Homodromous rotating guide vane device of centrifugal pump

Abstract

The invention discloses a synclastic rotating guide vane device of a centrifugal pump, which belongs to the technical field of fluid machinery and is additionally provided with 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 multiple sets of planet gear and planet gear shaft assemblies. The two clutches are respectively connected with the corresponding hubs; the motor shaft drives the pump shaft through the planet carrier and drives the impeller to rotate; the controller enables the guide vane to be instantly switched between a fixed state and a same-direction and different-speed rotation state by switching connection / separation of the two clutches. Guide vanes are fixed under design conditions, and high efficiency is kept; under the non-design working condition, the guide vane and the impeller rotate in the same direction in a differential mode, impact loss is remarkably reduced, vortexes and secondary flow are restrained, and therefore the efficient area is widened, and vibration and noise are reduced. The structure is compact, control is easy, and wide-working-condition efficient and stable operation of the centrifugal pump can be achieved on the premise that the pump inlet condition is not changed.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of fluid machinery, in particular to a centrifugal pump co-rotating guide vane device, and a planetary speed change mechanism in the device is a core component for realizing co-rotation or stop of the guide vane with the impeller. BACKGROUND

[0002] As a common fluid conveying device, centrifugal pumps are widely used in various fields such as industry, agriculture, and municipal administration. One of the core components of a centrifugal pump 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 to guide the fluid at the outlet of the impeller to flow smoothly in the designed direction through a specially designed diffuser flow channel. This process can significantly reduce hydraulic losses such as rotational flow and vortex, thereby effectively reducing the vibration and noise of the pump and improving the operating efficiency and stability of the pump.

[0003] However, in actual applications, centrifugal pumps often face various complex working conditions, especially under non-design conditions such as large changes in flow rate. The performance of traditional centrifugal pumps will decrease significantly under non-design conditions. This is because the flow characteristics of the fluid under non-design conditions differ greatly from those under design conditions, resulting in reduced energy conversion efficiency, increased hydraulic loss, and thus affecting the overall performance of the pump. In addition, the guide vane of a traditional centrifugal pump is usually of a fixed structure and cannot be dynamically adjusted according to changes in flow rate, which further limits the adaptability and performance of the pump under non-design conditions.

[0004] In order to solve this problem, some improvement measures have been tried in the prior art, such as optimizing the geometric shape and flow channel design of the guide vane to improve the performance of the pump. However, these improvement measures mainly focus on fixed conditions and have limited effect on performance improvement under non-design conditions. Therefore, how to further improve the performance of a centrifugal pump under non-design conditions so that it can maintain relatively good performance within a wider flow range has become a technical problem to be solved in the field. SUMMARY

[0005] The purpose of the present application is to provide a centrifugal pump co-rotating guide vane device. By introducing a planetary speed change mechanism, co-rotation or stop of the guide vane with the impeller is realized, so as to dynamically adjust the motion state of the guide vane according to different flow conditions, thereby improving the performance of the centrifugal pump under non-design conditions, effectively reducing hydraulic loss, reducing vibration and noise, and expanding the operating range of the centrifugal pump.

[0006] To achieve the above object, the application provides the following scheme: a centrifugal pump same-direction rotating guide vane device, comprising a pump body, an impeller and a guide vane, further comprising: a differential gear train, the differential gear train comprising a planet carrier, a first ring gear, a second ring gear and a plurality of planetary gear and planetary gear shaft assemblies; a first clutch and a second clutch, the first clutch being connected with a first hub, and the second clutch being connected with 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 with the impeller; a controller for controlling the engagement and disengagement of the first clutch and the second clutch; wherein the differential gear train realizes the same-direction rotation of the guide vane and the impeller or the fixation of the guide vane by controlling the working states of the first clutch and the second clutch.

[0007] Further, the first ring gear is fixedly connected with the first hub, and the second ring gear is fixedly connected with the second hub.

[0008] Further, the planetary gear and the planetary gear shaft are connected through a key to realize the rotation at the same angular velocity.

[0009] Further, the planet carrier is connected with the motor shaft and the pump shaft through a key and a shaft sleeve to realize the rotation at the same speed.

[0010] Further, the first clutch and the second clutch are both electromagnetic tooth clutches.

[0011] Further, the guide vane is bolted with the first hub through a connecting flange to realize power transmission.

[0012] Further, the centrifugal pump same-direction rotating guide vane device further comprises a plurality of sealing components and sealing rings for realizing the double sealing of a flow passage side and a lubrication side.

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

[0014] Further, in the first working condition, the motor shaft serves as an input shaft, the first clutch works, and the second clutch does not work, at this time, the guide vane is fixed, the impeller rotates, and the second hub idles; in the second working condition, the motor shaft serves as an input shaft, the first clutch does not work, and the second clutch works, at this time, the guide vane and the impeller rotate in the same direction at different speeds.

[0015] Further, the planetary gear has 23 teeth, a module of 4, right-hand rotation and a helix angle β of 9.8°; the first ring gear has 160 teeth, a module of 4, right-hand rotation and a helix angle β of 9.8°; the planetary gear shaft has 27 teeth, a module of 4.5, right-hand rotation and a helix angle β of 14.6°; the second ring gear has 151 teeth, a module of 4.5, right-hand rotation and a helix angle β of 14.6°; and the top clearance coefficients are all 0.25.

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

[0017] In the design working condition, the guide vane is fixed to ensure high efficient energy conversion; in the non-design working condition, the guide vane rotates at the same direction and different speed with the impeller to effectively improve the fluid flow characteristics, reduce the hydraulic loss, and improve the operation efficiency and stability of the pump. The device has compact structure and simple control, does not need to change the input mode, significantly widens the high efficient operation range of the centrifugal pump, reduces the vibration and noise, and is suitable for various complex working conditions. BRIEF DESCRIPTION OF DRAWINGS

[0018] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments. Obviously, the drawings in the following description only constitute some embodiments of the present application, and for those skilled in the art, other drawings can also be obtained from these drawings without creative labor.

[0019] Fig. 1 FIG. 1 is a structural schematic diagram of the centrifugal pump same-direction rotating guide vane device in the embodiment of the present application;

[0020] Fig. 2 FIG. 2 is a transmission route schematic diagram of the guide vane in the fixed working condition in the embodiment of the present application;

[0021] Fig. 3 FIG. 3 is a transmission route schematic diagram of the guide vane in the same-direction rotating working condition in the embodiment of the present application;

[0022] In the drawings: 1, pump body; 2, impeller; 3, guide vane; 4, first clutch; 5, second clutch; 6, steel sheet; 7, friction plate; 8, upper shell; 9, middle shell; 10, lower shell; 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 part one; 28, sealing part two. DETAILED DESCRIPTION

[0023] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the protection scope of the present application.

[0024] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the present application will be further described in detail below with reference to the drawings and specific embodiments.

[0025] Referring to Figs. 1 to 3 As shown in the figure, the embodiment provides a centrifugal pump co-rotating guide vane 3 device, which is realized by a differential gear train. The device includes three sets of planetary gears 18 and planetary gear shaft assemblies, a planetary carrier 20 assembly, two sets of hub and ring gear assemblies, a motor shaft 26 and a pump shaft 25, a connecting flange 13, an impeller 2 and a guide vane 3, wherein the central rotating assembly has eight components. Through a differential gear train, two working modes of fixing and co-rotating of the centrifugal pump guide vane 3 part are realized, the running performance of the centrifugal pump under non-design working conditions is improved, and the high-efficiency running range of the pump is widened.

[0026] The same direction rotating guide vane 3 device of the centrifugal pump of the embodiment comprises a pump body 1, an impeller 2, a guide vane 3, a first clutch 4, a second clutch 5, a steel sheet 6, a friction sheet 7, an upper shell 8, a middle shell 9, a lower shell 10, a cavity 11, a cover plate 12, a connecting flange 13, a first hub 14, a second hub 15, a first ring gear 16, a second ring gear 17, a planetary gear 18, a planetary gear shaft 19, a planet carrier 20, bearing cover one 21, bearing cover two 22, bearing cover three 23, bearing cover four 24, a pump shaft 25, a motor shaft 26, sealing component one 27, sealing component two 28, a shaft sleeve, a sealing ring, a deep groove ball bearing, a tapered roller bearing, a flat key, etc. In addition to standard parts such as clutches, bearings, bolts, sealing components, and sealing rings, the rest are forged stainless steel structures. The device switches the on-off of the first and second clutches 5 through the controller to make the steel sheet 6 and the friction sheet 7 combine or separate; when combined, the clutches and the hubs are integrated into one, and the corresponding hubs are braked. The first clutch 4 is connected to the first hub 14 through the steel sheet 6 / friction sheet 7, and the second clutch 5 is connected to the second hub 15 through the steel sheet 6 / friction sheet 7. The first ring gear 16 and the first hub 14, and the second ring gear 17 and the second hub 15 are respectively bolted. The inner teeth of the first ring gear 16 mesh with the planetary gear 18, and the inner teeth of the second ring gear 17 mesh with the planetary gear shaft 19. The planetary gear 18 and the planetary gear shaft 19 are connected into the same rotating body with a flat key, and three such components are supported on the planet carrier 20 by deep groove ball bearings. The planet carrier 20 is connected to the motor shaft 26 and the pump shaft 25 at the same time through a flat key and a shaft sleeve, and the three rotate at the same speed; the other end of the planet carrier 20 is positioned in the upper shell 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 a tapered roller bearing relative to the second hub 15, and the pump shaft 25 is provided with a tapered roller bearing relative to the first hub 14, and is axially fixed by bearing cover three 23 and a shaft sleeve respectively. The impeller 2 is assembled on the pump shaft 25 with bolts, flat keys, and shaft sleeves, and rotates synchronously with it; the guide vane 3 is placed between the outer circle of the impeller 2 and the pump body 1, and is bolted to the first hub 14 through the connecting flange 13, so as to rotate at the same speed with the first hub 14. Deep groove ball bearings are respectively arranged between the connecting flange 13 and the pump shaft 25, and between the lower shell 10 and the connecting flange 13, and are respectively matched with bearing cover one 21, bearing cover two 22, and a sealing ring; a deep groove ball bearing is also arranged between the cover plate 12 and the motor shaft 26, and is pressed tightly and sealed by bearing cover four 24. The sealing component one 27 is clamped between the impeller 2 and the guide vane 3, and the sealing component two 28 is clamped between the guide vane 3 and the pump body 1, realizing double sealing of the flow passage side and the lubrication side. The upper shell 8, the middle shell 9, and the lower shell 10 are bolted to the first clutch 4 and the second clutch 5 in turn to form a stationary tank; the cavity 11 is bolted to the lower shell 10 and the pump body 1 to form a whole, and a pad is added to the joint surface to keep sealing.

[0027] In the above embodiment, the first clutch 4 and the second clutch 5 are both electromagnetic tooth clutches, which are connected with the upper, middle and lower housings 10 through bolts. The housings are fixed structural members, and the locking and separation of the two clutches are controlled by a controller to realize the combination and separation of the steel sheet 6 and the friction plate 7. When the steel sheet 6 and the friction plate 7 are combined, they can be connected with the wheel hub to realize the braking of the parts. For example, when the first clutch 4 is locked, the first wheel hub 14 and the first ring gear 16 are braked, and the first ring gear 16 stops rotating.

[0028] In the above embodiment, the first ring gear 16 and the second ring gear 17 are both inner gear ring structures, which are processed by inner grinding and connected with the first wheel hub 14 and the second wheel hub 15 through hexagonal bolts to realize motion transmission. The outer sides of the first wheel hub 14 and the second wheel hub 15 are toothed, which are combined with the steel sheet 6 to rotate together.

[0029] In the above embodiment, the planetary carrier 20 assembly is composed of the planetary carrier 20 body and its left and right cover plates 12. The left and right cover plates 12 are installed on the planetary carrier 20 body through hexagonal bolts and are provided with axial positioning structures for fixing the deep groove ball bearings and the planetary wheel shaft assemblies. The planetary wheel 18 and the planetary wheel shaft 19 are connected through a flat key to realize the same angular velocity rotation. Each set of planetary wheel shaft assemblies is fixed on the planetary carrier 20 assembly through three deep groove ball bearings, and there are three sets in total, which are matched with the first ring gear 16 and the second ring gear 17 to form the core structure of the differential gear train.

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

[0031] In the above embodiment, the differential gear train as a whole adopts grease lubrication, and a general lithium-based lubricating grease is used. Bearing covers and sealing rings are used in the connection flanges 13, the cavities 11 and the cover plates 12 to realize overall sealing.

[0032] In the above embodiment, the motor shaft 26 is an input shaft, which is connected with the planetary carrier 20 assembly through a shaft sleeve and a flat key to realize power transmission. The conical roller bearing is installed between the motor shaft 26 and the second wheel hub 15, and the shaft neck and the bearing cover three 23 are used to realize axial positioning; the deep groove ball bearing is installed between the motor shaft 26 and the cover plate 12, and the shaft neck and the bearing cover four 24 are used to realize axial positioning.

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

[0034] In the above embodiment, the connecting flange 13 is connected to the first hub 14 through an internal hexagonal bolt 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 the axial positioning is achieved through the bearing cover and the retainer.

[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 member and form the box part of the differential gear train transmission device. Sealing pads are provided between the parts to achieve box sealing.

[0036] In the above embodiment, the impeller 2 is fixed on the pump shaft 25 by bolts, flat keys, and a shaft sleeve, and power is transmitted from the pump shaft 25 to the impeller 2. A sealing member 27 is installed between the impeller 2 and the guide vane 3; the guide vane 3 is fixed to the connecting flange 13 by an internal hexagonal bolt, and power is transmitted from the first hub 14 to the guide vane 3 through the connecting flange 13 to achieve the same direction rotation of the guide vane 3 and the impeller 2. A sealing member 27 is installed between the guide vane 3 and the impeller 2, and a sealing member 28 is installed between the guide vane 3 and the pump body 1 to achieve partial sealing of the pump body 1.

[0037] In the above embodiment, the pump body 1 is a fixed structural member; the cavity 11 is installed between the pump body 1 and the lower housing 10 by bolts to connect the pump body 1 and the transmission structure. Sealing pads are provided between the cavity 11, the pump body 1, and the lower housing 10 to prevent water leakage and lubricating grease leakage from the pump body 1.

[0038] The first working mode of the above embodiment: the motor shaft 26 as the input shaft, the first clutch 4 works, and the second clutch 5 does not work. At this time, the first clutch 4 brakes the first hub 14, the first hub 14, the connecting flange 13, and the guide vane 3 are fixed, the impeller 2, the pump shaft 25, and the planetary carrier 20 rotate with the motor shaft 26, and the second hub 15 idles. This working mode is suitable for the design working condition of the pump. The transmission ratio under this first working 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 with co-rotating guide vanes (3), comprising a pump body (1), an impeller (2), and guide vanes (3), 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 a first hub (14) and the second clutch (5) is connected to a 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 differential gear system controls the working state of the first clutch (4) and the second clutch (5) to achieve the same rotation of the guide vane (3) and the impeller (2) or the fixation of the guide vane (3).

2. The centrifugal pump co-rotating guide vane (3) device according to claim 1, characterized in that, 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).

3. The centrifugal pump co-rotating guide vane (3) 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.

4. The centrifugal pump co-rotating guide vane (3) device according to claim 1, characterized in that, The planetary carrier (20) is connected to the motor shaft (26) and the pump shaft (25) via a flat key and a bushing, so as to achieve rotation at the same speed.

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

6. The centrifugal pump co-rotating guide vane (3) device according to claim 1, characterized in that, The guide vane (3) is bolted to the first hub (14) via the connecting flange (13) to achieve power transmission.

7. The centrifugal pump co-rotating guide vane (3) 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.

8. The centrifugal pump co-rotating guide vane (3) 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 conditions, and the guide vane (3) and the impeller (2) rotate in the same direction but at different speeds under non-design conditions.

9. The centrifugal pump co-rotating guide vane (3) device according to claim 8, 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.

10. The centrifugal pump co-rotating guide vane (3) device according to claim 1 or 9, 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.

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