Carrier module for a fan and fan with a corresponding carrier module

Abstract

Carrier module for a fan comprising a motor and a fan wheel which is driven in rotation by the motor, in particular for a radial or mixed flow fan, for fastening the fan wheel between an upstream nozzle plate and a bottom plate which is placed spaced apart relative to the nozzle plate, wherein the motor is supported in the bottom plate or on the bottom plate against relative rotation together with the fan wheel and is held on the nozzle plate by means of a support which extends between the bottom plate and the nozzle plate, characterized in that the support is matched to the flow escaping from the fan wheel in a compact construction. The fan is equipped with a corresponding carrier module.

Description

Technical Field

[0001] The present invention relates to a support module for a fan comprising a motor and a fan impeller rotated by the motor, particularly for a radial or mixed-flow fan, the support module being used to secure the fan impeller between an upstream nozzle plate and a base plate spaced apart from the nozzle plate, wherein the motor and the fan impeller are supported together against relative rotation on or in the base plate and held on the nozzle plate by means of a bracket extending between the base plate and the nozzle plate.

[0002] The present invention also relates to a fan having a corresponding load-bearing module. Background Technology

[0003] Essentially, this relates to a support device for securing a motor and a fan impeller, wherein the motor and fan impeller are typically secured to a base plate of the support device. When the motor is mounted on the support device against relative rotation on its stator, the fan impeller rotates with the motor's rotor. The base plate assembly of the support device, containing the motor and fan impeller, is mechanically connected to, and in other words, held on, a nozzle plate, typically including an inlet nozzle. For this purpose, a bracket extending between the base plate and the nozzle plate is typically used. These relate to a broadly defined fastening mechanism that spacees the nozzle plate from the base plate and stabilizes the assembly containing the fan impeller between them. Due to the bracket measures, the aforementioned assembly should be understood individually as a structural unit.

[0004] Known in practice, the mounting systems for securing radial or mixed-flow fan impellers to nozzle plates present problems because the connected supports extend downstream of the air exhaust end and, due to their design, result in efficiency losses, aerodynamic performance degradation, and / or increased noise; at least, they do not increase static efficiency. Furthermore, known installations in practice typically require considerable space and are far from compact designs. Fans with known mounting systems exhibit significant, disruptive subharmonic noise, particularly at operating points with increased static pressure, because these mounting systems fail to stabilize the flow downstream of the impeller. Summary of the Invention

[0005] Therefore, the objective of this invention is to at least reduce the aforementioned disadvantages. Specifically, known load-bearing devices are optimized into load-bearing modules through the special design of their supports and possibly motor support plates or base plates, minimizing losses and noise increases, while maximizing efficiency and aerodynamic performance. In particular, when using special supports, the load-bearing function of the load-bearing module remains at least unchanged even without improvement, and the load-bearing module is compact in the radial direction.

[0006] Furthermore, a correspondingly optimized fan should be provided, which includes the load-bearing module according to the invention. In conjunction with the load-bearing module according to the invention, particularly when using a GR module with a so-called "planetary gear" structure, the fan should have a significantly higher static efficiency than the prior art. The load-bearing support of such a GR module is typically formed of a circular material. Compared to the prior art, the occurrence of subharmonic rotational noise is shifted to higher pressures or significantly reduced within the relevant operating range.

[0007] The aforementioned task is accomplished by the support module according to the invention. Thus, the support module, by its class, is characterized in that the support, in a compact structural manner, matches the flow escaping from the fan impeller.

[0008] In this respect, it should be noted that the term "support" should be understood in its broadest sense within the scope of the teachings, which are of paramount importance. Here, a stable gap maintainer is designed between the base plate supporting the motor and the fan impeller and the nozzle plate. The supports form a compact unit due to their rigidity / strength and their number and distribution around the fan impeller, and because they are matched to the flow escaping from the fan impeller, they at least reduce, and as far as possible eliminate, the disadvantages present in the prior art.

[0009] In principle, scaffolds can be flat, planar components, or configurable components, with different types of scaffolds combined together. It is also conceivable to replace one type of scaffold with another.

[0010] Specifically, the supports may have curvature and / or varying thickness in their cross-section. In particular, their shape and orientation are matched to the flow conditions after the air escapes radially from the fan impeller. This matching enables flow stabilization and improves efficiency, as well as reduces subharmonic noise, depending on the specific adjustments made.

[0011] In a favorable manner, the support is configurable, thereby achieving the aforementioned matching with the airflow. It is conceivable that the support could have a cross-sectional profile roughly the same as or similar to that of the fan impeller blades.

[0012] The support has an upstream edge and a downstream edge. More advantageously, the upstream edge of the support has a more rounded edge in cross-section, similar to that in the load-bearing wing, compared to the downstream edge, in order to ensure the aerodynamic stability of the support relative to the variable inflow angle.

[0013] In a more advantageous configuration, the support has a convexly arched suction side and a concavely arched pressure side. The profile support has different angles at its upstream edge compared to its downstream edge, due to their curvature, compared to the hypothetical radial direction. The leading and trailing edge angles are designed to result in high fan efficiency and low fan noise.

[0014] Of particular advantage is that the support is preferably arranged radially parallel to the impeller axis outside the air exhaust end of the downstream fan impeller. This minimizes the structural space required.

[0015] The number of supports can vary depending on the requirements. At least four supports should be installed, and it is possible to install six to ten supports depending on the required stability, depending on the structural dimensions and application of the wind turbine that carries the support module or includes the support module.

[0016] As described above, the support has a load-bearing function, holding the base plate, along with the motor and impeller, on the nozzle plate. Furthermore, depending on the specific design of the support discussed above, measures can be used to promote flow within the support.

[0017] Depending on the requirements, supports can be manufactured from different materials and using different methods accordingly. Supports can be manufactured into aluminum profiles or steel sheets through extrusion, or into plastic profiles through injection molding. It should be noted whether the support is the sole load-bearing component, or whether it is supported by other stable and therefore load-bearing members.

[0018] Attached to or replacing the support, lateral components can be located in or near the corner area of ​​the nozzle plate, extending between the nozzle plate and the base plate. Separate components connected to the nozzle plate and base plate can also be designed here. These lateral components are preferably arranged radially parallel to the impeller axis, outside the air exhaust end of the downstream fan impeller.

[0019] It should be emphasized that the lateral component mentioned above is a type of support, but other specific descriptions are used to supplement the above-described configured support, but may also replace it in certain cases.

[0020] The lateral components are advantageously arranged with a small gap between them and the corresponding supports, such that the leading edge of the lateral component is aligned with the trailing edge of the corresponding support with a small gap, so that the lateral component and the support form an aerodynamic unit with their leading and trailing edges.

[0021] In addition, the lateral components are advantageously arranged between the nozzle plate and the base plate, near the corner area and / or near the support, for example, directly adjacent to them.

[0022] The lateral components can be implemented as flat plastic injection molded parts or flat metal sheets, wherein stable embossing, ribs, etc. can be provided. In summary, it is advantageous to provide at least four such lateral components, wherein, depending on the size and purpose of the load-bearing module, six to ten lateral components can be provided individually or to compensate for the aforementioned support, for example, eight lateral components.

[0023] According to the above implementation scheme, the lateral components can have a load-bearing function and hold the base plate and motor together with the impeller on the nozzle plate. Furthermore, they should stabilize airflow, thereby improving efficiency and minimizing subharmonic noise.

[0024] It is also conceivable that the configured supports and relatively flat lateral components are connected to each other in pairs, preferably by means of a suitable connecting mechanism, thereby obtaining a specific arrangement and orientation of the paired supports and lateral components. Through this measure, the arrangement of the supports and lateral components can be specifically used as aerodynamic units and can promote flow.

[0025] Specifically, the supports and / or lateral components preferably have the smallest possible spacing between their upstream edges relative to the trailing edge of the impeller blades. This again facilitates a compact construction under favorable flow conditions.

[0026] For securing the brackets and lateral components, it is advantageous that they have fastening mechanisms at their axial ends for fixing them to the corresponding fastening areas on the base plate and the nozzle plate, wherein the connection can be established by screwing, riveting, bonding, or welding. Secure connections are crucial for achieving the desired stability or rigidity.

[0027] An advantage of the nozzle plate and base plate is that they have edge areas with folds, which reinforce or stabilize both plates. Importantly, the folds provide ideal fastening areas for the brackets and / or lateral components.

[0028] The base plate and, if necessary, the nozzle plate can be made of metal sheet or plastic, depending on the appropriate manufacturing method.

[0029] Furthermore, it is conceivable that the base plate can have a chamfered quadrilateral or polygonal profile, wherein the profile can also be rectangular in principle. A chamfered profile configuration is preferred when the fan, including the carrier module, is installed in an air passage or similar structure with an axial air continuation. Advantageously, the base plate of the carrier module extends radially by at least 10% over the entire periphery of the impeller or over the bottom disc of the impeller. Advantageously, the base plate of the carrier module has no openings or interruptions related to flow technology within its radial outer profile. These characteristics of the base plate of the carrier module ensure the stable flow effect of the carrier module, resulting in improved static efficiency and reduced subharmonic noise.

[0030] Finally, and importantly regarding the support module, the radial extension of the nozzle plate defines the radial structural space of the support module. This is due to the specific arrangement and design of the brackets and side components.

[0031] The fan according to the invention is equipped with the aforementioned type of support module, thereby reducing or even eliminating efficiency losses, aerodynamic performance losses, and noise increases due to the necessary support measures present in the prior art. The fan with the support module according to the invention is also very stable in a compact structural configuration. Attached Figure Description

[0032] There are now several feasible solutions for designing and improving the teachings of the present invention in an advantageous manner. The following description, taken in conjunction with the accompanying drawings, illustrates a preferred embodiment of a wind turbine according to the invention, having a carrier module also according to the invention. In conjunction with the description of the preferred embodiments of the invention in conjunction with the accompanying drawings, general preferred designs and improvements of the teachings are also described.

[0033] Figure 1 An embodiment of a wind turbine with a load-bearing module according to the present invention is shown in a perspective view from upstream.

[0034] Figure 2 The view is shown from the downstream cross-section and in an axial top view according to Figure 1 A wind turbine with a load-bearing module.

[0035] Figure 3 A perspective view taken from the side and shown as a cross-section on a plane passing through the axis. Figure 1 and Figure 2 An embodiment of a wind turbine with a load-bearing module.

[0036] Figure 4 A perspective view of another embodiment of a wind turbine with a load-bearing module according to the present invention is shown from an upstream perspective, wherein the load-bearing module does not have lateral plates.

[0037] Figure 5 An axial top view of the cross-section seen from upstream shows the data based on... Figure 4 A wind turbine with a load-bearing module.

[0038] Figure 6 The diagram is shown in an axial top view and in a cross-section viewed from downstream. Figure 4 and 5 A wind turbine with a load-bearing module.

[0039] Figure 6a It shows Figure 6 Detailed views are provided, in which schematic angular parameters are additionally identified.

[0040] Figure 7 An embodiment of a wind turbine with a load-bearing module according to the invention is shown in a perspective view from upstream. The load-bearing module has four profile supports.

[0041] Figure 8 The diagram illustrates the direction of static pressure increase at constant speed for a fan with a standard suspension and a fan with a load-bearing module according to the invention.

[0042] Figure 9 The schematic diagram illustrates the trends of static efficiency at constant speed for a wind turbine with a standard suspension and a wind turbine with a load-bearing module according to the invention.

[0043] Figure 10 The diagram illustrates the trend of the suction side acoustic power level at constant speed for a fan with a standard suspension and a fan with a load-bearing module according to the invention.

[0044] Figure 11 The diagram illustrates the acoustic pressure spectrum of the suction side of a fan with a standard suspension and a fan with a load-bearing module according to the invention at constant speed and the same volumetric flow rate.

[0045] Figure 12 The mounting inside the air passage is shown in an axial top view and a cross-section viewed from upstream. Figures 4 to 6 A wind turbine with a load-bearing module. Detailed Implementation

[0046] Figure 1 An embodiment of a fan according to the invention, having a support module 1, is shown in a perspective view from upstream. The fan impeller 3 can be seen internally, advantageously in a radial or diagonal configuration. The inlet nozzle 2, mounted on the nozzle plate 5, can also be seen upstream. In addition to the nozzle plate 5, the support module 1 includes, in particular, a base plate 6 and eight lateral supports 8 radially (downstream) from the air outlet end of the fan impeller 3. These supports are referred to hereinafter as profile supports 8 due to their design. The fan impeller 3 mainly consists of a bottom disc 9, a top disc 19, and blades 18 extending between them.

[0047] According to Figure 1In the embodiments, there are lateral components 7 implemented as lateral plates, which have a load-bearing function, i.e., they are the load-bearing connection between the nozzle plate 5 and the base plate 6. Four lateral plates 7 are advantageous whenever lateral plates are present or required. If load-bearing lateral plates 7 are present, the profile support 8 can advantageously be molded from plastic. The profile support 8 and the lateral plates 7 cover a portion of the downstream surface, thereby stabilizing the flow. The static efficiency of the fan, particularly in the high-pressure characteristic curve range, is improved. The lateral components 7, advantageously made of sheet metal, are flat in the embodiments, meaning they consist essentially of a single, continuous flat area. This is advantageous for the simple and cost-effective manufacture of the load-bearing module 1 and its lateral components 7.

[0048] Fastening measures 23 and 24 are provided for connecting the lateral component 7 to the nozzle plate 5 or the base plate 6. Furthermore, fastening measures 25 and 26 are provided for connecting the profile support 8 to the nozzle plate 5 or the base plate 6. This connection can advantageously be established, particularly by screwing, riveting, and welding. The nozzle plate 5, made of sheet metal, has a folded edge region 22 on its outer edge, which stabilizes the nozzle plate 5 and is integrated into part of the fastening measures 23 and 25. The base plate 6, also made of sheet metal, has a folded edge region 27 on its outer edge, which stabilizes the base plate 6 and is integrated into part of the fastening measures 24 and 26. In other embodiments, the base plate 27 may be formed of plastic.

[0049] The metal sheet 6 on the bottom plate side extends radially to the profile bracket 8 and the side component 7.

[0050] Figure 2 The view is shown from the downstream cross-section and in an axial top view according to Figure 1 The fan has a support module 1. The substantially flat, support-type lateral components 7 have an upstream edge 12 and a downstream edge 13. In cross-section, the profile support 8 is not flat, but has a cross-sectional profile approximating that of the support blades. This means they have curvature and non-constant thickness, and their shape and orientation are optimally matched to the flow pattern of air exiting radially from the impeller 3. The blades 18 of the impeller 3, also configured similarly, have an upstream edge 10 and a downstream edge 11. The profile support 8 has an upstream edge 14 and a downstream edge 15. The upstream edges 14 are more rounded in cross-section, similar to the support blades, to ensure aerodynamic stability of the profile support 8 relative to different inflow angles. They have a convex arched suction side face 42 and a concave arched pressure side 43. Compared to the hypothetical radial direction, the profile supports have different angles at their upstream edges 14 compared to their downstream edges 15, which manifests in cross-section as their curvature.

[0051] The leading and trailing edge angles are designed to ensure high fan efficiency and low noise generation. The leading edge 12 of the flat lateral member 7 is not rounded because the lateral member 7 is a flat profile. However, the leading edge 12 of the flat lateral member 7 is precisely aligned with the trailing edge 15 of the corresponding profile support 8 with a very small gap, so that the lateral member 7 and the corresponding profile support 8 function optimally, like the aerodynamic action unit 14 with leading edge 14 and trailing edge 13.

[0052] In this embodiment, the aerodynamically shaped profile support 8 extends parallel to the fan axis, which extends perpendicular to the plane of the drawing. Since the profile support 8 in this embodiment is non-load-bearing and advantageously manufactured by plastic injection molding, other orientations are also conceivable, such as not parallel to the axis or having a variable cross-section.

[0053] The nozzle plate 5 shows the upper-level system, such as the nozzle plate 5 on the ventilation equipment or air passage or the fastening measures 17 of the fan.

[0054] The support module 1 does not extend beyond the nozzle plate 5 in the line of sight parallel to the axis (as shown here), thus appearing particularly compact in the radial direction and therefore requiring very little installation space. The support module 1 has an approximately rectangular, advantageously approximately square, cross-section with a width w (37) (in the case of a rectangular cross-section, w is a larger width). W (37) is advantageously no greater than 1.25 times the average diameter of the trailing edge 11 of the impeller blade 18 relative to the fan axis.

[0055] Figure 3 A perspective view taken from the side and shown as a cross-section on a plane passing through the axis. Figure 1 and Figure 2An embodiment of a fan with a support module is described. During fan operation, air is drawn into the impeller 3 from the right through the inlet nozzle 2 and radially outward due to rotation. It then continues to flow out of the support module 1 through the profile support 8 and the side plates 7. The impeller 3, having blades 18 extending between the bottom disc 9 and the top disc 19, is driven by a motor 4, schematically shown. The motor 4 is connected to the impeller 3 on the rotor side and fixedly mounted on the base plate 6 on the stator side. On the base plate 6, the motor 4 is fixedly mounted in a central region 31, which in particular has a recess into which the motor 4 is inserted. Possible solutions are provided for centering and securing the motor 4. The inlet nozzle 2 is fastened to the nozzle plate 5 or, advantageously, formed directly into the nozzle plate 5, for example, by a deep drawing process. The nozzle plate 5 has a folded area 22, which stabilizes the nozzle plate 5 and can be integrated into fastening measures 23 and 25. The folded region 22 also has a function that is beneficial to flow conditions and therefore to aerodynamic performance and efficiency. Therefore, the flow in this region within the support module 2 is stabilized by the folded region 22, which has a positive effect on the secondary flow through the radial gap 44 between the inlet nozzle 2 and the top disc 19. For the description of the profile support 8 and the lateral plate 7, reference is made primarily to... Figure 1 and 2 The description.

[0056] exist Figure 4 Another embodiment of a wind turbine having the load-bearing module 1 according to the invention is shown in a perspective view from upstream. (Compared to...) Figures 1 to 3 Compared to the previous embodiment, the support module 1 has no lateral plates. This means that the profile support 8 bears the load and holds the base plate 6, motor, and impeller 3 on the nozzle plate 5. To meet the relevant strength requirements, the profile support 8 is advantageously made of metal. Designing the profile support 8 as an extruded aluminum profile has proven particularly advantageous and effective. However, they can also be made of high-strength plastic, cast aluminum, or steel sheet. In particular, extruded aluminum profiles can be attached to the nozzle plate 5 or base plate 6 by directly screwing suitable screws into a metal sheet (not shown) passing through the nozzle plate 5 or base plate 6. The impeller 3, having a bottom disc 9, a top disc 19, and blades 18, is advantageously injection molded from plastic as a single unit. Other types of impellers are also conceivable, for example, welded from steel or aluminum.

[0057] In other embodiments, it is also conceivable that the lateral profile support 8 is made of a metal sheet. For this purpose, the metal sheet can be bent or folded in a suitable manner to achieve a similar effect to... Figure 2 The cross-section shows the profile shape or at least the bending centerline of the profile shape.

[0058] exist Figure 5 The diagram shows the axial top view and the cross-section viewed from upstream, based on... Figure 4The fan 1 has a load-bearing module. The connection between the rotor of the motor 4, the impeller 3, and the chassis 9 of the motor 4 can be seen at the center. The aerodynamic advantages of the profile support 8's cross-section design are clearly visible, similar to the airfoil cross-section design, as well as the reference. Figure 1 As described. The air flowing radially from the impeller 3 flows with low loss on the profile supports 8, first through their leading edge region 14 and further through the thin trailing edge region 15 from the support module 1. The profile supports 8, by their design, ensure this by interacting with the nozzle plate 5 and the base plate 6 to stabilize the flow within the support module 1 and thus improve efficiency and / or reduce noise, at least subharmonic noise (frequency range below the blade repetition frequency, see also). Figure 11 (Description). The outer contour of the base plate 6 in the axial top view resembles a square with a chamfer of 45 degrees; it may also have an approximately rectangular contour. A contour with a chamfer of 45 degrees is particularly advantageous if the fan with the bearing module 1 according to the invention is installed in an air duct or the like with an axial air continuation; see also [reference needed]. Figure 12 .

[0059] According to Figure 5 In the axial top view, the base plate 6 of the support module 1, viewed in the radial direction, always extends beyond the outer contour of the base plate 9 of the impeller 3 throughout its entire periphery. Advantageously, it extends radially continuously beyond the base plate 9 of the impeller 3 by at least 10% throughout its entire periphery; more advantageously, it extends radially continuously beyond the entire impeller 3, including the blades 18 and the top disc 19, by at least 10% throughout its entire periphery. The base plate 6 has no obvious, flow-technically significant openings or interruptions within its outer contour (this excludes drill holes, cable breaks, gaps due to manufacturing tolerances, etc.).

[0060] Figure 6 The diagram is shown in an axial top view and in a cross-section viewed from downstream. Figure 4 and 5 The fan has a carrier module 1. The blades 18 of the impeller 3 and their trailing edges 11 have a relatively small gap with the upstream edge 14 of the profile support 8, which is beneficial to the radial compactness of the carrier module 1 and the fan, and also to achieving high efficiency. The blades 18 of the impeller 3 extend radially inward with their leading edges 10 beyond the inner edge of the top disc 19. The profile support 8 does not extend radially beyond the radial outer contour of the nozzle plate 5 with its trailing edges 15, that is, the radial extension of the nozzle plate 5 defines the radial structural space of the compact carrier module 1 and therefore the fan. Advantageously, a fastening mechanism 17 for fastening the fan to the upper system is provided on the nozzle plate 5.

[0061] Figure 6a yes Figure 6Detailed views, wherein the angles are additionally schematically indicated on the profile support 8, namely the leading edge angle α46 at the leading edge 14 and the trailing edge angle β47 at the trailing edge 15. Perpendicular to... Figure 6 In the cross-section on the plane of the axis shown in the diagram, the leading edge angle α46 is the angle between the local peripheral direction U48 and the profile centerline at the upstream edge 14 of the profile support 8. Perpendicular to the plane of the axis shown in the diagram... Figure 6 In the cross-section on the plane of the axis shown in the diagram, the trailing edge angle β47 is the angle between the local peripheral direction U48 and the profile centerline at the downstream edge 15 of the profile support 8. To achieve optimal flow conditions and therefore high efficiency and low noise, the leading edge angle α46 and the trailing edge angle β47 are optimally matched to the flow exiting the impeller 3. Advantageously, α46 is not equal to β47; more advantageously, α46 is greater than β47, particularly by at least 10°. α46 and β47 are advantageously less than 45°.

[0062] Figure 7 A further embodiment of a wind turbine having a load-bearing module 1 according to the invention is shown in a perspective view from upstream. (Compared to...) Figures 1 to 3 The implementation differs in that, in this embodiment, the support module 1 has only four profile supports 8, instead of independent profile supports without associated side plates. All four profile supports 8 are associated with side plates 7. The side plates 7 and their associated profile supports 8 are connected to each other by connecting elements 16 to ensure better alignment between the side plates 7 and the profile supports 8.

[0063] In other embodiments, it is conceivable that the lateral profile support 8 is made of a metal sheet. For this purpose, the metal sheet may be arched or possibly bent in a suitable manner to achieve a similar effect to... Figure 6a In the cross-section, the profile shape or at least the bending centerline of the profile shape is realized. In such an embodiment, the leading edge angle α46 and the trailing edge angle β47 will also be as previously determined... Figure 6 Choose as described in order to achieve high efficiency and low noise emission.

[0064] Figure 8A schematic diagram illustrates the direction of static pressure increase at constant speed for a fan with a standard suspension and a fan with a carrier module according to the invention. This diagram illustrates the operation of the carrier module according to the invention by comparing the characteristic curve of a fan with the carrier module according to the invention with that of a fan otherwise identical (particularly having the same impeller and the same motor, but with the housing replaced by a standard motor suspension, for example, a fluidically essentially neutral circular metal support). Curve 20 shows the direction of static pressure increase dependent on the delivery volumetric flow rate for a fan with a standard motor suspension (reference fan). The fan with the carrier module according to the invention has characteristic curve 21 for static pressure increase dependent on the delivery volumetric flow rate. By using the carrier module according to the invention, a significantly greater static pressure increase can be achieved, particularly in the region of medium to low delivery volumetric flow rates, compared to a fan without a housing, and depending on the embodiment, a maximum net gain of 2% to 15% of the static pressure increase can be achieved at the same speed and the same delivery volumetric flow rate. Dashed line 28 shows an exemplary volumetric flow rate, which also serves as the basis for the following description in the figures. At this delivery volume flow rate, for example by using the carrier module according to the invention, the static pressure increases from about 480 Pa to about 520 Pa, an increase of about 8%.

[0065] Figure 9 The diagram schematically illustrates the trends of static efficiency at constant speed for a fan with a standard suspension and a fan with a load-bearing module according to the invention. The static efficiencies achieved at constant speed are plotted as a function of volumetric flow rate. The dashed efficiency characteristic curve 29 was obtained by measuring a rearward-arched radial fan with a standard suspension (reference fan), while the solid efficiency characteristic curve 30 was obtained by measuring the same fan but using the load-bearing module according to the invention instead of the standard suspension. It is readily apparent, particularly in regions with medium to low volumetric flow rates, that is, with increasing static pressure (see...). Figure 9 The efficiency is significantly improved by the carrier module according to the invention. The improvement is relatively small with increases in high volumetric flow rate or low static pressure. In the region of medium to low volumetric flow rate or high static pressure increases, the improvement is several percentage points, particularly at the point of maximum increase, where it is at least 2 percentage points or at least 3%. Dashed line 28 shows... Figure 8 The exemplary volumetric flow rate is used as a basis. At this volumetric flow rate, by using the load-bearing module according to the invention instead of the standard suspension, the static efficiency is increased from about 74.5% to about 77.5%, a relative improvement of 3 percentage points or about 4%.

[0066] Figure 10The diagram illustrates the trends of the suction-side acoustic power levels of a fan with a standard suspension and a fan with a load-bearing module according to the invention at the same and constant rotational speed. The dashed curve 32 represents the trend of the suction-side acoustic power of the reference fan as a function of air volumetric flow rate, while the solid curve 33 represents the suction-side acoustic power of a fan that is otherwise identical but uses a load-bearing module according to the invention instead of a standard suspension. Over a large range of the characteristic curves, the acoustic power values ​​of the two fans are approximately the same, but slightly higher for the fan with the load-bearing module according to the invention. This is primarily due to the interaction between the impeller and the lateral components and / or profile supports, which is relatively close to the air exhaust end from the impeller or even closer to the trailing edge of the impeller blades, thereby achieving the high radial compactness of the fan with the load-bearing module according to the invention.

[0067] In addition, the constant air volume flow rate 28 is plotted as a dashed line. For comparison with... Figure 8 neutralization Figure 9 For the same air volume flow rate, Figure 11 The sound pressure spectrum is shown for comparison. It should be mentioned again at this point that... Figures 8-11 All the curves shown correspond to the same and constant speed, wherein at least the impeller and the motor with the same structure are always used.

[0068] Figure 11 The diagram shows a wind turbine with a standard suspension and a wind turbine with a load-bearing module according to the invention at constant speed and at... Figures 8-10 The diagram shows the acoustic pressure spectrum of the suction side at the same volumetric flow rate of 28. The dashed curve 39 shows the reference fan at a delivery volumetric flow rate of 28 ( Figures 8-10 The sound pressure spectrum at ) is shown, while the solid curve 40 shows the fan with the bearing module according to the invention at a conveying volumetric flow rate of 28 ( Figures 8-10The sound pressure spectrum is shown at a frequency resolution of 3125 Hz. However, the same effect can be qualitatively observed at other frequency resolutions. The three frequencies 34 plotted are the first, second, and third harmonics of the blade repetition frequency of the impeller of the wind turbine. They are compared to one, two, or three times the product of the impeller's rotational frequency (in revolutions per second) and the number of blades. The sound at the first harmonic of the blade repetition frequency is also called a rotational sound. Compared to the overall trend of the curves, the sound pressure increases significantly in these frequency ranges, not only in the case of the reference wind turbine (curve 39) but also in the case of the wind turbine with the support module according to the invention (curve 40), particularly in the case of the wind turbine with the support module according to the invention, where the sound pressure at the first blade repetition frequency is higher. This is particularly due to the interaction between the impeller blades and the lateral plates and / or profile supports. However, for the mode of operation of the support module according to the invention, the decisive factor is the super-high sound pressure curve in the form of a super-high region 41. The sound corresponding to this is called the subharmonic sound. In rearward-arching fans, this noise typically occurs at approximately 60% to 90% of the first blade repetition frequency, particularly at operating points with relatively high static pressure increases. It can be seen that, in the case of the illustrated volumetric flow rate, the subharmonic noise, which typically depends on the volumetric flow rate, is significantly reduced in fans with the carrier module according to the invention, by approximately 7 to 8 dB in the illustrated example, and generally by 1 to 15 dB depending on the volumetric flow rate and frequency resolution. There is also a slight frequency shift in the subharmonic noise, approximately 5% to 20% lower than the first blade repetition frequency. This reduction and frequency shift in the subharmonic noise at operating points with medium to low volumetric flow rates and relatively high static pressure increases is caused by the flow stabilization induced by the carrier module according to the invention. This is a very typical feature of the carrier module according to the invention. Depending on the embodiment, the remaining noise, such as the noise at the harmonic of the blade repetition frequency 34 or the broadband noise, may be higher or lower in fans with the carrier module according to the invention compared to the reference fan. Only the reduction in subharmonic noise is important for the described mode of operation in fans with housings. However, typically, the sound at the first harmonic of the blade repetition frequency is increased in a wind turbine having a load-bearing module according to the invention compared to a reference wind turbine. In a highly advantageous embodiment, this sound can be reduced by active noise cancellation, i.e., by introducing anti-phase sound to cancel the sound. This is technically simple because the blade repetition frequency can be easily determined when the wind turbine's rotational speed is known during operation.

[0069] Figure 12 The mounting in the air passage 35 is shown in an axial top view and in a cross-section viewed from upstream. Figures 4 to 6The fan has a support module 1. Inside, a fan impeller 3 with blades 18 and a bottom disc 9 can be seen, and eight profile supports 8 can be seen radially outward. The support module 1 has at least approximately 90° rotational symmetry with respect to the fan axis.

[0070] The carrier module 1 has a width w (37) in the shown cross-section or axial top view. It is determined by the side length of the smallest circumscribed square of the carrier module 1 in the cross-section in a plane perpendicular to the axis or in the axial top view. The width w (37) of the carrier module 1 is advantageously 1.15 to 1.3 times the average diameter D of the trailing edge 11 of the blade 18 of the impeller 3, which demonstrates the radial compactness of the carrier module 1 relative to the impeller 3. If the width w is variable for different cross-sections, the maximum width w must be used for evaluation over the entire axial height of the carrier module 1, without considering the nozzle plate.

[0071] The air passage 35 has four side walls 36. According to... Figure 12 The cross section has a width s (38). If the air passage has a roughly rectangular cross section with different side lengths s1 and s2, then s can either be determined as the smaller of s1 and s2, or it can be determined according to the formula s·s = s1·s2. If the plurality of fans with housings 1 are installed in parallel in the air passage, then only the imaginary area of ​​the air passage 35 associated with each fan is considered for each fan, as if the partition wall is always centrally inserted between adjacent fans parallel to the side wall 36 of the air passage 35. The width s (38) of the air passage 35 associated with the fan is advantageously in the range of 1.2 to 1.8 times the width w (37) of the subordinate carrier module 1 or in the range of 1.5 to 2.3 times the average diameter D of the trailing edge 11 of the blade 18 of the fan impeller 3.

[0072] If the ratio s / w of the width s(38) of the air passage 35 associated with the fan to the width w(37) of the associated support module 1 is less than 1.4, it is advantageous to have a chamfer 45 on the support module 1 so that the air flowing out in the axial direction has more flow surface between the base plate 6 and the air passage wall 36.

[0073] To avoid repetition, reference is made to the Summary of the Invention section of the specification regarding the carrier module according to the invention and a more advantageous design of the fan including the carrier module according to the invention.

[0074] Finally, it should be clearly stated that the above-described embodiments of the carrier module and the wind turbine according to the present invention are only for explaining the claimed teachings and are not intended to limit them to these embodiments.

[0075] List of reference numerals

[0076] 1. Bearing Module

[0077] 2. Inlet nozzle

[0078] 3. Fan impeller

[0079] 4 motors

[0080] 5 Nozzle Plate

[0081] 6. Base plate of the load-bearing module

[0082] 7. Lateral plates of lateral components and load-bearing modules

[0083] 8 Lateral profile brackets

[0084] 9. Bottom disc of impeller 3

[0085] 10. Upstream edge, leading edge of blade 18

[0086] 11 Downstream edge, trailing edge of blade 18

[0087] 12. Upstream edge of lateral plate 7

[0088] 13 Downstream edge of lateral plate 7

[0089] 14. Upstream edge of lateral profile bracket 8

[0090] 15. Downstream edge of lateral profile bracket 8

[0091] 16 Connecting elements for lateral plates 7 and lateral profile supports 8

[0092] 17. Fastening measures, fastening mechanisms, nozzle plate - upper system

[0093] 18. Blades of fan impeller 3

[0094] 19 Top plate component of the fan impeller

[0095] 20 Exemplary characteristic curves of static pressure with standard suspension

[0096] 21 has an exemplary characteristic curve of static pressure of the load-bearing module according to the present invention.

[0097] 22. Folded edge area of ​​nozzle plate 5

[0098] 23. Fastening measures for lateral plate 7 – Nozzle plate 5

[0099] 24. Fastening measures for lateral plates 7 – base plate 6 of load-bearing module 1

[0100] 25. Fastening measures between the lateral profile bracket 8 and the nozzle plate 5

[0101] 26. Fastening measures between the lateral profile bracket 8 and the base plate 6

[0102] 27. Folded edge area of ​​base plate 6

[0103] 28 Exemplary Operating Points (Volume Flow)

[0104] 29 Exemplary characteristic curves of static efficiency with standard suspension

[0105] 30 has an exemplary characteristic curve of the static efficiency of the carrier module according to the present invention.

[0106] 31 base plate 6 central area

[0107] 32. Exemplary characteristic curves of suction side sound power with standard suspension.

[0108] 33 has an exemplary characteristic curve of the suction side acoustic power of the carrier module according to the present invention.

[0109] 34. Harmonics of rotor blade frequency

[0110] 35 Air passage

[0111] 36 air passage 35 side wall

[0112] 37 The width w of the bearing module 1

[0113] 38 air passages with a width of 35 s

[0114] 39 Sound pressure spectrum of a standard suspension under exemplary volume flow 28

[0115] 40 has the sound pressure spectrum of the carrier module according to the invention under an exemplary volume flow 28.

[0116] Acoustic enhancement region of the 41st harmonic

[0117] 42. Profile support on the suction side 8

[0118] 43. Profile support on the pressure side 8

[0119] 44. Radial clearance between inlet nozzle 2 and top plate 19

[0120] 45 base plate 6 chamfer

[0121] 46 profile bracket 8 leading edge angle α

[0122] The trailing edge angle β of profile bracket 8 of type 47

[0123] 48 Circumferential direction relative to the axis

Claims

1. A carrier module for a fan comprising a motor and a fan impeller rotatably driven by the motor, wherein, The motor is supported against relative rotation together with the fan wheel on or in a relatively flat base plate and is kept spaced from the upstream nozzle plate by means of struts extending between the base plate and the upstream nozzle plate, wherein the struts connect the base plate with the nozzle plate independently of other connections between base plate and nozzle plate, the base plate having a profile of a quadrangular or polygonal shape with chamfered edges, characterized in that the struts are profiled, the struts having an upstream edge and a downstream edge, wherein a front edge angle between an upstream profile center line at the upstream edge of each strut and a first partial circumferential direction of the fan wheel is greater than a rear edge angle between a downstream profile center line at the downstream edge of each strut and a second partial circumferential direction of the fan wheel, wherein the struts match the flow escaping from the fan wheel such that the interaction of the fan wheel blades with the struts results in a reduction of the subharmonic sound corresponding to the high area in the sound pressure curve compared to the corresponding sound pressure curve of the same fan without the struts.

2. The load carrying module of claim 1, wherein, The struts have a curvature in cross section and the struts are matched in shape and orientation to the flow situation after the air has radially escaped from the fan wheel.

3. Load carrying module according to claim 1 or 2, characterized in that The struts have a varying thickness in cross section.

4. The load carrying module of claim 1 or 2, wherein, The cross sectional profile of the struts has a curvature and a non-constant thickness between the upstream edge and the downstream edge, and the upstream edge is rounded and the struts taper towards the downstream edge.

5. The load carrying module of claim 1 or 2, wherein, The struts have a more rounded edge in cross section upstream.

6. The load carrying module of claim 1 or 2, wherein, The struts have a convexly curved suction side face and a concavely curved pressure side face.

7. The load carrying module of claim 1 or 2, wherein, The struts are arranged radially beyond the air escape end of the fan wheel downstream parallel to the impeller axis.

8. The load carrying module of claim 1 or 2, wherein, 6 to 10 struts are provided.

9. The load carrying module of claim 1 or 2, wherein, The struts also have a load bearing function and hold the base plate and the motor together with the fan wheel on the nozzle plate.

10. The load carrying module of claim 1 or 2, wherein, The struts are manufactured in an extrusion process as aluminum profiles or steel sheet or in an injection molding process as plastic profiles.

11. The load carrying module of claim 1 or 2, wherein, Lateral parts are provided in or near the corner regions of the nozzle plate, the lateral parts extending between the nozzle plate and the base plate, wherein the lateral parts are arranged radially beyond the air escape end of the fan wheel downstream parallel to the impeller axis.

12. The load carrying module of claim 11, wherein, The lateral parts are arranged with little spacing to the corresponding struts such that the front edge of the lateral parts is aligned with little spacing to the rear edge of the corresponding struts, whereby lateral parts and struts form units for the aerodynamic action with their front and rear edges.

13. The load carrying module of claim 11, wherein, The lateral parts are arranged near the corner regions and / or near the struts between the nozzle plate and the base plate.

14. The load carrying module of claim 11, wherein, The lateral parts are embodied as flat plastic injection molded parts or flat metal sheets.

15. The load carrying module of claim 11, wherein, At least 4 lateral parts are provided.

16. The load carrying module of claim 11, wherein, The lateral parts have a load bearing function and hold the base plate and the motor together with the fan wheel on the nozzle plate.

17. The load carrying module of claim 16, wherein, Struts and lateral parts belonging to each other are connected to each other in pairs by means of a connection mechanism to define a specific arrangement and orientation to each other.

18. The load carrying module of claim 17, wherein, The brackets and side parts have fastening means on their end portions for fixing on corresponding fastening areas of the base plate and on the nozzle plate, wherein the connection is established by screwing, riveting, gluing or welding.

19. The load carrying module of claim 18, wherein, The fastening measures on the nozzle plate and on the base plate are assigned to respective flanges, which reinforce or stabilize the nozzle plate and the base plate.

20. The load carrying module of claim 1 or 2, wherein, The base plate and the nozzle plate are made of sheet metal or of plastic.

21. The load carrying module of claim 1 or 2, wherein, The radial extension of the nozzle plate defines a radial structural space for the bearing module.

22. The load carrying module of claim 1 or 2, wherein, In the case of a comparison of the narrow-band sound pressure spectrum on the suction side of a fan with a bearing module and of an otherwise identical fan in which the bearing module is replaced by a motor suspension which influences the flow conditions as little as possible, the maximum overtone sound pressure in the frequency range between 70% and 90% of the first blade repetition frequency is reduced by at least 3 dB in the sound pressure spectrum corresponding to the fan with the bearing module at a constant rotational speed in the region of a higher pressure increase of the delivery volume flow.

23. The load carrying module of claim 1 or 2, wherein, The front edge angle of the bracket is at least 10° greater than the rear edge angle, and both the front edge angle and the rear edge angle are less than 45°.

24. Fan with a motor and a fan wheel which is driven in rotation by the motor, the fan having a bearing module according to any one of claims 1 to 23.

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