A centrifugal pump co-rotating guide vane device

Abstract

The application discloses a centrifugal pump co-rotating guide vane device, belonging to the technical field of fluid machinery, which is characterized by adding a differential gear train, a first clutch, a second clutch, a motor shaft, a pump shaft and a controller on the basis of a pump body, an impeller and a guide vane; the differential gear train comprises a planet carrier, a first gear ring, a second gear ring and a plurality of planetary gear and planetary gear shaft assemblies; the two clutches are connected with corresponding wheel hubs respectively; the motor shaft drives the pump shaft through the planet carrier and drives the impeller to rotate; the controller switches the engagement / separation of the two clutches to make the guide vane switch between the two states of "fixing" and "co-rotating at different speeds" in real time. The guide vane is fixed in the design working condition to maintain high efficiency; the guide vane and the impeller co-rotate at different speeds in the non-design working condition to significantly reduce impact loss, inhibit vortex and secondary flow, thereby widening the high-efficiency area and reducing vibration and noise. The application has compact structure and simple control, and can realize wide-working-condition high-efficiency stable operation of the centrifugal pump without changing the pump inlet condition.

Description

Technical Field

[0001] This invention relates to the field of fluid machinery technology, and in particular to a centrifugal pump guide vane device that rotates in the same direction. The planetary speed change mechanism in the device is the core component that enables the guide vane to rotate in the same direction as the impeller or stop as needed. Background Technology

[0002] Centrifugal pumps, as a common fluid transport device, are widely used in various fields such as industry, agriculture, and municipal engineering. One of their core components is the guide vane. The main function of the guide vane is to efficiently convert the high-speed kinetic energy imparted to the fluid by the impeller into pressure energy, and guide the fluid at the impeller outlet to flow smoothly in the designed direction through a specially designed diffuser channel. This process can significantly reduce hydraulic losses such as swirling and eddy currents, thereby effectively reducing pump vibration and noise, and improving pump operating efficiency and stability.

[0003] However, in practical applications, centrifugal pumps often face a variety of complex operating conditions, especially under off-design conditions, such as when the flow rate varies significantly. In these cases, the performance of traditional centrifugal pumps deteriorates considerably. This is because the flow characteristics of the fluid under off-design conditions differ significantly from those under design conditions, leading to reduced energy conversion efficiency, increased hydraulic losses, and consequently affecting the overall performance of the pump. Furthermore, the guide vanes of traditional centrifugal pumps are typically fixed and cannot be dynamically adjusted according to changes in flow rate, further limiting the pump's adaptability and performance under off-design conditions.

[0004] To address this issue, existing technologies have attempted several improvements, such as optimizing guide vane geometry and flow channel design to enhance pump performance. However, these improvements primarily focus on fixed operating conditions, offering limited performance enhancements under non-design conditions. Therefore, further improving centrifugal pump performance under non-design conditions, enabling it to maintain relatively good performance across a wider flow range, has become a pressing technical challenge in this field. Summary of the Invention

[0005] The purpose of this invention is to provide a centrifugal pump guide vane device that rotates in the same direction. By introducing a planetary speed change mechanism, the guide vane and impeller can rotate or stop in the same direction, thereby dynamically adjusting the motion state of the guide vane according to different flow conditions. This improves the performance of the centrifugal pump under non-design conditions, effectively reduces hydraulic losses, reduces vibration and noise, and expands the operating range of the centrifugal pump.

[0006] To achieve the above objectives, the present invention provides the following solution: a centrifugal pump co-rotating guide vane device, comprising a pump body, an impeller, and guide vanes, further comprising: a differential gear train, the differential gear train comprising a planetary carrier, a first gear ring, a second gear ring, and multiple sets of planetary gears and planetary gear shaft assemblies; a first clutch and a second clutch, the first clutch being connected to a first hub, and the second clutch being connected to a second hub; a motor shaft and a pump shaft, the motor shaft serving as a power input shaft, and the pump shaft being connected to the impeller; a controller for controlling the engagement and disengagement of the first clutch and the second clutch; wherein, the differential gear train achieves co-rotation of the guide vanes and the impeller or fixation of the guide vanes by controlling the working states of the first clutch and the second clutch.

[0007] Furthermore, the first gear ring is fixedly connected to the first wheel hub, and the second gear ring is fixedly connected to the second wheel hub.

[0008] Furthermore, the planetary gears and planetary gear shafts are connected by a flat key to achieve rotation at the same angular velocity.

[0009] Furthermore, the planetary carrier is connected to the motor shaft and pump shaft via a flat key and a bushing to achieve rotation at the same speed.

[0010] Furthermore, both the first clutch and the second clutch are electromagnetic gear clutches.

[0011] Furthermore, the guide vane is connected to the first hub bolt via a connecting flange to achieve power transmission.

[0012] Furthermore, the centrifugal pump's co-rotating guide vane device also includes multiple sealing components and sealing rings to achieve dual sealing on the flow channel side and the lubrication side.

[0013] Furthermore, by controlling the working states of the first clutch and the second clutch, the guide vane is fixed under the design conditions, and the guide vane and the impeller rotate in the same direction but at different speeds under non-design conditions.

[0014] Furthermore, in the first operating condition, the motor shaft serves as the input shaft, the first clutch is engaged, and the second clutch is disengaged. At this time, the guide vane is fixed, the impeller rotates, and the second hub idles. In the second operating condition, the motor shaft serves as the input shaft, the first clutch is disengaged, and the second clutch is engaged. At this time, the guide vane and the impeller rotate in the same direction but at different speeds.

[0015] Furthermore, the planetary gear has 23 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; the first gear ring has 160 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; the planetary gear shaft has 27 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; the second gear ring has 151 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; and the clearance coefficient for all of them is 0.25.

[0016] Compared with the prior art, the present invention discloses at least the following beneficial effects:

[0017] Under designed operating conditions, the guide vanes remain fixed to ensure efficient energy conversion. Under non-designed operating conditions, the guide vanes and impeller rotate in the same direction but at different speeds, effectively improving fluid flow characteristics, reducing hydraulic losses, and enhancing pump operating efficiency and stability. This device has a compact structure, is easy to control, requires no changes to the input method, significantly expands the efficient operating range of centrifugal pumps, reduces vibration and noise, and is suitable for various complex operating conditions. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the co-rotating guide vane device of a centrifugal pump according to an embodiment of the present invention;

[0020] Figure 2 This is a schematic diagram of the transmission path of the guide vane under fixed working conditions in an embodiment of the present invention;

[0021] Figure 3 This is a schematic diagram of the transmission path of the guide vane of the present invention under the condition of unidirectional rotation.

[0022] In the diagram: 1. Pump body; 2. Impeller; 3. Guide vane; 4. First clutch; 5. Second clutch; 6. Steel plate; 7. Friction plate; 8. Upper housing; 9. Middle housing; 10. Lower housing; 11. Cavity; 12. Cover plate; 13. Connecting flange; 14. First hub; 15. Second hub; 16. First gear ring; 17. Second gear ring; 18. Planetary gear; 19. Planetary gear shaft; 20. Planetary carrier; 21. Bearing cover one; 22. Bearing cover two; 23. Bearing cover three; 24. Bearing cover four; 25. Pump shaft; 26. Motor shaft; 27. Sealing component one; 28. Sealing component two. Detailed Implementation

[0023] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0024] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0025] Reference Figures 1 to 3 As shown, this embodiment provides a centrifugal pump guide vane 3 rotating in the same direction device, implemented by a differential gear train. The device includes three sets of planetary gears 18 and planetary gear shaft assemblies, one planetary carrier 20 assembly, two sets of hub and gear ring assemblies, a motor shaft 26 and pump shaft 25, a connecting flange 13, an impeller 2 and guide vane 3, with a total of eight central rotating components. Through a differential gear train, both fixed and co-rotating operating modes of the centrifugal pump guide vane 3 are achieved, improving the centrifugal pump's operating performance under non-design conditions and expanding the pump's high-efficiency operating range.

[0026] The centrifugal pump co-rotating guide vane 3 device of this embodiment includes a pump body 1, impeller 2, guide vane 3, first clutch 4, second clutch 5, steel plate 6, friction plate 7, upper housing 8, middle housing 9, lower housing 10, cavity 11, cover plate 12, connecting flange 13, first hub 14, second hub 15, first gear ring 16, second gear ring 17, planetary gear 18, planetary gear shaft 19, planetary carrier 20, bearing cover one 21, bearing cover two 22, bearing cover three 23, bearing cover four 24, pump shaft 25, motor shaft 26, sealing component one 27, sealing component two 28, bushing, sealing ring, deep groove ball bearing, tapered roller bearing, flat key, etc. Except for standard parts such as clutches, bearings, bolts, sealing components, and sealing rings, the rest are all forged stainless steel structures. The device switches the on / off state of the first and second clutches 5 through a controller, so that the steel plate 6 and friction plate 7 are engaged or disengaged; when engaged, the clutch and hub are connected as one unit, and the corresponding hub is braked. The first clutch 4 is connected to the first hub 14 via steel plate 6 / friction plate 7, and the second clutch 5 is connected to the second hub 15 via steel plate 6 / friction plate 7. The first gear ring 16 is bolted to the first hub 14, and the second gear ring 17 is bolted to the second hub 15. The internal teeth of the first gear ring 16 mesh with the planetary gear 18, and the internal teeth of the second gear ring 17 mesh with the planetary gear shaft 19. The planetary gear 18 and the planetary gear shaft 19 are connected by a flat key to form a single rotating body. These three sets of components are supported on the planetary carrier 20 by deep groove ball bearings. The planetary carrier 20 is connected to the motor shaft 26 and the pump shaft 25 by a flat key and a bushing, and all three rotate at the same speed. The other end of the planetary carrier 20 is positioned on the upper housing 8 by a deep groove ball bearing and supported on the second hub 15 by a tapered roller bearing. The motor shaft 26 is provided with tapered roller bearings relative to the second hub 15, and the pump shaft 25 is provided with tapered roller bearings relative to the first hub 14, and are axially fixed by bearing caps 23 and bushings, respectively. Impeller 2 is bolted, keyed, and mounted on pump shaft 25, rotating synchronously with it. Guide vane 3 is placed between the outer ring of impeller 2 and pump body 1, and is bolted to first hub 14 via connecting flange 13, thus rotating at the same speed as first hub 14. Deep groove ball bearings are installed between connecting flange 13 and pump shaft 25, and between lower housing 10 and connecting flange 13, respectively, and are equipped with bearing cover 1 21, bearing cover 22, and sealing rings. Deep groove ball bearings are also installed between cover plate 12 and motor shaft 26, and are pressed and sealed by bearing cover 4 24. Sealing component 1 27 is sandwiched between impeller 2 and guide vane 3, and sealing component 2 28 is sandwiched between guide vane 3 and pump body 1, achieving double sealing on the flow channel side and lubrication side. Upper housing 8, middle housing 9, and lower housing 10 are bolted to first clutch 4 and second clutch 5 in sequence to form a stationary housing. Cavity 11 connects lower housing 10 and pump body 1 into a whole with bolts, and gaskets are added to the joint surface to maintain sealing.

[0027] In the above embodiments, both the first clutch 4 and the second clutch 5 are electromagnetic gear clutches, which are bolted to the upper, middle, and lower housings 10, respectively. The housing is a fixed structural component, and the locking and disengagement of the two clutches are controlled by a controller to achieve the engagement and disengagement of the steel plate 6 and the friction plate 7. When the steel plate 6 and the friction plate 7 are engaged, they can be connected to the wheel hub to achieve component braking. For example, when the first clutch 4 is locked, the first wheel hub 14 and the first gear ring 16 are braked, and the first gear ring 16 stops rotating.

[0028] In the above embodiment, the first gear ring 16 and the second gear ring 17 are internal gear ring structures, machined by internal grinding, and connected to the first hub 14 and the second hub 15 respectively by internal hexagonal bolts to achieve motion transmission. The outer sides of the first hub 14 and the second hub 15 are toothed and combined with the steel plate 6 to rotate together.

[0029] In the above embodiment, the planetary carrier 20 assembly consists of a planetary carrier 20 body and its left and right cover plates 12. The left and right cover plates 12 are mounted on the planetary carrier 20 body by hexagon socket head cap screws and are provided with an axial positioning structure for fixing the deep groove ball bearings and planetary gear shaft assemblies. The planetary gears 18 and planetary gear shafts 19 are connected by a flat key to achieve rotation at the same angular velocity. Each set of planetary gear shaft assemblies is fixed to the planetary carrier 20 assembly by three deep groove ball bearings, for a total of three sets, which cooperate with the first gear ring 16 and the second gear ring 17 to form the core structure of the differential gear train.

[0030] In the above embodiment, planetary gear 18 has 23 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; first gear ring 16 has 160 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; planetary gear shaft 19 has 27 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; second gear ring 17 has 151 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; and the clearance coefficient for all of them is 0.25.

[0031] In the above embodiment, the differential gear train is entirely grease-lubricated, using general-purpose lithium-based grease. Bearing caps and sealing rings are used in conjunction at the connecting flange 13, cavity 11, and cover plate 12 to achieve overall sealing.

[0032] In the above embodiment, the motor shaft 26 is the input shaft, which is connected to the planetary carrier 20 assembly via a bushing and a key to achieve power transmission. A tapered roller bearing is installed between the motor shaft 26 and the second hub 15, and axial positioning is achieved through the journal and bearing cover 23; a deep groove ball bearing is installed between the motor shaft 26 and the cover plate 12, and axial positioning is achieved through the journal and bearing cover 24.

[0033] In the above embodiment, the pump shaft 25 is connected to the planetary carrier 20 assembly via a bushing and a key. Power is input from the motor shaft 26 and drives the pump shaft 25 to rotate via the planetary carrier 20 assembly. A deep groove ball bearing is installed between the pump shaft 25 and the connecting flange 13, and axial positioning is achieved through the journal and bearing cover 21. A tapered roller bearing is installed between the pump shaft 25 and the first hub 14, and axial positioning is achieved through the positioning structure of the first hub 14 and the bushing.

[0034] In the above embodiment, the connecting flange 13 is connected to the first hub 14 by hexagon socket bolts to achieve motion transmission. A deep groove ball bearing is installed between the connecting flange 13 and the pump shaft 25; a deep groove ball bearing is also installed between the connecting flange 13 and the upper housing 8, and axial positioning is achieved by the bearing cap and retaining ring.

[0035] In the above embodiment, the upper housing 8, the first clutch 4, the middle housing 9, the second clutch 5, and the lower housing 10 are connected by bolts to form a fixed structural component, which constitutes the housing component of the differential gear train transmission device. Sealing gaskets are provided between each component to achieve housing sealing.

[0036] In the above embodiment, the impeller 2 is fixed to the pump shaft 25 by bolts, a flat key, and a bushing, and power is transmitted from the pump shaft 25 to the impeller 2. A sealing component 27 is installed between the impeller 2 and the guide vane 3; the guide vane 3 is fixed to the connecting flange 13 by hexagonal bolts, and power is transmitted from the first hub 14 to the guide vane 3 via the connecting flange 13, so that the guide vane 3 and the impeller 2 rotate in the same direction. A sealing component 27 is installed between the guide vane 3 and the impeller 2, and a sealing component 28 is installed between the guide vane 3 and the pump body 1 to achieve sealing of the pump body 1.

[0037] In the above embodiment, the pump body 1 is a fixed structural component; the cavity 11 is installed between the pump body 1 and the lower housing 10 by bolts, connecting the pump body 1 and the speed change structure. A sealing gasket is provided between the cavity 11 and the pump body 1 and the lower housing 10 to prevent water leakage and grease leakage from the pump body 1.

[0038] In the first operating mode of the above embodiment: the motor shaft 26 serves as the input shaft, the first clutch 4 is engaged, and the second clutch 5 is disengaged. In this mode, the first clutch 4 brakes the first hub 14, fixing the first hub 14, connecting flange 13, and guide vane 3. The impeller 2, pump shaft 25, and planetary carrier 20 rotate with the motor shaft 26, while the second hub 15 idles. This operating mode is suitable for the pump's design operating conditions. The transmission ratio under this first operating condition satisfies the following relationship:

[0039]

[0040] In the second operating mode of the above embodiment: the motor shaft 26 serves as the input shaft, the first clutch 4 is not engaged, and the second clutch 5 is engaged. In this mode, the second clutch 5 brakes the second hub 15, causing the impeller 2, pump shaft 25, and planetary carrier 20 to rotate with the motor shaft 26. The first hub 14 receives power through the differential gear train and rotates at a speed lower than that of the motor shaft 26, driving the guide vane 3 to rotate via the connecting flange 13, thus achieving the same-direction, different-speed rotation of the impeller 2 and the guide vane 3. This operating mode is suitable for non-designed operating conditions of the pump. The transmission ratio in this second operating condition satisfies the following relationship:

[0041]

[0042] By controlling the clutch, this differential gear train can achieve two working modes, expanding the high-efficiency operating range of the centrifugal pump while ensuring a compact structure and reliable strength.

[0043] The embodiments of the present invention have at least the following beneficial effects compared to the prior art:

[0044] I. Intelligent switching of the working state of guide vane 3 is realized: Through the differential gear train structure combined with the coordinated control of the first clutch 4 and the second clutch 5, the guide vane 3 is able to switch flexibly and reliably between the two working modes of "fixed" and "rotating in the same direction", so as to dynamically adjust the motion state of guide vane 3 according to the actual working conditions.

[0045] Second, it significantly improves performance under non-design conditions: Under non-design conditions (such as large flow rate changes), by controlling the clutch to make the guide vane 3 and impeller 2 rotate in the same direction but at different speeds, the flow characteristics of the fluid are effectively improved and hydraulic losses (such as swirling and eddy currents) are reduced, thereby improving the operating efficiency, stability and reliability of the centrifugal pump.

[0046] Third, it expands the high-efficiency operating range of centrifugal pumps: This device enables centrifugal pumps to maintain high efficiency over a wide flow range, broadens their high-efficiency zone, adapts to various complex working conditions, reduces energy consumption, and improves economy.

[0047] IV. This device has a compact structure and high reliability: It adopts a differential gear train structure, which has a high degree of integration, small size and light weight. At the same time, through reasonable bearing arrangement, sealing design and lubrication method, the overall structure's strength, sealing performance and long service life are ensured.

[0048] V. Simple control, no need to change the input method: The working mode can be switched by simply controlling the on and off of the two clutches. There is no need to change the input speed or direction of the motor. The system has a fast response, is easy to operate, and is easy to automate.

[0049] VI. This device reduces vibration and noise: By optimizing the motion relationship between the guide vane 3 and the impeller 2, the interference between dynamic and static phenomena is reduced, effectively reducing the vibration and noise of the pump body 1, and improving the operational stability and environmental friendliness of the equipment.

[0050] In the description of this invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0051] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Various modifications and improvements made by those skilled in the art to the technical solutions of the present invention without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. A centrifugal pump co-rotating guide vane device, comprising a pump body (1), an impeller (2), guide vanes (3), an upper casing (8), a middle casing (9), and a lower casing (10), characterized in that, Also includes: The differential gear train includes a planet carrier (20), a first gear ring (16), a second gear ring (17), and multiple sets of planet gears (18) and planet gear shaft assemblies; A first clutch (4) and a second clutch (5), wherein the first clutch (4) is connected to the first hub (14) and the second clutch (5) is connected to the second hub (15); The motor shaft (26) and pump shaft (25) are provided, wherein the motor shaft (26) serves as the power input shaft and the pump shaft (25) is connected to the impeller (2); A controller is used to control the engagement and disengagement of the first clutch (4) and the second clutch (5); The first gear ring (16) is fixedly connected to the first hub (14), and the second gear ring (17) is fixedly connected to the second hub (15); the planetary carrier (20) is connected to the motor shaft (26) and the pump shaft (25) through a flat key and a bushing; the guide vane (3) is bolted to the first hub (14) through a connecting flange (13); the upper housing (8), the first clutch (4), the middle housing (9), the second clutch (5), and the lower housing (10) are bolted together. The differential gear train controls the working state of the first clutch (4) and the second clutch (5) to achieve the rotation of the guide vane (3) and the impeller (2) in the same direction or the fixation of the guide vane (3).

2. The centrifugal pump co-rotating guide vane device according to claim 1, characterized in that, The planetary gear (18) and the planetary gear shaft (19) are connected by a flat key to achieve rotation at the same angular velocity.

3. The centrifugal pump co-rotating guide vane device according to claim 1, characterized in that, Both the first clutch (4) and the second clutch (5) are electromagnetic gear clutches.

4. The centrifugal pump co-rotating guide vane device according to claim 1, characterized in that, It also includes multiple sealing components and sealing rings to achieve dual sealing on the flow channel side and the lubrication side.

5. The centrifugal pump co-rotating guide vane device according to claim 1, characterized in that, By controlling the working states of the first clutch (4) and the second clutch (5), the guide vane (3) is fixed under the design working conditions, and the guide vane (3) and the impeller (2) rotate in the same direction but at different speeds under non-design working conditions.

6. The centrifugal pump co-rotating guide vane device according to claim 5, characterized in that, In the first working condition, the motor shaft (26) serves as the input shaft, the first clutch (4) is engaged, and the second clutch (5) is disengaged. At this time, the guide vane (3) is fixed, the impeller (2) rotates, and the second hub (15) idles. In the second working condition, the motor shaft (26) serves as the input shaft, the first clutch (4) is disengaged, and the second clutch (5) is engaged. At this time, the guide vane (3) and the impeller (2) rotate in the same direction but at different speeds.

7. The centrifugal pump co-rotating guide vane device according to claim 1 or 6, characterized in that, The planetary gear (18) has 23 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; the first gear ring (16) has 160 teeth, a module of 4, is right-handed, and has a helix angle β of 9.8°; the planetary gear shaft (19) has 27 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; the second gear ring (17) has 151 teeth, a module of 4.5, is right-handed, and has a helix angle β of 14.6°; the clearance coefficient of all of them is 0.25.

Images