force at this center. Therefore, when the filter has two openings, the excess amount of incoming air 33 finds it easier to move toward the center rather than distribute evenly across the pleats longitudinally, which is preferable for optimal filter function. To recover the kinetic energy of the rotating outgoing air for the purposes of pressurizing and ensuring even distribution, the present invention adds air barriers / end ledges 35, 36, seen in Figures 3A and 3B. The ledges 35, 36 prevent ambient air from disrupting and mixing with the pressure-recovery spin field in the outlet space outside the spinning pleated filter. For a typical filter 2 permeability and ledges as shown, this technique reduces the r oApproximately 50% of the energy of the tangential velocity at the outlet is recovered and converted into intake pressure, thus promoting filter flow and increasing the efficiency of the system. By lengthening the ledges 34, 34'' as shown in Figure 3C, and if the lower ledge 34'' is mirrored to the upper ledge 34 (not shown) so that they approach each other in a cymbal-like shape, the effective cross-sectional area of the outflowing air can be controlled so that even more pressure is recovered.

[0025]

[24] Figure 3C shows additional optional air directing collars 34' for directing and further stabilizing the outflow airflow. These air directing collars 34' may be placed and positioned by the user according to user requirements.

[0026]

[25] Figure 3D shows the airflow into and out of the pleated filter assembly shown in Figure 3C.

[0027]

[26] Filter device features are demonstrated in three exemplary embodiments of the present invention in Figures 3A-3C and 4A-4K. The spinning exiting air from filter 2 and centrifugal force create a significant suction effect that improves flow throughput. To avoid this reduction in suction by supplying air at ambient pressure, ledges 34, 34'', 35, and 36 are provided at the longitudinal ends of filter 2 to establish a physical air barrier between the external ambient pressure and the air exiting the outer radius of air filter 2. Ledges 34, 34'', 35, and 36 prevent ambient air from reaching the outlet of air filter 2, where it would normally impart and define its pressure. Instead, the ambient exerts its pressure after the jet begins to burn out, reducing the spin of the exiting air. Over this area, extending radially outward by several centimeters, the flow cross-sectional area increases. Conservation of flow means that the flow slows down, and as a result, pressure increases according to the Bernoulli equation if viscous losses in turbulent flow are negligible. In fact, this occurs in chaotic turbulent jets, with small jets from the pleats also contributing. Although the ledges only increase the overall flow in the system by 13% for short ledges, their most important role is to utilize the entire filter and create uniform flow in both the Z and longitudinal directions, which also significantly extends filter life. Instabilities are sufficiently prevented by the size and shape shown in Figures 4A through 4H.

[0028]

[27] As shown in Figures 4I to 4K, the addition of a set of statically positioned longitudinal membranes 48 surrounding the rotary cylindrical pleated filter and extending radially outward and tangential to the direction of the outgoing airflow may further improve the suction effect and overall flow rate.

[0029]

[28] There is also a hydrodynamic impact of negative pressure after air enters the z-end opening of the cylindrical pleated filter 2 along the rotation axis 20, making it difficult for the filter near the opening to suck the air out radially. To help overcome this, an air director inlet vent is placed before the inlet area where the incoming air is directed in the z-direction.

[0030]

[29] Rotary pleated air filters, as seen in some embodiments, may have stabilizing or reinforcing pleats 46, 2035 to support the filter shape during use. The reinforcing material may also hold other external elements of the pleated filter. The external elements may be a set of variable-angle encapsulated blades 49, as shown in FIG. 3E, that form air channels with outlet jets between them for directing the exiting air at a preferred angle relative to the horizontal. These encapsulated blades 49 are provided with an encapsulated blade connector element 49' at the center of the interior longitudinal direction of each encapsulated blade. This encapsulated blade connector element 49' may be provided in various embodiments, and in the particular embodiment shown, is a pivot pin 49'. Each pivot pin is configured to be gripped by a corresponding gripping element (not shown) at the center of the exterior of the pleated filter. This connection may be made in a click-on / click-off manner, and the pivot pin 49' provides a way to change the angular orientation of the encapsulated blades 49 around the pleated filter when the encapsulated blades 49 are installed. In one position, the encapsulated blade 49 is positioned with its lower region facing the pleated filter, flaring at the upper portion so that most of the jet escapes there. This position is typically chosen in winter to create an air vortex that doesn't confuse people. In the second, spinning, bistable position, the upper region rests on top of the lower portion facing the pleated filter, opening the jet so that the swirling air spins downward, providing a cooling effect similar to a smooth exhaust fan when it's hot. When one portion is positioned facing the pleated filter, the other end is positioned radially outward from the pleated filter, allowing air to more easily escape from these regions. Due to the pivot resistance of the pivot pin 49' connection, changing positions can be easily achieved by holding a finger super light toward the preferred side of the encapsulated blade 49 during rotation.

[0031]

[30] The external elements may be a set of longitudinal fan blades extending outward from the cylindrical pleated filter 2. In one embodiment, the longitudinal fan blades 144 extend perpendicularly from the cylindrical pleated filter 2, while in a different embodiment, the external fan blades are positioned to provide a jet effect by being approximately tangential to the exterior of the cylindrical pleated filter 2, as seen in FIG. 209. A variation of the external radial fan blades, having a more enveloping shape similar to that shown in FIG. 4K of the static longitudinal membrane 48, may be used to enhance the desired effect while adding to the visual aspect of the spin-type cylindrical pleated filter 2.

[0032]

[31] The present invention provides a significant filtering effect that impacts the power consumption resulting from propelling both dust particles and air through a rotating pleated filter. Compared to supply air systems where a fan works in conjunction with a static filter, hydrodynamic turbulence energy losses or fan losses are nearly eliminated. The result is a significant reduction in power consumption. Compared to products of similar function and size, power consumption can be reduced by 40-90%.

[0033]

[32] Please refer to Figures 2A and 2B, which show a pleated filter having a longitudinal cylindrical shape.

[0034]

[33] The filter of the present invention has an inner radius r i and outer radius r o Between and the inner radius r i and the length f along the rotation axis 20 h For example, if the filter is placed in a centrifugal fan of a flat-room heat exchanger, the inner radius r i If is too large and the RPM is too high, the incoming air will collide too violently with the pleats, and energy will be lost to turbulence and noise rather than increasing pressure. In such cases, the outer radius r must be increased to provide sufficient centrifugal driving pressure to overcome the pressure drop across the filter. ocan be chosen to be larger, but this would result in too much energy being put into the spinning outgoing air since the tangential exit velocity corresponds to r. On the other hand, the inner radius r of the pleated filter i If the opening is too small, the small inlet area to the channels in the pleated filter will result in high air inlet velocities, making it difficult to supply the filter sections closest to the inlet, resulting in uneven filter utilization. The same negative effect of high air inlet velocities is seen when air is supplied through only one filter opening. An additional negative effect of a single opening is that more motor torque is required to maintain performance, which in turn requires a larger, more expensive motor.

[0035]

[34] The usefulness of various embodiments of rotary pleated filters depends on a series of evaluation scales or parameters that may be weighted differently for different embodiments. Product size is important to most customers, as is the price increase associated with larger products. Other critical parameters when used in air purifiers are noise and clean air delivery rate (CADR), the latter often defined as the floor area that the air purifier can cover. After thoroughly studying the range of prior art air purifiers available and the complex physics that hold the key to the potential of rotary pleated filters, it has been discovered that a new relationship can be uncovered that surprisingly well describes the commercial usefulness of the rotary pleated filter of the present invention as an air purification element.

[0036]

[35] For proper operation without other functional pressure improving components installed, i , r o , pleat spacing p s , filter efficiency ε, and the length of the spin-pleated filter f h The relationship between the pore size and the flow rate can be expressed by a dimensionless number, referred to herein as the Gu number, which also applies to rotary pleated filters used in ventilation systems.

[0037]

[36] This relationship is based on phenomenology and experimentation, and is derived from CFD (computational fluid dynamics) simulations, 3D printing and measurements on numerous models, as well as testing various filters. The Gu number is defined as:

[0038]

[37] Gu number = f h *p r / (2*r o *ε 1 / 4 )

[0039]

[38] where r o p may represent the pressure generating outer radius of an optional additional filter, such as a carbon filter. r is (r o -r i ) / p s is defined by, where p s is the pleat spacing. While Gu number accuracy increases with increasing usefulness, boundary layers need to be more appropriately considered for improved accuracy as systems scale. These considerations will be investigated as the invention is further developed. Smaller systems than those tested are expected to perform poorly. In fact, larger systems will also perform poorly, since spinning very thick filters is not advisable. As Gu numbers increase, exceeding 10, interpreting usefulness becomes more difficult, depending on which parameters are changed and how the effects resulting from these changes are perceived by the observer. Such variations may be related to how observers perceive product size and how they perceive different levels of noise. The degree and type of pollution in the environment also contribute, and the recommended air change rate (room air changes per hour) typically varies from two to four or more times.

[0040]

[39] The Gu number takes into account the fluid dynamics of all relevant parameters, but in any case, it is not trivial to isolate or address why and how these parameters contribute, and therefore to apply it. To the best of our ability, it can be concluded or explained that all parameters contribute significantly over a relatively wide range. This relationship applies to filter efficiencies from 20% to well over 90%.

[0041]

[40] To be able to prove the inherent positive effects of rotary pleated filters, it was necessary to conduct experiments within the interval shown in FIG. 17B. Outside this interval, Gu≦0.8, the high noise per CADR makes it impossible to explore the benefits. Prior art implementations have not recognized the effects discussed and hypothesized above and have run at Gu numbers below 0.8. Also, prior art embodiments have run at too high RPMs without considering or even considering the relationships discussed above, causing manufacturers to focus their attention and development elsewhere, leaving hidden potential undiscovered.

[0042]

[41] An example of a product with radial blades according to the invention and having a shape factor Gu approximately equal to 1 is shown in Figures 21A to 21C. The invention claims the following intervals:

[0043]

[42] Gu>0.8

[0044] [Table 1]

[0045]

[43] Table 1 shows experimental tests of the best available prior art compared to two or three versions of the present invention where the claimed residential utility in relation to Gu number is embodied in the first test using CADR / L at 35 dB constant noise measured at 1 meter. L is the longest device length on the horizontal plane. Looking at the embodiment of the present invention depicted in Figures 21A-21C, due to the snail house design, L is approximately 1.25 * pleated filter diameter = 1.25 * 2 * r o is.

[0046]

[44] Table 1 is plotted in the embodied graph of Figure 17C showing the interval of Gu values from 0 to 5, the first row relating to a prior art spin filter shape replica with Gu = 0.8.

[0047]

[45] The next three rows show numbers relating to three embodiments of the invention, namely, the embodiments of Figures 21A to 21C, 4A, and 202, respectively, without a casing and unmodified fan blades.

[0048]

[46] A second test using the volume of a CADR / filter cylinder with a constant noise of 35 dB measured at 1 m.

[0049]

[47] Table 1 is plotted in the embodied graph of Figure 17D showing the interval of Gu values from 0 to 5, the first row relating to a prior art spin filter shape replica with Gu = 0.8.

[0050]

[48] The next two rows show numbers relating to two embodiments of the invention, namely the embodiment of Figures 21A-21C and Figure 4A without the casing and unmodified fan blades, respectively.

[0051]

[49] Common to all filters is ε=0.88.

[0052]

[50] The conclusion that can be drawn from experimental testing is that the filter design of the present invention confirms the unique and unparalleled performance of the present invention.

[0053]

[51] In an embodiment, when a pleated filter having two openings indoors and radial impellers 40, 40' on the inside or radial blades 53 on the inside, outside, or both the inside and outside of the pleated filter is rotated, the performance is affected by the angle of attack α of the blades. b , inner blade height r when two or more blades are used 内側ブレード or the total blade height. The attack blade edge in contact with the incoming air may advantageously be rounded. According to FIG. 3F, which shows the principle of the inner radial blade 53 (pleated filter not shown), the angle of attack α b is r i , f h and r 内側ブレード The inner filter radius r may be less than 75°, preferably between 75° and 30°, depending on the angle. i Inner blade height r from 内側ブレード is larger than 12 mm, preferably mainly f h Depends on 0.2*r i <r 内側ブレード <0.4*r i Let's say.

[0054]

[52] At the same flow rate and other similar shape factors, the matched attack inner blade r 内側ブレード = 10 mm resulted in approximately 4.5 dB noise improvement compared to standard forward-inclined blades where the radial fan geometry is optimized for unobstructed flow. Forward generally refers to the outer part of the blade, so it is angled "the other way" than in our case. Double the blade length r 内側ブレード A matched attack blade with φ = 20 mm provides a noise improvement of up to approximately 10 dB.

[0055]

[53] Similarly, improvements in power consumption savings of up to 30% are observed in terms of radial blade configurations.

[0056]

[54] The extruded shape of the radial blades 53 may be trimmed for even better performance. The morphed blades 40, 40' inside the filter have no characteristic length requirement as they constantly change shape over their length.

[0057]

[55] Gu numbers close to or below the threshold for residential utility, or approximately 130 / r o If filter parameters are chosen to exceed a noise-critical RPM above 1 / 2, one or more of the effects studied in connection with this invention, including matching media permeability, will result in a weak function with noise due to backflow and turbulence. This may be why industry development has focused on other filter solutions. In outdoor applications without noise regulations, none of these relationships need to be met.

[0058]

[56] When considering the outer blades, all rotating channels consisting of either pleats or blades are considered, and therefore r o should be stipulated.

[0059]

[57] At 4.8 Gu, the flow rate through a separate rotating cylindrical pleated filter with an internal carbon filter was shown to be higher and less noisy than when the same filter was designed and optimized for a prior art high-quality air purifier and used in static operation. By spinning a filter without internal blades at 1220 RPM, the filter produced the same CADR as a fine-tuned prior art air purifier running at full speed using two axial impellers in series at a higher RPM. The noise generated by the filter was 50 dB compared to 56 dB generated by the product itself. With internal blades and two openings, the potential is much greater. The fluid dynamic principles of the present invention are novel and improved, and performance improvements may be obtained without additional external fans and other components that take up space and increase the product size. Thus, the spin filter 2 itself constitutes a first embodiment of the present invention, as shown in Figure 1.

[0060]

[58] For example, when implementing the spinning pleat filter 2 shown in Figures 3A, 3B and 3C, such a design configured for attachment to a ceiling light power output, the rotating pleat filter within the frame 32 is substantially silent and has a total weight including the motor of less than 1 kg, providing a 230 m 3 The same small geometry can filter over 460m with 80% filter efficiency and an outstanding 44dB. 3 / h. This equates to a performance per size and weight many times greater than the best prior art technology available in commercially available products. Without the central axial-radial impeller structure 40, 40', 44, 44' shown in Figures 4A-4H, the spin filter would generate more noise and be less efficient than a filter that spins with the impeller structure 40, 40', 44, 44'.

[0061]

[59] Further data for an exemplary embodiment using a spin pleated filter of the present invention with an axial flow radial impeller compared to a traditional static filter assembly follows: RPM:946 ·r i :0.05m ·r o :0.072m f h :0.2m ε:0.88 Gu number when using one entrance: 3.33 Noise dBA-1m: 29.5dB CADR188 (ASHRAE 0.3um, 88% efficiency) 1 / 4 space occupancy rate 1 / 5 acoustic power (-16dB) @ same CADR, full speed

[0062]

[60] The lampshade assembly shown in Figures 201 to 207 occupies 20% less volume than the prior art high quality air purifier considered in the example above, but the test was conducted without a carbon filter. CADR310m 3 To achieve this, the lampshade assembly achieved a torque power of 2.4 watts, while the commercial product consumed 29 W. For a motor efficiency of 0.5, which equates to 4.8 W, corresponding to a power ratio of 8 in favor of spinning lampshades. The corresponding dB level was 56 dB for the commercial product, while the present invention was 26 dB.

[0063]

[61] Because pressure is used to make this happen, rotary pleated filters alone, or more preferably in combination with a rotating axial-radial impeller 40, 40' inside the pleated filter as shown in Figures 4A and 4B, significantly improve the clean air delivery rate (CADR) per noise compared to static filters with externally driven flow. Fan efficiency is superior to the standards achieved with large, well-designed fans (50-75%) because the tangential velocity of the incoming air matches the tangential velocity at the filter inlet. This is achieved by the axial-radial impeller. As discussed above, even a bare spin-pleated filter 2 has inherent and previously undiscovered potential for air purification applications because the air within the pleated filter can pass relatively easily through all of the effects discussed. Utilization of these effects has been demonstrated, and product realizations ranging from simple spin-pleated filters in their purest form to more advanced versions with superior performance have been demonstrated.

[0064]

[62] A first embodiment of an air purifying device 30 of the present invention is shown in Figures 2A, 2B, 3A, 3B and 3C. The pleated filter 2 rotates (21) within a frame 32, and this rotation is provided by an electric motor 31. However, the pleated filter 2 has a height of 2*f h , outer radius r o , and the inner radius r i The filter can be considered to consist of two symmetrically connected pleated filters 2 with two openings having a pleat thickness f t =r o -r i The cylindrical pleated filter has a pleat inflow angle α i Pleat outlet channel angle α is greater than o This also promotes a lower effective permeability, especially for tightly pleated filters.

[0065]

[63] By spinning the filter, airflow through the cylindrical filter is maintained by centrifugal force and the suction effect of the escaping air, allowing for a more uniform airflow than would be possible if air were pushed into or sucked from a static filter configuration, assuming the pleats have the proper shape, resulting in a reduction in the total pressure required as well as an increased filter life.

[0066]

[64] To distribute the flow and properly purify the air in the room, the air purifying device 30 may be designed with air directing foils 34 arranged radially around the purifying device 30, as illustrated in Figure 3C.

[0067]

[65] As the air purifier 30 rotates (21), the movement of air through the filter 2 draws a constant inflow of air 33 into the space inside the filter. As the exhaust air spins away from the filter surface (39), the suction effect, as previously discussed, increases the flow rate through the filter.

[0068]

[66] Typical shapes for the filter 2 are cylindrical or conical-cylindrical. Conical-cylindrical shapes are typically used in embodiments such as filter cassettes for ventilation systems where air input to the filter comes from only one side, typically the widest opening of the filter. Uniformly shaped cylindrical filters are more suitable for air purifiers. Depending on where the purifier is located, air input comes from one or both of the longitudinal faces of the filter.

[0069]

[67] In a further embodiment of the air purification device 30 of the present invention, an axial-radial fan 40, 1126 is provided that is positioned within and rotatably connected to the pleated filter 2, as shown, for example, in FIGS. 4A-4H. The fan may be configured for airflow from one or both longitudinal faces. The exploded view of the filter assembly in FIG. 4A includes the axial-radial fan 40, 40′, the filter end caps 41, 41′, and the filter 2. In FIGS. 4E-4H, a spin / support shaft 45 enters the filter assembly through the upper end cap 41, passes through the interior of the filter assembly, and connects to the center of the lower end cap 41′. The spin / support shaft 45 is connected to a motor 31, which rotates the filter assembly.

[0070]

[68] The end caps 41, 41' may include end cap foils 42 positioned radially outward from the central axis 43. The radial foils 42 are formed to guide incoming air from multiple directions axially, avoiding the impact effect observed in openings where the air entering the filter compartment converges inward toward the center. The resulting uniform flow allows for more even distribution by the impeller blades.

[0071]

[69] The axial-radial fan 40, 40' distributes the airflow across the filter. Even distribution is ensured in part by morphed fan blades. The fan blades begin at the inlet by attacking the incoming air at a velocity-matching angle, then gradually change shape to distribute the flow from axial to radial according to the remaining air fraction and radial and axial cross-sectional area. Better control of the airflow deeper along the filter's inner surface is provided by the integral conical fan element 44, 44', configured to taper from a maximum diameter located at the deepest point as the air exits the filter. The cone tapers away from the filter interior toward the inlet area of the filter assembly. Due to the rotational relationship between the axial-radial fan 40, 1126 and the pleated filter 2, the axial-radial fan 40, 1126 delivers airflow at approximately the same angular velocity as the filter and a tangential velocity close to the tangential velocity of the inner surface of the pleated filter 2. Therefore, a relatively small amount of rotation-related turbulence and energy dissipation occurs. As the figure shows an assembly providing incoming air from both sides of the filter, two oppositely disposed conical fan elements 44, 44' with associated axial-radial fan blades assist in incoming air distribution.

[0072]

[70] The efficiency obtained with the embodiment after adjusting the system and with all the components of the present invention in place is extremely high. The efficiency, calculated from the motor operation and flow throughput used by the rotary filter assembly, was measured to be higher than when the same filter was used in a flat configuration in combination with a lossless duct system and lossless fan. This is based on a flat filter configuration with an efficiency greater than 100%. The motor efficiency of both systems is ignored here. In traditional air purifiers, the combined duct system losses and fan losses typically consume several times the power that the theoretical work would consume in a flat filter. Therefore, an air purifier based on the principles of the present invention will outperform all traditional air purifiers.

[0073]

[71] Also, when the static filter of a traditional fan-filter assembly becomes clogged, the fan must overcome greater pressure. This causes the fan blades to operate outside their designed optimum flow-pressure region, resulting in turbulence, energy loss, and increased noise. However, when the filter rotates and acts as a pump, the increase in angular velocity can compensate, delivering the required pressure without the corresponding increase in noise and energy loss that occurs in traditional fan-filter assemblies. Thus, the noise emitted over the life span of the present invention is significantly lower than that of traditional fan-filter assemblies.

[0074]

[72] One advantage of such a rotary pleated filter of the present invention is that by generating both suction and pressure, it eliminates the need for glueing the filter edges when the filter is secured between two soft seals / frames 32 at its longitudinal ends along the axis of rotation 20, such as lids, each of which receives an end of the filter. In this way, the force acts radially on the filter, maintaining its shape and eliminating the need for glueing or fear of leaks. Therefore, the filter can be used immediately upon exiting the pleating machine, making it very cost-effective.

[0075]

[73] The present invention with spin filters also provides easier access for air to the bottom of the inner outlet channel of the rotary pleated filter due to the pillar effect. Also contributing are the axial radial fan, the radially expanding outlet channel and the suction field at the outlet flow.

[0076]

[74] The rotating connection between the radiating element of the axial radial fan and the inside of the pleated filter eliminates much of the noise-generating turbulence traditionally associated with fan-filter configurations, resulting in unprecedented noise, efficiency, and energy costs.

[0077]

[75] While the use of pleated filters is advantageous in the present invention, there are significant advantages to using any type of radial spin filter in combination with the axial radial fan described herein.

[0078]

[76] One such advantageous embodiment may be the use of a spinning radial carbon filter in a kitchen stove air filter unit downstream of a grease droplet trap collector downstream of a wire mesh aerosol stopper (not shown). Such a rotating assembly may improve the ability to gently suck and centrifuge grease and steam without dripping onto the food below. Also, a rear membrane 2002 may be optimal in this combination to avoid unpleasant drafts in the room.

[0079]

[77] Also in accordance with the present invention, there is provided a spin-on filter assembly including a pleated filter and a carbon filter or other type of filter disposed radially inside or outside the pleated filter.

[0080]

[78] All types of filters may be constructed from two or more parts. In the larger embodiments 2001, separation into four or six parts is optimal for ease of filter replacement and ease of product assembly.

[0081]

[79] In yet another embodiment of the rotational pleated filter, the air directing device comprises a concentric or conical-cylindrical rigid cover 50, 2124, 2125 with multiple jet nozzles 51, 2150, as shown in Figures 5a, 5b, 212B, 214A and 214B, and Figures 215A, 215B, and 215C. The nozzles may also be in the form of continuous or partially continuous slits between capsule-shaped blades 48 with variable inclination angles, as seen in Figure 3E. As a result, the exhaust jets propel the rotation of the filter 2, further reducing power consumption. A sleeve 52 may be provided around the pleated filter assembly to provide an output guide channel for air exiting the pleated filter assembly. Further exemplary embodiments of the present invention are now described, as shown in simplified Figures 6, 7, 8, 9, 10, and 11.

[0082]

[80] A casing 70 having at least four walls 73 is provided. The casing 70 is provided to enclose one or more, typically four, of any of the rotary pleated filter assemblies discussed above, with air directed from above to a central area of the filter, the inside of the filter assembly having a filter bottom 165 that provides an airtight seal, and all air must exit through the filter. The pleated filter assembly is configured so that outflowing air exits the casing in the same direction as the inflowing air. Thus, the casing has a casing inlet side 73 and a casing outlet side 74.

[0083]

[81] In one embodiment, a casing 70 adapted to enclose one filter assembly, such as that shown in Figure 6, includes longitudinal guide walls 71 disposed inside the casing 70 for directing airflow from the outlet of the spin filter to the exhaust side 74 of the casing. The guide walls 71 may be positioned to seal each corner space 75 of the casing 70 that is not occupied by the cylindrical rotary filter. The guide walls themselves may typically have cylindrical or conical-cylindrical sections and sections with an angular width of 90° or less.

[0084]

[82] The guide walls 71 are fitted with a first longitudinal side 76 having a radius 78 from the center of the filter that is slightly larger than the outer radius of the pleated filter, and a second longitudinal side 77 having a radial length equal to the distance from the center of the filter assembly to the central part of the casing 70, to which it may typically be fixed. In practice, this provides a longitudinal slit opening 60 between the first longitudinal side 76 of one guide wall 71 and the second longitudinal side 77 of the adjacent guide wall 71. Exhaust air 90 leaving the filter assembly accumulates and rotates with the spin-type filter assembly between the outside of the filter assembly and the inside of the guide wall 71 towards the longitudinal slit 60, with the majority of the air exiting between the first longitudinal side 76 of the next guide wall and the wall of the casing 70.

[0085]

[83] The curved airfoil 72 may be positioned outside the guide wall 71 to guide the outflow air 90 to the exhaust side 74 of the casing 70. The inlet portion 61 of the curved airfoil 72 may also be used to define an opening width between the first longitudinal side 76 and the wall of the casing 70. The curved airfoil may be curved to the exhaust side 74 of the casing 70, and the outlet portion 62 of the airfoil 72 may have a different depth, for example, greater than the depth of the inlet portion 61.

[0086]

[84] As a result, as the filter assembly spins, exhaust flow 90 is directed out of the filter assembly and vented through corner spaces 75 of casing 70 .

[0087]

[85] Figure 11 shows a horizontal cross-sectional embodiment of four filter assemblies arranged in a four-walled casing viewed from below. In this embodiment, the conical filter assemblies are typically arranged one per filter assembly in a separate cylindrical casing. These cylindrical casings may be bucket-type, allowing one bucket containing a filter assembly to be easily replaced.

[0088]

[86] Yet another exemplary embodiment of the present invention is described, shown in simplified Figures 12, 13, 14, 15 and 16.

[0089]

[87] Figure 12 shows a different configuration in which two or more cylindrical or conical filters are assembled concentrically.

[0090]

[88] Figure 14 shows a cross section of the top of one embodiment using multiple such filters 140, 141, 142 of different diameters. The filters may be mounted in an assembly in which each space between the filters is provided with an obliquely arranged airtight sleeve 160 that provides an input guide channel 161 for air to enter the interior space of the filter 140, 141 that is located outside the smaller diameter filter 141, 142 shown in the assembly cross section in Figure 16. The same airtight sleeve therefore provides an output guide channel 162 for air to exit to the exterior space of the filter 141, 142 that is located inside the larger diameter filter 140, 141.

[0091]

[89] Radial foils 144 may be positioned inside and outside (between) the filters to provide radially directed airflow. Thus, as the multi-filter assembly rotates (21), the incoming air 33 is forced into the interior of each filter, and centrifugal force forces the air through the filter; in the case of pleated filters, outlet channels between the pleats further enhance airflow through the filter.

[0092]

[90] An axial-radial impeller 150 is located in the input casing lid 151. Its purpose is to smoothly spin the air up to the angular velocity of the assembly, which provides the radial fan function of the filter assembly. Similar to an axial fan, the airfoil 163 has an angle of attack that matches the incoming air, but unlike an axial fan, which strives for low exit spin, the air leaves the airfoil 163 with a spin similar to a rotary pleated filter.

[0093]

[91] A rotating exhaust director unit 164 may be rotatably mounted on the exhaust side of the filters 140, 141, 142 of the assembly to provide an opposite outlet direction to the rotation (21). Air inflow 31 enters the interior of each cylindrical filter and exits the filter at the outlet flow 34 shown. The foil may also be angled upward from the lowest radius toward the filter for more uniform pressure to the director outlet.

[0094]

[92] The following description will explain in more detail the effects of how spun pleated filters improve the transport of air molecules through the filter and is illustrated by the details of Figures 17A and 18.

[0095]

[93] In Figure 17A, a half cross section of a spin filter and axial-radial impeller 40 blade is shown with airflow 33, 34 building up a radial pressure p as it passes through the impeller. Ideally, p = 0.5 * ρ * ω 2 *(r o 2 -r a 2 ) where r i is the inner radius r of the pleated filter i and r a is the characteristic radius depending on the inlet radius for each streamline, more specifically, the morphed impeller here enhances the radial pressure over the axial pressure. ρ is the air density and ω is the angular frequency. The radius r o and r a is defined in Figure 17A. However, real pressure fields are much more complex, making it difficult to express a useful relationship in simple analytical terms.

[0096]

[94] The pressure zone can be simply divided into the following sections: 1) Pressure increase zone from axial to radial direction 2) Radial spin pressure 3) The pressure distribution in the filter 4) Rotational outflow air pressure

[0097]

[95] A phenomenological representation of how tangentially averaged pressure distributes radially is shown at the bottom of Figure 17A. However, the actual pressure will vary greatly depending on how both the blades and pleats of the filter accelerate and decelerate both about the z-axis and radially. The impeller blades are shaped to distribute pressure evenly in both the z-direction and around the circumference of the z-axis. The diagram shows how the exit velocity and spin field have a suction effect on air molecules exiting the pleated filter.

[0098]

[96] In Figure 18, we can see an exaggerated example of the flow lines through a pleated filter under stationary and rotating conditions, and how the buildup of slow air molecules in a static filter increases the pressure drop compared to a spin-on filter. I. Corridor effect (discovered): Air molecules entering the outlet channel perpendicularly are partially accelerated by the high-velocity core flow (B), and then, in a static state, by the high pressure at the bottom of the outlet channel. Therefore, the resulting increased pressure compared to that in parallel flow is assumed to be the corridor effect. When a pleated filter is spun, centrifugal forces pull / accelerate the newly supplied air molecules along with the columns and core, so the core velocity can decrease to exit the same amount of air. The corridor effect is then reduced, resulting in a more uniform velocity profile at the exit and a reduced pressure drop in the outlet channel. Efficiency is increased by fewer viscous losses and kinetic energy losses in the outlet jet (A). The corridor effect becomes more important when the outlet channel is narrow and the media velocity is high. II. Column effect during spinning (discovered): The centrifugal force helps to pull the column together, so the actual pressure rise along the outlet channel is reduced. Considering the proper pleat geometry, a spin-pleated filter allows for a more uniform pressure that promotes flow through the innermost part of the outlet channel compared to the situation in a static pleated filter. A more uniform flow is created, which in turn reduces the differential pressure on the filter media. The pressure drop in the inlet channel is not considered, but this is important to understand the whole picture. III. Consequences of the pillar effect during spinning and reduction of the corridor effect: More flow can enter the bottom of the exit channel A' at a lower radius. The media pressure difference is reduced due to more uniform filter utilization (B'). The core velocity in the exit channel is reduced so less pressure is needed to accelerate the core C'. This reduces the pressure deep in the exit channel, promoting flow through the filter media at a lower R. Dynamic losses in the exit channel are reduced as the air exits at a slower velocity.

[0099]

[97] Figure 19 shows how the cylindrical shape of a pleated filter, which results when the pleated filter is curved into a cylindrical shape, promotes wider outlet channels than the input channels. The present invention advantageously reverses the flow direction in cylindrical filters from the method typically used today, where air passes through the filter from the outside to the inside of the filter, because the pressure drop in the outlet pleated channels is greater than in the inlet pleated channels of the same size. Furthermore, when other positive effects discovered to exist in rotary pleated filters are added, the advantages of rotary filters become very significant. IV. Cylindrical geometry: Widening the exit channel reduces the exit velocity. Pressure buildup and gallery effects are further reduced. V. Spinning outside the exit channel promotes suction / pull, reducing the final exit velocity and therefore energy losses. This increases the efficiency of the system.

[0100]

[98] Some or all of the features discussed in connection with Figures 17-19 are independent of the embodiment configuration in which the pleated filter is implemented. It is clear that outlet suction has less of an effect on filter performance when filters of different diameters are mounted on top of each other and / or when the filters are installed in a casing 70, as shown in Figures 12-16.

[0101]

[99] Further embodiments may include using the impeller and reverse jet technology discussed above in a kitchen stove ventilation unit (not shown) with a rotary filter that is not necessarily pleated. Filter types may include carbon filters, aluminum mesh filters, aluminum metal filters, knitted mesh filters, food grease filters, etc.

[0102]

[0100] Furthermore, the centrifugal force of almost any type of spin filter, such as a spin carbon filter, in which an axial radial impeller operates inside a spin cylindrical filter, is said to have characteristics that are incomparable to filters of the same configuration installed for static operation.

[0103] 20A to 20D show a floor-mounted air purifying device 200 that uses the rotary pleated filter described above. The device may have two or more rotary pleated air filters 2 mounted inside a housing 201, 2141, the housing having an inlet vent 202 and an outlet vent 203, 2136, and a rotary air collector 204, 2132 that directs the exiting air according to the air flow path established by the rotary pleated filter 2. The cross-sectional area formed between the collector 204, 2132 and the surface of the rotary pleated air filter 2 gradually increases along the circumference of the rotary pleated air filter 2.

[0104]

[0102] The collector 204 surrounds only a portion of the corresponding rotary cylindrical pleated air filter 2 so that when two or more rotary cylindrical pleated air filters are stacked and mounted vertically as shown in the figure, air exits primarily from the sides of the lower rotary cylindrical pleated air filter 2 and primarily upward from the topmost rotary cylindrical pleated air filter 2.

[0105]

[0103] Static air barriers 205 are provided on the front and rear surfaces of the floor-mounted air purification device 200.

[0106]

[0104] The present invention also provides an air filter device comprising one or more rotary pleated air filters (2) and a motor (31) for rotating the pleated air filters, the air filters having a cylindrical shape, and further satisfying the relationship Gu = f h *p r / (2*r o *ε ^1 / 4 )>0.8, where the Gu number is correlated to a function of commercial usefulness based on or taking into account key customer needs such as CADR, dB, product size, functionality, and cost, where p r =(r o -r i ) / pleat spacing (p s ), pleat spacing (p s ) is the inner radius (r i ) and ε is the ASHRAE efficiency.

[0107]

[0105] A second embodiment of the air filter device according to the first embodiment, in which Gu>1.2.

[0108]

[0106] A third embodiment of the air filter device according to the first embodiment, wherein Gu>1.5.

[0109]

[0107] A fourth embodiment of an air filter device relating to any one of the first to third embodiments, wherein the cylinder is open at one or both ends so that when the rotary pleated air filter 2 rotates 21, centrifugal force forces air through the pleated filter, creating a suction force that sucks air in from one or two open ends on the upstream side of the rotary pleated air filter 2, and the filtered air flows radially outwards in all directions on the downstream side of the rotary pleated filter.

[0110]

[0108] A fifth embodiment of an air filter device relating to any one of the first to fourth embodiments, further comprising a radial fan blade arranged inside the rotary pleated air filter 2, the radial fan blade being rotatably connected to the rotary pleated air filter 2, and the overall height of the blade being ≧12 mm.

[0111]

[0109] A sixth embodiment of an air filter device according to the fifth embodiment, wherein the overall height of the blades is ≧15 mm. The radial blade geometry is the inner radius R of the rotary pleated air filter 2 i forward angle of attack α between 15° and 75° b A seventh embodiment of the air filter device according to the fifth or sixth embodiment, comprising:

[0112]

[0110] An eighth embodiment of an air filter device according to the fifth or sixth embodiment, in which the radial fan blades are formed as a radial flow impeller arranged on the outside of the rotary pleated air filter 2.

[0113]

[0111] A ninth embodiment of an air filter device according to any one of the fifth to eighth embodiments, wherein the radial fan blades are formed as a radial flow impeller arranged inside the rotary pleated air filter 2.

[0114]

[0112] A tenth embodiment of the air filter device according to any one of the first to ninth embodiments, further comprising an inlet impeller for imparting spin to inlet air to the rotary pleated air filter 2.

[0115]

[0113] An eleventh embodiment of the air filter device according to the ninth embodiment, in which the fan blades are formed with an axial angle of attack and the inlet impeller is rotatably connected to the rotary pleated air filter 2.

[0116]

[0114] A twelfth embodiment of an air filter device according to the eleventh embodiment, in which the inlet impeller and the radial flow impeller are combined into one impeller having morphed blades acting as an axial radial fan to provide uniform airflow along and within the pleats of the rotary pleated air filter 2.

[0117]

[0115] A thirteenth embodiment of an air filter device relating to any one of the first to twelfth embodiments, further comprising pleated filter end caps 32, 41 arranged and connected to one or both longitudinal ends of the rotary pleated air filter 2.

[0118]

[0116] A fourteenth embodiment of an air filter device relating to any one of the first to thirteenth embodiments, further comprising one or more ring-shaped foils 42 arranged at the inlet opening of the rotary pleated air filter 2 for directing the incoming air (47, 47') and thus providing a safety grill inside the rotary pleated air filter 2.

[0119]

[0117] A fifteenth embodiment of an air filter device relating to any one of the first to fourteenth embodiments, in which air barriers 35, 36, 34', 34'' are provided on the inlet side of the rotary pleated air filter 2, arranged approximately perpendicular to the longitudinal direction, to prevent ambient air flow from mixing with the air flow exiting the rotary pleated air filter 2.

[0120]

[0118] A sixteenth embodiment of an air filter device according to any one of the first to fifteenth embodiments, further comprising air directing foils 34, 34', the air directing foils 34 being arranged radially around the rotary pleated air filter 2.

[0121]

[0119] A 17th embodiment of an air filter device according to the 15th embodiment, in which one or more rotary pleated air filters 2 are mounted inside a housing 201, 2141, and the housing is equipped with an inlet vent 202 and an outlet vent 203, 2136 and a collector 204, 2132 for guiding air leaving the rotary pleated filters according to the air flow path created by the one or more rotary pleated air filters 2.

[0122]

[0120] An 18th embodiment of an air filter device according to the 17th embodiment, in which the cross-sectional area formed between the collector 204, 2132 and the surface of the rotary pleated air filter 2 gradually increases along the circumference and rotational direction of the rotary pleated air filter 2, and the collector 204, 2132 surrounds only a portion of the corresponding pleated air filter 2.

[0123]

[0121] A nineteenth embodiment of an air filter device according to the eighteenth embodiment, in which the part of the first air filter of the one or more pleated air filters 2 that is not surrounded by the collector 204, 2136 faces mainly upwards.

[0124]

[0122] A twentieth embodiment of an air filter device according to the nineteenth embodiment, in which the portion of the second air filter of one or more pleated air filters 2 that is not surrounded by the collector 204, 2136 faces primarily toward the upward rotation side of the pleated air filter 2.

[0125]

[0123] A 21st embodiment of an air filter device according to the 18th embodiment, in which a static air barrier 205 is provided on the inlet side of the rotary pleated air filter 2, arranged approximately perpendicular to the air inflow direction, and the static air barrier 205 has a corresponding opening (206) arranged at the inlet of the rotary pleated air filter 2 to prevent ambient air flow from mixing with the air flow exiting the rotary pleated air filter 2.

[0126]

[0124] A 22nd embodiment of an air filter device relating to any one of the 1st to 21st embodiments, further comprising a set of statically arranged longitudinal thin films 48 surrounding the rotary circular pleated air filter 2 and extending radially outward and tangentially to the direction of the outgoing air flow to further improve the suction effect and overall flow rate.

[0127]

[0125] A 23rd embodiment of an air filter device according to any one of the 1 to 22 embodiments, wherein the cylindrical pleated air filter 2 has a conical shape, the cone diameter being greatest at the inlet opening.

[0128]

[0126] A 24th embodiment of an air filter device relating to any one of the 1st to 23rd embodiments, further comprising a pleated air filter assembly formed to include two or more radially spaced cylindrical pleated air filters 2.

[0129]

[0127] A 25th embodiment of the air filter device of the 24th embodiment, in which a cylindrical airtight sleeve 160 is arranged between any two adjacent radially spaced cylindrical pleated air filters 2, the cylindrical sleeve 160 is connected to the inside of the outermost cylindrical air filter on the output side and has a diameter that decreases relative to the cylindrical air filters towards the inlet side of the cylindrical air filters, and is connected to the outside of the innermost cylindrical air filter closest to the input side of the device so that an outlet space 162 for discharging filtered air to the outside of the innermost filter and an inlet space 161 for guiding inlet air to the inside of the outermost filter are defined between the two cylindrical air filters.

[0130]

[0128] A 26th embodiment of an air filter device according to the 25th embodiment, in which the radial fan blades are mounted radially spaced apart and arranged as longitudinal thin films 144 shaped to maintain a static distance between the cylindrical airtight sleeve and the cylindrical air filter.

[0131]

[0129] A 27th embodiment of an air filter device relating to any one of the 1st to 26th embodiments, further comprising an outer casing 70 defining a confinement by an inlet side 73 and an outlet side 74, the inlet side 73 corresponding to the inlet end of the filter and the outlet side corresponding to the side to which the outlet air from the rotary cylindrical pleated air filter 2 is directed.

[0132]

[0130] A twenty-eighth embodiment of the air filter device according to the twenty-seventh embodiment, in which the outer casing 70 has a generally square duct shape.

[0133]

[0131] A 29th embodiment of an air filter device relating to any one of the 1st to 28th embodiments, further comprising a low-noise air directing device 48, 50 arranged around the filter for directing exhaust flow with a directional distribution to the outside of the filter to provide optimal flow distribution.

[0134]

[0132] A thirtieth embodiment of the air filter device according to the twenty-ninth embodiment, in which the air directing device 50 is rotatably connected to the filter.

[0135]

[0133] A 31st embodiment of an air filter device according to the 30th embodiment, in which the air directing device has a nozzle opening 51 for providing an air jet flow in a direction opposite to the rotational direction of the rotary fan assembly to reduce power consumption and outlet air velocity.

[0136]

[0134] A thirty-second embodiment of an air filter device relating to any one of the first to thirty-first embodiments, wherein one rotary cylindrical pleated air filter 2 further comprises an integrated conical fan element 44, 44' configured to taper from a maximum diameter located at the deepest point as air exits the rotary cylindrical pleated air filter 2, the cone tapering away from the filter interior towards the inlet area of the rotary cylindrical pleated air filter 2, resulting in better control of the distribution of airflow deeper along the inner surface of the filter.

[0137]

[0135] A thirty-third embodiment of an air filter device according to the thirty-second embodiment, in which two oppositely arranged conical fan elements 44, 44' with associated impellers 40, 40' ensure inlet air distribution from both sides of the filter.

[0138]

[0136] A 34th embodiment of an air filter device relating to any one of the 1st to 33rd embodiments, further comprising a set of variable angle capsule blades 49 arranged on the outside of the rotary cylindrical pleated air filter 2 to provide air channels with outlet jets therebetween for directing outlet air at a preferred angle relative to the horizontal plane, the capsule blades 49 having a capsule blade connector element 49' at the middle of the inner longitudinal direction of each capsule blade 49.

[0139]

[0137] A thirty-fifth embodiment of the air filter device of the thirty-fourth embodiment, in which the capsule-type blade connector elements 49' are pivot pins and each pivot pin 49' is formed to be gripped by a corresponding gripping element in the central portion of the exterior of the rotary cylindrical pleated air filter (2).

[0140] First priority applications: Nos. 20190246 and 20190522

[0138] Therefore, the overall objective of the first and second priority inventions is to provide an ultra-compact and complete ventilation device and system for indoor ventilation in which the above-mentioned trade-offs are eliminated or significantly reduced.

[0141]

[0139] In a first embodiment, the present invention provides a ventilation device and system including a unit casing, a compact rotary heat exchange unit disposed inside the unit casing, a dual-acting fan, a filter unit, and a first embodiment of a room unit. The components included in the ventilation device provide a dual airflow channel design that allows optimized airflow in both directions simultaneously through the ventilation device.

[0142] In a further second embodiment, a ventilation apparatus and system is provided comprising a unit casing, a dual mode fan assembly disposed within the unit casing, and an optional filter unit, and a second embodiment of a room unit, allowing simultaneous bidirectional optimized airflow through the ventilation apparatus optimized for ventilating the house and room when it is desired to maintain the interior of the house / room at a higher or lower temperature than outdoors. The internal duct assembly may comprise a static filter.

[0143]

[0141] In another further third embodiment, the unit casing is provided with a duct extension assembly which is correspondingly extended to provide a length corresponding to the wall thickness, and the ventilation device of the first or second embodiment is optimized for placement in thick-walled structures.

[0144]

[0142] The first and second embodiments may be provided as a multi-operating mode device in which the rotary heat exchange unit and room unit of the first embodiment are interchangeable with a summer mode assembly comprising the internal duct assembly, optional large static filter, and room unit of the second embodiment.

[0145]

[0143] In a fourth embodiment of the invention, the dual mode fan may be combined with a counterflow heat exchanger to provide an optimization unit for drying rooms with moisture and / or radon problems, such as basements.

[0146]

[0144] Additional features and advantages of the present invention are described in, and will be apparent from, the following brief description of the drawings and the detailed description that follows. Figure 100 - Shows the cross section of the ventilation unit. Figure 102 - Shows the ventilation unit with the heat exchange module in the extracted position. Figure 103 - Shows an exploded view of the internal elements, winter heat exchange module, from the filter to the end cap. Figure 104 - Shows a cross section of the ventilation unit with the heat exchange module in the extracted position. Figure 105 - Exploded view of the ventilation unit without modules, impeller module, casing and end protection caps. FIG. 106A—Illustrates an exploded view of the dual mode fan assembly. FIG. 106B—Shows an outline perspective view of the dual mode impeller. FIG. 106C—Shows a top view of the dual mode impeller. FIG. 106D—Schematic showing airflow relative to the impeller. FIG. 107 - Shows one embodiment of a flow restrictor design. FIG. 108 - Detail of the flow restrictor of FIG. 107. FIG. 109 - Showing the heat exchange module and outer flow separator knife. FIG. 110 - Shows the static outer flow separator knife. Figure 111 - Shows the filter unit. Figure 112 - Filter shown. Fig. 113 - Shows a bottom perspective view of the central duct structure. Fig. 114 - Shows a top perspective view of the central duct structure. Figure 115 - Shows the outer air direction unit for the ducted extension version of the ventilation and fan assembly. Figure 116 - Showing the outer air director. Figure 117 - Cross section of dual mode fan assembly and outer air director. FIG. 118 - Cross section of dual mode impeller, outer air director, and sleeve expander. FIG. 119A—Summer module and room unit. FIG. 119B—Shows cross section of summer module and room unit. FIG. 119C—Shows cross sections of summer module, fan unit, and room unit. Fig. 120 - Cross-section of heat exchange module, fan unit and room unit. FIG. 121A—View from the outside of the impeller assembly w / rotating filter. FIG. 121B—View from outside of impeller assembly w / rotating filter and casing, motor and motor fastening means. FIG. 121C—Cross-sectional side view of impeller assembly w / rotating filter. FIG. 121D—Cross-sectional perspective view from the outdoor side of the impeller assembly w / rotating filter. FIG. 121E—Indoor view of impeller assembly w / rotating filter and casing, motor and motor fastening means. FIG. 122A - Cross section of ventilation unit with impeller assembly w / rotating filter shown with heat exchange module in extracted position. FIG. 122B—Cross-sectional side view of ventilation unit with impeller assembly w / rotating filter. FIG. 122C—Cross-sectional perspective view of ventilation unit with impeller assembly w / rotating filter. FIG. 123A - Cross section of ventilation unit with impeller assembly w / rotating filter. FIG. 123B—Cross section of ventilation unit with impeller assembly w / rotating filter with heat exchange module assembly extracted. FIG. 123C—Cross section of ventilation unit with impeller assembly w / rotating filter, with heat exchange module assembly and impeller assembly extracted.

[0147]

[0145] In the following description, the use of certain terms shall be construed broadly and at least in the meanings defined below.

[0148] Air / Gas Flow Direction:

[0147] Intake air: defined as air from the intake side passing through the ventilator.

[0148] Exhaust air: Return air going in the opposite direction to the supply air passing through the ventilation system.

[0149] Outdoor: Used to define the intake side of a ventilation system, while indoors is the opposite side of the ventilation unit.

[0150]

[0150] Dual Mode Impeller: A rotating device for simultaneously forcing intake and exhaust air in two opposing directions.

[0151]

[0151] Dual Mode Fan: Dual mode, or bi-directional, impeller, motor, motor casing and air director.

[0152] Air: Although the apparatus of the present invention is primarily suitable for use for air ventilation, the device and system can be used in any type of gaseous environment. When the term "air" is used herein, it shall be understood to mean any type of gas.

[0153] Heat Transfer Medium: A porous medium with a large temperature gradient that transfers heat between exhaust and supply air.

[0154] Heat Exchange Module: A heat transfer medium that includes components that direct the flow of air through the heat transfer medium.

[0155] Summer Module: A static module that takes the place of a heat exchange module, optionally with a large filter.

[0156]

[0156] Filter module: A filter casing and a filter for filtering the intake air. The filter module may be in rotational connection with the heat transfer medium to transfer the angular momentum required to rotate the heat transfer medium.

[0157]

[0157] Unit casing: A casing adapted to receive all the components of a ventilation unit.

[0158] Motor Housing: A rigid housing that serves as the casing for an impeller motor and may support one end of a central shaft that carries the heat transfer medium.

[0159]

[0159] Intake Air Director: The part of a dual mode fan that supports the motor housing and has foils that may reduce the rotational spin of the intake airflow from the impeller.

[0160] Room Unit: A unit on the room side of an interior wall that includes a box / housing / chassis and ductwork suitable for optimum throughput of intake and exhaust air in various embodiments of a ventilation system.

[0161]

[0161] Valve Assembly: An airflow restriction mechanism comprising multiple movable restrictors, typically made of elastomer, a valve motor and a valve gear assembly for dynamically throttling the air intake and / or exhaust.

[0162]

[0162] The present invention will now be described in more detail with reference to the drawings as needed.

[0163]

[0163] In the following, the ventilation device of the present invention will be described as part of a complete air handling system configured to ventilate a room, the room having a wall structure with a duct sleeve provided between the room itself and the external fresh air environment in which the ventilation device will be located. The ventilation device may comprise modules for heat exchange, simultaneous bidirectional airflow, a dual-mode fan, a valve assembly, an air filter, and an airflow direction guide, as well as a duct sleeve and a unit casing. It will be understood that the various modules may be implemented as a whole or in various combinations without departing from the concept of the present invention. It is the claims that define the scope of protection of the present invention.

[0164] In a first embodiment shown in FIGS. 101 to 108, a ventilation device 1001 of the present invention includes a dual mode fan 1200 having a dual mode impeller 1002 attached to a motor shaft 1004 via a motor shaft casing 1104 that receives a protrusion of the motor shaft 1004. The motor shaft casing 1104 is disposed in a central longitudinal direction of the dual mode impeller 1002 and provides a resilient holding force for the received motor shaft 1004. When the dual mode impeller 1002 rotates due to the force of the rotating motor shaft, it generates intake airflows 1016, 1017 and exhaust airflows 1018, 1019. The dual mode impeller 1002 may be rotated by an impeller motor 1103 disposed on the interior side of the impeller 1002 within the ventilation device 1001. The motor is driven by a power source (not shown) connected to the motor by cables and control lines (not shown).

[0165] A control unit 1105, which may be incorporated into the air supply director 1107 that provides the casing that supports the motor housing 1041 on the interior side of the dual mode impeller 1002, may include integrated circuits and programs for monitoring sensors, processing and / or communicating sensor data, and controlling the dual mode fan. The sensors and electronics may be incorporated into any part of the ventilation unit and may sense one or more physical characteristics such as fan speed, air volume, air pressure, air temperature, noise, vibration, humidity, etc. Control mechanisms may be implemented in the control unit 1105 to avoid malfunctions and optimize efficiency.

[0166] In one embodiment of the present invention, the impeller 1002 is designed with the shape shown in detail in Figures 1, 2, 5 and 6A / B. When the motor 1103 starts and causes the impeller 1002 to spin 1060, the airflow 1016 is drawn into a set of supply channels 1061 in the central area 1181 on the outdoor side of the impeller 1002. The impeller supply channels act like a turbine, and the air is carried by a radial acceleration field, increasing its pressure as it exits the outer annular ring area 1182 on the indoor side of the impeller 1002. Thus, the supply air gains rotational force as it exits the impeller 1002.

[0167] After entering, the air supply channels 1061 occupy only a portion of the cross-sectional area, separating to provide space for exhaust channels 1062 that cross-flow between the supply channels 1062. The walls of the supply channels 1061 are shaped to simultaneously provide the walls of the aerodynamic exhaust channels 1062. The exhaust channels 1062 carry exhaust air from the inner central portion 1102 on the indoor side of the dual mode impeller 1002 to the outer annular area 184 on the outdoor side of the dual mode impeller 1002. Thus, the dual mode impeller 1002 drives airflow in two directions simultaneously: from the outdoor side 1016 to the indoor side 1017, and from the indoor side 1018 to the outdoor side 1019.

[0168]

[0168] Figure 106D shows a schematic of how air flows into and out of the impeller, with the outdoor side above the horizontal line and the indoor side below the horizontal line.

[0169]

[0169] Typically there are 12 separate channels in each direction, although other designs may have fewer or more channels.

[0170]

[0170] Looking now at the first embodiment of the ventilation device 1001 from the outdoor side toward the indoor side, the supply airflow flows from the dual mode impeller unit through an air director unit 1107 having a foil 1106. The foil 1106 of the air director 1107 is provided to block most of the rotational force on the supply air resulting from the rotation of the dual mode impeller 1002. The foil 1106 may be positioned to provide two or more inlet heights h1, h2 to reduce the surfing effect that occurs when impinging on the boundary layer on a "low angle" approach. The air director 1107 is positioned with an annular inlet channel outside the periphery of a central duct 1111 in which the motor housing 1041 is located. The air director unit 1107 also provides a support structure for fastening a compartment for the optional printed circuit board 1105 and for fastening the motor housing 1041, which has a central portion 1177 on its indoor side to provide a connection point for the fixed central duct structure 1109, 1112. The support structure for the air director unit 1107 may also include an outer circular wall 1113 having an outer diameter that matches the inner diameter of the unit casing 1003, so that when placed in the unit casing 1003, the support structure for the air director unit 1107 provides a fixed support for the motor and an air labyrinth seal for the rotating parts of the ventilation device 1001. The dual mode impeller 1002 is one such rotating part, and a first air labyrinth seal 1114 is provided at the junction between the outer wall of the dual mode impeller 1002 in a region on the indoor side of the impeller 1002 and the inside of the outer circular wall 1113 in a region on the outdoor side of the outer circular wall 1113. A second air labyrinth seal 1115 or seal sliding surface is provided between the outer annular ring area 1182 on the indoor side of the dual mode impeller 1002 and the inner central portion 1102 on the indoor side of the dual mode impeller 1002, and will sealingly interact with a corresponding annular area 1123 of the support structure. The second air labyrinth seal 1115 will also provide an airtight seal between airflows flowing in different directions simultaneously through the dual mode impeller 1002.

[0171] Located on the indoor side of the air director unit 1107 is an air filter unit 1300 that provides an annular compartment for the intake air flow 1321 and a central duct for the exhaust air flow 1322. The annular compartment for the intake air flow 1321 has an inner enclosure 1302 and an outer enclosure 1301 and is provided to house the air filter 1108, providing airtight seals 1116, 1117, 1118 for the longitudinal intake air flow 1321 path through the air filter toward the central duct for the exhaust air flow 1322. The air filter 1108 extends approximately perpendicular to the longitudinal direction and may be provided with an inner and outer wall structure that has sufficient sealing properties to make either or both of the inner and outer enclosure walls 1302, 1301 of the air filter unit 1300 unnecessary, and thus may be incorporated into the design of the filter unit 1300. The filter unit 1300 may further be fixedly connected to the heat exchange module 1110. The air filter unit 1300 further provides a filter unit hub 1306 through which the connection 304 of the motor-side ball bearing 1119 passes and is positioned with a central duct hub 1325 of the central duct structure 1109. The connection 1304 of the motor-side ball bearing 1119 facilitates easy rotation of the air filter unit 1300 and the heat exchange module 1110. The central duct hub 1325 is fixedly held inside a central duct collar 1328 of the central duct structure 1109 by central spokes 1327. The central duct collar 1328 defines a pipe duct section of the central duct structure 1109 that defines a duct for the exhaust air flow 1322 toward the central duct of the air filter unit 1300. The air filter unit 1300 and the heat exchange module 1110 are further rotationally hingedly connected to an indoor-side ball bearing 1120 positioned in a central opening 1310 in a bottom wall 1121 of the heat exchange module 1110. The airflow velocity and any residual rotational forces in the airflow on the outdoor side of the filter unit 1300 cause the heat exchange module 1110 and the filter module 1300 to rotate about their own central longitudinal axis 1166. Sensors (not shown) may be provided to detect the rotational speed of the heat exchange module 1110 and the filter module 1300.Further braking means (not shown) may be provided to control the rotational speed of the heat exchange module 1110 and the filter module 1300.

[0172]

[0172] On the opposite indoor side of the central duct structure 1109, another central duct hub 1168 is fixedly held inside the central duct structure 1109 by a central spoke 1169. The other central duct hub 168 has a protrusion on its indoor side that is positioned from a central opening 1310 in the bottom wall 1121 of the heat exchange module 1110, and the distal end 1167 of the protrusion has a shape that corresponds to a center hole / recess 1317 of a static end cap 1316 that is positioned therein, thereby holding the central duct structure in a stationary position in all operating modes. The static end cap 1316 is mounted on the indoor end of the ventilation unit. Typically, the shape of the distal end 1167 and the corresponding center hole / recess 1317 are formed into a male-female torques (torqs) configuration. Other connection configurations or mechanisms may be selected without departing from the concept of the present invention.

[0173]

[0173] For further stability, a central axis may be provided that extends from the center of the motor side ball bearing 1119 to the center of the indoor side ball bearing 1120 located in the center of the bottom wall 1121.

[0174] The heat exchange module 1110 is typically shaped as a cone with an inside and an outside, where the cone may be widest at its largest diameter toward the outdoor side of the ventilation device 1001 and taper to a smaller diameter toward the indoor side. This shape provides a path for supply air 1016, 1017 to flow from the inside to the outside into the cone of the heat exchange module 1110, while exhaust air flows 1018, 1019 flow in the opposite direction. Other shapes may also be provided. For example, if the cone shape of the heat exchange module were oriented in the opposite direction, with its widest end toward the indoor side of the ventilation unit, supply air 1016, 1017 would flow from the inside to the outside of the cone of the heat exchange module 1110, and exhaust air flows 1018, 1019 would flow from the outside to the inside.

[0175]

[0175] The cone of the heat exchange module 1110 rotates freely about its central axis, rotating the thermal mass of the heat exchange medium between the intake air flow path and the exhaust air flow path. The lamellas of the cone of the heat exchange module 1110 may be made of any type of low thermal conductivity material, such as a plastic compound, wood, cardboard, ceramic, etc. The low thermal conductivity material of the heat exchange module 1110 may be in the form of a thin film, a porous molding compound, etc., but hereinafter thin film will be used as a general term without excluding any form or material that meets the required heat exchange properties.

[0176]

[0176] During operation, the thin film has a temperature gradient that results in high thermal efficiency of the heat exchanger.

[0177] The central duct structure 1109 is formed to direct the intake airflow from the filter 108 from inside the heat exchange module 110 towards a first vertical half of the heat exchange module 110. The central duct structure 1109 vertically bisects the internal volume of the heat exchange module 1110, and vertical tight-fitting central duct knives 1307, 1308 are provided corresponding to the interior vertical shape of the heat exchange module 1110, effectively bisecting the space inside the exchange module 1110 and preventing airflow leakage between the intake and exhaust airflows flowing in opposite directions inside the heat exchange module 1110. The central duct structure 1109 is formed as a vertical half of a pipe in the indoor portion of the central duct structure 1109, which indoor portion is typically at least half the length of the central duct structure 1109. At the outdoor portion of the central duct structure 1109, the half-pipe shape expands to include the full pipe shape of a central duct collar 1328 corresponding to the central duct of the filter module. On the outdoor side of the central duct structure 1109 on the opposite longitudinal half of the pipe in the indoor portion of the central duct structure 1109, an encircling collector channel 1320 is provided, the outer diameter of which corresponds to the diameter of the outer enclosure 301 of the air filter unit 1300 and the inner diameter of which is defined by the central duct collar 1328. The collector channel 1320 collects the supply air heading towards the filter 1108 from the entire orbital interface and directs it into a longitudinal half defined by the outer sides of the longitudinal halves of the pipe in the indoor portion of the central duct structure 1109, which is confined on its side by central duct knives 1307, 1308.

[0178]

[0178] The central duct knives 1307, 1308, the inside of the vertical halves of the pipes in the indoor part of the central duct structure 1109, and the underside of the surrounding collector channel 1320 provide a channeling path for the exhaust flow from the inside of the vertical halves of the pipes in the indoor part of the central duct structure 1109 through the inside of the central duct collar 1328 towards the central duct for the exhaust flow 1322 of the air filter unit 1300.

[0179] The central duct structure 1109 directs exhaust air from the indoor side of the heat exchange module 1110 through the second vertical half of the heat exchange module 1110 towards the center of the air filter module 1300. The central duct knives 1307, 1308 fit snugly towards the inside of the heat exchange module 1110 to ensure a minimum airflow exchange between the two inner vertical half-spaces defined by the central duct structure 1109. The tapered shape of the heat exchange module 1110 is provided to ensure a uniform pressure differential across the membrane along the longitudinal length of the heat exchange module, ensuring a uniform transverse velocity through the membrane to optimize efficiency.

[0180] The intake air filter 1108 of the filter module 1300 may be of any shape, such as donut, cylindrical orbit, cone, flat, bellows-shaped, porous, etc. If the filter is not provided with longitudinal outer and inner walls for sealing, this is provided by the inner and outer surrounding walls 1302 and 1301 of the air filter unit 1300 itself.

[0181] As the supply airflow leaves the supply air director, it is directed through a rotary low resistance air filter 1108 before being directed by a static central duct structure 1109, which directs the air from the filter to the front half of the rotary heat exchange module 1110. The filter 1108 and heat exchange cone 1110 may be rotationally connected and will rotate about its own central longitudinal axis due to the residual rotational force of the supply airflow still present after the airflow leaves the supply air director foil 1106.

[0182] On the indoor side of the rotary heat exchange module 1110 is provided a sleeve air guide assembly 1330 with static outer flow separator knives 1312, 1313 having an inward profile that matches the tapered outer shape of the rotary heat exchange module 1110 and an outward profile that matches the inside of the unit casing 1003. The static outer flow separator knives 1312, 1313 divide the space between the outside of the rotary heat exchange module 1110 and the inside of the unit casing 1003 in the area of the rotary heat exchange module 1110 into two longitudinal halves: one half providing a channel for the intake air flow and the other half providing a channel for the exhaust air flow in the opposite direction. The rest positions of the static outer flow separator knives 1312, 1313 correspond to the rest positions of the longitudinal tight-fitting central duct knives 1307, 1308. The effect of these longitudinal knives 1307, 1308, 1312, 1313 is that as the rotary heat exchange module 1110 slowly rotates, the airflow passing through the rotary heat exchange module 1110 is directed into one longitudinal half of the rotary heat exchange module 1110 statically defined in a first direction by the positions of the longitudinal static outer flow separator knives 1312, 1313 and the longitudinal tight-fitting central duct knives 1307, 1308, and in the other direction through the opposite longitudinal half of the heat exchange module 1110. The rotation of the vertical heat exchange module 1110 results in heat exchange between the airflows flowing in each direction. When the indoor temperature is higher than the outdoor temperature, the exhaust air will warm the rotating heat exchange module in the vertical half area defined by the tight-fitting central duct knives 1307, 1308, and as the heated area of the heat exchange module 1110 rotates and enters the opposite side defined by the tight-fitting central duct knives 1307, 1308, the supply air will be heated by the higher temperature of the heat exchange module 1110.

[0183]

[0183] The indoor side of the sleeve air guide assembly is provided with a plurality of surrounding air direction foils 1314 to achieve even distribution to the indoor room units. End caps 1316 are provided to support and hold the rotary heat exchange module 1110 during assembly. A center hole 1317 is provided to hold the static central duct structure 1109 by receiving its protruding member 1167, the base of which may form the center of the indoor ball bearing 1120. The sleeve air guide assembly 1330 may include one or more surrounding foil support rings 1311 toward the outdoor end of the sleeve air guide assembly 1330 to ensure accurate and stable positioning of the vertical static outer flow separator knives 1312, 1313.

[0184]

[0184] Experiments show that the rotating heat exchange module 110 solves the condensation problem under almost all conditions.

[0185] In a further embodiment of the invention, an air filter may be attached to the indoor side of the impeller as shown in Figures 121A to 121E and 122A to 122C. In this embodiment, the impeller 1210 and filter 1211 are both connected together in a rotating relationship. Extending from the indoor side of the impeller is a circular impeller duct 1213 having an inner diameter adapted to fit the outer diameter 1214 of the impeller's exhaust inlet. An exhaust spinning element 1232 is attached internally to a central portion 1231 of the impeller structure and comprises a plurality of propeller blades / segments equally spaced in an annular shape about the central portion 1231, the central portion 1231 extending longitudinally towards the indoor side, the propeller blades pointing outward from the central portion 1231 and optionally attached externally to the circular impeller duct 1213, the propeller blades being curved towards the exhaust inlet of the impeller so as to help direct the exhaust towards the rotating impeller and impart a spin to it before it enters, as the impeller rotates, thereby reducing noise and resistance to the exhaust 1018, 1019 flow.

[0186] The filter 1211 is pipe-like, preferably formed as a cone, and is attached to the outside of the impeller 1210 and impeller duct 1213 in a longitudinal direction spanning the intake air outlet channels of the impeller 1210 and impeller duct 1213 such that the intake air 1016, 1017 flows towards the inside of the longitudinally oriented first part of the conical filter 1211 as it leaves the impeller 1210. A second part of the conical filter 1211 spans the outside of the circular impeller duct 1213. The conical shape of the conical filter 1211 has a larger inner diameter on the impeller side. The smaller inner diameter of the conical filter 1211 matches the outer diameter of the circular impeller duct 1213, and the narrow end of the conical filter 1211 fits into the impeller duct 1213 in a closed position to force all of the air through the air filter 1211 approximately perpendicular to the vertical air intake flow path 1224 as the air intakes 1016, 1017 are distributed along the inside of the conical filter 1211. The conical filter 1211 rotates with the impeller 1210. An inner spacing member (not shown) may be placed outside the impeller duct to allow sufficient space for the air intakes 1016, 1017 to reach the entire vertical interior surface of the conical filter 1211. These spacing members may be omitted if the air pressure from the rotating impeller 1210 can sufficiently push the conical filter 1211 outward to allow sufficient space for the flow of the supply air 1016, 1017 along the filter's inner surface. The impeller may have a protruding flange 1215 formed as a base on its indoor-facing side for receiving the outdoor end of the conical filter 1211 in this embodiment. The outer portion of the outdoor-facing side of the protruding flange 1215 comprises an air labyrinth seal or seal sliding surface, which operates in engagement with a corresponding static seal-like flange 1216 fixedly attached to the impeller unit casing 1218. The static seal-like flange 1216 defines the height at which the assembly of the impeller 1210, conical filter 1211, and impeller duct 1213 is located in the impeller unit casing 1218 and filter casing 1219.

[0187] The supply air 1016, 1017 flows outwardly through the conical filter 1211 as the impeller 1210 and conical filter 1211 rotate. Outside the conical filter 1211, a portion of the static filter casing 1219 may include a filamentary auger member 1221 between its inner static seal-like flange 1216 and the air director unit 1220 that defines a space and path for the supply air to exit the outer surface of the conical filter 1211 and flow toward the air director unit 1220. The air director unit 1220 includes an air director inner ring 1222 whose diameter is comparable to the inner tip diameter 1223 of the impeller duct 1213. An impeller inner duct air seal (not shown) is provided between the air director inner ring 1222 and the inner tip diameter 1223 of the impeller duct 1213. The impeller inner duct air seal (not shown) prevents the air supply passages 1016, 1017 from separating from the exhaust passages 1018, 1019. The filamentous auger member 1221 directs the air downstream toward the indoor side in a controlled helical trajectory, which also reduces the tunneling effect.

[0188]

[0188] The impeller 1210, the impeller duct 1213, and the conical filter 1211 are connected to each other and rotate together when the motor 1103 is driven. The motor is included in an impeller motor housing 1212 located in the center of the impeller 1210, which may be an integral central part of the impeller 1210 and further provides an opening facing the outdoors so that the motor 1103, which is fixedly attached to the static impeller unit casing 1218, can enter the impeller motor housing 1212 from the outdoors side. The impeller 1210, the impeller duct 1213, and the pipe-shaped circular filter 1211 may be removed by pulling them out of the static impeller unit casing 1218 on the indoor side of the ventilation unit 1230. The pipe-shaped circular filter 1211 may then be removed by pulling it away from the impeller 1210 and the impeller duct 1213. The impeller 1210 may be cleaned and a new pipe-shaped circular filter 1211 can be installed around the impeller duct 1213 before being attached to the static impeller unit casing 1218 by pushing the assembly of the impeller 1210, impeller duct 1213 and pipe-shaped circular filter 1211 into the static impeller unit casing 1218 until the air labyrinth seal or seal sliding surface of the protruding flange 1215 connects with the static seal-like flange 1216 which is fixedly attached to the static impeller unit casing 1218, and the impeller 1210 connects to the motor 1103.

[0189]

[0189] The static filter casing 1219 air director unit 1220 may be integrally formed, with at least the static filter casing 1219 having an outer diameter dimensioned to fit snugly inside the unit casing 1003 in a non-slip manner when pressed inside the unit casing 1003.

[0190] Next, one embodiment of the ventilation unit 1230 is assembled as shown in cross-sectional view 122C, where the indoor cover 1264 and unit casing 1003 hold and support the ventilation assembly, which includes the rotary heat exchange module 1110 and the fixed central duct structure 1109 connected to the static end caps 1316 via the indoor-side ball bearings 1120. The indoor-side ball bearings 1120 also provide the rotational connection points for the rotary heat exchange module 1110. On the outdoor side of the fixed central duct structure 109, a central duct hub 1325 is provided, which is fixedly held by central spokes 1327 connected at the outdoor-most side of the fixed central duct structure 109. The motor-side ball bearing 1119 also rotationally holds the impeller assembly, including the impeller 1210 and conical filter 1211, in place, pushing it against the static sealing flange 1216, which is fixedly attached to the impeller unit casing 1218. A retaining central recess of the impeller with a shaft casing 1104 for receiving the motor shaft 1004 provides a rotational connection between the motor and impeller assembly, and the shaft casing 1104 may be designed to provide a resilient spring force to retain the motor shaft 1004 when the impeller assembly is installed. Other connection mechanisms may also be provided, such as, but not limited to, male and female protrusions and recesses, bolt and nut connections, click connectors, splinting the shaft to the central duct of the impeller assembly, etc.

[0191] A further embodiment of the ventilation unit is shown in Figures 123A to 123C, with the heat exchange module removed in Figure 123B and the impeller and rotary filter removed in Figure 123C. The paths of the supply air 1016, 1017 and exhaust air flows 1018, 1019 are shown in Figure 123A.

[0192] In a further embodiment, the ventilation unit 1001 may be adapted to provide maximum ventilation effect / airflow. In such a case, the rotary heat exchange module 1110, room unit, and filter unit 300 may be replaced with a static module 1190, room module, and optional filter (hereinafter referred to as a summer module) as shown in FIGS. 119A to 119C. The summer module is primarily used when heat exchange is not required and high airflow for filtering and / or transporting excess heat is more important. The summer module 1190 is located in the unit casing 1003 on the indoor side of the dual-mode fan 1200. The summer module 1190 comprises an inner central duct 1193 and an annular vertical duct 1194 defined by the outer surface of the wall of the inner central duct 1193 and the inner surface of the unit casing 1003. The summer module 1190 provides a direct path for exhaust air flow from the indoor side of the ventilation unit 1001 through an inner central duct 1193 and into the inner central portion 1102 on the indoor side of the dual mode impeller 1002 of the dual mode fan 1200. In the opposite direction, supply air is directed from the outer annular ring area 1182 on the indoor side of the impeller 1002 of the dual mode fan 200 directly to the indoor side of the ventilation unit 1001 through annular vertical duct 1194.

[0193]

[0193] The summer module 1190 may further be provided with a pollen / smog filter 1192 for filtering the supply air, which is disposed in the path of the supply airs 1016, 1017. The pollen / smog filter 1192 may be formed into a cone shape with a wide outer periphery by the indoor side of the pollen / smog filter 1192, and may be disposed in an annular vertical duct 1194 defined by the outer surface of the wall of the inner central duct 1193 and the inner surface of the unit casing 3. The inner diameter of the narrow end of the pollen / smog filter 1192 closest to the dual-mode fan 1200 has an inner circumference that matches the outer diameter of the inner central duct 1193, so that the supply air cannot slip through the inside of the pollen / smog filter 1192. At the other end, the outer diameter of the widest part of the pollen / smog filter 1192 closest to the indoor side of the ventilation unit matches the inner diameter of the unit casing 1003 so that the supply air cannot slip past on the outside without passing through a filter before entering the room unit of the ventilation unit 1001. In this way, the supply air must pass through the pollen / smog filter 1192 as it flows from the dual mode fan 1200 to the indoor side of the ventilation unit 1001. The filtering characteristics may be adapted to throughput requirements and the degree of pollen and pollution.

[0194] In one embodiment of the present invention, the rotary heat exchange module 1110 and room unit of the first embodiment are provided as an interchangeable assembly and can be easily replaced with a second embodiment of the room unit comprising a static summer module 1190 and optional pollen / smog filter 1192. This makes the unit a powerful air purifier as well as an effective cooler in warmer climates / seasons.

[0195]

[0195] The indoor side of the ventilation unit 1001 terminates in a room unit having peripheral surrounding flow guides 1260, 1263 and indoor covers 1122, 1264, which may be defined by an assembly that can partially restrict airflow in one or both directions.

[0196] In one embodiment of the room unit, as shown in Figure 120, the airflow is guided by a plurality of foils 1263 arranged perpendicular to the airflow in a peripheral annular ring between the indoor cover 1264 and the enclosing base 1265. When the room unit is placed on a ventilation unit 1001 with a rotating heat exchange module 1110 and vertical static outer flow separator knives 1312, 1313, supply air will blow out between the foils 1263 on one half of the peripheral annular ring between the indoor cover 1264 and the enclosing base 1265, and exhaust air will be drawn in the opposite half. The foils are hinged for rotation on one side 1266, 1267 and connected to foil rotation means (not shown) on the opposite side 1266, 1267 so that they can be rotated to introduce more foil area into the airflow, which may result in restricting the airflow to either flow direction. The rotating means may be driven by one or more small electric motors located in the room unit, allowing both flows to be throttled independently. Thus, for example, four modes may be provided: low supply / low exhaust, low supply / high exhaust, high supply / low exhaust, and high supply / high exhaust. Fewer modes may be used, and even intermediate positions may be selectable. It is also possible to provide vacuum, equilibrium, or overpressure conditions on the indoor side of the ventilation unit. This allows the unit to be balanced for maximum efficiency during pressure differential changes.

[0197] In one exemplary scenario, a "Sleep Mode" can ensure that the ventilation unit provides minimal ventilation, for example in a bedroom during the day. Both the intake and exhaust airflows may be throttled to their maximum to prevent excessive leakage of hot air on a windy day.

[0198]

[0198] A further scenario where individual throttles are required is the use of summer modules during pollen season: on windy days, the throttles may be set to provide overpressure to the interior side, forcing the intake air containing clean, pollen-free air into the house, thereby maintaining overpressure inside the house and preventing pollen from leaking into the house through small gaps and cracks.

[0199] In a second embodiment of a room unit for use with a static summer module 1190, as shown in Figures 119A-119C, the supply airflows 1016, 1017 flow from an annular longitudinal duct 1194 defined by the outer surface of the wall of the inner central duct 1193 and the inner surface of the unit casing 1003, through an optional pollen / smog filter 1192, and exit the ventilation unit 1001 by being guided by a plurality of house unit foils 1263 arranged perpendicular to the airflow in a peripheral annular ring between an inlet cover 1195 and an enclosing base 1265. The enclosing base 1265 may be omitted by using the room wall itself as a channeling surface. The inlet cover 1195 is formed as an outwardly curved flange connected at one end to the indoor end of the inner central duct 1193, and extends in diameter outward to guide the supply air through the house unit foils 1263. The house unit foils 1263 are hinged for rotation on one side 1266, 1267 and connected to foil rotation means (not shown) on the opposite side 1266, 1267, allowing them to rotate to introduce a larger foil area into the airflow, which may result in restricting the intake airflow. The rotation means may be driven by one or more small electric motors located in the room unit. Exhaust air 1018, 1019 is introduced to the room units by a circular room unit exhaust duct 1196 defined by the outer surface of the inlet cover 1195 and the inner surface of the exhaust cover 1191. The exhaust cover 1191 may advantageously be formed with a concave shape that mirrors the curve of the inlet cover 1195, so that the exhaust air flow is less turbulent as it passes through the circular room unit exhaust duct 1196 and into the inner central duct 1193. Additional house unit foils (not shown) may be positioned in the path of the exhaust flow of the circular room unit exhaust duct 1196, and these foils may also be rotationally hinged and connected to foil rotation means (not shown) as described above.

[0200]

[0200] In further embodiments shown in Figures 101, 104, 105, 107, and 108, the room unit flow guide 1260 may have a perforated 1261 surface through which the airflow must pass. The flow guide 1260 may also have a dynamically changeable restriction function. This may be achieved by adding a second movable perforated film 1262 to the flow guide 1260. By adding a control means such as a stepper motor connected to the second movable perforated film 1262, it is possible to slide the perforations of the second movable perforated film 1262 over the perforations 1261 of the flow guide 260, thereby changing the flow resistance as it passes through the flow guide 1260. The airflow is directed toward the indoor side on one half of the flow restrictor and in the opposite direction on the other half. The flow may be restricted to one or both halves of the flow guide 1260, thereby allowing the ventilation unit 1001 to create a pressurization or vacuum effect on the indoor side of the ventilation unit 1001.

[0201]

[0201] While the room unit is involved in the optimal operation of the ventilation unit of the present invention, it is recognized that any of the above room unit embodiments may be provided as a stand-alone device for implementing other ventilation unit types.

[0202]

[0202] In one embodiment, the ventilation unit 1001 is installed in a wall between the outdoor environment and the interior of a room. The wall typically includes a through-channel having a cross-section corresponding to the outer cross-section of the unit casing 3, including tolerances. The cross-sectional shape may be uniform throughout the depth of the wall (wall thickness), as is also the case for the ventilation unit. The ventilation unit may have a cylindrical outer shape. A duct sleeve (not shown) may be provided for installation in the through-channel in the wall. The internal shape of the duct sleeve may match the outer shape of the ventilation unit 1001 and its additional wiring and optional sensor connections. The duct sleeve may have through-holes for power and optional control signal wiring and connectors adapted to connect to wiring provided in the ventilation unit for powering the motor, sensors, and electronics included in the ventilation unit 1001. The connector and shape may be such that the ventilation unit 1001 can be slid into the duct sleeve and a snap-latch lock can hold it in place and fully operational. Other locking mechanisms may be used to provide both a continuous mode of operation and an embodiment that allows for switchable heat exchange mode and summer mode assemblies.

[0203]

[0203] The ventilation unit 1001 is installed so that the impeller side is oriented toward the outdoor environment so that the impeller can operate freely. Attaching an impeller protective cover to the outside of the impeller is optional, and the impeller protective cover may also guide and separate the incoming airflow 1016 and the outgoing airflow 1019 relative to the impeller 1002.

[0204] In a third embodiment of the ventilation unit 1001, shown in Figures 115, 116, 117, and 118, a separate extender duct and separate air directing module are provided to allow installation of the ventilation unit 1001 in thicker walls. Therefore, in such walls, the standard-length version of the impeller 1002 would be positioned somewhat within the wall when viewed from the outside. The extender provides an inner central extender duct 1180 to direct the supply air 1016 from the outdoor side of the ventilation unit to the impeller 1002, and a concentric outer duct 1181 around the inner central extender duct 1180 to direct the exhaust air 1019 from the impeller 1002 to the outdoor side of the ventilation unit 1001. A longer extender duct may advantageously provide a separate air directing module 1160 to stop the air spin of the exhaust air 1019 exiting the impeller 1002 and heading towards the outdoor side of the ventilation unit 1001. An air labyrinth seal 1170 is provided on an annular flange 1171 separating the inlet channel from the outlet channel of the outdoor-facing impeller 1002 and connects to the inner portion 1161 of the concentric inner flange of another air directing module 1160. Similarly, the circular inner portion 1182 of the inner central extender duct 1180 is sealingly positioned against the outer portion 1162 of the concentric inner flange of another air directing module 1160, so that the supply air flowing through the inner central extender duct 1180 does not leak into the exhaust air flowing in the opposite direction through a concentric outer duct 1183 around the inner central extender duct 1180 that directs the exhaust air 1019 from the impeller outward.

[0205]

[0205] Further embodiments of the heat exchange module and filter module (not shown) may include a non-rotating, stationary filter module and a motor-driven, rotating heat exchange module. The heat exchange module may be driven by a geared shaft connected to the impeller motor or by a separate motor used solely to rotate the heat exchange module.

[0206] In a further embodiment of the invention, the dual-mode fan may be combined with a counterflow heat exchanger installed in a wall duct, operating alone as a mobile device or providing an optimization unit for drying rooms with moisture and / or radon problems, such as in basements. In such environments, neither heat exchange nor air filtering is important; the challenge is to transfer a sufficient amount of air from the indoor room to the airflow. Exhaust air must be transported to the outside, and dry air must be supplied. Therefore, a typical counterflow unit with exhaust capacity may be connected in series with the fan unit.

[0207]

[0207] Embodiments of the ventilation unit defined above or combining any number of features from the above embodiments individually may be provided with wired or wireless communication means allowing communication contact with a provided remote monitoring and control system. This remote monitoring and control system may comprise an application / app, communication means and analysis program provided as a cloud service or on a standalone handheld computer such as a laptop, tablet, smartphone etc. Thus, monitoring and control of ventilation characteristics may be provided as a service or user-defined from a remote control device. Sensors and motors of the ventilation unit may be remotely controlled.

[0208]

[0208] Two or more ventilation units may be in communication contact via communication means included in the ventilation units or via a remote monitoring and control system. Sensors may also be installed in the indoor environment of the ventilation units to communicate with the control unit 1105 of the ventilation units and / or the remote monitoring and control system to provide more flexible control functions for the ventilation system.

[0209]

[0209] The present invention further provides a dual mode impeller assembly for use in a room ventilation unit, comprising a dual mode impeller 1002, 1210 and a motor 1103 for imparting rotational force to the dual mode impeller 1002, 1210, wherein the dual mode impeller 1002, 1210 has a cylindrical shape for rotation about its longitudinal central axis 1166 and comprises a plurality of air intake channels 1061 and air exhaust channels 1062, wherein as the dual mode impeller 1002, 1210 rotates, the air intake channels 1061 direct air intake 1016, 1017 from a central portion 1181 on a first side of the dual mode impeller 1002, 1210 towards an outer annular portion 1182 on a second side of the dual mode impeller 1002, 1210 and 1210 to the central portion 1181 of the first side of the dual mode impeller 1002, 1210, and exhaust channels direct the exhaust 1018, 1019 in the opposite direction from the central portion 1102 of the second side of the dual mode impeller 1002, 1210 towards the outer annular ring area 1184 of the first side of the dual mode impeller 1002, 1210 and from the outer annular ring area 1184 of the first side of the dual mode impeller 1002, 1210 to the central portion 1102 of the second side of the dual mode impeller 1002, 1210, and the walls of the intake channels 1061 form part of the walls of the exhaust channels 1062 that intersect and flow between the intake channels 1061.

[0210]

[0210] A second dual mode impeller assembly according to the first device embodiment, further comprising a circular air filter 1108, 1211 arranged on a second side of the dual mode impeller 1002, 1210, the circular air filter 1108, 1211 having a first surface facing the dual mode impeller for receiving the supply air 1016, 1017 flowing out from the outer annular portion 1182 on the second side of the dual mode impeller 1002, 1210.

[0211]

[0211] A longitudinal central duct 1111, 1213 is provided for separating the outer air supply 1016, 1017 and the inner air exhaust 1018, 1019 on the second side of the dual mode impeller 1002, 1210, the first portion of the longitudinal central duct 1111, 1213 having a diameter adapted to match the diameter of the central portion 1102, 1214 of the second side of the dual mode impeller 1002, 1210, and 1, 1213 is sealingly disposed on the dual mode impeller 1002, 210 to ensure little or no mixing of air between the intake air streams 1016, 1017 and the exhaust air streams 1018, 1019, and at least a portion of the circular air filter 1108, 1211 is disposed above and outside the longitudinal central duct 1111, 1213.

[0212]

[0212] A fourth dual mode impeller assembly relating to any of the first to third device embodiments, further comprising a circular static air director 1107, 1220 arranged in the intake air flow 1016, 1017 path on the second side of the dual mode impeller 1002, 1210, the circular static air director 1107, 1220 having a foil arranged in an annular inlet path outside the periphery of the central duct 1111, 1222, the foil of the air director 1107, 1220 being provided to block most of the rotational force of the intake air resulting from rotation of the dual mode impeller 1002, 1220.

[0213]

[0213] A fifth dual mode impeller assembly according to the fourth device embodiment, having two or more inlet heights h1, h2 to reduce the surf-riding effect that occurs when the foil impacts the boundary layer on a "low angle" approach.

[0214]

[0214] A sixth dual mode impeller assembly according to the first apparatus embodiment, wherein the dual mode impeller further comprises a central longitudinally disposed motor shaft casing 104 having a central recess for receiving and retaining a portion of the motor shaft 4.

[0215]

[0215] A seventh dual mode impeller assembly according to the sixth device embodiment, wherein the motor shaft casing 104 includes one of a resilient material, male and female protrusions and recesses, a bolt and nut connection, a click connector, or a splint fixing of the shaft to the central duct of the impeller assembly to provide a holding force to the received motor shaft 4.

[0216]

[0216] The dual mode impeller further comprises a heat exchange module 1110 arranged longitudinally on a second side thereof, the heat exchange module 1110 being configured to rotate around a half-pipe shaped central duct structure 1109, the heat exchange module 1110 further comprising an enclosed collector channel 1320 for receiving all inlet air 1016, 1017 flowing from the outer annulus 1182 on the second side thereof and directing it into one longitudinal half of the heat exchange module 1100, the exhaust air 1018, 1019 flowing through the other longitudinal half of the heat exchange module 1110, the central duct structure 1109 comprising a half-pipe structure for longitudinally bisecting the airflow inside the heat exchange module 1110, the central duct structure 1109 further comprising a central duct extending outwardly on each side thereof an air guide assembly 1330 having static outer flow separator knives 1312, 1313 with an inward profile that matches the tapered outer shape of the rotary heat exchange module 1110 and an outward profile that matches the inside of the unit casing 1003; and an eighth dual mode impeller assembly according to any of the first to seventh device embodiments, wherein the central duct knives 1307, 1308 have duct knives 1307, 1308 on their sides, the central duct knives 1307, 1308 having radially peripheral end shapes that match the inner curvature of the heat exchange module 1110; and the dual mode impeller assembly further comprises a sleeve air guide assembly 1330 having static outer flow separator knives 1312, 1313 with an inward profile that matches the tapered outer shape of the rotary heat exchange module 1110 and an outward profile that matches the inside of the unit casing 1003; and the central duct knives 1307, 1308 and the static outer flow separator knives 1312, 1313 are aligned in pairs longitudinally on the inside and outside of the heat exchange module.

[0217]

[0217] A ninth dual mode impeller assembly relating to any of the second to eighth device embodiments, in which a dual mode impeller 1002, 1210 and a circular air filter 1211 are connected together in a rotating relationship, and the circular air filter 1211 is pipe-shaped and extends approximately vertically across a portion of the second side of the dual mode impeller 1002, 1210 and a portion of the vertical central duct 1213, providing an air intake flow path 1224 that is approximately perpendicular to the vertical direction through the air filter 1211.

[0218]

[0218] A tenth dual mode impeller assembly relating to any of the second to eighth device embodiments, in which the heat exchange module 1110 and the circular air filters 1108, 1211 are connected together in a rotating relationship, and the circular air filters 1108, 1211 extend in a direction approximately perpendicular to the vertical direction, providing a vertical intake air flow 1321 path through the air filter 1108.

[0219]

[0219] A first ventilation unit embodiment having a dual mode impeller assembly relating to any one of the first to tenth device embodiments, further comprising a peripheral surrounding flow guide 1260, 1263 and an indoor cover 1122, 1264 for terminating the indoor side of the ventilation unit.

[0220]

[0220] A second ventilation unit according to the first ventilation unit embodiment, wherein the flow guides 1260, 1263 may be defined by an assembly that can partially restrict airflow in one or both directions.

[0221] Third priority application: No. 20190732

[0221] The object of the third priority invention is to provide an air fan / filtration unit for use in domestic dwellings either as a ceiling mounted unit or as a unit adapted to be placed on a table / floor, which solves all or part of the above problems by reducing the secondary effects caused by tangential air velocity.

[0222]

[0222] A low noise emission air purification device is provided.

[0223]

[0223] In a first embodiment of the present invention, an air filtration unit is provided for ceiling mounting, preferably at an optical / electrical connection point / outlet. The unique design of the filtration unit allows for higher air flow rates than traditional air fans, while producing significantly less noise and producing less tangential air movement from the fan / filter unit. Therefore, it can achieve submicron particle purification capabilities that are superior to comparable air fan / filter units.

[0224]

[0224] In a further embodiment of the present invention, an air fan / filtration unit is provided that is configured to be placed on a table or placed on the floor. Such devices face the additional challenge of shielding the rotating elements of the air filter device from the environment. A shielded device is provided with unique features for partially or completely eliminating such operating noise. Traditional problems associated with tangential air movement from the unit often prohibit placement of the device near people because drafts can become unacceptably strong. One embodiment of the present invention includes a casing that holds a horizontally mounted fan / filter unit, directing the airflow partially or completely vertically upward.

[0225]

[0225] Common to all embodiments is the reduction of undesirable drafts and noise without increasing size or reducing throughput.

[0226]

[0226] Alternative embodiments of the present invention include additional features such as carbon filtration, ionization, light, heat, added fragrance, humidification, and speakers.

[0227] A key feature of various embodiments of the present invention includes a low noise discharge air purifier assembly that utilizes the jet effect of a low noise air directing device located downstream of the filter that delivers air counter to the spin direction of the fan / filter. The jet effect of the low noise air directing device facilitates the motor driving the rotating assembly, thereby reducing power consumption and eliminating some of the resistance to the spin of the assembly.

[0228]

[0228] Additional features and advantages of the present invention are described in, and will be apparent from, the following brief description of the drawings and the detailed description that follows. Figure 201 - Shows a side view of the ceiling fan assembly. Figure 202 - Shows a perspective view from below of the ceiling fan assembly. Figure 203 - Shows a cross-sectional perspective view from above of a ceiling fan assembly. Figure 204 - Showing a cross-sectional side view of the ceiling fan assembly. Figure 205 - Shows a view from below of a ceiling fan assembly. Figure 206 - Showing a cross-sectional exploded view of the ceiling fan assembly. Figure 207 - Showing a cross-sectional partially exploded view of the ceiling fan assembly. Figure 208 - Shows a side view of the table fan assembly. Figure 209 - Shows a top view of the table fan assembly. Figure 210 - Shows a cross-sectional side view of the table fan assembly. FIG. 211 - Shows a cross-sectional perspective view from above of the table fan assembly. FIG. 212A—Table fan assembly exploded view showing vertical outer foils. FIG. 212B—Table fan assembly exploded view showing the concentric cylindrical rigid cover. Fig. 213A - Principle of floor fan assembly, showing vertical outer foils. Figure 213B - Floor fan assembly principle, showing air director mesh. 214A to 214B - Showing the inside of the air director mesh. 215A to 215C - Showing the outside of the air director mesh. 216A to 216B - Showing an embodiment of a cap and a cross-sectional side view. 216A-216B—Cross-sectional side views of an embodiment of a helmet are shown.

[0229]

[0229] In the description that follows, the use of certain terms shall be construed broadly and at least in the meanings defined below.

[0230]

[0230] CMH: Cubic meters per hour

[0231] CADR: Clean Air Delivery Rate. There are typically three values measured: smoke, pollen, and dust. CADR is usually measured according to the ANSI / AHAM AC-1 standard and is the rate at which a standard 28.5m 3 sieve is filtered to remove all particles of smoke, pollen, or dust in a specified fraction multiplied by the flow throughput. 3 gives the value of the room volume fraction of the air in the room, in other words, the amount of clean air supplied.

[0232] Air: Although the devices of the present invention are primarily adaptable for use in air filtration, the devices and systems may be used in any type of gaseous environment. When the term "air" is used herein, it shall be understood to mean any type of gas.

[0233]

[0233] The present invention will now be described in more detail with reference to the drawings as needed.

[0234]

[0234] Figures 201 to 207 show a first embodiment of the present invention in which a ceiling mounted air fan / filter assembly 2001 comprises a rotary fan assembly made up of at least one set of annularly mounted fan blades 2003 each mounted in a longitudinal direction 2100 which impart an axial fan geometry to an intake section 2040 and a radial fan geometry to an outlet section 2041, which is a spinner of incoming air as the fan / filter assembly rotates 2020 about a longitudinal central axis 2038.

[0235] The airflow generated by the fan blades 3 is distributed along the inside of a filter 2004 included in the air fan / filter assembly 2001. The filter 2004 may be formed as a circular concentric sleeve of, for example, pleated filter media attached to the outside of the circle of the longitudinal fan blades 2003. Other filter materials may also be used. The filter 2004 is rotatably attached to the fan blades 2003 and rotates together with the fan blades 2003 about the longitudinal central axis 2038.

[0236] The fan blades 2003 may be shaped to contact the incoming airflow 2010 at a matching foil angle, pre-spinning the air and exerting radial pressure on the filter 2004. The air is partly pushed by the blades 2003 and partly drawn into the inner duct 2013 by the suction created by the rotating filter 2004 and outer frame 2002. The illustration shows an embodiment in which air is drawn into the fan / filter assembly 2001 only from below, and the top of the fan / filter assembly 2001 is closed by a circular end cap 2036. It should be understood that in different embodiments, the end cap may be formed as a mesh, plate, or the like with openings that allow air to pass through as well, in which case the fan blades 2003 are shaped to propel air through both longitudinal openings of the fan / filter assembly 2001, i.e., from below and from above, as the fan / filter assembly 2001 rotates. The fan blade assembly may include one or more guard rings 34 that provide equal distance between the blades 2003 .

[0237] The air fan / filter assembly 2001 further comprises a set of longitudinal outer foils 2002 arranged around the filter 2004 and the fan blades 2003. The outer foils 2002 are rotatably connected to the filter 2004 and the fan blades 2003 and are arranged approximately tangential to the outside of the filter 2004, with their inner side edges 2050 located outboard of the filter 2004 and their outer side edges 2051 located radially outward of the inner side edges 2050 of the adjacent outer foil 2002 opposite the spin direction 2020. The inlet area / spacing 2052 defined by the area between all of the inner side edges 2050 of the outer foils 2002 is greater than the outlet area defined by the area / spacing 2053 between all of the outer side edges 2051 of the outer foils 2002, thereby creating a plurality of low noise air directing devices, the outlet area forming a type of outlet nozzle 2053.

[0238] The outer foil 2002 may be hinged to the frame 2035, 2039, 2039' and the variation of the nozzle opening 2053 may be done by changing the orientation of the foil 2002 relative to the outside of the filter 2004, i.e. by changing the outlet area. The variation of the angle of the outer foil may be continuous or according to a set of predetermined angles, and the variation of the angle may be done by a manually operated device or by an automatic or remotely operated device.

[0239]

[0239] The outer foil 2002 assembly may include one or more foil guard rings 2035 to maintain the shape and spacing between the outer foils 2002.

[0240]

[0240] The outer foil 2002 assembly may be provided in a non-periodic pattern where the spacing between the outer foils 2002 may further enhance noise reduction.

[0241] As the air fan / filter assembly 2001 rotates, airflow 2010 is drawn into the inner duct 2013 of the air fan / filter assembly 2001 from below (optionally from both below and above), and the energy imparted to the airflow by the fan blades 2003 is used partly to push the air out of the filter (2011) and partly to increase the airflow velocity through the low noise air director outlet opening 2012 in the outer foil 2002. Air is therefore expelled from the air fan / filter assembly 2001 in a direction opposite to the spin direction 2020 of the air fan / filter assembly 2001.

[0242]

[0242] The effect of the jet generating outer foil 2002 of the low noise air directing device is to eliminate all or part of the tangential air velocity as it exits the filter 2004, thereby also eliminating / reducing drafts and noise.

[0243]

[0243] The present invention can provide the same clean air delivery rate (CADR) with a smaller product size (diameter) and lower power consumption than prior art devices, which can result in highly efficient pollen and dust filtration in domestic dwellings with limited ceiling height.

[0244]

[0244] Without the static outlet grille and the noise associated with air passing through such an opening, ceiling embodiments of the present invention are open to the use of lower grade, more permeable filters, which can move much larger amounts of pollen-depleted air without adding noise. In table and floor embodiments, the higher permeability of filter 2004 will remove more noise components as the velocity of the reverse jet increases. Thus, the tangential velocity, and therefore the outflow velocity through the outlet vent, decreases.

[0245] In one embodiment of the invention, the outer foil 2002 may be positioned at a slight angle (not shown) to the longitudinal direction 2100 to deflect the airflow upwards or downwards. In yet another embodiment, the outer foil 2002 may be designed in a fishbone pattern from an "equator" level 2101 (not shown), thus emitting air upwards from the top half of the outer foil 2002 and downwards from the bottom half of the outer foil 2002.

[0246]

[0246] In a further embodiment of the invention, the outer foil may be changed between two or more positions / orientations so that the airflow as it exits the air fan / filter assembly 2001 may be varied.

[0247]

[0247] The position / orientation may be dynamically changeable by a mechanical manual switch, remote control, or automatic switching.

[0248] In yet another embodiment, the outer foil 2002 may change its position / orientation / angle between different modes of operation, for example, between a position that provides a first tangential air velocity due to a jet effect and a position that provides a second, lower tangential air velocity. In a further embodiment, multiple positions may be provided. The latter mode of operation may cause the air fan / filter assembly 2001 to operate in a manner that mimics a traditional ceiling fan.

[0249]

[0249] In yet another embodiment of the present invention, an outer foil 2002 is provided that is designed in a variety of patterns to allow for many different outlet airflow patterns and thus meet custom needs related to the airflow pattern exiting the air fan / filter assembly 2001 with a customized low noise air directing effect.

[0250] In yet another embodiment, the low noise air directing device of the outer foil 2002 may be replaced by a concentric cylindrical rigid cover 2124, 2125 with multiple jet nozzles 2150, as shown in Figures 212B, 214A and B, and Figures 215A, 215B and 215C. Figures 214A and 214B show one embodiment of a section of such concentric cylindrical material viewed from the inside 2125 facing the filter where the airflow is introduced (2151) into the nozzles 2150, while Figures 215A, 215B and 215C show a section of a similar exemplary embodiment viewed from the outside 2124 where the airflow exits the jet nozzles 2150 (2152). FIG. 212B shows the concentric cylindrical covers 2124, 2125 positioned on the table version of the air fan / filter assembly 80 described below, although the concentric cylindrical covers 2124, 2125 may also be implemented on both the ceiling-mounted air fan / filter assembly 2001 described above and the floor-mounted air fan / filter assembly 2131 described below.

[0251]

[0251] Additionally, a ceiling bracket 30 may be provided for mounting the air fan / filter assembly 2001 to a ceiling connection point, comprising electrical wiring for supplying power to the motor and controller, the controller, a communications module and connector 2031, and a motor 20 2032 provided with a motor shaft 2033 for driving and controlling the air fan / filter assembly 2001.

[0252]

[0252] The connection between the fan blades 2003, filter 2004, and outer foil 2002 may be made by circular end collars 2036, 2037 at the lower end of the air fan / filter assembly 2001 and / or an end cap 2036 at the upper end of the air fan / filter assembly 2001.

[0253] 206 and 207 show two versions of the air fan / filter assembly 2001 in exploded view. During maintenance, as shown in FIG. 207, the filter 2004 may be removed by removing the circular end collars 2036, 2037, after which the filter may be pulled out of the air fan / filter assembly 2001. A new filter may be inserted and the circular end collars 2036, 2037 reinstalled. The fan blades and outer foils are attached to the end cap 2036.

[0254] 208 to 212 show an embodiment of the present invention of a tabletop version of the air fan / filter assembly 80. The same principles as above apply with the addition of an optional mesh 2121 placed around the air fan / filter assembly 80 to prevent accidental contact between the spinning outer foils and people / animals. A breathable fabric / cover 2122 may additionally be placed on the outside of the mesh 2121. A central cone 2102 is provided for additional channeling of airflow when input from both above and below. A motor 2032 may be located within the stand 2105, along with other components (not shown) for controlling power and wiring.

[0255]

[0255] Fig. 211 shows how airflow 2011 flows through filter 2004 and the remaining air pressure is directed through the jet generating outer concentric devices 2002, 2124, 2125 of the low noise air directing device and discharged in a direction 2012 opposite to the direction of rotation of the fan / filter assembly 2080. The direction of outflow air 2012 is indicated by an arrowhead 2022 symbol representing movement towards the reader opposite to the direction of rotation 2020.

[0256]

[0256] In yet another embodiment, a tabletop version of the air fan / filter assembly 2080 may be provided as a free-hanging device from the ceiling, for example, suspended from a power cord or string (battery operated).

[0257]

[0257] Bottom cap 2123 and top cap 2123' are provided and statically positioned to protect the underside as well as the top side of air fan / filter assembly 80. Bottom cap 2123 and top cap 2123' have mesh cover openings on their inner portions that match the inner diameter of filter 2004. The inner portions of bottom cap 2123 and top cap 2123' admit airflow into air fan / filter assembly 2080. The mesh cover openings may also have a high-breathability filter (not shown) to prevent larger dust particles from being blown into filter 2004 of air fan / filter assembly 80. Bottom cap 2123 and top cap 2123' are connected to stand 2105, bottom cap 2123 directly and top cap 2123' via mesh 2121 / sleeve 2122 and bottom cap 2123.

[0258]

[0258] The mesh 2121 may be designed with only non-vertical mesh elements because the vertical elements have a larger noise pattern when horizontal airflow passes through the mesh 2121. The diagonal mesh elements will have a lower noise pattern.

[0259]

[0259] The mesh 2121 and sleeve are statically connected to the stand 105.

[0260]

[0260] It is also within the scope of the present invention to provide the protective mesh 2121 described above for the table version on the ceiling mounted air fan / filter assembly 2001 as well.

[0261] 213A shows a principle sketch of a floor-standing casing 2130 with only a partial view of the air fan / filter assembly 2131. A snail's house shaped collector channel 2132 is arranged around the air fan / filter assembly 2131 to collect the airflow from the low noise air directing device outer foil and direct the airflow towards an opening at the top of the casing 2130. The top opening 2137 is provided with an air directing foil 2133 which directs the airflow, for example directly upwards.

[0262]

[0262] In a further embodiment, the floor-mounted casing 2130 may be partially or completely covered by a highly permeable fabric or cover (not shown) to prevent unexpected items from entering the air outlets 2136, 2137.

[0263] The floor standing casing 2130 is provided in two embodiments, one with the above disclosed fan / filter assembly 2001 shown in FIG. 213A, and one in which the fan / filter assembly 2001 does not have an outer low noise air director jet but does have an air director mesh 2135 for reducing the output speed of the fan / filter assembly shown in FIG. 213B.

[0264] The air director mesh 2135, located between the casing 2130 and the rotating assembly 2131, will reduce tangential velocities, and the air director mesh 2135 is designed for optimal uniform throughput across the air director mesh 2135. By selecting a good mesh, it is possible to reduce tangential velocities while suppressing noise-generating turbulence. In other words, the present invention balances vertical and tangential permeability through the size and shape of the mesh to avoid noise-generating turbulence as the airflow passes through the air director mesh 2135.

[0265]

[0265] The permeability of the air director mesh 2135 is balanced so that the radial flow throughput is evenly distributed over the desired exit openings 2136, 2137.

[0266] The reduced exit velocity significantly reduces potential noise from turbulence and thus gives freedom in the design of the exit grilles 2133, 2136 so that the shape / form can be chosen according to the desired design criteria of the casing. The air director mesh, balanced for uniform distribution of air, partially preserves the local velocity direction.

[0267] In a further embodiment of the floor-standing assembly, the air fan / filter assembly 2131 may not be provided with an outer foil 2002. Such a version may emit air vertically upwards, providing a device that can purify large volumes of air, as drafts or adverse effects may be neglected. The casing 2130 and directional foil 2133 control the incoming airflow from the air fan / filter assembly 2131.

[0268]

[0268] The floor mounted air fan / filter assembly 2131 comprises a fan having an axial fan to provide a radial fan mode of operation. A unique feature of the present invention is that a filter 2004 is mounted around the rotatably connected fan / impeller 2003. The air fan / filter assembly 2131 may further comprise a filter / mesh module that covers the air inlet orifice 2134 to capture larger dust particles.

[0269]

[0269] The floor-mounted air fan / filter assembly 2131, like the table version air fan / filter assembly 2080, has an air intake orifice 2134 on either side of the fan, and as a result, two filter / mesh modules may optionally be provided covering each air intake orifice 2134.

[0270]

[0270] The filter / mesh module may be self-cleaning.

[0271]

[0271] A common possibility for all of the above embodiments is to combine one or more additional features such as carbon filtration, ionization, light, heat, added fragrance, humidification, speaker, etc.

[0272]

[0272] The carbon filtration may be incorporated into the filter 2004, for example, in a sandwich-type configuration, so that the carbon filter rotates with the filter 2004.

[0273] Lighting may be an additional feature where a socket for a lighting device may be provided when implemented with a ceiling mounted low noise emission air purifying device according to the present invention. The socket may be located on the top or bottom of the motor 2032 and may use the same power source / supply as the motor 2032.

[0274] All embodiments of the present invention may include one or more of electrical wiring for supplying power to the motor and controller, a controller, a communication module and connector 2031, and a motor 2032. The controller and communication module may communicate with a remote device via a wired or wireless communication channel. The remote device may be one or the like of a simple physical switch, a smartphone APP, a cloud service and cloud-connected computer application, a wireless communication device over any type of communication protocol including Wi-Fi and Bluetooth.

[0275] In yet another embodiment, a very narrow implementation of the present invention is placed in headgear, such as a helmet, cap, or protective hood, to provide a continuous flow of purified air toward the facial area of the person wearing the headgear. This air may be delivered in a focused manner with no or very low noise. An example of such an implementation is shown in FIG.

[0276] The present invention also provides a low noise emission air purification device, comprising: a radial fan having a plurality of fan blades 2003 rotating about a longitudinal central axis 38, the fan blades 2003 being mounted longitudinally 100 to provide an axial fan shape in an intake section 2040 and a radial fan shape in an outlet section 2041; a rotary fan assembly (2001, 2080, 2131) including a filter (2004) radially mounted on the outside of the radial fan and rotatably connected to the radial fan; Low noise emission air purifier further a low noise air directing device disposed around the fan assembly; and a motor 32 for rotating the fan assembly in a rotational direction 2020.

[0277]

[0277] A second device embodiment of a low noise emission air purifying device according to the first device embodiment, wherein the air directing device directs airflow in a directional distribution that provides optimal flow distribution.

[0278]

[0278] A third device embodiment of a low noise emission air purifying device according to the first or second device embodiments, in which the air directing device is rotatably connected to a fan assembly 2001, 2080, 2131.

[0279]

[0279] A fourth device embodiment of a low noise emission air purifying device according to any one of the first to third device embodiments, wherein the air directing device comprises nozzle openings 2053, 2150 for providing an air jet flow 2012 in a direction opposite to the direction of rotation 2020 of the rotary fan assembly 2001, 2080, 2131 to reduce power consumption and outgoing air velocity.

[0280]

[0280] A fifth device embodiment of a low noise emission air purifying device according to the fourth device embodiment, in which the nozzle openings 2053, 2150 are provided with a non-periodic pattern.

[0281] an air directing device comprising a plurality of longitudinal outer foils 2002 arranged around the filter 2004 and the fan blades 2003, the outer foils configured to direct the airflow from the air purifying device in a defined pattern; A sixth device embodiment of a low noise emission air purifying device according to any one of the first to fifth device embodiments, wherein the outer foil 2002 is rotatably connected to a rotary fan assembly 2001, 2080, 2131.

[0282]

[0282] A seventh device embodiment of a low noise emission air purifying device according to the sixth device embodiment, wherein the outer foil 2002 is hingedly connected to the frame 2035, 2039, 2039' and the nozzle opening 2053 may be changed between two or more outlet areas.

[0283]

[0283] An eighth device embodiment of a low noise emission air purification device according to the seventh device embodiment, in which the change in angle of the outer foil 2002 is continuous and the change in angle can be performed by a manually operated device or an automatic or remotely operated device.

[0284]

[0284] A ninth device embodiment of a low noise emission air purification device according to the fourth or fifth device embodiment, wherein the air directing device comprises concentric cylindrical rigid covers 2124, 2125 having nozzle openings 2150 for providing air jet flows 2152 having a direction 2012 opposite to the direction of rotation 2020 of the rotary fan assemblies 2001, 2080, 2131.

[0285]

[0285] A tenth device embodiment of a low noise emission air purifying device according to any one of the first to ninth device embodiments, further comprising a ceiling bracket 2030 for mounting the air fan / filter assembly 2001 to a ceiling connection point.

[0286]

[0286] An eleventh device embodiment of a low noise emission air purifying device according to any one of the first to ninth device embodiments, further comprising a stand 2105 for placing the air fan / filter assembly 2080 on a table.

[0287]

[0287] comprising a floor-standing casing 2130 having a front face 2138 and a rear face 2139, at least one of the front face 2138 and the rear face 2139 having an air inlet orifice 2134, two sides 2141, 2142, a bottom face 2143 and a top face 2144; A twelfth device embodiment of a low noise emission air purification device according to any one of the first to ninth device embodiments, wherein the top surface 2144 has an opening 2137, the floor-mounted casing 2130 further has a collector channel 2132, and the rotary fan assembly 2131 is mounted horizontally.

[0288] a collector channel 2132 having a snail's house design and disposed around the rotary fan assembly 2131 to collect the airflow from the rotary fan assembly 2131 and direct the airflow towards openings 2137 in the top surface 2144 of the casing 2130; A thirteenth device embodiment of a low noise emission air purifying device according to the twelfth device embodiment, wherein the upper surface 144 comprises an air directing foil 2133 configured to direct airflow, for example directly upwards.

[0289]

[0289] A fourteenth device embodiment of a low noise emission air purification device relating to the first or second device embodiment, comprising a floor-mounted casing 2130 having a front surface 2138 and a rear surface 2139, at least one of the front surface 2138 and the rear surface 2139 having an air intake orifice 2134, two sides 2141, 2142, a bottom surface 2143 and a top surface 2144, the top surface 2144 having an opening 2137, the floor-mounted casing 2130 further comprising a collector channel 2132, and a rotary fan assembly 2131 mounted horizontally.

[0290]

[0290] A fifteenth device embodiment of a low noise emission air purifying device according to the fourteenth device embodiment, in which the side portions 2141, 2142 are positioned upstream relative to the top surface 14 in the spin direction 2020 of the rotary fan assembly 2131 and are provided with an air outlet 2136.

[0291]

[0291] A sixteenth device embodiment of a low noise emission air purification device according to the fourteenth or fifteenth device embodiments, further comprising one or more air director meshes 2135 positioned between the casing 2130 and the rotating assembly 2131 so that the radial flow throughput is evenly distributed across the desired outlet openings 2136, 2137.

[0292]

[0292] A seventeenth device embodiment of a low noise emission air purification device relating to any one of the fourteenth to sixteenth device embodiments, wherein the upper surface 2144 is provided with an air directing foil 2133 configured to direct the airflow, for example directly upwards.

[0293]

[0293] An eighteenth device embodiment of a low noise emission air purification device relating to any one of the first to seventeenth device embodiments, further comprising one or more of carbon filtration, ionization, light, heat, added fragrance, humidification, and a speaker.

[0294]

[0294] A 19th device embodiment of a low noise emission air purification device relating to any one of device embodiments 1 to 9 and 12 to 18, wherein the low noise emission air purification device is arranged on the headgear to direct purified air towards the facial area of a person wearing the headgear.

Claims

1. Rotary pleated air filter (2), A motor (31) for rotating the pleated air filter and the axial radial impeller, wherein the rotary axial radial impeller (40, 40') is positioned inside the pleated air filter and rotatably connected to the pleated air filter, and the axial radial impeller (40, 40') has morphing fan blades that gradually change shape to impart a tangential velocity to the incoming air that coincides with the filter inlet of the pleated air filter and to change the flow from axial distribution to radial distribution, and the motor comprises: The pleated air filter has a cylindrical shape and is of the following formula: Gu=f ｈ ×p ｒ / (2×r Ｏ ×ε １／４ )>0.8 Designed according to the Gu number represented by, Here, f ｈ This is the length of the filter along the axis of rotation, p ｒ = (r Ｏ - r ｉ ) / Pleat interval (p ｓ ) and r ｉ This is the inner radius of the pleated air filter, r Ｏ This is the outer radius of the pleated air filter, Pleat spacing (p ｓ ) is the inner radius (r ｉ ) This is the distance between the tops of two adjacent pleats, ε is the filter efficiency. Air filter device.

2. The air filter device according to claim 1, wherein Gu is greater than 0.8 and less than 20, or more preferably greater than 0.8 and less than 10.

3. The air filter device according to claim 1, wherein Gu is greater than 1.2, and more preferably greater than 1.

5.

4. The rotary, cylindrical pleated air filter (2) is further equipped with an integrated conical fan element (44, 44') located at the deepest point, which tapers from its maximum diameter, so that air can be expelled from the rotary, cylindrical pleated air filter (2). The air filter device according to any one of claims 1 to 3, wherein the cone moves away from the inside of the filter and tapers toward the inflow area of ​​the cylindrical pleated air filter (2) in a rotating manner, and as a result, the distribution of deeper airflow along the inner surface of the air filter is better controlled.

5. The air filter device according to claim 4, wherein two opposingly positioned conical fan elements (44, 44') having associated impellers (40, 40') ensure the distribution of incoming air from both sides of the air filter.

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