Diffuser unit and method of diffusing a gas flow

Abstract

This disclosure provides a diffuser device having a damper compartment with multiple damper orifices. The damper orifices are opened or closed by corresponding baffles to induce swirling airflow exiting the diffuser via an air deflector, which may be a diffuser with diffuser blades or a perforated plate. Alternative embodiments relate to a method for diffusing airflow and a method for determining the airflow rate of a diffuser unit.

Description

Technical Field

[0001] Embodiments of the present invention relate to a variable air volume (VAV) swirling diffuser, which is used, particularly but not specifically, as a ceiling swirling diffuser with an integrated VAV terminal unit to maintain control over indoor air temperature and / or indoor air quality (IAQ) as part of an installed air delivery system. Background Technology

[0002] Many buildings have air conditioning or ventilation systems that distribute air throughout the building via ducts connected to diffusers. The diffusers distribute the supply air, which is typically heated or cooled, to the spaces to be air-conditioned or ventilated. This supply air can be varied via VAV terminal units, each of which alters the air supply to a group of diffusers (comprising multiple diffusers) to change the cooling or heating capacity provided to the hot areas served by that group of diffusers. The air handling fan speed can be controlled at a static pressure setpoint upstream of the VAV terminal unit, which can be reset as a function of heat load.

[0003] Standard ceiling diffusers in buildings are typically designed to exhaust horizontally overhead, with a throw distance that essentially covers the area served by each diffuser. For such standard diffusers with fixed horizontal exhaust, high airflow rates generally increase the throw distance, often resulting in excessive throw distance. This can lead to crosswinds where airflow from adjacent diffusers collides or hits obstacles such as walls or partitions. Conversely, low airflow rates typically result in reduced throw distance, often leading to stagnant air and warmer areas beyond the diffuser's throw distance. Cold spots or even crosswinds may occur near or below each diffuser due to the dense, cold supply air being poured into the occupied space. Therefore, in VAV cooling applications, whether the heat load is high or low, these standard ceiling diffusers can cause discomfort due to either excessive or insufficient throw distance, regardless of whether the throw distance is too large or too small.

[0004] Compared to four-way blower ceiling diffusers or similar low-intake air diffusers, ceiling vortex diffusers typically offer a higher level of thermal comfort and efficiency, especially in VAV applications. The high-intake vortex exhaust of a ceiling vortex diffuser draws in a large volume of indoor air and mixes it with the exhaust supply airflow, rapidly dispersing the supply air to the room temperature difference, thus providing a more uniform temperature distribution throughout the living space, while also resulting in a rapid decrease in exhaust velocity. This reduces the risk of cross drafts at high airflow rates, improving thermal comfort within the space. The high-intake characteristic also increases the effective air exchange rate per hour in the space, reducing the risk of stagnation at lower airflow rates, further enhancing thermal comfort. It is easy to achieve ADPI (Air Distribution Index) values ​​exceeding 90%, i.e., improved comfort.

[0005] Ceiling vortex diffusers also offer the potential for fan energy savings by reducing the supply air temperature to a level that would otherwise prevent spillage. This is because high intake results in a strong dilution of the supply airflow by the indoor air, reducing the density difference between the supply and indoor air. Even so, the approximately 25% to 30% VAV reduction to achieve the NC30 sound pressure level and the minimum specific airflow rate of approximately 1 liter / second / m² typically limit the lower operating limits of high-quality fixed-blade ceiling vortex diffuser systems operating in cooling mode, especially when the temperature difference between the supply and indoor air is high (typically up to 16K). Therefore, to prevent spillage and avoid stagnation, the minimum airflow rate that can be reduced for the VAV system is often higher than the airflow rate required to meet heat load or indoor air quality (IAQ) standards. This results in wasted fan energy, as it leads to unnecessarily high airflow rates at lower heat loads. It can also cause discomfort due to overly cold spaces unless more energy is wasted reheating the supply air before it is exhausted. Alternatively, if a lower gas flow rate is used, the gas supply still needs to be reheated to prevent spillage, which also wastes energy.

[0006] To increase the range of heat loads that each VAV system can handle and reduce the minimum permissible airflow rate of the diffuser and the minimum specific airflow rate of the diffuser system, a system design with actuator-driven variable geometry VAV diffusers can replace the design of VAV terminal units with matching diffusers. Each such diffuser is equipped with a VAV damper with a variable geometry exhaust port that alters the effective exhaust orifice of the diffuser or the adjacent orifice upstream of the fixed blades of the diffuser. This allows for VAV airflow regulation from each diffuser while maintaining a substantially constant exhaust velocity when the diffuser operates at a substantially constant static pressure. This operation limits the extent to which the delivery distance is reduced when the diffuser airflow is throttled, thus allowing for greater throttling. This improves comfort by reducing the risk of overcooling and spillage and stagnation in the space, while also reducing energy consumption by reducing fan energy and reheating requirements. Furthermore, this approach allows each diffuser to be controlled as an independent VAV terminal, rather than as part of a larger VAV group, thereby further improving thermal comfort and energy efficiency by reducing size and increasing the number of hot zones in the system, since each diffuser can be an independent hot zone.

[0007] Adjustable VAV dampers in such variable geometry VAV diffusers are typically adjusted by thermally or electrically driven actuators. Hybrid actuator schemes also exist, incorporating thermal actuators with electrically heated jackets to allow the actuators to respond to thermal output regulated by an electronically controlled controller, as do pneumatically operated actuators, especially for explosive environments.

[0008] Thermally driven actuators convert temperature changes into axial pushing / pull motion of the piston by mechanical force applied to it by a phase-change expansion material encapsulated in a thermally conductive housing. Advantageously, thermal actuators do not require an external power source or control unit, thus eliminating the need for power supply and wiring, as they are entirely thermally driven and typically maintenance-free for about ten years.

[0009] On the other hand, electric actuators typically include a temperature sensor connected to a computing device, which operates the electric actuator (e.g., an electric motor) when a certain predetermined temperature is sensed. Therefore, it should be recognized that the term "thermal actuator," as used herein, includes both the sensor and the actuator, as these devices mechanically respond to temperature changes.

[0010] For purely cooling applications, typically only one thermal actuator is needed to sense the indoor air temperature. The indoor air temperature setpoint can usually be manually adjusted within a range of 20°C to 26°C or nearby. The supply air jet, located within the housing behind the diffuser panel, typically draws in indoor air through the indoor air inlet and entrains it through the thermal actuator, which is unseen and responds to the indoor air temperature. The mixture of the supply air and the entrained indoor air is then exhausted back into the room to a location away from the indoor air inlet.

[0011] For combined cooling / heating applications, two or more thermal actuators are required: at least one actuator responds to the indoor air temperature as described above, and at least another actuator is connected to the air supply to operate in cooling or heating mode in response to the air supply temperature.

[0012] Electrically driven diffusers are typically powered by a low-voltage external power supply, such as a 24-volt supply, which can be daisy-chained from one diffuser to the next. Each diffuser is equipped with an electrical actuator (usually a brushless DC motor or stepper motor) to drive the VAV damper. Diffusers, which typically contain printed circuit boards, can communicate with each other or with remote controls or sensors via communication cables or wirelessly (e.g., via Wi-Fi). Typically, communication cables are used and are usually combined with the power cables into a single common cable. While more expensive than thermally driven solutions, electrically driven diffusers offer more refined and energy-efficient operation, such as through PI (proportional-integral) or adaptive VAV damper control, global adjustment of cooling and heating setpoints as a function of outdoor temperature or other relevant parameters, minimum airflow regulation based on indoor air quality, operation based on occupied diffusers, and operation where the diffuser "votes" on the overall determination of the mechanical cooling / heating mode rather than being completely independent of the diffuser.

[0013] Electrically actuator-driven variable geometry VAV diffusers can accommodate various electronic sensors, including those located remotely. For example, remote sensors can be housed in a chest-high enclosure mounted on a wall within the room, and can include an indoor air temperature sensor with a setpoint adjustment button, a humidity sensor, a volatile organic compound (VOC) or carbon dioxide (CO2) sensor for measuring indoor air quality, and a passive infrared (PIR) sensor for determining room occupancy. A supply air temperature sensor can be incorporated into the diffuser to determine cooling / heating operation. Diffuser airflow can be determined via a pressure sensor measuring total or dynamic air pressure at the diffuser interface, or via one or more hot-wire anemometer sensors measuring air velocity within the diffuser. This allows VAV airflow control to be independent of system static pressure, further improving temperature control. It also facilitates commissioning. PIR sensors can optionally be arranged within the diffuser surface to determine space occupancy, and an intake system that draws in indoor air can also be integrated into the diffuser to allow for measurement of indoor air temperature. Thus, in most cases, remote sensors are unnecessary unless indoor air quality or humidity needs to be measured, as existing electrically actuated variable geometry VAV diffusers do not have sufficient space to accommodate these sensors. Eliminating remote sensors is often desirable because it helps simplify rental renovation changes (no rewiring required) or reduce maintenance requirements (if communication is wireless, there is no need to replace sensor batteries or deal with wireless interference that interrupts communication).

[0014] The most widely used thermally or electrically variable geometry VAV diffusers have a square face designed to fit into a standard ceiling joist (typically approximately 600 mm x 600 mm square). Visible components are primarily made of powder-coated metal. The top inlet port for connecting to the supply duct is typically located at the apex of a dome-shaped housing extending downwards to the periphery of the diffuser face. Alternatively, a connection box with side inlet ports can be arranged on the diffuser, typically sealed to the back of the outer edge of the diffuser housing. In this case, supply air flows from the supply duct through the side inlet ports into the connection box and then into the top inlet port of the diffuser. A centrally located and substantially horizontally aligned array of dampers or damper blades, driven by an actuator, lies beneath the diffuser housing. The actuator drives this damper or blade array to adjust the vertical orifice between the damper or blade array and the diffuser housing, thereby metering the airflow exiting through the diffuser face at a substantially constant rate (for a given supply pressure). When viewed in a floor plan, the most common arrangement is a wide, continuous square or circular exhaust slit around a large square or circular panel (called a slat), which directs the air supply directly toward the diffuser perimeter. The airflow is then drawn in via the Coanda effect and attached to the ceiling, dispersing away from the diffuser in a substantially 360° pattern without spillage. The VAV actuators, damper mechanisms, and intake system (if present) are essentially located above the large slat that conceals these components and are typically removable for easy access. A substantially horizontal array of dampers or blades, positioned above the plane of the slat, at least partially obstructs the airflow path to the continuous exhaust slit.

[0015] Sometimes a planar swirl diffuser is used, which comprises a circular array of swirl blades arranged substantially radially around a circular hub, instead of exhausting through continuous exhaust slots. The hub replaces the cladding of a variation of the non-swirl diffuser, but is generally slightly smaller so that the effective area of ​​the swirl blades is not significantly limited. The VAV actuator, damper mechanism, and intake system (in use) are located substantially behind the hub. A damper or blade array located above the plane of the diffuser surface at least partially obstructs the airflow path to the swirl blades. The plurality of swirl blades are typically folded or pressed into the metal surface of the diffuser in a generally radial pattern with circular outer boundaries. These blades decompose the exhaust supply air into multiple airflows, each of which is directed in a direction substantially perpendicular to the radial arrangement of two adjacent swirl blades in the plan view. These airflows adhere to the ceiling and disperse away from the diffuser in a substantially 360° pattern.

[0016] US Patents 4,523,713, 6,857,577 B2, and 6,176,777 B1 describe some widely used actuator-driven variable geometry VAV diffusers with continuous exhaust slots around the trim panel. US Patents 4,231,513 and 10,337,760 include embodiments illustrating variable geometry VAV diffusers with swirling diffuser exhaust ports.

[0017] While existing actuator-driven variable geometry VAV diffusers offer many advantages, they also have many disadvantages that need to be overcome.

[0018] Most manufacturers of this prior art actuator-driven variable geometry VAV diffuser recommend controlling the AHU (Air Handling Unit), supply fan, and associated branch duct dampers to maintain a predetermined static pressure setpoint (which can vary during operation) at approximately two-thirds of the effective length of the branch duct to which the diffuser is connected, the length between the first and last diffuser branch points on the branch duct.

[0019] Multiple such diffusers are typically connected to one or more branch ducts via flexible conduits. Each diffuser has a minimum permissible static pressure, typically 12 Pa, at which its intake system (if any) can operate and the diffuser can operate stably without spillage. Each diffuser also has a maximum recommended static pressure, typically 60 Pa, to prevent excessive airflow noise.

[0020] Due to additional duct pressure losses (such as pressure losses in the flexible ducts connected to the diffusers, pressure losses from the balancing dampers serving the individual diffusers, or pressure losses caused by changes in the pressure distribution throughout the duct system as diffuser dampers open and close), such static pressure measurements at a single remote point in the duct cannot represent the actual static pressure at each diffuser. Therefore, some diffusers may operate below their minimum permissible static pressure, resulting in impaired performance and potential spillage; or the safety factor may be increased, in which case the entire system may operate at excessive pressure, wasting energy and generating excessive noise. Furthermore, if a single duct static pressure sensor fails, static pressure control in that duct is lost, potentially causing the entire system to fail.

[0021] In existing technologies, to determine the airflow rate of each diffuser, each diffuser is typically equipped with multiple velocity sensors or pressure sensors (measuring dynamic or total pressure) connected to an array of pressure measurement points. An array of multiple velocity sensors or pressure points is needed to balance the asymmetric air velocity distribution in the diffuser interface caused by the bending of the duct upstream of the diffuser. Even so, both solutions tend to be inaccurate, especially at higher airflow rates, due to the asymmetric and often turbulent airflow conditions entering each diffuser interface. Furthermore, since dynamic pressure is a function of the square of the air velocity, and accurate velocity sensors are very expensive, dynamic pressure sensors become increasingly inaccurate at low airflow rates.

[0022] To minimize HVAC costs, it is generally desirable for each diffuser to exhaust as much air as possible without creating drafts, excessive airflow noise, or requiring excessive fan pressure. For the prior art actuator-driven variable geometry VAV diffusers described in the aforementioned patent, the top inlet interface configuration necessitates a thin diffuser housing profile to allow installation in ceiling-constrained spaces. The substantially horizontally oriented damper or blade array abruptly changes the airflow direction, resulting in limited exhaust orifices due to the thin diffuser housing and at least partially obstructing continuous exhaust slots. This increases the diffuser's pressure loss, thereby increasing the energy demand on the system fan.

[0023] The flexible duct that typically connects to the top inlet diffuser interface usually lies on the adjacent ceiling panel before reaching the connection point on the diffuser interface via a near 90-degree upward bend followed by a downward bend of over 90 degrees in a "gooseneck" motion. These abrupt and opposite bends significantly increase the pressure drop in the duct and cause strong asymmetrical airflow at the diffuser interface, resulting in excessive noise and asymmetrical exhaust from the diffuser face. Furthermore, if the diffuser is equipped with total pressure or dynamic pressure sensors at the diffuser interface to determine airflow, the accuracy of these measurements is severely compromised, leading to incorrect airflow control.

[0024] While one of the key objectives of variable geometry VAV exhaust systems is to achieve a substantially constant delivery distance over a wide VAV operating range, this objective is not actually achieved. This is because delivery distance is proportional to the square root of the product of volumetric flow rate and exhaust velocity, and existing variable geometry VAV diffusers vary the volumetric flow rate of the exhaust gas at a substantially constant exhaust gas velocity (for a given supply static pressure), thus affecting delivery distance substantially according to the square root of the gas flow rate. Therefore, as the exhaust gas flow rate of existing actuator-driven variable geometry VAV diffusers decreases, the delivery distance also decreases, further increasing the threat of stagnation and heat buildup, thereby compromising thermal comfort and indoor air quality, or requiring closer spacing between diffusers due to an increase in the number of diffusers, which increases investment costs.

[0025] Because the exhaust pattern of wide and continuous exhaust slots is not highly intake-oriented, crosswinds can occur, especially at higher airflow rates, and this type of exhaust is generally unsuitable for supply air temperatures below 12°C. This can lead to discomfort and increase the system airflow required for cooling the space, thereby increasing the number of diffusers needed and consequently raising fan energy demands.

[0026] Using a swirling exhaust surface instead of a wide, continuous slot reduces the risk of drafts and allows for lower supply air temperatures, but adds further restrictions to the air path. Due to the obstruction of the damper, only a small portion of the diffuser surface is fully functional, and the airflow is further restricted by additional abrupt changes in airflow direction caused by the swirling blades. Diffuser airflow noise is significantly increased, the maximum permissible diffuser flow rate is significantly reduced, and the maximum permissible operating pressure is significantly reduced to prevent excessive airflow noise. More diffusers are needed to serve the space, thus increasing investment costs; a static pressure recovery duct design may be required to minimize pressure distribution variations in the duct system, thus increasing investment costs; and this often makes such diffusers unsuitable for retrofit applications unless existing ducts are replaced; moreover, the VAV operating range is reduced, thus increasing operating costs and compromising thermal comfort.

[0027] Ceiling heights are often very limited in modern multi-story buildings to reduce overall building height and thus overall construction costs. Diffusers with top inlet interfaces require considerable ceiling height to allow air ducts to enter from one side and then bend at least 90 degrees to attach to the top inlet interface. Even if the diffuser has a side inlet junction box, this box must be high enough to allow air supply to easily flow from the junction box into the diffuser's top inlet interface. The higher the diffuser's airflow rate, the greater this height needs to be. Therefore, the space requirements for diffusers with large airflow rates are often too high to fit into commonly limited ceiling spaces, requiring more diffusers and increasing investment costs; or this results in flexible ducts being excessively sharp-turned or even twisted at the top of each diffuser, significantly increasing pressure drop, noise, and fan energy requirements.

[0028] Newly constructed multi-story commercial buildings are initially designed with air conditioning in their base building, which is primarily composed of open floors. Ideally, these open floors have a small number of ceiling diffusers, each exhausting a large volume of air over a large floor area. This helps minimize base building HVAC costs. After leasing, lease renovations occur, where portions of each floor are partitioned into offices, meeting rooms, etc., and each room is typically conditioned by diffusers that usually exhaust a smaller volume of air (if the room being served is small), while the open areas remain essentially unchanged compared to the base building installation. The existing base building diffusers with their larger airflow need to be replaced with corresponding diffusers suitable for smaller airflow volumes. Base building diffusers are often unusable for such smaller airflow volumes because their top inlet interfaces are too large to connect to smaller ducts, and their large damper system specifications do not provide adequate VAV authority for smaller airflow volumes. These extremely expensive existing VAV diffusers become redundant and, in effect, must be discarded and replaced by other, extremely expensive existing VAV diffusers with smaller airflow volumes. This increases the HVAC costs of the lease renovation.

[0029] Due to the height limitations of thin diffuser housings and the space requirements for damper motors and mechanisms, the available space under the damper baffles or blade arrays of existing electrically actuated variable geometry VAV diffusers is extremely limited. Without increasing diffuser height or throttling diffuser airflow, there is typically insufficient space to accommodate additional components beyond the printed circuit board, room temperature sensor, PIR sensor, and associated intake system. This is especially true when the diffuser has a swirling surface, as the intake system (including its inlet and outlet) must be fully fitted and sealed to the smaller hub of the swirling surface. Therefore, remote sensors are still required to accommodate bulky CO2, VOC, and RH indoor air sensors. This increases project costs and reduces flexibility in rental fit-outs.

[0030] Due to the aforementioned space constraints, the intake systems of existing VAV diffusers are severely limited, especially in variable geometry VAV diffusers with swirling exhaust. Their inlet sizes are small, and their intake chambers are short, resulting in low intake ratios and weak secondary airflows from the room into the intake system. This not only leads to slow thermal response times to changes in room temperature but also to inaccurate steady-state room temperature measurements, as thermal bridges (especially from the swirl vanes to the hub) significantly affect the boundary layer air temperature below the hub and within and around the intake inlet, unless a strong secondary airflow is used to dilute the air with more representative room-temperature air. Such existing diffuser intake systems cannot generate such strong secondary airflows due to space constraints above the diffuser trim or, in particular, the smaller size of the swirl vane hub. The accuracy of indoor air temperature sensing is compromised, leading to poor indoor air temperature control, reduced comfort, and increased HVAC energy costs.

[0031] To increase the auxiliary airflow into the intake system to some extent, higher main airflow rates are sometimes used in existing actuator-driven variable geometry VAV diffusers. This limits the operating range of the VAV, especially at lower maximum airflow rates, resulting in discomfort and energy waste due to overcooling when the heat load is reduced.

[0032] Assuming the diffuser intake system operates continuously, even when there is no need for air conditioning in the space, such as when the HVAC system is running but the problematic diffuser is serving a space that is not rented or occupied, discharging the main cooling / heating airflow into the space will still waste additional energy. Summary of the Invention

[0033] A diffuser unit for supplying gas to space, the diffuser unit comprising:

[0034] Pressure chamber, which has an air inlet for receiving variable flow rates of air;

[0035] An air deflector through which air is discharged into the space, the air deflector being arranged to disperse the discharged air in a plane substantially parallel to the exhaust surface of the diffuser unit, the air deflector forming an outlet to the pressure chamber;

[0036] A damper compartment, located within a pressure chamber and connected to an air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment also including a plurality of baffles, each baffle being associated with at least one corresponding orifice and operable between an open position and a closed position;

[0037] Furthermore, the damper compartment and damper orifice are arranged such that the air entering the damper compartment from the pressure chamber through the damper orifice forms a swirling flow before leaving the damper compartment through the air guide.

[0038] The damper orifice and the wind deflector can be configured and operated to maintain a substantially constant speed or delivery distance of the air discharged from the air deflector.

[0039] Pressure chambers, damper compartments, and / or baffles may include one or more surfaces configured to apply a tangential velocity to air flowing into the damper compartment. The surfaces may be angled.

[0040] In some embodiments (e.g.) Figures 4a to 4 (l) When the damper is opened and closed, the angle of one or more surfaces relative to the damper compartment remains constant. In such an embodiment, at least for a portion of the possible positions of the damper, a constant velocity of the air discharged from the outlet can be maintained.

[0041] In other embodiments (e.g., Figures 5 and 6), Figure 7 (as shown in Figure 8), the angle of one or more surfaces changes as the damper opens and closes. In these embodiments, one or more surfaces may be the surfaces of the damper. The damper may pivot relative to the damper compartment. In such embodiments, at least for a portion of the possible positions of the damper, a substantially constant delivery distance of the air discharged from the airflow device can be maintained, and a larger tangential velocity component of the exhaust velocity can be obtained when the orifice is smaller compared to the case where the angle of the surface relative to the damper compartment remains constant.

[0042] The unit may be a ceiling diffuser unit adapted to be mounted on the ceiling defining the space. Alternatively, the diffuser unit may be adapted to be mounted in an upper position facing the space. For example, in some embodiments, the unit may be suspended from the ceiling or roof and positioned overhead.

[0043] The diffuser device may have a perforated baffle associated with the air inlet of the pressure chamber.

[0044] The pressure chamber can be a connection box. The pressure chamber may have a low or essentially zero dynamic pressure relative to the duct connected to the air inlet of the pressure chamber.

[0045] The damper compartment can be radially symmetrical.

[0046] The damper compartment can be truncated conical in shape.

[0047] Each windshield can move between the open and closed positions.

[0048] One or more dampers may include blades extending tangentially to the surface of the damper compartment. Alternatively or additionally, the damper compartment may have multiple edges defining an orifice, and the damper compartment has blades formed at these edges.

[0049] The blades can extend away from the outer surface of the damper compartment (e.g.) Figures 4a to 4 h). Alternatively, the blades can extend into the interior of the compartment (e.g., Figure 4 i to Figure 4 l). In another embodiment (not shown), the blade extends into and out of the compartment.

[0050] The wind deflector can be connected to a control mechanism. This control mechanism can be a sliding mechanism that allows the wind deflector to slide relative to the compartment, thereby opening and closing the corresponding opening.

[0051] For all doors, a single mechanism can be provided so that the position of each door relative to the corresponding opening is the same for all windproof doors.

[0052] The windbreak can be formed by an outer sleeve that engages with and slides relative to the windbreak compartment.

[0053] Alternatively, multiple windbreaks can each have a corresponding windbreak control mechanism, and each corresponding windbreak control mechanism can operate independently, so that multiple windbreaks can selectively move relative to the corresponding openings to open or close the openings.

[0054] One or more dampers can be installed to pivot relative to the damper compartment about their respective axes (e.g., Figure 5 and...). Figure 7The axis can be located substantially coincident with or very close to the leading edge of the corresponding damper. Alternatively, the axis can be located substantially equidistant between the leading and trailing edges of the corresponding damper, or closer to the trailing edge of the damper than the distance from the leading edge. The position of the axis allows the static pressure in the pressure chamber to exert an opening force, balancing force, or closing force on the corresponding damper when it is in the closed position.

[0055] The rotation axes of the dampers can be vertical or inclined. When the axes are vertical, they can be oriented substantially orthogonal to the plane of the diffuser unit's exhaust surface. These axes can also be oriented substantially coincident with the surface of a cylinder. When the axes are inclined, they can be oriented substantially coincident with the surface of a cone.

[0056] The rotation axes of the dampers can be parallel to the centerline of the diffuser, or they can be inclined relative to the centerline of the diffuser. When the axes are parallel, they can be oriented substantially orthogonal to the plane of the exhaust surface of the diffuser unit. These axes can also be oriented substantially coincident with the surface of the cylinder. When the axes are inclined, they can be oriented substantially coincident with the surface of the cone.

[0057] When in the closed position, the damper can essentially provide a seal for the corresponding opening.

[0058] Each wind deflector may have a trailing edge. This trailing edge may be serrated. The serrations may be one or more of a sawtooth shape, a sinusoidal wave shape, or an irregular shape. One or more wind deflectors may be formed at the trailing edge by a perforated or porous material.

[0059] The profile of the trailing edge may deviate from the profile of the portion of the damper other than the trailing edge. The damper may include a sealing edge. This sealing edge may be located at or near the trailing edge. The trailing edge may deviate from the tangent of the damper surface at the sealing edge. The trailing edge may have an arcuate profile. The arcuate shape may extend toward the compartment.

[0060] Unless the context otherwise indicates, the terms “front” and “rear” are used relative to the airflow when the unit is in use.

[0061] The damper may include corresponding surfaces impacted by airflow, wherein at least one of the surfaces has one or more protrusions to reduce noise generated when airflow passes over it. Each surface may form a corresponding trailing edge. Each surface may form a corresponding sealing edge.

[0062] The protrusions can be one or more of the following shapes: substantially planar, serrated, rectangular, triangular, truncated triangular, substantially sinusoidal, or irregular. The protrusions can project from the surface at an angle between 20° and 90°, or between 30° and 60°. The closest distance between adjacent protrusions can be between 0.5 mm and 5 mm, or between 1 mm and 3 mm. The width of the protrusions can be between 1 mm and 2 mm, or between 3 mm and 10 mm. One or more wind deflectors can have a first set of protrusions in one of the shapes described above and a second set of protrusions in another of the shapes described above. A wind deflector can have more than two sets of protrusions, each set having a different shape.

[0063] The protrusion can be a vortex generator. Other or alternative shapes of the protrusion may include a twisted pyramid shape with a triangular base, a blade shape, or one or more hemispherical shapes.

[0064] In addition to the protrusions formed on the surface of the damper, the damper compartment may also include one or more blades formed at the edge of the defining orifice.

[0065] The damper compartment may include an inlet surface for forming a seal with a corresponding door. This inlet surface may have a circular inlet upstream of the sealing location. The radius of this circular inlet may be between 5 mm and 30 mm, preferably between 10 mm and 20 mm. The circular inlet helps reduce noise.

[0066] One or more doors may include locks for locking the doors relative to their corresponding openings. The locks can lock the doors in the closed position. The locks may be manually operable and accessible through a venting element.

[0067] This unit may include a first door type and a second door type. The first door type may be smaller than the second door type. The circumferential range of the first door type may be smaller than the circumferential range of the second door type. The unit may include multiple doors of the first door type and multiple doors of the second door type. The doors of the first door type may be arranged alternately with the doors of the second door type on the circumference of the damper compartment. Alternatively, the number of doors of the second type may be twice the number of doors of the first type. One or more groups of doors of the second type may be provided, each group including two or more doors of the second type. Each group of doors of the second type may be arranged alternately with the doors of the first type on the circumference of the damper compartment.

[0068] At least one door may include a switch arranged to be activated when the door is in a fully closed or fully open position. Alternatively, a compartment may include a switch arranged to be activated by the closing or full opening of at least one door. The switch may be activated by a door actuator. When activated, the switch may send a signal to zero the position of the corresponding door. A switch may be provided associated with each door.

[0069] The unit may include one or more baffle sections for blocking a portion of the airflow through the unit. The one or more baffle sections may be arranged to block the exhaust element. Two baffle sections may be provided. Each baffle section may be shaped as a wedge. The wedge shape may be a 90° wedge. Figure 7 d to Figure 7 f).

[0070] The air vents can be arranged symmetrically around the perimeter of the compartment.

[0071] The arrangement of the orifices can be radially symmetrical.

[0072] The unit may include an actuator for opening and closing a door. This actuator may be connected to a sensor. The sensor may be a supply air sensor arranged to measure the supply air temperature. The sensor may also be an indoor air sensor arranged to measure the air temperature of the space.

[0073] This unit may include an air supply sensor and an indoor air sensor. Each of the air supply sensor and the indoor air sensor may be connected to a corresponding actuator, or to the same actuator.

[0074] The actuator may include one or more arms that engage with their respective door flaps. In the case of a truncated conical compartment, the arms may translate in a direction substantially parallel to the central axis of the compartment. The arms may be connected to a connecting ring. The actuator may also include a drive for incrementally translating the position of the arms. This drive may engage with the connecting ring. The drive may include a stepper motor or a brushless DC motor. The doors may be pushed open by supplying air pressure to their respective arms. Alternatively, gravity may pull the doors open onto their respective arms. The arms may be magnetically engaged with their respective doors.

[0075] In an alternative embodiment, the arm can be rotated and translated relative to the damper compartment. The arm can be rotated and translated relative to the damper compartment, or it can be translated linearly in a direction substantially parallel to the central axis of the compartment.

[0076] The unit may include a translation ring and a docking ring. In cases where the actuator comprises multiple arms, one or more of the arms may have a locking mechanism that selectively engages a corresponding arm with either the translation ring or the docking ring. Figures 8i to 8l ).

[0077] Air deflectors may include perforated plates. Air deflectors may include multi-cone diffusers.

[0078] An air deflector may include a swirling diffuser having multiple exhaust elements arranged substantially radially. An air deflector may include more than one swirling diffuser. In one embodiment, an air deflector includes two, three, or more swirling diffusers. Where the outlet includes more than one swirling diffuser, these diffusers may be arranged adjacent to each other.

[0079] The exhaust element may include blades. Each blade may have a trailing edge and a leading edge.

[0080] The diffuser unit may include a core portion defined by a core duct from the damper compartment.

[0081] Although the core portion is located at the center in the illustrated and discussed embodiments, it should be recognized that in other embodiments, the core portion may be located in other locations.

[0082] The core conduit may include a shroud having an inlet and an outlet, through which air from the pressure chamber enters the shroud and through which it exits the shroud.

[0083] The core section can house one or more actuators.

[0084] The core portion may include a partition dividing it into an upper portion associated with a pressure chamber and a lower portion associated with a space into which air exhausted from the diffuser unit enters during use. The partition may have one or more intake inlets. These intake inlets may be nozzles. The partition may have a removable proximal portion sealed to a distal portion, wherein the distal portion is formed with nozzles. The removable proximal portion facilitates the removal of the actuator for maintenance. Figure 11 a and Figure 11 b).

[0085] The core component may include a protective cap, and the protective cap may be perforated.

[0086] The protective cap can be manually removed to access the core section. In cases where the core section houses one or more sensors (such as temperature and / or pressure sensors), the manually removable cap allows for relatively easy access to these sensors (and any other components housed in the core section, such as one or more actuators) for maintenance without requiring the removal of the entire unit.

[0087] The core component may include a second inlet located at the lower part, wherein airflow flowing through the intake inlet causes the intake airflow to flow through perforations in the cap and enter the shroud through the second inlet to form a mixed airflow exiting the shroud through an outlet. The second inlet may be located in the upper part of the lower part.

[0088] The unit may include a protrusion located in the lower part of the core portion, which separates the perforation in the cap from the shroud outlet. In the case of rotational symmetry of the shroud (e.g., a partially conical or cylindrical shape), the protrusion may extend along a line parallel to the central axis of the shroud. The protrusion may form a second inlet located in the lower part of the shroud. The protrusion may be formed of a cylinder.

[0089] The intake inlet can be configured to apply a vortex to the mixed airflow. In the case where the intake inlet includes one or more nozzles, these nozzles can be angled relative to the central axis of the unit.

[0090] The unit may include an induction damper. The induction damper can operate between a closed position that restricts or blocks the intake airflow and an open position that allows the intake airflow.

[0091] In cases where the unit includes an actuator for opening or closing a damper, the intake damper can be connected to the actuator. The actuator can actuate to close the damper and move the intake damper to the closed position. The actuator can also actuate to open the damper and move the intake damper to the open position. Alternatively, the actuator can first close the damper and then move the intake damper to the closed position. Or, the actuator can first move the intake damper to the open position and then open the damper. Finally, the actuator can actuate such that the intake damper also opens when the damper is opened.

[0092] The core component may include a first sensor located in the upper part and / or a second sensor located in the lower part.

[0093] The first sensor can sense the air temperature in the pressure chamber, and the second sensor can sense the temperature in the space. The first and / or second sensors can be thermal actuators. The first and / or second sensors can be connected to their respective actuators for actuating the orifice gate.

[0094] The unit may include one or more pressure sensors for measuring the static pressure of the supply air relative to the space. In one embodiment, the pressure sensor is located in the lower part, with a vent tube extending into the pressure chamber outside the damper compartment and the upper part. If the unit includes an intake damper, the intake damper can close the upper part of the pressure chamber in a closed position. In this case, even when the intake damper is closed, pressure measurement can be permitted by the vent tube having an inlet that extends directly into the pressure chamber rather than into the upper part.

[0095] A method for diffusing airflow using a diffuser unit, the diffuser unit comprising:

[0096] A pressure chamber with an air inlet;

[0097] An air deflector through which air is discharged into a space, the air deflector comprising a plurality of exhaust elements arranged to disperse the discharged air in a plane substantially parallel to the exhaust surface of the exhaust unit, the air deflector forming an outlet to the pressure chamber;

[0098] A damper compartment, located within a pressure chamber and connected to an air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment further including at least one baffle, the baffle being associated with a corresponding orifice and operable between an open position and a closed position;

[0099] The method includes:

[0100] It receives a variable air supply flow through the air inlet into the pressure chamber;

[0101] Open one or more dampers to allow airflow into the damper compartment;

[0102] A vortex airflow is generated within the damper compartment; and

[0103] Air is allowed to leave the diffuser unit and enter the space in a swirling manner through the air guide in a plane substantially parallel to the exhaust surface of the exhaust unit.

[0104] The windbreak angle can be described. This windbreak angle can be related to the airflow rate allowed through the corresponding orifice.

[0105] The vortex airflow within the damper compartment can have a helix angle. For most of the vortex airflow in the compartment, this helix angle can be the helix angle of the vortex airflow relative to the plane of the air guide surface.

[0106] The airflow rate and helix angle of the vortex airflow in the compartment can increase as the damper angle increases.

[0107] The method may further include maintaining adhesion between the airflow exiting the air deflector and the surface of the air deflector. The air deflector may include diffuser blades, wherein the method includes maintaining adhesion through the diffuser blades. The air deflector may include a perforated plate, wherein the method includes maintaining adhesion through the perforated plate acting as a baffle.

[0108] This method may include closing a damper and achieving a greater delivery distance for air leaving the air deflector. Closing the damper can achieve a higher far-side tangential velocity relative to the near-side tangential velocity of the vortex airflow within the damper compartment. Thus, the airflow leaving the air deflector can include an extended delivery distance and a reduced airflow rate. The static pressure within the pressure chamber can be substantially constant. When the damper is closed, the delivery distance of the airflow leaving the air deflector can be substantially constant, or it can be greater than the delivery distance under conditions where the tangential velocity distribution of the air deflector is substantially constant.

[0109] This method may include substantially or completely closing the air deflector. When the air deflector is substantially or completely closed, a small but not negligible vortex airflow can be formed in the compartment. In this case, the airflow exiting the diffuser unit via the air guide can exit in a swirling manner in a plane substantially parallel to the exhaust surface of the exhaust unit.

[0110] The unit may include more than one door. The method may include locking one or more doors.

[0111] The unit may include a blocking section, and the method may include using the blocking section to block a portion of the airflow through the unit.

[0112] The method may include sensing the temperature of the supplied gas and / or the temperature of the space. The door may be operated in response to a determined temperature. The door may be operated based on the temperature of the supplied gas and / or the temperature of the space.

[0113] The unit may include an intake chamber having an intake inlet, the method comprising drawing air from the space into the intake chamber by an intake caused by an airflow originating from a pressure chamber passing through the intake inlet, to form a combined airflow discharged through a diffuser outlet. The intake chamber may be defined by a partition located in the core portion of the diffuser unit.

[0114] The combined airflow exiting the diffuser outlet can be discharged in a substantially 360° pattern within a plane substantially parallel to the diffuser surface. The combined airflow exiting the diffuser outlet can also be ejected away from the diffuser outlet in a direction substantially parallel to the plane defined by the diffuser outlet surface. The mixed airflow exiting the diffuser outlet helps suppress leakage from the damper. This helps prevent leaked gas from short-circuiting into the intake chamber.

[0115] Another embodiment relates to a method for determining the gas flow rate of a diffuser unit, the diffuser unit comprising:

[0116] Pressure chamber, which has an air inlet for receiving a variable flow of air supply;

[0117] An air deflector through which air is discharged into the space includes a plurality of exhaust elements arranged to disperse the discharged air in a plane substantially parallel to the exhaust surface of the diffuser unit, and the air deflector forms an outlet to the pressure chamber.

[0118] A damper compartment, located within a pressure chamber and connected to an air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment further including at least one intake damper or baffle, the intake damper or baffle being associated with a corresponding orifice and operable between an open position and a closed position;

[0119] The method includes:

[0120] Determine the static pressure in the pressure chamber;

[0121] Determine the location of the intake damper or air deflector; and

[0122] Calculate the gas supply flow rate based on the determined static pressure and valve position.

[0123] The damper compartment and damper orifice can be arranged such that air entering the damper compartment from the pressure chamber through the damper orifice forms a swirling flow before leaving the damper compartment through the air guide.

[0124] The door can be positioned between the open and closed positions, as well as in several intermediate positions between the open and closed positions.

[0125] The door can be actuated by a drive mechanism. The door's position can be determined by referring to the drive mechanism. The drive mechanism can increment a counter, and the position can be determined by referring to the counter.

[0126] The unit may include a switch that is activated when the door is closed or opened to reset the counter to zero. Attached Figure Description

[0127] The following detailed description is made with reference to the accompanying drawings, which are not drawn to scale and form part of the detailed description.

[0128] For the same part that appears in multiple figures, use the same figure reference numerals.

[0129] The exemplary embodiments described in the detailed description, depicted in the accompanying drawings, and defined in the claims are not limiting. Other embodiments may be utilized, and other variations may be made without departing from the spirit or scope of the subject matter presented. It will be readily understood that the various aspects of this disclosure, as generally described herein and illustrated in the accompanying drawings, can be arranged, substituted, combined, separated, and designed in a variety of different configurations, all of which have been considered in this disclosure.

[0130] Various embodiments will now be described by way of example with reference to the accompanying drawings, in which:

[0131] Figure 1a This is a schematic diagram illustrating a typical prior art thermal actuator variable geometry VAV ceiling diffuser, which has a substantially throttling damper;

[0132] Figure 1b This is a schematic diagram illustrating a typical prior art electrically driven variable geometry VAV ceiling diffuser with a substantially open damper.

[0133] Figures 2a to 2c This is a schematic diagram of a typical prior art electrically actuated variable geometry VAV ceiling vortex diffuser, which has substantially open, substantially closed and substantially throttling dampers, respectively.

[0134] Figures 3a to 3c This is a schematic diagram illustrating a typical modified electric actuator variable geometry VAV ceiling vortex diffuser of the prior art, which has essentially throttled, essentially closed, and essentially open dampers, respectively.

[0135] Figures 4a to 4 f is a schematic diagram illustrating an embodiment of a thermally actuator-VAV cyclone diffuser with a rotating damper;

[0136] Figure 4 g to Figure 4 l is a schematic diagram illustrating an alternative embodiment of an actuator-driven VAV cyclone diffuser with a rotary damper;

[0137] Figures 5a to 5e This is a schematic diagram illustrating a preferred embodiment of an actuator-driven VAV cyclone diffuser with swirl blade exhaust surfaces;

[0138] Figure 6a and Figure 6b This is a schematic diagram illustrating an alternative actuator-driven VAV cyclone diffuser with a perforated exhaust surface according to one embodiment;

[0139] Figure 7 a to Figure 7c is a schematic diagram showing an actuator-driven VAV cyclone diffuser with an alternative damper embodiment;

[0140] Figure 7 d to Figure 7 f is a schematic diagram illustrating an exhaust mode blocking section according to one embodiment;

[0141] Figures 8a to 8f This is a schematic diagram showing a swirl damper arrangement for a VAV cyclone diffuser and an electric actuator with a worm gear mechanism according to one embodiment;

[0142] Figure 8h This is a schematic diagram showing the door lock on each vortex deflector according to one embodiment;

[0143] Figures 8i to 8l This is a schematic diagram illustrating an alternative windshield locking mechanism according to one embodiment;

[0144] Figure 9 a to Figure 9 p is a schematic diagram illustrating two different sizes and cross-operation swirl dampers according to one embodiment, as well as the noise reduction features of the dampers;

[0145] Figure 10 a to Figure 10 c is a schematic diagram showing the swirl damper arrangement for a VAV cyclone diffuser and an electric actuator with a planetary gear mechanism according to one embodiment;

[0146] Figure 11 a and Figure 11 b is a schematic diagram illustrating an embodiment in which the electric actuator, sensor, and printed circuit board are removed from below;

[0147] Figure 12 a and Figure 12 b is an isometric view illustrating an embodiment in which the electric actuator, sensor, and printed circuit board are removed from below;

[0148] Figure 13 a is shown in Figure 10 a to Figure 10 c and Figure 11 The isometric side cross-sectional view of the embodiment schematically shown in b;

[0149] Figure 13 b is shown in Figure 5. Figures 8a to 8h , Figure 9 c. Figure 9 d、 Figure 9 g、 Figure 9 j、 Figure 9 p and Figure 11 The isometric side cross-sectional view of the embodiment schematically shown in Figure a includes a fully open windshield and a half-sized windshield;

[0150] Figure 13 c is Figure 13 b shows an isometric top cross-sectional view of the embodiment, but only half-size windshields are shown in the open state; and

[0151] Figures 14a to 14c This is a schematic diagram showing the arrangement of cylindrical and conical swirl dampers, the side inlet and top inlet connection boxes, and the multi-cone exhaust element. Detailed Implementation

[0152] The embodiments described herein generally relate to an air diffuser assembly for ceiling exhaust, the air diffuser assembly having an air source supplied from a pressure chamber or duct.

[0153] For simplicity, the following illustration shows a diffuser exhaust port that is substantially coincident with a plane, which coincides with the diffuser exhaust plane. Those skilled in the art will understand that the exhaust ports do not necessarily have to coincide with a plane (e.g., they can be located on a curved surface), and they do not necessarily have to coincide with the diffuser exhaust plane (e.g., the diffuser exhaust plane can be a more downstream perforated plate).

[0154] For simplicity, the power and communication wiring connected to and within the diffuser is not shown.

[0155] Those skilled in the art will understand that many changes and / or modifications can be made as shown in the specific embodiments without departing from the spirit or scope of this specification. Therefore, the present embodiments are to be considered exemplary in all respects and not limiting.

[0156] Unless otherwise indicated, any references to prior art contained herein shall not be construed as an admission that the information is common general knowledge.

[0157] Figure 1a and Figure 1b This is a schematic side cross-sectional view of typical thermal and electric actuator VAV ceiling diffusers 1a and 1a' of the prior art. Each diffuser has a low-flow exhaust flow 9 and a high-flow exhaust flow 9' and 9'" of four-way or radial exhaust relative to the diffuser design airflow (i.e., the maximum airflow required to achieve the maximum cooling or heating capacity of the considered application). The diffuser face 1 is located in a T-shaped track 2 of the ceiling joist, the centerline dimension G1 of which is approximately 600 mm. The plane of the diffuser face 1 substantially coincides with the plane of the lower side 2' of the ceiling joist, which in turn defines the plane of the ceiling (not shown). Figure 1a Low airflow supply airflow 3 and Figure 1bA high-volume supply airflow 3 flows from the supply air duct 5 into the diffuser inlet 4. An air supply fan or motorized damper upstream of the supply air duct 5 is not shown for blowing the supply air 3 into the supply air duct 5 at a substantially constant static pressure upstream of the diffuser inlet 4, or a pressure relief damper upstream of the diffuser inlet 4 for releasing excessive pressure. A damper 6 is located at... Figure 1a The middle is shown to be in a state of basically throttling, in Figure 1b The damper 6, shown as size A1 fully open to the exhaust port 7a, can be adjusted by the indoor air thermal actuator 10a and the supply air thermal actuator 10b in response to the indoor air temperature and the supply air temperature, respectively, thereby regulating... Figure 1a The airflow rate of the damper 7 in the system is adjusted by the electric actuator 10c in response to control signals from the printed circuit board (PCB) 10d, which are input from the indoor air temperature sensor 10e, the indoor supply air temperature sensor 10f, and the dynamic air pressure sensor 10g. Figure 1b The airflow rate of the damper airflow 7' in the middle. By changing the position of the damper 6, the airflow rates of the low damper airflow 7 and the high damper airflow 7' are adjusted at a substantially constant speed to obtain a substantially constant static pressure of the airflow 3, thereby increasing or decreasing the airflow rate and delivery distance of the exhaust airflow 9 or 9' and 9" respectively, each of which is drawn in by the Coanda effect and attached to the diffuser surface 1 and the adjacent ceiling (not shown) to be sprayed into the room 18 as a low airflow diffuser airflow 9a or a high airflow diffuser airflow 9a' and 9a" without spillage.

[0158] exist Figure 1a and Figure 1b The image also shows an intake nozzle 11 located behind a diffuser panel 8 (typically a round or square panel), which is parallel to but offset from the plane of the diffuser surface 1, such that the plane of the panel 8 is lower than the plane of the lower side 2' of the ceiling joists. The intake nozzle 11 discharges the main airflow 12 and introduces the secondary airflow 13 into the intake channel 15, thereby drawing in supplementary airflow 14 from the room 18 through the panel inlet 14a and the room temperature sensor 10e.

[0159] For maintenance from room 18, diffuser panel 1b can be folded down to access damper 6 and related mechanisms, actuators 10a, 10b and 10c, sensors 10e and 10f, and printed circuit board 10d; alternatively, the aforementioned components can be attached to removable diffuser panel 8.

[0160] Advantageously, the change in delivery distance required to achieve a diffuser airflow end velocity of 0.25 m / s for 9a or 9a' and 9a” caused by the change in the position of damper 6 is not as large as when the airflow rate and static pressure of the supply airflow 3 increase or decrease simultaneously when damper 6 is upstream of diffuser interface 4, because the delivery distance is proportional to the product of the square root of the airflow rate and the square root of the exhaust velocity, while in the aforementioned prior art VAV diffusers, the exhaust velocity remains substantially constant. This reduces the sensitivity of the delivery distance to airflow rate regulation, which reduces the extent to which the diffuser airflow 9a or 9a' and 9a” is delivered too far or too far into room 18, thus potentially improving the comfort in the occupied space compared to the comfort achieved in conventional VAV systems with non-variable geometry VAV diffusers (commonly referred to as fixed aperture diffusers). Another advantage is that, since the exhaust airflow 9 or 9' and 9" is essentially constant, even at extremely low airflow rates, the diffuser airflow 9a or 9a' and 9a" can be kept attached to the ceiling by the Coanda effect, thus allowing the exhaust airflow 9 or 9' and 9" to be reduced to a lower airflow rate without spilling.

[0161] Figure 1b The diagram illustrates the centrifugal effect bias of the high-flow-rate supply air 3a toward the outer edge of the curved duct 5a, and the potential stall and turbulence 3b along the inner edge of the curved duct 5a. This results in high dynamic pressure 3c and low dynamic pressure 3d, as well as a potential negative dynamic pressure 3f, in the airflow entering the pressure tube array 10h, leading to a low static pressure zone 3g. This creates a low-damper airflow 7' and a high-damper airflow 7”, which in turn results in asymmetrical airflow rates and delivery distances of the diffuser airflows 9a' and 9a” due to the low and high velocities of the exhaust airflows 9' and 9”, respectively. Furthermore, due to the uneven dynamic pressure distribution and the turbulence entering the pressure tube array 10h, inaccuracies occur in measuring the dynamic pressure and thus calculating the airflow rate of the supply airflow 3, especially under high airflow conditions.

[0162] When the velocity of the air supply flow 3 is low, inaccurate airflow measurement will also occur at low airflow rates because the dynamic pressure of the airflow 3a is extremely low, since the dynamic pressure is proportional to the square of the velocity, and the air velocity is very low at low airflow rates.

[0163] The top inlet of the gas supply duct 5 requires a considerable ceiling height H1 (typically 500 mm to 800 mm), which may be disadvantageous.

[0164] Disadvantageously, since panel 8 is below the plane of the lower side 2' of the ceiling joists, panel 8 protrudes into room 18, which may be architecturally undesirable.

[0165] In order to optimize the airflow regulation authority through damper 6 without excessive pressure drop, the ratio of the area of ​​diffuser interface 4 to the annular area of ​​the maximum damper orifice 7a should be substantially constant for all diameters of diffuser interface 4, and thus substantially constant for the maximum airflow capacity. This requires the diameter of damper 6 and the maximum stroke A1 of orifice 7a to increase approximately proportionally to the diameter of diffuser interface 4. Diffuser inlets 4 are typically circular and generally come in one of five nominal diameters: 150 mm, 200 mm, 250 mm, 300 mm, and 350 mm. This is suitable for increasing the airflow range to approximately 300 to 330 L / s at a maximum sound power level of approximately 45 dB(A), which corresponds to a sound pressure level of approximately NC30 in a room 18 based on a room absorption capacity of 10 dB. Therefore, the specifications of the damper 6 and the maximum damper travel A1 of the orifice 7a are typically set to suit these different diffuser inlet diameters. However, it should be noted that the diffuser static pressure of approximately 300 to 330 L / s is typically well above 40 Pa, which is significantly higher than the 30 Pa maximum static pressure preferred to minimize fan energy requirements. Therefore, the travel of the diffuser damper and related mechanisms is not interchangeable between diffuser inlet specifications if optimal performance is to be achieved across all inlet specifications.

[0166] Figure 2a and Figure 2b A side cross-sectional view of a prior art electrically actuated VAV ceiling swirl diffuser 1b is shown, wherein high-flow-rate damper airflows 7' and 7" and low-flow-rate damper airflows 7' and 7" are respectively discharged into diffuser chamber 16 and then flow onto radially arranged swirl blades 17, which apply vortices to the high-flow-rate exhaust airflows 9' and 9" or the low-flow-rate exhaust airflows 9' and 9" respectively. The exhaust airflows are guided substantially in the plane of diffuser surface 1, thereby being drawn in by the Coanda effect and attached to the diffuser surface 1 and the adjacent ceiling (not shown) as high-flow-rate, highly turbulent diffuser airflows 9a' and 9a" or low-flow-rate, highly turbulent diffuser airflow 9a.

[0167] The figure also shows an intake nozzle 11 located behind the diffuser hub 8a. The intake nozzle 11 discharges the main airflow 12 and introduces the secondary airflow 13 into the intake channel 15. Both airflows are then discharged through the hub exhaust port 15a. The intake nozzle 11 draws supplementary airflow 14 from the room 18 through the panel inlet 14a and the room temperature sensor 10e.

[0168] Advantageously, the high-intake vortex diffuser exhausts 9a, 9a' and 9a” can improve thermal comfort in room 18 under both high and low airflow conditions, and can use lower temperature supply airflows 3 without spillage.

[0169] Advantageously, no part of the diffuser 1b protrudes into the room 18, because no part is located below the plane of the diffuser surface 1, which substantially coincides with the plane of the lower side 2' of the ceiling joists.

[0170] Potentially disadvantageous is that the multiple abrupt changes in airflow direction from the supply airflow 3 to the diffuser airflows 9a' and 9a'' result in extremely high pressure drops and airflow noise, especially at high airflow rates. Furthermore, when the damper 6 is fully open, it prevents the exhaust airflows 7' and 7'' from blowing across the entire radial length of each swirl vane 17, causing swirl vane sections 17a to be ineffective even at high airflow rates, resulting in a high pressure drop in the effective swirl vane sections 17a'. This further increases pressure drops and airflow noise, while severely limiting the maximum airflow capacity, typically to less than 200 L / s at a sound power level of 45 dB(A), and also generating supply vortices 7s and vortex exhaust 7s' towards the diffuser hub 8a, which partially short-circuits into the intake inlet 14a, leading to inaccurate room temperature sensing by the room temperature sensor 10e.

[0171] A considerable ceiling height H1 is required, typically 450 to 750 mm, which may be a disadvantage.

[0172] Due to space constraints and the complexity required to overcome the positive pressure in the diffuser chamber 16 to seal the intake system components, maintenance of the damper 6 and related mechanisms, actuator 10c, sensors 10e and 10f, and printed circuit board 10d cannot be performed from room 18.

[0173] like Figure 1a and Figure 1b Like the prior art non-swirling actuator VAV diffuser shown, when operating at high gas flow rates, asymmetrical exhaust occurs due to the top inlet bend 5a in the gas supply duct 5, and the dynamic pressure measurement of the pressure sensor 10g is inaccurate. At low gas flow rates, the dynamic pressure measurement is also inaccurate due to the low velocity of the gas supply flow 3.

[0174] Figure 2c It is shown Figure 2a and Figure 2bThe schematic diagram of the prior art embodiment shown depicts a damper 6 that is closed or nearly completely closed, causing the damper airflow 7 generated by the small damper orifice 7a or leakage to lack sufficient momentum to generate an exhaust airflow that adheres to the diffuser surface 1 after passing through the swirl vanes 17. Instead, a short circuit occurs because the low-speed exhaust airflow 9 creates a cavitation 19 below the diffuser surface 1, which is drawn into the intake inlet 14a and above the indoor air temperature sensor 10e. The temperature of the cavitation 19 is strongly influenced by the temperature of the exhaust airflow 7 and may therefore deviate significantly from the temperature of the indoor air 18, resulting in errors in the indoor air temperature measurement by the indoor air temperature sensor 10e.

[0175] Figures 3a to 3c This is a side cross-sectional view showing an alternative embodiment of the prior art electric actuator VAV ceiling vortex diffuser 1c, wherein the damper 6 is shown in a substantially closed, substantially throttled, and fully open state, respectively, at the damper orifice 7a.

[0176] Air supply 3 enters the connector box 20 through the side inlet interface 4'. The flared inlet extension 4” attached to the diffuser interface 4 guides the air supply flow 3a' to the pressure tube array 10h with a substantially uniform dynamic pressure 3d', so as to obtain a reliable dynamic pressure reading by the pressure sensor 10g when the air supply flow 3a' is high. In order to ensure that the air supply flow 3a' is substantially unrestricted, a connector box height H2 of approximately 350 mm is required for an air supply flow rate of approximately 200 liters / second 3.

[0177] The embodiment not shown has a connection box height H2 of approximately 250 mm and does not include the flared inlet extension 4”, pressure sensor 10g, and dynamic pressure conduit array 10h (which would provide unstable dynamic pressure measurements without the flared inlet extension 4”). It will be apparent to those skilled in the art that such an embodiment would result in a significant increase in pressure drop and airflow noise, and is unsuitable for applications requiring the determination of the volumetric flow rate of the supply air 3 within the diffuser 1c.

[0178] The damper 6 is perforated and sealed to the shroud 6” by a bellows 6’, which in turn seals to the proximal portion of the swirl vanes 17 radiating from the hub 8a, all of which surround the damper chamber 16’. The guide airflow 7”’ flows into the damper chamber 16’ and exits into the chamber 18 only by the proximal portion of the swirl vanes 17 as the exit guide airflow 9”’, which is drawn in by the Coanda effect and attached to the diffuser surface 1 and the surrounding ceiling (not shown) as the diffuser guide airflow 9a”’, which induces… Figure 3a The low-speed exhaust airflow 9 is far from the intake inlet 14a, even when the damper orifice 7a is substantially closed or leaking. Figure 3cAs shown, when damper 6 is fully open, the guide airflow 7”' and the exhaust guide airflow 9”' are typically 25% of the supply airflow 3. Therefore, it is impossible to reduce it below approximately 25%. Figure 3a ).

[0179] The minimum descent percentage and minimum airflow rate depend on the pressure. For example, if the system static pressure rises above a pressure (typically around 30 Pa) that would allow the supply airflow 3 to equalize the desired diffuser design airflow rate delivered when damper 6 is fully open, then the guide airflow 7”' and the exhaust guide airflow 9”' will increase to 25% above the desired diffuser design airflow rate. For instance, if the system static pressure at the diffuser rises from 30 Pa to 60 Pa (which is the typical maximum permissible pressure to prevent excessive noise), then the effective diffuser descent value will increase from 25% to 35% relative to the design airflow rate. This high and pressure-dependent diffuser descent value is unfavorable.

[0180] Figures 4a to 4 The diagram shows a side cross-sectional view and a top cross-sectional view of a VAV cyclone diffuser 1d as an embodiment suitable for cooling and heating applications. The VAV cyclone diffuser 1d has a rotating damper 6a, an air supply thermal actuator 10b, and an indoor air thermal actuator 10a.

[0181] An alternative purely cooling embodiment (not shown) does not include the gas-supply thermal actuator 10b.

[0182] The orifice 7a is regulated by a rotary damper 6a rotating on a ball bearing or slider 22 in response to the expansion or contraction of the indoor air thermal actuator 10a and the supply air thermal actuator 10b due to the temperature of each of the drawn indoor air and supply air. A supply air fan or motorized damper that blows the supply air 3 into the connecting box 3 at a substantially constant static pressure upstream of the side inlet interface 4' is not shown.

[0183] Figure 4a and Figure 4bThese are top and side cross-sectional views, respectively. The rotating damper 6a rotates around the diffuser centerline 0 and the damper housing 6b, and is equipped with external cyclone inlet blades 6c, allowing the damper orifice 7a to be fully open. A high-volume supply airflow 3, relative to the diffuser design airflow (i.e., the maximum airflow required to achieve the maximum cooling or heating capacity for the considered application), enters the connecting box 20 via a perforated baffle 21 and a side inlet interface 4'. The perforated baffle 21 disperses the supply airflow 3, causing it to flow as a swirling airflow 7b with high airflow and high tangential velocity into the cyclone chamber 16', which is essentially defined by the truncated conical housing 6b, and is then expelled by the exhaust cone 100 in a plane substantially parallel to the diffuser surface 1. The 360° pattern is discharged into room 18 as a high-flow-rate, high-tangential-velocity exhaust airflow 9, which is deflected by a row of swirl blades 17 outside the shroud 6”, thereby being drawn in by the Coanda effect and attached to the diffuser surface 1 and the surrounding ceiling (not shown), as a high-flow-rate, high-velocity diffuser airflow 9a dispersed in a plane that is substantially coincident with or parallel to the diffuser surface 1, which in turn substantially coincides with the plane of the lower side 2' of the ceiling joists that defines the ceiling (not shown).

[0184] Advantageously, no part of the diffuser 1d protrudes into the room 18, because no part is located below the plane of the diffuser surface 1 and thus below the plane of the lower side 2' of the ceiling joists.

[0185] In an alternative embodiment, interface 4' is located on top of the connection box 20.

[0186] In another embodiment, the diffuser 1d is freely suspended in the room 18, rather than the diffuser surface 1 resting in the ceiling joists 2.

[0187] The partition, in the form of mounting plate 42, divides the cavity within the core, which is enclosed by the shroud 6”, into a main chamber 54 and a secondary chamber 14b. A protrusion in the form of a cylinder 6”’ extends upward from the area near the face of the diffuser unit and enters the secondary chamber, forming the venturi tube wall. The gap between the venturi tube wall 6”’ and the mounting plate 42 forms the intake inlet 15’. The conduit between the venturi tube wall 6”’ and the shroud 6” forms the venturi tube.

[0188] The main air 12' flows through the air supply heating element 10b in the main chamber 54 and is then discharged into the intake passage 15 by the intake nozzle array 11' as the main airflow 12. This airflow 13 is introduced from the secondary chamber 14b through the intake inlet 15' above the venturi wall 6”' into the upper part 52 of the intake passage 15. The two airflows are then merged and discharged only by the proximal portion of the swirl blades 17 contained within the shroud 6” as the discharged guide airflow 9”'. This allows the supplementary airflow 14 to be drawn from the chamber 18 through the panel inlet 14a in the hub cap 8b and through the chamber thermal actuator 10a into the secondary chamber 14b.

[0189] exist Figure 13 The image better illustrates that the nozzles of the intake nozzle array are angled relative to the central axis of the unit. This creates vortices in the exhaust guide airflow 9”' to match the diffuser airflow 9a, and the venturi wall 6”' ( Figure 13 b) Restricting the intake passage 15 creates negative static pressure, increasing the intake of the secondary airflow 13 through the intake inlet 15'.

[0190] like Figure 4a As shown, when the damper 6 is fully open, the main airflow 12 typically does not exceed about 10% of the supply airflow 3.

[0191] Figure 4c and Figure 4d They are Figure 4a and 4 The top and side cross-sectional views of embodiment b are shown, in which the damper orifice 7a is partially throttled. A supply airflow 3 with a moderate flow rate relative to the diffuser design airflow (i.e., the maximum airflow required to achieve the maximum cooling or heating capacity of the considered application) enters the connecting housing 20 through the side inlet interface 4', flowing into the cyclone chamber 16', which is essentially defined by the housing 6b, as a damper airflow 7b with a moderate flow rate producing a vortex 23 with a higher distal tangential velocity and a lower proximal tangential velocity, and is discharged by the exhaust cone 100 into the chamber 18 in a 360° pattern in a plane substantially parallel to the diffuser surface 1, as a vortex 23 with a moderate flow rate and a higher distal tangential velocity. The exhaust airflow 9, with its tangential velocity and lower proximal tangential velocity, is directed toward the shroud 6” and deflected at least by the distal portion of the swirl vanes 17 outside the shroud 6”, thereby being drawn in by the Coanda effect and attached to the diffuser surface 1 and the surrounding ceiling (not shown). As a diffuser airflow 9a of moderate volume dispersed in a plane substantially coincident with or parallel to the diffuser surface 1, a greater diffusion distance of diffuser airflow 9a is achieved compared to the diffusion distance achievable when the exhaust airflow 9 has a substantially uniform dispersion velocity across the span of the swirl vanes 17 outside the shroud 6”.

[0192] It will be apparent to those skilled in the art that, since the diffuser delivery distance (not shown) required to achieve a fixed terminal velocity (typically taken as 0.25 m / s) is proportional to the square root of the product of the volumetric flow rate and the discharge velocity, it is assumed that the static pressure of the supply airflow 3 flowing towards the side inlet interface 4' is substantially constant, even if the distal exhaust velocity remains substantially constant, but considering the reduction in volumetric flow rate, due to Figure 4c and Figure 4d The diffuser delivery distance under the medium airflow generated by the medium damper orifice 7a will also be less than that generated by the medium airflow. Figure 4a and Figure 4b The diffuser delivery distance under high airflow generated by the large air damper orifice 7a.

[0193] Figure 4e and Figure 4f They are Figure 4a and Figure 4b The illustrated embodiment shows a top and side cross-sectional view, with the damper orifice 7a fully closed. Advantageously, when the damper 6a is fully closed or slightly open, the leaking or small damper airflow 7 can generate a vortex 23, which brings early stability to the exhaust airflow 9, thereby producing a Coanda effect attached to the diffuser surface 1 and the surrounding ceiling (not shown). Furthermore, the guide airflow 9”', composed of the main airflow 12 and the secondary airflow 13, is discharged in a 360° pattern in a plane substantially parallel to the diffuser surface 1, possessing sufficient momentum to be drawn in and attached to the diffuser surface 1 and the surrounding ceiling (not shown) via the Coanda effect, serving as the diffuser guide airflow 9a”'. This airflow induces a low-speed discharge airflow 9 generated by leakage from the damper orifice 7a of the damper airflow 7, thereby improving the stability of the very low airflow volume discharge airflow 9 and increasing the rotational momentum of the discharge airflow. This increases the delivery distance when the damper airflow 7 is strongly throttled, reduces the risk of spillage or short-circuiting into the panel inlet 14a in case of leakage, and allows the variable air volume (VAV) to be reduced to an extremely low airflow rate. Figures 8a to 8f The lieutenant general will further elaborate on these principles and the operation of the inhalation system.

[0194] Alternative embodiments using an electric actuator instead of one or more thermal actuators to rotate the rotary damper 6a are also possible.

[0195] For the high damper orifice 7a and medium damper orifice 7a settings corresponding to the high airflow 7 and medium airflow 7 respectively, many alternative embodiments of the rotary damper 6a and damper housing 6b can achieve a swirling flow 23 with a substantially constant distal tangential velocity in the cyclone chamber 16”, thereby achieving a substantially constant distal velocity of the exhaust flow 9 and the diffusion flow 9a over a wide range of damper orifices 7a for the supply airflow 3 with a substantially constant static pressure at the side inlet interface 4'. Figure 4g to Figure 4 l illustrates two examples of such alternative embodiments.

[0196] Figure 4 g and Figure 4 h is a schematic diagram illustrating an alternative embodiment of the rotary damper 6a and damper housing 6b, wherein the cyclone inlet blades 6c' are located outside the rotary damper 6a. When the orifice 7a is fully open, a high-tangential-velocity vortex 23 is generated by the high damper airflow 7, such as... Figure 4 As shown in g. (Not shown) Figure 4c and Figure 4d Similarly, a swirling flow 23 with high far-side tangential velocity and reduced near-side tangential velocity is generated when the damper orifice 7a is partially throttled. Disadvantageously, when the rotary damper 6a is fully closed ( Figure 4 When h) or almost completely closed, a reverse leakage airflow 7' without swirl is generated, which may cause the diffuser to guide the airflow 9a”' ( Figure 4e Unstable.

[0197] Figure 4 i to Figure 4 l is a schematic diagram illustrating an alternative embodiment of the rotary damper 6a and damper housing 6b, wherein the cyclone inlet blades 6c' are located inside the rotary damper 6a and are configured to overlap only partially with the fully open damper orifice 7a, thereby producing a... Figure 4 The damper airflow 7 shown in i has a weakened swirl 23' with maximum airflow and weak tangential velocity, which is similar to... Figure 4 The damper airflow 7b shown in j has a reduced airflow rate and an increased distal tangential velocity, which is the opposite of the enhanced swirl 23. Advantageously, for a wide range of rotary damper 6a positions, this embodiment can achieve an increased distal velocity of the exhaust airflow 9 as the volumetric flow rate of the exhaust airflow 9 decreases, potentially achieving a substantially constant delivery distance of the diffuser airflow 9a over a wide range of airflow rates. Another advantage of this embodiment is that the rotary damper 6a is strongly throttled ( Figure 4 k) or completely off ( Figure 4 When the damper airflow 7 or leakage occurs, it is discharged with the swirl 23. This improves the stability of the discharge airflow 9 at very low airflow rates (including less than 15% of the maximum airflow rate) and increases rotational momentum, thereby improving the delivery distance under strong throttling or the stability of Coanda effect intake to diffuser surface 1 under leakage, and allowing the variable air volume (VAV) to be reduced to extremely low airflow rates without spillage. Disadvantageously, this embodiment partially obstructs the fully open damper orifice 7a, thus reducing the maximum airflow rate.

[0198] Figures 4a to 4The rotating damper shown in Figure 1 rotates around the centerline O of the diffuser and is therefore independent of pressure. The air pressure in the connecting box 20 does not exert a force on the damper mechanism, which is advantageous for mechanisms including thermal actuators, as the force generated by the thermal actuator is typically very weak.

[0199] Figure 5a and Figure 5b These are side and top sectional views of an embodiment of the VAV cyclone diffuser 1d, wherein the cyclone chamber 16” surrounds the shroud 6 (which houses the actuator, intake system, etc., as described above; all these components are not shown for clarity) and is substantially defined by a plurality of baffles 6a', which, when fully closed (not shown), substantially form a frustum around the diffuser’s centerline O. Each baffle 6a' has a door rotation axis 6a” that coincides with or is very close to the leading edge of the baffle 6a' and coincides with or is very close to the door housing 6b, when viewed in plan view ( Figure 5b When observed in the cyclone chamber 16", the rotation axis 6a” of the door is arranged substantially radially, so that each baffle 6a', when closed (not shown), essentially seals the damper housing 6b from the inside of the cyclone chamber 16”, and opens by swinging the baffle angle α inward, thereby opening the damper orifice 7a between the damper housing 6b and the trailing edge 6a”’ of the baffle 6a’. The trailing edge 6a”’ of the baffle may be serrated to suppress vortices in the damper airflow 7, thereby reducing airflow noise. When the damper orifice 7a is fully open, the baffle angle α ( Figure 5b The angle is typically 25° to 30°.

[0200] Advantageously, no part of the diffuser 1d protrudes into the room 18, because no part is located below the plane of the diffuser surface 1, which substantially coincides with the plane of the lower side 2' of the ceiling joists.

[0201] In an alternative embodiment, the interface 4' through which the supply airflow 3 enters the connection box 20 is located on the top of the connection box 20 rather than on the side.

[0202] In another embodiment, the diffuser 1d is freely suspended in the room 18, rather than the diffuser surface 1 resting in the ceiling joists 2.

[0203] For a given static pressure in the connecting box 20, the airflow 7 from the damper is relative to a plane parallel to the diffuser surface 1. Figure 5aThe airflow rate and swirl angle β of the diffuser airflow 9a increase with the increase of the damper orifice 7a, and therefore increase with the increase of the damper angle α. For a small damper orifice 7a, the swirl angle β is small enough for the small airflow rate of the damper airflow 7 relative to the diffuser design airflow rate (i.e., the maximum airflow rate required to achieve the maximum cooling or heating capacity of the considered application) to achieve Coanda effect attachment of the diffuser airflow 9a to the diffuser surface 1 and the surrounding ceiling (not shown), and to distribute it in a plane substantially coinciding with or parallel to the diffuser surface 1. For a large damper orifice 7a, the swirl angle β is too large for the large airflow rate of the damper airflow 7 relative to the diffuser design airflow rate (i.e., the maximum airflow rate required to achieve the maximum cooling or heating capacity of the considered application) to achieve stable Coanda effect attachment of the diffuser airflow 9a to the diffuser surface 1 and the surrounding ceiling (not shown). In this case, the swirl blades 17 deflect the exhaust airflow 9 to reduce the exhaust angle from the swirl angle β to a sufficiently small exhaust angle δ. Figure 5a This allows the diffused airflow 9a to adhere to the diffuser surface 1 and the surrounding ceiling (not shown) through the Coanda effect, thereby distributing the diffused airflow 9a in a plane that is substantially coincident with or parallel to the plane of the diffuser surface 1.

[0204] like Figure 5a and Figure 5b As shown, when the damper orifice 7a is fully open, the high-volume supply airflow 3 enters the connecting box 20 through the perforated baffle 21 and the side inlet interface 4'. The perforated baffle 21 distributes the supply airflow 3 at a large damper angle α, thereby applying a high tangential velocity to the high-volume damper airflow 7, thereby generating a vortex 23 in the cyclone chamber 16”. This vortex 23 is discharged into the room 18 by the exhaust cone 100 in a 360° pattern in a plane substantially parallel to the diffuser surface 1, as an exhaust airflow 9 with a high airflow and a high tangential velocity. This exhaust airflow 9 is deflected by a row of swirl blades 17 outside the shroud 6”, thereby being absorbed by the Coanda effect and attached to the diffuser surface 1 and the surrounding ceiling (not shown), as a high-volume and high-velocity diffuser airflow 9a distributed in a plane substantially coincident with or parallel to the diffuser surface 1.

[0205] Compared to a fully open regulating damper orifice 7a, for the same static pressure in the connecting box 20, when the damper orifice 7a is opened to a moderate setting (not shown), the supply airflow 3 with a reduced airflow rate enters the connecting box 20 via a perforated baffle 21 through a side inlet interface 4'. This perforated baffle 21 distributes the supply airflow 3, causing it to flow into the cyclone chamber 16'. This airflow 7, with a reduced airflow rate and a high tangential velocity (i.e., a velocity similar to that when the damper orifice 7a is fully open), is discharged by the exhaust cone 100 into the room 18 in a 360° pattern within a plane substantially parallel to the diffuser surface 1. The exhaust airflow 9, with a low airflow rate and a high distal tangential velocity and a low proximal tangential velocity, is discharged toward the shroud 6”. This exhaust airflow 9 is deflected at least by the distal portion of the swirl vanes 17 outside the shroud 6”, thereby being drawn in by the Coanda effect and adhering to the diffuser surface 1 and the surrounding ceiling (not shown). As a diffuser airflow 9a with a reduced airflow rate, it is distributed in a plane substantially parallel to the diffuser surface 1. Thus, a greater delivery distance of the diffuser airflow 9a is achieved in a plane substantially coincident with or parallel to the diffuser surface 1, compared to the delivery distance achievable when the velocity is uniformly distributed on the swirl vanes 17 outside the shroud 6”.

[0206] and Figure 4 k and Figure 4 The airflow pattern shown in l is similar. When the damper 6a' is strongly throttled or completely closed but leakage exists, the damper airflow 7 or the leakage is discharged as a swirling flow 23. This improves the stability of the very low-volume exhaust airflow 9 and increases rotational momentum, thereby improving the delivery distance under strong throttling or promoting Coanda effect intake towards the diffuser surface 1, reducing the risk of spillage in case of leakage, and allowing the variable air volume (VAV) to be reduced to extremely low airflow rates, including to less than 15% of the airflow rate when the damper orifice 7a is fully open. This is in Figure 8e and Figure 8f Further explanation is provided below.

[0207] and Figures 4a to 4 Compared to the embodiment shown in Figure 1, for a given connection box height H3, Figure 5a and Figure 5b The embodiment described above can have a much higher maximum airflow capacity because the cumulative opening area of ​​the damper orifice 7a in the latter is much larger. Furthermore, the latter has the advantage that the compression door seal is easily made airtight when the damper 6a' is closed, whereas the sliding action of the rotary damper 6a in the former is more difficult to seal and may lead to leakage or increased friction during the operation of the rotary damper 6a.

[0208] Figure 5cThis is a bottom view of an embodiment of a swirling diffuser 1d, which has radially offset swirling blades 17 connected to the diffuser surface 1, and guides the airflow 9”' to be discharged in a 360° pattern in a plane substantially parallel to the diffuser surface 1 by a shroud 6” of the intake system (not shown), and is guided away from the hub cap 8b, thereby preventing short-circuiting into the airflow. Figures 4a to 4 f、 Figures 8a to 8g , Figure 10 a to Figure 10 c and Figure 11 a and Figure 11 Panel entrance 14a in the embodiment described in b.

[0209] Figure 5d and Figure 5e This is a schematic diagram showing leading-edge barbs 17' and angled trailing-edge serrations 17" respectively arranged on one embodiment of the swirl vane 17 to reduce airflow noise. The leading-edge barbs 17" are bent at an angle θ with radius R, achieving a shallower leading-edge angle than the angle ε of the swirl vane 17 relative to a plane parallel to the diffuser surface 1, while the trailing-edge serrations 17" are angled ε relative to the swirl vane 17, thus being parallel to or coincident with the diffuser surface 1. In the plan view, the leading-edge barbs are shown with continuously increasing absolute orientation angles, such that the centerline angle δ2 of the proximal barb is greater than the centerline angle δ1 of the distal barb, causing the tip of the proximal barb to protrude outward relative to the tip of the distal barb.

[0210] An alternative embodiment, not shown, has a leading-edge barb that curves upward to a steeper angle ε than that of the swirl blade 17 relative to a plane parallel to the diffuser surface 1.

[0211] Another embodiment, not shown, increases the absolute angle of attack of the leading edge of the tip of the barb 17' continuously by changing the angle θ shown in the X section AA from a larger value of the distal barb 17' to a smaller value of the proximal barb 17', where θ ≤ ε.

[0212] Because the absolute orientation of the leading edge barbs 17' is inconsistent, the absolute angle of attack of each successive barb tip in the side view increases by decreasing θ as it evolves towards the proximal direction. Furthermore, each successive barb tip protrudes outward in the plan view, making δ2 > δ1. This is beneficial for reducing noise and air pressure drop, especially for... Figure 5a , Figure 5b , Figure 7 a to Figure 7 c. Figures 8a to 8i , Figure 9 a to Figure 9 o and Figure 10 a to Figure 10 Example c is shown.

[0213] The curved leading edge barbs 17' are preferred embodiments because they reduce noise more effectively than trailing edge serrations 17" and are less aesthetically jarring, and also reduce diffuser pressure drop.

[0214] The preferred dimensions of Hl are 5 mm to 20 mm, the preferred dimensions of Wl are 1 mm to 5 mm, the preferred dimensions of R are 5 mm to 50 mm, the preferred dimensions of Ht are 5 mm to 20 mm, the preferred dimensions of Wt are 1 mm to 5 mm, and the preferred dimensions of ε are 20° to 50°.

[0215] Figure 6a and Figure 6b The figures show a side and top sectional view of an alternative embodiment of the VAV cyclone diffuser 1d, wherein the cyclone chamber 16” surrounds the shroud 6 (which houses the actuator, intake system, etc.; all of these components are not shown) and is substantially defined by a plurality of baffles 6a' which, when fully closed (not shown), substantially form a frustum around the centerline O of the diffuser. Each baffle 6a' has a substantially radially arranged door rotation axis 6a” that coincides with or is very close to the leading edge of the baffle 6a' and coincides with or is very close to the door housing 6b. Figure 6b When observed in the cyclone chamber 16", the door rotation axes 6a” are arranged substantially radially, so that each baffle 6a’, when closed (not shown), essentially seals the damper housing 6b from the inside of the cyclone chamber 16”, and opens by swinging the baffle angle α inward, thereby opening the damper orifice 7a between the damper housing 6b and the trailing edge 6a”’ of the baffle 6a’. The trailing edge 6a”’ of the baffle may be serrated to suppress vortices in the damper airflow 7, thereby reducing airflow noise. When the damper orifice 7a is fully open, the baffle angle α ( Figure 6b The angle is typically 25° to 30°.

[0216] Advantageously, no part of the diffuser 1d protrudes into the room 18, because no part is located below the plane of the diffuser surface 1, which substantially coincides with the plane of the lower side 2' of the ceiling joists.

[0217] In an alternative embodiment, the interface 4' through which the supply airflow 3 enters the connection box 20 is located on the top of the connection box 20 rather than on the side.

[0218] In another embodiment, the diffuser 1d is freely suspended in the room 18, rather than the diffuser surface 1 resting in the ceiling joists 2.

[0219] For a given static pressure in the connecting box 20, the airflow 7 from the damper is relative to a plane parallel to the diffuser surface 1. Figure 6aThe airflow rate and swirl angle β increase with the increase of the damper orifice 7a, and therefore with the increase of the damper angle α. For a small damper orifice 7a, the swirl angle β can be small enough to achieve Coanda effect adhesion of the diffuser airflow 9a to the diffuser surface 1 and the surrounding ceiling (not shown), and to distribute it in a plane that is substantially coincident with or parallel to the diffuser surface 1. For the large damper orifice 7a, the swirling spiral angle β is too large for the damper airflow 7 at atmospheric flow rate to achieve a stable Coanda effect attachment of the diffuser airflow 9a to the diffuser surface 1 and the surrounding ceiling (not shown). In this case, the perforated baffle 17' deflects the exhaust airflow 9, causing it to spread substantially within the shroud cavity 24' below the shroud 24. This allows the exhaust airflow 9 to pass through the perforated baffle 17' at a sufficiently large acute angle into the room 18, as a diffuser airflow 9a with high flow rate and swirling flow, thereby being drawn in and attached to the diffuser surface 1 and the surrounding ceiling (not shown) by the Coanda effect, as a high-flow-rate diffuser airflow 9a spread in a plane substantially coinciding with or parallel to the plane of the diffuser surface 1.

[0220] like Figure 5a and Figure 5b The and Figure 6a and Figure 6b As shown, the fully open damper orifice 7a generates a high swirling flow 23 in the cyclone chamber 16”, which is discharged into the room 18 by the entire surface of the perforated baffle 17' outside the shroud 6” as an exhaust airflow 9 with high airflow and swirling flow, thereby being drawn in by the Coanda effect and attached to the diffuser surface 1 and the surrounding ceiling (not shown), as a diffuser airflow 9a with high airflow and high velocity distributed in a plane substantially coincident with or parallel to the diffuser surface 1.

[0221] When operating at the same static pressure as described above in the connecting box 20 and with the damper orifice 7a opened to a moderate setting (not shown), the damper airflow 7, with a reduced airflow rate and a high tangential velocity (i.e., a velocity similar to that when the damper orifice 7a is fully open), generates a swirling flow with a higher distal tangential velocity and a lower proximal tangential velocity. This swirling flow is deflected by the perforated baffle 17' and is essentially shaped by the distal portion of the diffuser baffle 17' outside the shroud 6" in a plane substantially parallel to the diffuser surface 1 at a 360° angle. The exhaust airflow 9, which is discharged into room 18 as a swirling flow with a reduced airflow rate and a higher distal tangential velocity and a lower proximal tangential velocity, is drawn in by the Coanda effect and adheres to the diffuser surface 1 and the surrounding ceiling (not shown). As a diffuser airflow 9a with a reduced airflow rate, which is distributed in a plane substantially parallel to the diffuser surface 1, the diffusion airflow 9a achieves a greater delivery distance than that achievable when the velocity is uniformly distributed on the baffle 17' outside the shroud 6”.

[0222] When the damper 6a' is strongly throttled or completely closed but leakage occurs, the damper airflow 7 is discharged as a swirling flow 23, which improves the stability of the very low airflow volume of the discharged airflow 9 and increases the rotational momentum, thereby improving the delivery distance under strong throttling or promoting the Coanda effect intake to the diffuser surface 1, reducing the risk of spillage in case of leakage, and allowing the variable air volume (VAV) to be reduced to extremely low airflow, including when the damper orifice 7a is fully open, it is reduced to less than 15% of the airflow volume.

[0223] and Figure 5a and Figure 5b Compared to the embodiment shown, when viewed from room 18, Figure 6a and 6b The embodiments in the text have perforated diffusers, which do not have the aesthetic appeal of swirling diffusers, but can have a lower maximum airflow capacity for a given area of ​​diffuser surface 1'.

[0224] Figure 7 a to Figure 7 c shows a top sectional view of an alternative preferred embodiment of the structure and arrangement of multiple wind deflectors 6a', wherein the rotation axis 6a” of each wind deflector 6a' is substantially located at the center of the wind deflector 6a', or slightly offset towards the rear edge 6a”' of the wind deflector, such that when the wind deflector 6a' is closed, the static pressure P in the connecting box 20 is balanced or offset on the wind deflector 6a' to apply a slight closing force, such as Figure 7 As shown in c. The leading edge seal 6a”” can seal each windshield 6a’ when each windshield 6a’ is closed, and closes substantially against the trailing edge 6a”’ of the adjacent windshield 6a’.

[0225] As in Figure 5a , Figure 5b , Figure 6a and Figure 6b As described above, the trailing edge 6a”' can be serrated to reduce airflow noise.

[0226] As in Figure 5a , Figure 5b , Figure 6a and Figure 6b As described above, for a given static pressure in the connecting box 20, such as Figure 7 As shown in b, the arrangement of the windbreak 6a' with a medium-sized damper orifice 7a generates a diffused airflow 9a with a medium airflow volume, thereby generating a vortex with a higher far-side tangential velocity and a lower near-side tangential velocity on the swirl blades 17 outside the shroud 6”. As a result, a greater delivery distance of the deflected diffuser airflow 9a is achieved in a plane that coincides with or is substantially parallel to the diffuser surface 1, compared to the delivery distance that can be achieved when the velocity is uniformly distributed across the span of the swirl blades 17 outside the shroud 6”.

[0227] Similarly, such as Figure 5a , Figure 5b , Figure 6a and Figure 6b As described above, when the windshield 7a is substantially closed or there is a leak, such as Figure 7 As shown in c, the damper airflow 7 is discharged as a swirling flow 23, which improves the stability of the very low airflow volume of the discharged airflow 9 and increases the rotational momentum, thereby improving the delivery distance under strong throttling or promoting the Coanda effect intake to the diffuser surface 1, reducing the risk of spillage in case of leakage, and allowing the variable air volume (VAV) to be reduced to extremely low airflow, including to less than 15% of the airflow volume when the damper orifice 7a is fully open.

[0228] Advantageously, the substantially balanced static air pressure on the damper 6a' allows the damper to operate substantially independently of pressure, as this eliminates or reduces the air pressure on the damper mechanism and (one or more) actuators, which is particularly advantageous for thermal actuators, as these actuators are very weak.

[0229] The disadvantage, especially for electrically actuated VAV diffusers (in which case a completely sealed deflector 6a' is highly advantageous), is... Figure 5a , Figure 5b , Figure 6a and Figure 6b Compared to the embodiment shown, the door rotation axis 6a” located substantially at the center on each windshield 6a' makes sealing the top and bottom of each windshield 6a' more complex.

[0230] Figure 7 d to Figure 7 f is like Figures 4a to 7The top cross-sectional view of embodiment c shows that one or two shielding sections 25 located directly upstream of the swirl vane 17 or the shroud 24 partially block the airflow 7 from the damper, so that the exhaust airflow 9 is discharged in a 270° (three-way), 180° (two-way asymmetric), or 2×90° (two-way symmetric) pattern, respectively, instead of a 360° pattern.

[0231] Figures 8a to 8f The diagram shows a top and side sectional view of one embodiment, in which a printed circuit board 10d, a pressure sensor 10g, and an electric actuator 10c are located in a sub-chamber 14b. A processor, an integrated indoor air temperature sensor 10e, a carbon dioxide (CO2) sensor, a volatile organic compound (VOC) sensor, a relative humidity (RH) sensor, and a Bluetooth antenna are not shown; these may optionally be included on the printed circuit board 10d. A passive infrared (PIR) sensor 10h may be inserted into the printed circuit board 10d and may be oriented to extend through the hub cap 8b to sense occupancy in room 18. The pressure sensor 10g is connected to the mounting plate 42 via a pressure tube 10g” and then senses the static pressure in the connection box 20 relative to the static pressure in the sub-chamber 14b, which is substantially equal to the static pressure in room 18, via a vent tube 10g’.

[0232] An electric actuator 10c is connected to a worm gear 26, which drives a worm nut 27, which is fixedly connected to the bottom of an intake damper 29 and a damper spring 28. The damper spring 28 is compressed and pushes multiple damper spokes 30 towards the lower side of the intake damper 29, which in turn acts as a stop to prevent the damper spokes 30 from passing over. The damper spokes 30 are fixedly attached to a translation ring 31, and multiple damper arms 32 are fixedly attached to the translation ring 31, each damper arm terminating at one of multiple magnets 32'. The multiple magnets 32' are positioned relative to an equal number of dampers 6a' (only when...). Figure 8a and Figure 8c (Schematally shown) The arrangement includes each windshield 6a' comprising an ferrous metal sliding surface, such that each magnet 32' is magnetically attracted to the ferrous metal sliding surface of the windshield 6a' in contact with it. The static pressure of the airflow 3 in the connecting box 20 further pushes the windshields 6a' against their respective magnets 32' to open, and the gravity acting on the windshields 6a' further pulls them against their respective magnets 32' to open.

[0233] In an alternative embodiment, the intake damper 29 is located above the damper housing 6b and is mechanically connected to the worm nut 27 to open upward from the damper housing 6b.

[0234] Figure 8a , Figure 8c and Figure 8e This is a top cross-sectional view of the embodiment, in which the main air 12' flows through the supply air temperature sensor 10f in the main chamber 54, which is separated from the secondary chamber 14b by the mounting plate 42, and is then discharged into the intake channel 15 by the intake nozzle array 11' as the main airflow 12 to introduce the secondary airflow 13 from the secondary chamber 14b into the upper part 52 of the intake channel 15. Then both airflows are discharged in a 360° pattern into a plane substantially parallel to the diffuser surface 1 as the guide airflow 9"' discharged by the proximal portion of the swirl blades 17 contained in the shroud 6". This draws in the supplementary airflow 14 from the room 18 via the panel inlet 14a in the hub 8b and through the printed circuit board 10d (and through the indoor air temperature sensor 10e, not shown) into the secondary chamber 14b to provide accurate sensing of indoor air temperature, relative humidity and carbon dioxide (CO2) and to cool the printed circuit board 10d.

[0235] The airflow rate of the air supply 3 is calculated by a processor (not shown) on the printed circuit board 10d or by a remote processor as a function of the static air pressure in the connecting box 20 and the position of the worm nut 27, which in turn determines the door angle α of the windshield 6a". The processor can determine the position of the worm nut 27 by calculating the number of revolutions of the worm gear 26, and, when the worm nut 27 is fully lowered, utilizes a microswitch 40 (e.g., Figure 10 a to Figure 10 c and Figure 11 (b) Reset the position of the electric actuator 10c to zero.

[0236] Figure 8a and Figure 8b These are top and side cross-sectional views, respectively. The worm nut 27 has been fully lowered by the electric actuator 10c, and the damper spokes 30 slide in the shroud slot 30' parallel to the diffuser centerline 0, thereby rotating the constraint translation ring 31 around the diffuser centerline 0. This causes the gravity acting on the dampers 6a' and the attraction of the multiple magnets 32' to fully pull them open, and the air pressure inside the connecting box 20 to fully push open the multiple dampers 6a' (only when...). Figure 8a (Illustrated schematically) such that the dampers 6a' open to a door angle α about their respective rotation axes 6a” which are substantially perpendicular to the inlet cone 101, the door angle α being at approximately 25° to 30° relative to a plane parallel to the tangent of the damper housing 6b at each respective rotation axis 6a”, resulting in a high airflow and high tangential velocity exhaust airflow 9a.

[0237] In an alternative embodiment, the shroud slot 30' forms an acute angle with respect to the diffuser centerline 0.

[0238] Figure 8c and Figure 8dThese are top and side cross-sectional views, respectively. The worm nut 27 has been partially driven upwards by the electric actuator 10c, causing the gravity acting on the windshield 6a' and the attraction of the multiple magnets 32' to partially pull it open, and the air pressure in the connecting box 20 to partially push open the multiple windshields 6a' (only in...). Figure 8c (shown schematically in the diagram), causing the wind deflectors 6a' to partially open about their respective axes of rotation 6a", resulting in an exhaust airflow 9a with a moderate airflow rate and a high distal tangential velocity and a low proximal tangential velocity.

[0239] For a given static pressure in the connecting box 20 Figure 8b The speed of the airflow 7 in the damper and Figure 8d The velocities of the airflows 7 at the dampers are substantially equal in magnitude. Therefore, the arrows depicting the airflows 7 at the dampers are shown to be of equal length. However, relative to the diffuser housing 6b, Figure 8d The tangential velocity component T2 of the airflow 7 in the damper is greater than Figure 8a The tangential component T1 in the middle leads to Figure 8c The distal velocity of the exhaust gas flow 9a may be greater than Figure 8a The distal velocity of the exhaust airflow 9a. Therefore, it is assumed that... Figure 8c The decrease in the volumetric flow rate of the diffuser gas 9a can be substantially compensated by the corresponding increase in the velocity at the far side of the gas, thus the momentum of the two exhaust gas streams 9a can be substantially equal, leading to... Figure 8c The delivery distance (not shown) of the diffuser airflow 9a in the plane coinciding with or substantially parallel to the diffuser surface 1 is substantially equal to... Figure 8a The delivery distance in the middle, or at least greater than the delivery distance that can be achieved when the exhaust airflow 9 has a substantially uniform diffusion velocity across the span of the swirl blades 17 outside the shroud 6”.

[0240] Figure 8e and 8f The figures are a top cross-sectional view and a side cross-sectional view, respectively, in which the worm nut 27 has been substantially driven upward by the electric actuator 10c, causing multiple magnets 32' to push multiple dampers 6a' and thereby close these dampers 6a' around their respective axes of rotation 6a”. The guide airflow 9”', consisting of the main airflow 12 and the secondary airflow 13, is discharged in a 360° pattern in a plane substantially parallel to the diffuser surface 1, and has sufficient momentum to be drawn in and attached to the diffuser surface 1 and the surrounding ceiling (not shown) by the Coanda effect. As the diffuser guide airflow 9a”', the diffuser guide airflow 9a”' induces the low-speed exhaust airflow 9 generated by leakage from the damper orifice 7a through the damper airflow 7 to also attach to the diffuser surface 1 and the surrounding ceiling, thereby preventing the leaked or exhaust airflow 9 from pouring out and short-circuiting into the panel inlet 14a and passing through the indoor air temperature sensor 10e (not shown).

[0241] Figure 8g It is a top cross-sectional view in which the worm nut 27 has been fully driven to the upper side by the electric actuator 10c, so that the intake damper 29 seals the intake seal 33, cutting off the airflow to the intake nozzle array 11', and as the multiple magnets 32' push the multiple wind deflectors 6a' so that these wind deflectors 6a' close around their respective rotation axes 6a", the damper spring 28 is compressed.

[0242] exist Figures 8a to 8g In one embodiment, the damper arm 32 translates in a direction substantially parallel to the diffuser centerline 0. In another embodiment, the damper arm 32 translates with rotation relative to the diffuser centerline 0. In yet another embodiment, the damper arm 32 translates parallel to the diffuser centerline 0 and rotates about the diffuser centerline 0.

[0243] Figure 8h The diagram shows a top cross-sectional view of a preferred embodiment, wherein each damper 6a' is equipped with an unlocked latch 34 and an unlocked latch handle 34' (which may be in the form of a screwdriver slot or a hex socket) or a locked latch 34a and a locked latch handle 34a'. A tool, such as a screwdriver or hex wrench, can be inserted through the face of the diffuser (not shown) to turn the latch handle of the closed damper to the locked position 34a', thereby locking the corresponding latch 34a onto the damper housing 6b (or, in reverse operation, turning it from the locked position 34a' to the unlocked position 34a). When the translation ring 31 and the plurality of damper arms 32 move to open the unlocked (and thus active) damper 6a', the corresponding magnet 32' disengages from the closed damper 6a'. This allows the diffuser, according to the embodiment, to be configured, or potentially reconfigured in the field, for one of multiple airflow ranges, each with a full VAV operating range up to a reduction of 15% or less when the unlocked dampers are fully open. To achieve a substantially uniform 360° airflow pattern in a plane substantially parallel to diffuser surface 1, ideally, at least four dampers 6a' should be unlocked. For a given static pressure in the connection box 20, this equates to a reduction of the maximum airflow rate by approximately 60% for the lowest airflow range (for the configuration shown) compared to having all dampers 6a' active, while maintaining a VAV reduction ratio of less than 15% for each airflow range.

[0244] Figures 8i to 8l A top and side sectional view of an alternative windshield locking embodiment is shown, wherein a screwdriver, hex wrench, or similar tool 37 can be inserted through the surface of the diffuser to engage one of a plurality of locking shafts 36, each locking shaft being associated with a corresponding windshield 6a' that can be locked or unlocked (only when...). Figure 8k(Illustrated in the image) corresponds to, where Figure 8i and 8j The tool 37 is shown to rotate 90°, causing the locking shaft 35 and associated locking pins 36, 36' and 36"', as well as the locking disc 36"', to rotate. This causes the door arm ring 31' to disengage from the translation ring 31 and engage securely with the housing ring 31"', thereby locking the corresponding door arm 32 so that its magnet 32' is pushed against the corresponding windshield 6a', thus locking the windshield. The locking pins 36, 36' and 36"' of all other locking shafts, as well as the locking disc 36"'', securely attach the door arm ring 31' to the translation ring 31 and disengage it from the housing ring 31"''.

[0245] Figure 8k and 8l It shows that, in addition to Figure 8i and 8l All wind deflectors 6a' except the locked wind deflector are pulled open by the corresponding magnets 32' when the translation ring 31 is driven downward by the electric actuator 10c.

[0246] Figure 9 Figures a through 9 show side and top cross-sectional views of another embodiment, in which multiple half-sized wind deflectors 6a'1 are spaced apart between multiple wind deflectors 6a', each wind deflector 6a' incorporating a magnetic recess 6a'2 and various noise reduction features. The wind deflectors 6a' and half-sized wind deflectors 6a'1 pivot about their respective axes of rotation 6a'' via door arms 6a1. A smooth leading edge 6b1 and angled trailing edge serrations 6a4 reduce pressure drop and noise generated by airflow. A turbulence generator 6a3 further reduces airflow noise, particularly pitch noise, at the small-aperture openings of the wind deflectors 6a' and half-sized wind deflectors 6a'1.

[0247] Figure 9 A through 9d are schematic diagrams showing the rear sealing edge 6a5 of the wind deflector 6a' and the half-size wind deflector 6a'1, which is pushed relative to the corresponding wind deflector rotation axis 6a" by a magnet 32' attached to the damper arm 32, thereby closing against the damper seal 6b2 of the damper housing 6b. The circular inlet 6b1 of the damper housing 6b reduces noise generated by airflow and pressure drop of the wind deflectors 6a' and 6a'1. The radius R is preferably between 5 mm and 30 mm, and most preferably between 10 mm and 20 mm.

[0248] Each magnet 32' corresponding to a windshield 6a' is located within the door slot 6a'2 of that windshield, while each magnet 32' corresponding to a half-size windshield 6a'1 is located directly on the windshield 6a'1. For ease of comparison, Figure 9 a and Figure 9The unlabeled dashed lines in b depict the damper arm 32, magnet 32', wind deflector 6a', and half-size wind deflector 6a'1. Figure 9 h and Figure 9 The marked position in i.

[0249] Figure 9 e to Figure 9 g is a schematic diagram showing a turbulence generator 6a3 located on a windshield 6a' and a half-size windshield 6a'1, wherein the turbulence generator 6a3 is located as shown in the diagram. Figure 9 c. Figure 9 i and Figure 9 The location shown in o, or located on the door sealing surface, is designed to reduce noise, particularly the tonal noise generated by airflow through the small damper opening 7a of the partially open door. The turbulence diffuser 6a3 can be substantially planar, protruding from the dampers 6a and 6a' at an angle γ, which can be between 20° and 90°, preferably between 30° and 60°, and the turbulence diffuser 6a3 can be as shown in o. Figure 9 The shape shown as e can be a rectangle, a triangle or a truncated triangle (not shown), or a substantially sinusoidal or irregular shape (not shown). Dimension G is preferably between 0.5 mm and 5 mm, and most preferably between 1 mm and 3 mm. Dimension W is preferably between 1 mm and 20 mm, and most preferably between 3 mm and 10 mm.

[0250] Alternatively, the turbulence generator 6a3 can be configured as a vortex generator, one embodiment of which is a plurality of non-planar solid bodies (see [link]). Figure 9 f) Each non-planar solid body is shaped like a twisted pyramid with a triangular base. The apex and front side of the twisted pyramid suspend at an angle β1 above the bottom apex of the leading edge, resembling the bow of a ship. The rear side extends downwards from the apex at an angle γ. β1 can be between 5° and 60°, or between 20° and 55°. γ can be between 5° and 80°, or between 10° and 40°. Dimension G can be between 0.5 mm and 5 mm, or between 1 mm and 3 mm. Dimension W can be between 1 mm and 20 mm, or between 3 mm and 10 mm.

[0251] Figure 9 Figure g illustrates an alternative vortex generator embodiment, wherein the vortex body has a blade shape with parallel leading and trailing edges, a sloping upper edge, and sloping sides. Dimension A can be between 2 mm and 10 mm, or between 3 mm and 6 mm. Dimension z can be between 2 mm and 10 mm, or between 2 mm and 4 mm. Dimension W1 can be between 5 mm and 20 mm, or between 7 mm and 15 mm. Dimension λ can be between 10° and 30°, or between 15° and 25°.

[0252] In another embodiment, not shown, the turbulence generator 6a3 is a plurality of hemispherical protrusions with a radius of 1 to 2 mm and a center-to-center spacing of 3 to 5 mm.

[0253] Other embodiments of the turbulence generator 6a3 may consist of any combination of the turbulence generators described above.

[0254] Figure 9 h to Figure 9 j is a schematic diagram showing the windshield 6a' being pushed to the closed state by the corresponding magnet 32', and the half-size windshield 6a'1 being partially pulled open. For ease of comparison, Figure 9 g and Figure 9 The unmarked dashed lines in h depict the damper arm 32, magnet 32', wind deflector 6a', and half-size wind deflector 6a'1. Figure 9 The marked positions in m and 9n.

[0255] Figure 9 p is a schematic diagram showing the door diffuser 6a4 with an angle ζ deviating from the tangent of the rear sealing edge 6a5. The angle ζ is preferably between 10° and 45°, and most preferably between 25° and 35°. Figure 9 k to 9m are schematic diagrams showing the sawtooth 6a4' at the rear edge of the door diffuser 6a4. The combination of these two elements interrupts the vortex shedding from the rear edge of the door and reduces the exhaust velocity of the damper airflow 7 from the damper orifice 7a, thereby reducing airflow noise generated by the damper 6a', the half-size damper 6a'1, and the swirl vane 17 (not shown), and reducing pressure drop. The sawtooth profile 6a4' can be sawtooth-shaped (e.g., Figure 9 As shown in j), a sine wave (as shown in j) Figure 9 (as shown in k) or irregular shape (not shown), and can be defined to the transition to the perforated or porous trailing edge material 6a4”, such as Figure 9 As shown in m. For dimension A, the preferred trailing edge dimension is 10 mm to 30 mm, and the most preferred dimension is 20 mm to 25 mm. For dimension Wd, the preferred dimension is 1 mm to 5 mm, and the most preferred dimension is 2 mm to 3 mm.

[0256] In an alternative embodiment, the half-size windshield 6a'1 can be locked individually, or can be unlocked to open and close, as shown below. Figure 8h or Figures 8i to 8jAs shown. To achieve a substantially uniform 360° airflow pattern in a plane substantially parallel to diffuser surface 1, four half-size dampers 6a'1 should be unlocked for the minimum airflow range. For the illustrated configuration and given air static pressure in connection box 20, this is equivalent to reducing the maximum airflow by approximately 80% for the minimum airflow range compared to having all dampers 6a' and half-size dampers 6a'1 active, while maintaining a VAV reduction ratio of less than 15% for each airflow range. The maximum airflow reduction in this embodiment is greater than that achievable with the same total number of dampers and each damper being the same size.

[0257] Figure 10 a to Figure 10 c shows Figures 8a to 8e The diagram shows a side cross-sectional view of an alternative embodiment, in which a printed circuit board 10d, a pressure sensor 10g, and an electric actuator 10c are located in the sub-chamber 14b. A processor, an integrated indoor air temperature sensor 10e, a carbon dioxide (CO2) sensor, a volatile organic compound (VOC) sensor, a relative humidity (RH) sensor, and a Bluetooth antenna are not shown; these may optionally be included on the printed circuit board 10d. A passive infrared (PIR) sensor 10h may be inserted into the printed circuit board 10d and may be oriented to extend through the hub cap 8b to sense occupancy in room 18. The pressure sensor 10g is connected to the mounting plate 42 via a pressure tube 10g" to sense the static pressure in the main chamber 54 relative to the static pressure in the sub-chamber 14b, which is substantially equal to the static pressure in the connection box 20, while the static pressure in the sub-chamber 14b is substantially equal to the static pressure in room 18.

[0258] An electric actuator 10c is connected to a sun gear 38, which meshes with and drives planetary gears 38'1 and 38'2. Planetary gears 38'1 and 38'2, in turn, mesh with and rotate within a ring gear 38" which is fixedly attached to the housing 6b and centered on the diffuser centerline 0. The rotation axes of planetary gears 38'1 and 38'2 are attached to a cam sleeve 39, which rotates within the housing 6" around the diffuser centerline 0 and is axially constrained by a constraint groove 41' around a constraint pin 39' fixed to the housing 6" and cannot move parallel to the diffuser centerline 0. The constraint groove 41' is substantially located in a plane parallel to the diffuser surface 1.

[0259] like Figure 10 a and Figure 13As shown in Figure a, magnet 32' is attached to arm 32, arm 32 is attached to translation ring 31, and translation pin 39" is attached to translation ring 31 and extends into door cam groove 41" located in cam sleeve 39, so that when translation ring 31 is fully lowered, windshield 6a' (only when...) Figure 10 (Illustrated in a) When fully open, the intake pin 39”’ in the intake cam groove 41”’ located in the cam sleeve 39 is fully driven to the upper side, thereby fully opening the intake damper 29 to allow the main air 12’ to be discharged by the intake nozzle array 11’.

[0260] The intake pin 39” slides in the shroud groove 30” parallel to the diffuser centerline 0, thereby constraining the rotation of the translation ring 31 about the diffuser centerline 0. Features that similarly constrain the rotation of the intake damper 29 about the diffuser centerline 0 are not shown.

[0261] Figure 10 b shows that planetary gears 38'1 and 38'2 have been driven 180 degrees around the diffuser centerline 0 by the electric actuator 10c, thereby rotating the cam sleeve 39 180 degrees around the diffuser centerline 0. This causes the translation pin 39" to be fully driven upward by the door cam groove 41", and the intake pin 39"' to continue to be fully driven upward, thereby driving the translation ring 39 upward, fully closing the wind deflector 6a', while keeping the intake damper 29 fully open. The airflow 7 is completely cut off by the damper, while the main air 12' continues to flow into the intake nozzle array 11', as... Figure 8e and 8f As described in the airflow description.

[0262] Figure 10 c shows that the cam sleeve 39 has been further rotated 90° around the diffuser centerline O by planetary gears 38'1 and 38'2 (both out of view), such that the translation pin 39" continues to be held fully upward by the door cam groove 41" and the intake pin 39"' is fully driven downward by the intake groove 41"', thereby continuing to hold the translation ring 39 fully upward, thus keeping the damper 6a' fully closed, while simultaneously fully closing the intake damper 29. The switch connector 40' of the micro switch 40 is pressed down by the arm 40" of the intake damper 29, zeroing the actuator 10c to the fully closed position. All airflow is cut off, as Figure 8g As shown.

[0263] exist Figure 10In steps a through 10c, the main airflow 12' flows through the supply air temperature sensor 10f in the main chamber 54, which is separated from the secondary chamber 14b by the mounting plate 42, and is then discharged as the main airflow 12 into the intake channel 15 by the intake nozzle array 11' to introduce the secondary airflow 13 from the secondary chamber 14b into the upper part 52 of the intake channel 15. Then, these two airflows are discharged in a 360° pattern in a plane substantially parallel to the diffuser surface 1 by the proximal portion of the swirl blades 17 contained within the shroud 6”, as the discharged guide airflow 9”', thereby drawing supplementary airflow 14 from the room 18 into the secondary chamber 14b via the panel inlet 14a in the hub 8b. The supplementary airflow 14 passes through the printed circuit board 10d (and through the indoor air temperature sensor 10e, not shown) to provide accurate sensing of indoor air temperature, relative humidity, and carbon dioxide (CO2), and cools the printed circuit board 10d and prevents short-circuit leakage into the secondary chamber 14b.

[0264] exist Figure 10 In embodiments a through 10c, the damper arm 32 translates in a direction substantially parallel to the diffuser centerline O. In an alternative embodiment, the damper arm 32 translates with rotation relative to the diffuser centerline O. In another embodiment, the damper arm 32 translates parallel to and about the diffuser centerline O.

[0265] Figure 11 a and Figure 11 b are respectively Figures 8a to 8g and Figure 10 a to Figure 10 The exploded side cross-sectional view of embodiment c shows the removal or installation of the supply air temperature sensor 10f, pressure sensor 10g, printed circuit board 10d (which may include an indoor air temperature sensor 10e (not shown) and a VOC or CO2 sensor (not shown)), RH sensor (not shown), PIR sensor 10h, and hub cap 8b from the diffuser 1d of the electric actuator 10c. When installing the above components, Figure 11 The electric actuator shaft 10c' in a meshes with the worm gear 26, or Figure 11 In b, the sun gear 38 meshes with planet gears 38'1 and 38'2, and the mounting plate 42 seals the nozzle plate seal 42'.

[0266] Advantageously, the above and Figure 11 The removal or installation of the components shown in 11a and 11b does not require removing the diffuser 1d from the ceiling joists 2 or approaching the ceiling space above the ceiling joists 2. This helps to simplify rental maintenance and reconfiguration for rental changes, such as in cases where the printed circuit board 10d needs to be upgraded to include a CO2 or VOC sensor.

[0267] Figure 12 a is Figure 11 The isometric view of the embodiment shown in figure a shows the hub cap 8b removed from the hub 8a of the diffuser 1d and placed below the diffuser surface 1. A printed circuit board 10d is attached to the hub cap 8b. A pressure sensor 10g is attached to the printed circuit board 10d, as are optional PIR sensors 10h and sensors not visible in the view, such as an indoor air temperature sensor 10d, optional CO2, relative humidity (RH), and VOC sensors, and a Bluetooth antenna 10d1.

[0268] Also shown is a mounting plate 42 removed from the diffuser 1d, which is connected to the pressure sensor 10g via a pressure tube 10g”. An electric actuator 10c is fixedly attached to the underside of the mounting plate 42, with the actuator shaft 10c' extending through the mounting plate 42. A supply gas temperature sensor 10f, not visible in the view, also extends through the mounting plate 42.

[0269] The above embodiments provide the ability to access the diffuser from below without removing the diffuser from the ceiling joists 2 (not shown) to install, remove, or replace the printed circuit board 10d, all sensors (including 10e, 10f, 10g, 10h), Bluetooth antenna 10d1, and electric actuator 10c.

[0270] Figure 12 b is Figure 11 The isometric view of embodiment b shows the hub cap 8b removed from the hub 8a of diffuser 1d and placed below diffuser surface 1. Mounting plate 42, removed from diffuser 1d, is also shown. Electric actuator 10c is fixedly attached to the upper side of mounting plate 42, and sun gear 38 is attached to the electric actuator shaft (not shown). Supply air temperature sensor 10f extends through mounting plate 42. Pressure pipe fitting 10g”, suitable for connection to pressure pipe 10g' (not shown), also extends through mounting plate 42. Printed circuit board 10c is attached to the lower side of mounting plate 42. Pressure sensor 10g (not shown) may optionally be attached to printed circuit board 10d. Optional PIR sensor 10h, indoor air temperature sensor 10e, and Bluetooth antenna 10d1 are shown attached to printed circuit board 10d. Optional CO2, relative humidity (RH), and VOC sensors (all not shown) may also be attached to printed circuit board 10d.

[0271] The above embodiments provide the ability to access the diffuser from below without removing the diffuser from the ceiling joists 2 (not shown) for the purpose of installing, removing, or replacing the printed circuit board 10d, all sensors (including 10e, 10f, 10g, 10h), Bluetooth antenna 10d1, and electric actuator 10c.

[0272] Figure 13a is shown Figure 10 a to Figure 10 c and Figure 11 The isometric top cross-sectional view of the embodiment is schematically shown in b. For simplicity, the connecting box 20 is not shown. An electric actuator 10c attached to the upper side of the mounting plate 42 drives the sun gear 38, which in turn drives the planetary gears 38'1 and 38'2 to rotate within the ring gear 38", thereby rotating the cam sleeve 39 with the planetary gears 38'1 and 38'2 attached within the shroud 6". The intake pin 39"' extending into the intake cam groove 41"' is constrained (not visible in the view) to move only parallel to the diffuser centerline O. This intake pin 39"' moves the intake damper 29 up and down, thereby opening and closing the air passage to the nozzle array 11', as shown. Figure 10 a to Figure 10 As described in c. Similarly, the translation pin 39' (not visible in the view and constrained to move only parallel to the diffuser centerline O) extends into the cam slot 41', moving the cam sleeve 39 up and down, thereby opening and closing the damper 6a', as described in c. Figure 10 a to Figure 10 As shown in c.

[0273] Figure 13 b is shown in Figure 5. Figures 8a to 8h , Figure 9 c. Figure 9 d、 Figure 9 g、 Figure 9 j、 Figure 9 p and Figure 11 The isometric cross-sectional view of the embodiment schematically shown in Figure a. An electric actuator 10c, attached to the lower side of the mounting plate 42, rotates the worm gear 26 to vertically drive the worm nut 27, thereby opening and closing the intake damper 29, and vertically driving the translation ring 31, damper arm 32, and magnet 32', as shown. Figures 8a to 8g As shown. When magnet 32' moves upward, the windshield 6a' and half-size windshield 6a'1 are pushed to the closed state. When magnet 32' moves downward, the windshield 6a' and half-size windshield 6a'1, to which magnet 32' is magnetically attached, are magnetically attached and magnetically pulled open, as well as being attached and pulled open by gravity, and are also pushed open by the air pressure in the connecting box 20. Furthermore, when windshield 6a' and half-size windshield 6a'1 are fully open, the microswitch 40 is activated by the arm 40” attached to the intake damper 29 or the worm nut 27, thereby zeroing the electric actuator 10c to the fully open position y. The bottom edge of the windshield 6a' substantially abuts against the inlet cone 101, thereby reducing eddies at the edge of the door, thus reducing pressure drop and noise. The exhaust cone 100, abutting against the distal edge of the swirl vane 17, further reduces pressure drop and noise.

[0274] Figure 13 c is Figure 13The isometric top cross-sectional view of embodiment b (connecting box 20 is not shown for simplicity) only shows half-size windshields 6a'1 being pulled open by gravity and magnets 32', as each windshield 6a' is locked by its respective locking latch 34a, causing its respective magnets 32' to separate as the translation ring 31 moves downward.

[0275] Figure 13 a to Figure 13 The nozzle array 11' shown in Figure c has a minimum main airflow 12 requirement of 6 liters / second (achieved when the minimum static pressure in the connecting box 20 is 10 Pa) to adequately induce the secondary airflow 13 for accurate temperature sensing of the indoor air temperature via the indoor air temperature sensor 10d. The intake damper 29 can be adjusted by the stepper motor 10c based on the static pressure in the connecting box 20 measured by the pressure sensor 10g and the calculated position of the intake damper 29 (e.g., by calculating the rotational speed of the worm gear 26 via the stepper motor 10c) to maintain the main airflow 12 at a flow rate of 6 liters / second, making it independent of the static pressure in the connecting box 20. Therefore, the minimum permissible static operating pressure of the diffuser 1d is 10 Pa, and the minimum airflow (when the damper 6a is fully closed) is 6 liters / second, independent of the static pressure in the connecting box 20 (provided that the pressure is greater than or equal to 10 Pa). Therefore, 6 liters / second is the minimum permissible reduction value, regardless of the static pressure of the connection box 20 or the various maximum airflow configurations of the dampers 6a' and half-size dampers 6a'1, which in turn depend on the number of dampers that are active due to the unlocked latches 34a. Figure 8h and Figure 8i ).

[0276] When the air deflector 6a is partially throttled, the diffuser 1d provides a greater far-side exhaust velocity and a reduced near-side exhaust velocity in a plane parallel to the diffuser surface 1, thereby increasing the delivery distance of the diffuser airflow 9a. Thus, for various maximum airflow configurations of the air deflector 6a' and the half-size air deflector 6a'1, under the conditions that the static pressure in the connecting box 20 is about 30 Pa and the temperature difference between the supplied air and the indoor air is -15 K, when the airflow is reduced to 15% of the maximum airflow, a specific airflow of less than 0.4 L / s / m² (relative to the floor area of ​​room 18) can be achieved at more than 90% of the ADPI (Air Distribution Indicator).

[0277] When providing partial load heating, diffuser 1d reduces the vertical temperature gradient in room 18 because a greater distal exhaust velocity and a reduced proximal exhaust velocity are achieved when damper 6a is partially throttled, thereby extending the delivery distance of diffuser airflow 9a and increasing air turbulence in room 18. This improves comfort by reducing the risk of occupants of room 18 experiencing a "hot head / cold feet" sensation.

[0278] To ensure that the room sound pressure level does not exceed NC30 (based on a room absorption capacity of 10 dB) or the static pressure in the connection box 20 is 30 Pa, the maximum air flow rate of supply air 3 is approximately 230 liters / second for a neck size DN with a diameter of 355 mm and approximately 450 liters / second for a neck size DN with a diameter of 500 mm.

[0279] For a neck size DN with a diameter of 355 mm, the minimum face size G1' is approximately 495 mm; for a neck size DN with a diameter of 500 mm, the minimum face size G1' is approximately 595 mm. These sizes are suitable for minimum ceiling joist centerline sizes G1 of approximately 500 mm and approximately 600 mm, respectively. The wall thickness of the connecting box 20 can be up to 25 mm, which is suitable for achieving an R1 insulation rating.

[0280] For a neck size DN with a diameter of 355 mm, the interface 4' typically has a maximum effective diameter of approximately 300 mm, while for a neck size DN with a diameter of 500 mm, the maximum effective diameter is approximately 400 mm.

[0281] Based on the junction box 20 with a maximum wall thickness of 25 mm (suitable for achieving R1 insulation class), the minimum junction box height H3 is 200 mm. Typical junction box heights H3 range from 250 mm to 450 mm, depending on the maximum air flow rate of the air supply 3.

[0282] The corners and edges of the connecting box 20 can be in the form of facets 20', so as to facilitate the installation of the assembled diffuser unit, including the diffuser 1d and the connecting box 20, into the ceiling joists 2 from below without disassembling the ceiling joists 2.

[0283] Figures 14a to 14c It shows a side inlet interface ( Figure 14a and Figure 14b ) and top entry interface ( Figure 14c Examples of embodiments, and these embodiments having a damper rotation axis parallel to the centerline O ( Figure 14a ) and the damper rotation axis inclined relative to the diffuser centerline 0 ( Figure 14b and Figure 14c It also has a multi-cone diffuser (Fig. 17c), which includes a plurality of substantially truncated cone diffuser elements centered on the diffuser centerline O, and these diffuser elements have different base diameters.

[0284] Figure 14a and Figure 14bMultiple wind deflectors 6a' are shown, whose rotation axes 6a”' and 6a” are arranged substantially parallel and substantially inclined, respectively, and substantially coincide with the surfaces of the truncated cylinder and the truncated cone, and are centered on the diffuser central axis O.

[0285] The latter embodiment may be preferred for the following reasons:

[0286] A vertical damper rotation axis 6a”' may result in a confined turbulence chamber 120 relative to the sidewall of the connecting box 20, which may restrict the flow of damper airflow 7 toward the baffle 6a’. In contrast, an inclined damper rotation axis 6a” increases the average distance from the sidewall of the connecting box 20 to the baffle 6a’ (as shown in shaded area 110), thereby improving the airflow from the turbulence chamber 120 to the baffle 6a’, reducing pressure drop, and making the exhaust from the baffle 6a’ more uniform.

[0287] Air supply 3 (not shown) flows from side inlet port 4' (shown in hidden detail) to a baffle 6a' (not shown, as this component is located near the side wall of the connecting box 20, which is substantially opposite to side inlet port 4'). Figure 14b As the observer moves forward, the shaded area 110 created by the inclined damper rotation axis 6a” provides a path for the air supply 3 through the intermediate damper 6a' (shown), thereby reducing pressure drop and making the exhaust from the damper 6a' more uniform.

[0288] exist Figure 14c In the middle, the shaded area 110 formed by the inclined damper rotation axis 6a” provides an extended path for the air supply 3 to flow from the top inlet interface 4'1 into the turbulence chamber 120 and then onto the damper 6a', thereby reducing pressure drop and making the exhaust from the damper 6a' more uniform.

[0289] Compared to the substantially parallel damper rotation axis 6a”', the inclined damper rotation axis 6a”' positions the damper 6a’ in an orientation that partially directs the damper airflow 7 toward the multi-cone guide 7c (especially when the damper 6a’ is fully open), thereby reducing pressure drop and noise.

[0290] Compared to the substantially parallel damper rotation axis 6a”', the inclined damper rotation axis 6a”' causes the damper 6a’ to be in a partially downward orientation (assuming the diffuser centerline 0 is vertically oriented, which is the case when the diffuser surface 1 is horizontal), so gravity helps to pull the damper 6a’ onto the magnet 32’.

[0291] Compared to the substantially parallel damper rotation axis 6a”', the inclined damper rotation axis 6a”' positions the damper 6a’ in a partially open orientation in a direction parallel to the diffuser centerline 0, thereby facilitating the opening and closing of the damper 6a’ by a simple worm gear (26) mechanism with a DC stepper motor (10c) drive via the movement of the damper arm 32 in a direction parallel to the diffuser centerline 0.

[0292] In another embodiment, not shown, the rotation axis of the damper is arranged substantially radially around the diffuser centerline O in the diffuser neck DN1. Figure 14b Compared to this embodiment, based on a given minimum connection box height H3 ( Figure 13 b) The inclined damper rotation axis 6a” allows the damper 6a' to provide a larger opening area for the damper airflow 7, resulting in lower pressure drop and noise. The given minimum connection box height H3 is equal to 200 mm in some embodiments to allow the side inlet interface 4' to be attached to the connection box 20 and to allow the air supply 3 to enter the connection box 20 and diffuser neck DN1 from the side.

[0293] Potential advantageous features of the embodiments described herein

[0294] Air delivery systems incorporating the diffusers described herein can offer the potential for significant energy savings, increased VAV reduction, increased distribution during reduction, complete shutdown, lower supply air temperatures, and more efficient performance, as well as the potential for improved thermal comfort, enhanced indoor air quality, reduced capital costs, increased flexibility in responding to changes, and improved aesthetics.

[0295] HVAC systems that supply air into space via actuator-driven VAV cyclone diffusers according to embodiments of the present invention can be designed to operate within HVAC systems with variable-speed driven fans or incorporating devices such as duct pressure-controlled dampers, thereby potentially reducing airflow during periods of low heat load and thus saving fan energy. This is because the air supply in diffusers, as described in some embodiments, is essentially discharged within or parallel to the ceiling plane, and these diffusers can supply air at lower temperatures (as low as 7°C, compared to 10°C to 12°C in the prior art). Therefore, for the same cooling capacity, air can be supplied at a lower airflow rate (typically 30% less airflow) without creating cross drafts.

[0296] Furthermore, diffusers according to some embodiments can have a greater VAV operating range (typically 20% greater) because they can be reduced to much lower airflow rates compared to equivalent swirling diffusers of the prior art. This is equivalent to reducing the flow rate to less than 6 liters per second, or less than 15% of the diffuser's maximum airflow rate, regardless of pressure. Equivalent swirling diffusers of the prior art typically have a minimum pressure-dependent reduction ratio of 25%, which is equivalent to reducing the flow rate to a value greater than 25% when the pressure exceeds the design pressure (e.g., if the system pressure at the diffuser increases from the design static pressure of 30 Pa to 60 Pa, the flow rate can only be reduced to 35%). Lower minimum airflow rates reduce the risk of space overcooling or the need for reheating to prevent overcooling, thereby improving comfort and reducing energy costs.

[0297] Another potential advantage is that diffusers according to some embodiments can achieve a much larger airflow reduction under conditions where the supply air temperature difference with the room is -15K and the ADPI in the room exceeds 90%, and maintain a substantially constant delivery distance in a plane parallel to the diffuser surface, or, when reduced under the same conditions, can achieve a greater delivery distance than comparable swirling diffusers of the prior art, thereby potentially increasing the floor area that a single diffuser can serve. This can reduce the number of diffusers required, thus potentially saving on investment costs.

[0298] Furthermore, as described in some embodiments, the maximum airflow that the diffuser can discharge can be greater than the maximum airflow of comparable swirling diffusers in the prior art (more than 75% greater). This could potentially allow for the use of fewer diffusers (potentially 40% fewer diffusers) for diffusers fitted into ceiling joists of approximately 600 mm × 600 mm, or the selection of smaller diffuser face sizes, such as diffusers suitable for 500 mm × 500 mm ceiling joists and capable of achieving a maximum airflow of 230 L / s at an indoor SPL of NC30 (based on a room absorption capacity of 10 dB), thereby further reducing investment costs and improving aesthetics.

[0299] Other embodiments allow for the reconfiguration of the diffuser's airflow range, and this can be done in situ without removing the diffuser from the ceiling. This provides flexibility in responding to lease changes; for example, a diffuser previously serving a large space requiring high airflow can be reconfigured to serve a smaller space requiring low airflow. Importantly, this can be achieved without reducing the diffuser's downsizing ratio or minimum airflow. Existing diffusers do not include such features.

[0300] Diffuser embodiments may include using static pressure measurements within a connection box mapped to the damper location to determine the airflow rate. This allows for relatively accurate determination of the diffuser airflow rate even at very low flow rates, and also allows for the determination of the actual diffuser static pressure for each diffuser, potentially allowing system pressure to be controlled (e.g., via system fans) to at least relatively accurately maintain the minimum allowable static pressure (typically 10 Pa) for each diffuser, or to achieve the required static pressure for the diffuser with the highest demand. Furthermore, measuring the static pressure at each diffuser provides redundancy. If a pressure sensor fails, only the actual static pressure at that diffuser is lost (and can be estimated from other pressure sensors), potentially without affecting the operation of the entire system or causing system failure.

[0301] Some embodiments can incorporate an indoor air intake system to allow for integrated sensing of indoor air temperature, humidity (RH), and indoor air quality (CO2 or VOC), thereby eliminating the need for external wiring for remote sensors.

[0302] Embodiments of the diffuser may include an intake system that exhausts air in a 360° pattern in a plane parallel to the diffuser surface, thereby suppressing leakage when the damper is closed, preventing drafts caused by pouring, and preventing leakage or short-circuit flow of the supply air into the intake system from the diffuser. This improves the accuracy of the overall sensing of indoor air temperature, humidity, and indoor air quality (CO2 or VOC), and evenly distributes the exhaust main airflow and secondary airflow of the intake system into the regulated space.

[0303] Embodiments that also include intake dampers can allow each diffuser to close completely, for example, when the space it serves is not occupied (this occupancy can be sensed by an optional integrated PIR sensor), thereby potentially saving energy.

[0304] Furthermore, embodiments with an intake damper can allow adjustment of the intake damper position to deliver a constant airflow to the intake system, thereby providing a pressure-independent minimum airflow discharge from the diffuser equal to the minimum airflow required for the operation of the intake system.

[0305] According to some embodiments, diffusers can have a thinner profile than comparable diffusers in the prior art that deliver similar airflow rates, potentially reducing the ceiling height requirements for a given diffuser airflow rate. For a given ceiling height, this can allow each diffuser to achieve a larger airflow rate, potentially reducing the number of diffusers required, or it can allow for lower inter-floor heights in the building. This can result in significant investment cost savings.

[0306] In the embodiments, a shielding section can be used to change the exhaust direction. When viewed in a plan view, the exhaust direction can be changed from 360° to 270°, 180°, or 2×90° modes, which allows the diffuser to be placed close to a wall or other obstruction.

[0307] Embodiments of the present invention can provide the ability to keep the diffuser in place in the ceiling while accessing it through the diffuser hub to remove or replace any sensors, printed circuit boards, or electric actuators, thereby potentially contributing to improved ease of maintenance and reconfiguration of the diffuser for lease changes.

[0308] Diffuser embodiments may include noise suppression features such as sawtooth, turbulence diffusers, and trailing edge diffusers, enabling the diffuser to operate even at high supply static pressures. This makes these diffusers suitable for non-static pressure recovery duct design systems, such as constant velocity or isofriction duct designs. This simplifies new duct design and makes the diffusers of these embodiments suitable for retrofit applications that reuse existing duct systems.

[0309] In the appended claims and in the foregoing description, the word “comprising” or its grammatical variations are used in a encompassing sense, except where otherwise required in the context due to the language of expression or the necessary meaning, that is, indicating the presence of the stated features but not excluding the presence or addition of other features in various embodiments.

Claims

1. A diffuser unit for supplying gas to space, the diffuser unit comprising: A pressure chamber having an inlet for receiving a variable flow rate of air; At least one air deflector through which air is discharged into the space, the air deflector being arranged to disperse the discharged air in a plane substantially parallel to the exhaust surface of the diffuser unit, the air deflector forming an outlet to the pressure chamber; A damper compartment, located within a pressure chamber and connected to the at least one air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment further including a plurality of wind deflectors, each wind deflector being associated with at least one corresponding orifice and operable between an open position and a closed position; Furthermore, the damper compartment and the damper orifice are arranged such that air entering the damper compartment from the pressure chamber through the damper orifice forms a swirling flow before leaving the damper compartment through the at least one air guide.

2. The diffuser unit of claim 1, wherein, When the damper orifice is throttled, the damper orifice can be operated to achieve a higher far-side tangential velocity and a lower near-side tangential velocity of the air discharged from the air deflector.

3. The diffuser unit according to claim 1 or 2, comprising a perforated baffle associated with the air inlet of the pressure chamber.

4. The diffuser unit according to claim 1 or 2, wherein, The damper compartment is truncated conical in shape.

5. The diffuser unit according to claim 1 or 2, wherein, Each windshield can move between the open and closed positions.

6. The diffuser unit according to claim 1 or 2, wherein, One or more wind deflectors include blades that extend tangentially to the surface of the deflector compartment.

7. The diffuser unit according to claim 1 or 2, wherein, The damper compartment has multiple edges defining the orifice, and the damper compartment has blades formed at the edges.

8. The diffuser unit of claim 1 or 2, wherein, The windbreak is formed by an outer sleeve that engages with and slides relative to the windbreak compartment.

9. The diffuser unit of claim 1 or 2, wherein, One or more windbreaks are installed to pivot about an axis relative to the windbreak compartment.

10. The diffuser unit of claim 1 or 2, wherein, One or more windshields have a serrated trailing edge.

11. The diffuser unit according to claim 10, wherein, The sawtooth is one or more of the following: sawtooth shape, sine shape.

12. The diffuser unit according to claim 10, wherein, The one or more windshields are perforated at the rear edge.

13. The diffuser unit of claim 10, wherein, The one or more windshields are formed of a porous material at the rear edge.

14. The diffuser unit according to claim 1 or 2, wherein, One or more windshields have a trailing edge, and the profile of the trailing edge is different from the profile of a portion of the windshield excluding the trailing edge.

15. The diffuser unit according to claim 1 or 2, wherein, One or more wind deflectors have surfaces that are impacted by airflow, and these surfaces are formed with one or more protrusions to reduce noise generated by the air flowing over them.

16. The diffuser unit according to claim 15, wherein, The surface forms a trailing edge and / or a sealing edge.

17. The diffuser unit of claim 15, wherein, The protrusion is substantially planar.

18. The diffuser unit of claim 15, wherein, The protrusion is triangular.

19. The diffuser unit of claim 15, wherein, The protrusion is one or more of the following: serrated, rectangular, truncated triangular, or substantially sinusoidal.

20. The diffuser unit of claim 15, wherein, The protrusion is a vortex generator shaped as a twisted pyramid, blade, or hemisphere with a triangular base.

21. The diffuser unit of claim 1 or 2, wherein, The damper compartment includes an inlet surface for forming a seal with a corresponding damper, the inlet surface defining a circular inlet upstream of the sealing portion.

22. The diffuser unit of claim 1 or 2, wherein, One or more windshields include locks for locking the windshield relative to the position of the corresponding opening.

23. The diffuser unit according to claim 1 or 2 further includes one or more shielding sections for blocking a portion of the airflow through the unit.

24. The diffuser unit according to claim 1 or 2, wherein, The air vents are arranged symmetrically around the perimeter of the compartment.

25. The diffuser unit according to claim 1 or 2, comprising at least one actuator for opening and closing the windshield.

26. The diffuser unit of claim 25 further includes a sensor for measuring air temperature, the sensor being connected to the at least one actuator such that the damper can open or close in response to the measured air temperature.

27. The diffuser unit of claim 26 further includes an air supply sensor arranged to measure the air supply temperature and an indoor air sensor arranged to measure the air temperature of the space.

28. The diffuser unit according to claim 25, wherein, The at least one actuator includes one or more arms that engage with a corresponding windshield, wherein the actuator is arranged to translate the arm in a direction substantially parallel to the central axis of the compartment, thereby moving the windshield between an open position and a closed position.

29. The diffuser unit of claim 1 or 2, further comprising a core duct configured to define a core portion from the damper compartment.

30. The diffuser unit according to claim 29, wherein, The core conduit includes a shroud having an inlet and an outlet, through which air from the pressure chamber enters the shroud and through which it exits.

31. The diffuser unit according to claim 29, having a perforated cap, wherein, The core portion includes a partition that divides the core portion into an upper portion associated with a pressure chamber and a lower portion associated with a space into which air exhausted by the diffuser unit enters during use. The lower portion has a venturi wall. The partition forms one or more intake inlets. The core portion also has a second inlet located above the venturi wall of the lower portion. Airflow flowing through the intake inlet causes the drawn-in airflow to enter the shroud through perforations in the shroud via the second inlet, thereby forming a mixed airflow exiting the shroud through an outlet.

32. The diffuser unit according to claim 31, wherein, The intake inlet is configured to apply a vortex to the mixed airflow.

33. The diffuser unit of claim 31 further includes an intake damper operable between a closed position that restricts or prevents intake airflow and an open position that allows intake airflow.

34. The diffuser unit of claim 33 further includes an actuator for closing the windshield, then moving the intake damper to the closed position, and opening the windshield after moving the intake damper to the open position.

35. The diffuser unit according to claim 1 or 2, comprising one or more pressure sensors for measuring the static pressure of the supply gas relative to space.

36. A method for diffusing an airflow using a diffuser unit, the diffuser unit comprising: A pressure chamber with an air inlet; An air deflector through which air is discharged into a space, the air deflector comprising a plurality of exhaust elements arranged to disperse the discharged air in a plane substantially parallel to the exhaust surface of the diffuser unit, the air deflector forming an outlet to the pressure chamber; A damper compartment located within a pressure chamber and connected to an air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment further including at least one baffle associated with a corresponding orifice and operable between an open position and a closed position; The method includes: It receives a variable air supply flow through the air inlet into the pressure chamber; Open one or more dampers to allow airflow into the damper compartment; A vortex airflow is generated within the damper compartment; and Air is allowed to exit the diffuser unit and enter the space in a swirling manner through the air guide in a plane substantially parallel to the exhaust surface of the diffuser unit.

37. The method of claim 36, wherein: The windbreak door defines a windbreak door angle, which is related to the allowable airflow through the corresponding orifice. The vortex airflow within the damper compartment has a helical angle, and wherein, The airflow rate and helix angle of the vortex airflow in the compartment increase as the angle of the windshield increases.

38. The method of claim 36 or claim 37, further comprising maintaining the attachment between the airflow leaving the air deflector and the surface of the air deflector.

39. The method according to claim 36 or 37, further comprising closing the damper to obtain a higher far-side tangential velocity relative to the near-side tangential velocity of the vortex airflow in the damper compartment and a reduced airflow rate of the airflow leaving the air deflector; and, when the damper is closed, the delivery distance of the airflow leaving the air deflector is substantially constant in a plane parallel to the exhaust surface of the diffuser unit.

40. The method of claim 39, wherein, The static pressure in the pressure chamber remains substantially constant.

41. The method of claim 39, wherein, When the windshield is closed, the airflow leaves the diffuser unit in a swirling manner through the air deflector.

42. The method of claim 36 or 37, wherein, The unit includes more than one windshield, and the method includes locking one or more windshields.

43. The method of claim 36 or 37, wherein, The unit includes a blocking section, and the method includes using the blocking section to block a portion of the airflow through the unit.

44. The method of claim 36 or 37, comprising sensing the temperature of the supplied air and / or the temperature of the space, and operating the windshield in response to the determined temperature.

45. The method of claim 36 or 37, wherein, The unit includes an intake chamber with an intake inlet, and the method includes drawing air from the space into the intake chamber by intake caused by airflow originating from the pressure chamber through the intake inlet, to form a combined airflow that exits through a diffuser outlet.

46. The method of claim 36 or 37, wherein, The combined airflow exiting through the diffuser outlet is discharged in a substantially 360° pattern in a plane substantially parallel to the exhaust surface of the diffuser unit.

47. The method of claim 36 or 37, wherein, The combined airflow exiting through the diffuser outlet is ejected from the diffuser outlet in a direction substantially parallel to the plane defined by the surface of the diffuser outlet.

48. The method according to claim 36 or 37, wherein, The mixed airflow exiting through the diffuser outlet is used to suppress leakage from the windshield.

49. A method for determining the gas flow rate of a diffuser unit, the diffuser unit comprising: Pressure chamber, which has an air inlet for receiving a variable flow of air supply; At least one air deflector through which air is discharged into the space, the at least one air deflector comprising a plurality of exhaust elements arranged to disperse the discharged air, the air deflector forming an outlet to the pressure chamber; A damper compartment, located within a pressure chamber and connected to the at least one air deflector, such that the air deflector forms at least one face of the damper compartment, the damper compartment having a plurality of damper orifices forming an inlet to the damper compartment, the damper compartment further including at least one intake damper or baffle damper associated with a corresponding orifice and operable between an open position and a closed position; The method includes: Determine the static pressure in the pressure chamber; Determine the location of the intake damper or air deflector; and Calculate the air supply flow rate based on the determined static pressure and the position of the damper. The damper compartment and the damper orifice are arranged such that air entering the damper compartment from the pressure chamber through the damper orifice forms a swirling flow before leaving through the at least one air guide.

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