Runner device of a new type of water turbine

Abstract

The application belongs to the technical field of hydroelectric power generation equipment, and particularly relates to a runner device of a novel water turbine, which comprises a water inlet shaft, cover plates, flow straightening ribs, a reverse guide vane structure ring and a reverse water outlet channel. The cover plates are arranged at intervals, the flow straightening ribs and the reverse guide vane structure ring are both sealingly and fixedly installed between the cover plates, the water inlet shaft is fixedly installed at the center of the cover plates, and the water inlet shaft, the flow straightening ribs, the reverse guide vane structure ring and the reverse water outlet channel are sequentially arranged from inside to outside along the radial direction of the water inlet shaft. Through a novel energy conversion mechanism of closed cyclone-reverse injection-backwash work, there is basically no energy loss in the closed space, the pressure energy of high-pressure water can be basically completely converted into the rotary mechanical energy of the runner, and the energy conversion efficiency reaches 98% or even more than 98%.

Description

Technical Field

[0001] This invention belongs to the technical field of hydropower equipment, specifically relating to a novel turbine runner device. Background Technology

[0002] A water turbine is a device that converts the pressure energy of water flow into rotational mechanical energy, and it is widely used in the field of hydropower generation. According to traditional working principles, water turbines are mainly divided into two categories: impulse turbines and reaction turbines. The working principle of impulse turbines (such as bucket turbines and oblique-flow turbines) is as follows: before entering the turbine, the water flow passes through nozzles, converting all its pressure energy into the kinetic energy of a high-speed jet. The jet impacts the buckets on the runner, doing work, and the runner rotates in the air. The working principle of reaction turbines (such as mixed-flow, axial-flow, and through-flow turbines) is as follows: the water flow fills the entire flow channel, and the conversion of pressure energy and kinetic energy occurs simultaneously in the runner. The runner rotates and does work due to the reaction force of the water flow.

[0003] Both types of traditional water turbines mentioned above have inherent energy conversion losses. The energy losses of impulse turbines mainly include five types: braking loss, mixing loss, impact loss, wind resistance loss, and mechanical loss. Braking loss, also known as outlet residual velocity loss, is mainly caused by the squeezing effect of the high-speed rotating bucket's back surface on the discharged water flow. Mixing loss mainly includes two parts: first, when the jet flies in the air, the jet surface experiences intense friction with the air, and turbulent diffusion and air entrainment occur internally; second, after the jet enters the bucket, the large velocity gradient between fluid particles leads to uneven mixing, which intensifies jet diffusion and splashing, causing energy loss. Impact loss mainly... The energy loss stems from two main factors: first, the inlet impact. When the relative velocity direction of the jet is not aligned with the tangential direction of the water bucket inlet, an angle of attack is generated, causing the jet to impact the water bucket and create splash. Second, the cutting of the water blades. Because the water blades rotate synchronously with the runner, their geometry and spatial angles are constantly changing relative to the jet. This dynamic mismatch inevitably leads to the jet being broken up, exacerbating splash and causing energy loss. Wind resistance loss refers to the resistance loss caused by friction and eddies generated by the violent agitation of air by multiple non-streamlined water buckets during the runner's rotation. Mechanical loss refers to the energy loss caused by friction and braking of mechanical components such as bearings and seals during operation. The energy losses of a reaction turbine mainly include three types: hydraulic loss, volumetric loss, and mechanical loss. Hydraulic loss is the energy loss caused by friction, eddies, impact, and residual velocity at the outlet in the flow path. Volumetric loss is the loss caused by some water leaking from the gap between rotating and stationary parts, resulting in some water not participating in work. Mechanical loss is the energy loss caused by friction and braking of mechanical components such as bearings and seals.

[0004] Due to limitations in their working principles, the efficiency of existing impulse turbines is typically between 80% and 87%, while that of reaction turbines is typically between 85% and 93%, making fundamental breakthroughs difficult. By the end of 2025, my country's conventional hydropower installed capacity reached approximately 380 million kilowatts, accounting for about 55% of the technically exploitable installed capacity. Nearly half of the high-quality hydropower resources remain to be developed and utilized. Therefore, there is an urgent need for a new type of turbine that breaks away from traditional working principles and achieves a breakthrough in the fundamental mechanism of energy conversion to meet the demands for higher efficiency and better economic benefits in hydropower development. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a new type of turbine runner device, which solves the problem that traditional impulse turbines and reaction turbines cannot break through the efficiency bottleneck due to the limitations of their working principle, and converts the head pressure energy into almost all of the rotational mechanical energy.

[0006] To achieve the above objectives, the technical solution adopted by the present invention is as follows: a novel turbine runner device, comprising an inlet shaft, cover plates, flow straightening ribs, a reverse guide vane structure ring, and a reverse outlet channel. Two cover plates are spaced apart. The flow straightening ribs and the reverse guide vane structure ring are sealed and fixedly installed between the two cover plates. The inlet shaft is fixedly installed at the center of the two cover plates. The inlet shaft, flow straightening ribs, reverse guide vane structure ring, and reverse outlet channel are arranged sequentially from the inside to the outside along the radial direction of the inlet shaft. Multiple guide ports are provided on the inlet shaft between the two cover plates, forming a closed guide cavity between the guide ports and the reverse guide vane structure ring. Water flowing out of the guide ports forms a swirling flow in the guide cavity after passing through the flow straightening ribs. Several reverse outlets are provided on the reverse guide vane structure ring, which are arranged opposite to the swirling flow direction. The reverse outlets are connected to the reverse outlet channel, and the end of the reverse outlet channel is provided with a backflush nozzle.

[0007] Preferably, the water inlet shaft includes a solid shaft section, a hollow hub section, and a hollow tube shaft section arranged sequentially. The hollow hub section is connected to the inner cavity of the hollow tube shaft section. The hollow hub section is located between two cover plates. The flow guide is opened on the hollow hub section. A flow guide structure is provided on the outer side of the hollow hub section corresponding to each flow guide. The inner side of the flow guide structure is a flow guide surface. The water flowing out of the flow guide enters the flow guide cavity along the tangential direction of the flow guide surface.

[0008] Preferably, the height of the flow guide is the same as the distance between the two cover plates, and the width of the flow guide is 1 / 40 to 1 / 10 of its height.

[0009] Preferably, a central mounting port is provided on the two cover plates, the water inlet shaft is installed at the central mounting port, and the gap between the two cover plates and the hollow hub section is less than or equal to 0.001mm.

[0010] Preferably, the cross-section of the rectifier rib is rhomboid, and the side of the rectifier rib perpendicular to the radial direction of the inlet axis is arc-shaped.

[0011] Preferably, multiple rectifier ribs are arranged in a ring around the water inlet shaft to form a rectifier layer. Multiple rectifier layers are provided in the flow guide cavity. The spacing between each rectifier layer is 10~40mm, and the spacing between adjacent rectifier ribs in the same rectifier layer is 5~20mm.

[0012] Preferably, the width of the rectifier rib is 1 / 15 to 1 / 5 of its length, and the thickness of the rectifier rib is 1 / 10 to 1 / 3 of its width.

[0013] Preferably, the included angle at the end of the cross-section of the rectifying rib is 15° to 60°, and the included angle at the end is the angle between the tangent of the arc side and the adjacent side side.

[0014] Preferably, the reverse guide vane structure ring includes an upper structure ring and a lower structure ring, which are connected by a sealing solid ring segment. The sealing solid ring segments are evenly arranged along the circumferential direction, and there are generally but not limited to two sealing solid ring segments. Several reverse guide vanes are also arranged between the upper structure ring and the lower structure ring, forming a reverse outlet between adjacent reverse guide vanes.

[0015] Preferably, the angle between the tangents of the anti-guide vane and the inner side of the anti-guide vane structural ring is 20° to 45°.

[0016] Preferably, an upper ring hoop, a lower ring hoop, and a rim plate are provided on the outer side of the reverse guide vane structure ring, forming a reverse water outlet channel between the upper ring hoop, the lower ring hoop, the rim plate, and the reverse guide vane structure ring. The upper ring hoop and the lower ring hoop are both constructed by welding multiple layers of ring hoops. The upper ring hoop and the lower ring hoop are respectively fixedly connected to the two cover plates and the reverse guide vane structure ring. The rim plate is fixedly connected between the upper ring hoop and the lower ring hoop. A baffle is sealed at one end of the reverse water outlet channel, and a backflush nozzle is sealed at the other end of the reverse water outlet channel.

[0017] Compared with the prior art, the technical solution of the present invention has the following beneficial effects: 1. This invention achieves a breakthrough in energy conversion efficiency. The runner is a sealed environment. High-pressure water enters the sealed runner through the inlet shaft and is finally ejected from the end of the reverse outlet channel. Through a novel energy conversion mechanism of sealed swirling flow-reverse jet-reverse recoil work, it avoids the energy losses of traditional impulse turbines, mainly braking losses, mixing losses, impact losses, and wind resistance losses, as well as the energy losses of traditional reaction turbines, mainly hydraulic losses and volumetric losses. It can convert almost all the pressure energy of high-pressure water into the rotational mechanical energy of the runner, with an energy conversion efficiency of 98% or even higher. This is far higher than the 80%~87% energy conversion efficiency of traditional impulse turbines and the 85%~93% energy conversion efficiency of reaction turbines, approaching the physical limit of energy conversion.

[0018] 2. Simplified structure and improved reliability: The runner rotates in the air to do work, eliminating the need for the underwater sealing structure and tailrace pipe of traditional reaction turbines, which greatly reduces manufacturing and maintenance costs and improves operational reliability.

[0019] 3. Wide adaptability to various operating conditions: Since the energy conversion does not depend on the flow conditions around a specific airfoil, but is based on the momentum exchange between the overall swirling flow and the reverse jet within a closed flow channel, the present invention has a significantly better adaptability to changes in head and flow rate than traditional water turbines. Attached Figure Description

[0020] Figure 1 This is a cross-sectional view of the impeller, where the arrows indicate the direction of water flow.

[0021] Figure 2 for Figure 1 Schematic diagram of cross-section at point AA.

[0022] Figure 3 This is a longitudinal sectional view of the water inlet shaft, where the arrows indicate the direction of water inlet.

[0023] Figure 4 for Figure 3 A cross-sectional view at point BB, where the arrows indicate the direction of water flow.

[0024] Figure 5 This is a schematic diagram of the rectifier rib structure.

[0025] Figure 6 for Figure 5 A cross-sectional view at point CC.

[0026] Figure 7 This is a longitudinal sectional view of the anti-guide blade structure ring.

[0027] Figure 8 for Figure 7 A cross-sectional view at point DD, where the arrows indicate the direction of water flow.

[0028] Figure 9 This is a physical image of the rotor of the present invention.

[0029] Figure 10 This is a photograph of the actual object at the back jet nozzle of the present invention. The components include: 1. Inlet shaft; 101. Solid shaft section; 102. Hollow tube shaft section; 103. Hollow hub section; 104. Flow guide structure; 105. Flow guide port; 2. Rectifying ribs; 3. Reverse guide vane structure ring; 301. Upper structure ring; 302. Lower structure ring; 303. Sealing solid ring section; 304. Reverse guide vane; 305. Reverse outlet; 4. Wheel flange plate; 5. Backflush nozzle; 6. Baffle; 7. Upper cover plate; 8. Lower cover plate; 9. Upper ring clamp; 10. Lower ring clamp; 11. Reverse outlet channel; 12. Center mounting port. Detailed Implementation

[0030] like Figures 1-2 As shown, Figure 1 and Figure 2 The attached diagrams describe the overall structure. Both are cut symmetrically at the most exposed positions within the rotating wheel. Figure 1 This is a schematic cross-sectional view of the overall structure of the rotary device, and Figure 2 exist Figure 1 The image shows a longitudinal sectional view of the overall structure of the rotary device, cut at point AA. Figure 2 Only half is drawn to make the contact relationships between the parts clearer. Figure 1 This will qualitatively reveal all the structural components inside the 360° rotating wheel.

[0031] As shown in the figure, the turbine runner device of the present invention includes an inlet shaft 1, a cover plate, a flow-rectifying rib 2, a reverse guide vane structure ring 3, and a reverse outlet channel 11. Two cover plates are spaced apart, namely an upper cover plate 7 and a lower cover plate 8, which are mirror-symmetrical. The flow-rectifying rib 2 and the reverse guide vane structure ring 3 are sealed and fixedly installed between the two cover plates. The inlet shaft 1 is fixedly installed at the center of the two cover plates. The inlet shaft 1, the flow-rectifying rib 2, the reverse guide vane structure ring 3, and the reverse outlet channel 11 are arranged sequentially from the inside to the outside along the radial direction of the inlet shaft 1. A closed guide cavity is formed between the two cover plates, the inlet shaft 1, and the reverse guide vane structure ring 3. Water flowing out from the guide port 105 forms a swirling flow within the guide cavity after passing through the flow-rectifying rib 2. The flow guiding cavity contains multiple rectifying ribs 2 arranged in a ring-shaped rectifying layer. These rectifying layers are sequentially spaced outside the inlet shaft 1. A reverse guide vane structure ring 3 is located outside the outermost rectifying layer, and a reverse outlet channel 11 is located outside the reverse guide vane structure ring 3. High-pressure water enters the impeller through the inlet shaft 1. After being rectified by the rectifying ribs 2 inside the impeller, it is finally ejected tangentially from the back jet nozzle 5 at the end of the reverse outlet channel 11. The ejected high-pressure water exerts a counter-current force on the impeller in the same direction as the swirling flow, driving the impeller to rotate and perform work in the air.

[0032] The inlet shaft 1 is hollow, and high-pressure water enters the inlet shaft 1 through the lower end of the inlet shaft 1. Multiple guide ports 105 are opened in the circumferential direction in the hollow section of the inlet shaft 1 between the two cover plates. Each guide port 105 is opened in the same rotation direction. The high-pressure water flowing out of the guide port 105 enters the impeller. Each guide port 105 is tangentially set. The high-pressure water flowing out tangentially enters each rectifier layer and forms a steady vortex after being rectified by each rectifier layer. Several reverse outlets 305 are set on the reverse guide vane structure ring 3, which are opposite to the vortex direction. Under the action of centrifugal force and pressure, the vortex enters the corresponding reverse outlet channel 11 on the outside through the reverse outlets 305 on the reverse guide vane structure ring 3. The vortex gathers in the reverse outlet channel 11 and is finally ejected through the backflush nozzle 5 at the end of the reverse outlet channel 11.

[0033] like Figures 3-4 As shown, Figure 3 This is a longitudinal sectional view of the inlet shaft 1. Figure 4 yes Figure 3 A cross-sectional view of the hollow hub section 103 at the middle BB section, tangentially to the guide port 105. The water inlet shaft 1 is essentially developed from a rotating solid main shaft, with the water inlet pipe shaft section and the water inlet hub section. Its core purpose is to construct a water inlet system in the center of the rotor and generate a swirling flow system, thereby creating a centrifugal physical effect of the water body, which obeys well-known physical theorems.

[0034] As shown in the figure, the water inlet shaft 1 includes a solid shaft section 101, a hollow hub section 103, and a hollow tube shaft section 102 arranged in sequence. The water inlet shaft 1 is integrally formed, and the inner cavity of the hollow hub section 103 is connected to the inner cavity of the hollow tube shaft section 102. A central mounting port 12 is provided on the upper cover plate 7 and the lower cover plate 8. The solid shaft section 101 passes through the central mounting port 12 on the upper cover plate 7, and the hollow tube shaft section 102 passes through the central mounting port 12 on the lower cover plate 8. The central mounting ports 12 on the two cover plates are respectively press-fitted with the solid shaft section 101 and the hollow tube shaft section 102 and welded to fix them. The hollow hub section 103 is set between the two cover plates. The gap between the two cover plates and the hollow hub section 103 is less than or equal to 0.001mm, that is, it must not leak water, otherwise it will form turbulence that disturbs the swirling flow. The upper and lower cover plates are structural components that resist the radial centrifugal force of the impeller and the expansion force of the impeller cavity. They should be made of corrosion-resistant and high-strength alloy materials. The guide port 105 is opened on the hollow hub section 103. 03. The guide ports 105 are evenly arranged along the circumference. A guide structure 104 is provided on the outer periphery of the hollow hub section 103 corresponding to each guide port 105. The inner side of the guide structure 104 is a guide curved surface. The water flowing out of the guide port 105 enters the guide cavity along the tangent direction of the guide curved surface. Generally, but not limited to, 3 to 12 guide ports 105 are opened. In this embodiment, 4 guide ports 105 are opened. The height of the guide port 105 is the same as the distance between the two cover plates. The width of the guide port 105 is generally, but not limited to, 1 / 40 to 1 / 10 of its height. The guide ports 105 are arranged in a streamlined shape along the circumference. The water inlet shaft 1 is precisely integrated and machined on a CNC machine tool. Its material is corrosion-resistant and suitable for long-term rotation alloy steel.

[0035] The solid shaft section 101 is used to connect with the external bearing and the generator, and the hollow tube shaft section 102 is used to rotate and seal with the external bearing and the pressure water pipe. Since the connection method is a conventional technical means in this field, it will not be described in detail here.

[0036] like Figures 1-2 as well as Figures 5-6 As shown, Figure 5 This is a front view schematic diagram of rectifier rib 2. Figure 6 for Figure 5 A cross-sectional view of the rectifier rib 2 in the CC. The spacing between rectifier layers and the circumferential spacing between rectifier ribs 2 within the same rectifier layer are determined by the high-pressure swirling water pressure inside the impeller cavity. The spacing between each rectifier layer is generally, but not limited to, 10~40mm. The spacing between adjacent rectifier ribs 2 within the same rectifier layer is generally, but not limited to, 5~20mm. The upper and lower ends of each rectifier rib 2 are fixedly installed on the two cover plates. Mounting holes for the rectifier rib 2 are correspondingly provided on the upper cover plate 7 and the lower cover plate 8. The upper and lower ends of the rectifier rib 2 are sealed and welded to the upper cover plate 7 and the lower cover plate 8 respectively to ensure no water leakage.

[0037] The length of the rectifier rib 2 is the sum of the distance between the two cover plates and the thickness of the two cover plates. The width of the rectifier rib 2 is generally, but not limited to, 1 / 15 to 1 / 5 of its length. The thickness of the rectifier rib 2 is generally, but not limited to, 1 / 10 to 1 / 3 of its width. In order to reduce the swirling resistance, the cross-section of the rectifier rib 2 is rhomboid. The side of the rectifier rib 2 perpendicular to the radial direction of the inlet axis 1 is an arc-shaped side. The curvature of the arc-shaped side is adapted to the annular shape of the rectifier layer. The included angle at the end of the rhomboid cross-section of the rectifier rib 2 is generally, but not limited to, 15° to 60°. The included angle at the end is the angle between the tangent of the arc-shaped side and the adjacent side. The two core functions of the rectifier rib 2 are flow stability and bearing structural force. Flow stability requires the surface of the flow passage to be smooth, that is, the surface of the rectifier rib 2 is smooth and streamlined. Bearing structural force requires the use of high-quality anti-corrosion alloy steel and accurate calculation of structural stress.

[0038] like Figures 7-8 As shown, Figure 7 This is a front view schematic diagram of the anti-guide blade structure ring 3. Figure 8 for Figure 7 A cross-sectional schematic diagram of the reverse guide vane structure ring 3 at the DD position. The reverse guide vane structure ring 3 is fixedly welded between the upper cover plate 7 and the lower cover plate 8. The reverse guide vane structure ring 3 includes an upper structure ring 301 and a lower structure ring 302. The upper structure ring 301 is sealed and welded to the upper cover plate 7 to form a sealed whole, and the lower structure ring 302 is sealed and welded to the lower cover plate 8 to form a sealed whole. The upper structure ring 301 and the lower structure ring 302 are connected by a sealing solid ring segment 303. The sealing solid ring segment 303 is a trajectory channel reserved for the recoil nozzle 5 to spray water in the air. The sealing solid ring segments 303 are evenly arranged along the circumference. There are generally, but not limited to, two sealing solid ring segments. In this embodiment, [the specific number of segments is not specified]. The device is equipped with two sealed solid ring sections 303. Several reverse guide vanes 304 are also provided between the upper structural ring 301 and the lower structural ring 302. Reverse outlets 305 are formed between adjacent reverse guide vanes 304. The angle between the tangents of the reverse guide vanes 304 and the inner side of the reverse guide vane structural ring 3 is generally, but not limited to, 20°–45°. The function of the reverse guide vanes 304 is to reverse the flow of the swirling water inside the reverse guide vane structural ring 3 under centrifugal effect, meaning that the high-pressure water flowing out from the reverse outlet 305 of the reverse guide vane structural ring 3 rotates in the opposite direction to the swirling flow inside the impeller. The thickness of the reverse guide vanes 304 is generally, but not limited to, 5–40 mm, and the circumferential spacing between the reverse guide vanes 304 is generally, but not limited to, 20–80 mm. The reverse guide vane structural ring 3 can be machined as a whole by CNC machine tools or welded from parts, and its material is corrosion-resistant alloy steel.

[0039] In this embodiment, two reverse water outlet channels 11 are provided corresponding to the two sets of reverse water outlets 305. The two reverse water outlet channels 11 are symmetrically arranged, that is, the reverse water outlet channels 11 are formed between the upper ring hoop 9, the lower ring hoop 10, the wheel flange plate 4, and the reverse guide vane structure ring 3. The reverse water outlet channels 11 have a square longitudinal section and an arc horizontal section. The upper ring hoop 9 and the lower ring hoop 10 are load-bearing structural components, which bear most of the radial force to prevent the impeller from disintegrating. To ensure the overall safety of the impeller, a multi-layer overlapping welding technology is adopted. The upper ring hoop 9 and the lower ring hoop 10 are both composed of multiple ring hoops welded together in sequence. The number of layers of the ring hoops is generally but not limited to 3 to 6 layers. The material is corrosion-resistant high-strength alloy steel. The upper ring hoop 9 and the lower ring hoop 10 are respectively fixedly welded to the two cover plates and the reverse guide vane structure ring 3. On the guide vane structure ring 3, the rim plate 4 is a sealing structure, which is sealed and welded to the rim between the upper ring hoop 9 and the lower ring hoop 10. Along the path of the backflush nozzle 5, the rim plate 4 is bent into a baffle 6, forming a space channel for water to enter the air at one end of the reverse water outlet channel 11. This baffle 6 is sealed and welded to all surrounding contact parts. A backflush nozzle 5 is sealed at the other end of the reverse water outlet channel 11. The backflush nozzle 5 is located at the end of the reverse water outlet channel 11, and its spray direction is opposite to the swirling direction inside the impeller, spraying tangentially. The backflush nozzle 5 consists of a nozzle seat and a nozzle. The nozzle seat is square on the outside and circular on the inside, and the nozzle has a circular tapering structure. The nozzle seat and nozzle are threaded together, and the nozzle seat is firmly welded to the corresponding surrounding contact parts, requiring a sealed weld. The nozzle seat and nozzle are commercially available or mature technologies, and can be purchased or customized.

[0040] like Figures 9-10 The image shown is a physical picture of the present invention, wherein... Figure 9 This is a photograph of the actual rotating wheel in this invention. Figure 10 This is a photograph of the actual object at the recoil nozzle 5 in this invention.

[0041] In use, high-pressure water from the water head enters the hollow hub section 103 from the hollow tube shaft section 102 on the lower side. It then enters the fully sealed inner cavity of the rotor tangentially through the guide port 105 on the hollow hub section 103 and forms a swirling flow. With the support of numerous orderly arranged rectifier ribs 2, an orderly swirling flow is formed from the center of the rotor to the rim. The flow is stably swirling to the reverse guide vane structure ring 3. When the swirling flow reaches the inner side of the reverse guide vane structure ring 3, it is forced into the reverse guide vane structure ring 3 under the action of centrifugal effect. It is then rectified by the reverse guide vane 304 into a reverse flow of water and enters the reverse outlet channel 11 through the reverse outlet 305. The rotation direction of the water flow entering the reverse outlet channel 11 is opposite to the rotation direction of the swirling flow inside the rotor. Finally, it is ejected from the back jet nozzle 5 set at the end of the reverse outlet channel 11 and enters the air. The resulting back jet force drives the rotor to rotate and do work. The energy conversion path of this invention is fundamentally different from the traditional impact and counterattack methods. It abandons the traditional mode of open jet impact work and submerged pressure kinetic energy gradual conversion work, and instead adopts a brand-new mechanism of constraining the swirling flow in a closed space and achieving counterattack work through reverse jetting in the air, thereby converting almost all of the water pressure energy into rotational mechanical energy.

[0042] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention in any other way. Any person skilled in the art may make changes or modifications to the above-disclosed technical content to create equivalent embodiments. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the protection scope of the present invention.

Claims

1. A novel turbine runner device, characterized in that: The system includes an inlet shaft (1), a cover plate, a flow straightening rib (2), a reverse guide vane structure ring (3), and a reverse outlet channel (11). Two cover plates are spaced apart. The flow straightening rib (2) and the reverse guide vane structure ring (3) are sealed and fixedly installed between the two cover plates. The inlet shaft (1) is fixedly installed at the center of the two cover plates. The inlet shaft (1), flow straightening rib (2), reverse guide vane structure ring (3), and reverse outlet channel (11) are arranged sequentially from the inside to the outside along the radial direction of the inlet shaft (1). Multiple guide ports (105) are provided on the water inlet shaft (1). A closed guide cavity is formed between the guide ports (105) and the reverse guide vane structure ring (3). The water flowing out from the guide ports (105) forms a swirling flow in the guide cavity after passing through the straightening ribs (2). Several reverse water outlets (305) are provided on the reverse guide vane structure ring (3) with the opposite direction of the swirling flow. The reverse water outlets (305) are connected to the reverse water outlet channel (11). The end of the reverse water outlet channel (11) is provided with a backflush nozzle (5).

2. The runner device of a novel water turbine according to claim 1, characterized in that: The water inlet shaft (1) includes a solid shaft section (101), a hollow hub section (103), and a hollow tube shaft section (102) arranged in sequence. The hollow hub section (103) is connected to the inner cavity of the hollow tube shaft section (102). The hollow hub section (103) is located between two cover plates. The guide port (105) is opened on the hollow hub section (103). A guide structure (104) is provided on the outer periphery of the hollow hub section (103) corresponding to each guide port (105). The inner side of the guide structure (104) is a guide curved surface. The water flowing out of the guide port (105) enters the guide cavity along the tangential direction of the guide curved surface.

3. The runner device of a novel water turbine according to claim 1 or 2, characterized in that: The height of the flow guide (105) is the same as the distance between the two cover plates, and the width of the flow guide (105) is 1 / 40 to 1 / 10 of its height.

4. The runner device of a novel water turbine according to claim 1, characterized in that: The cross-section of the rectifier rib (2) is rhomboid, and the side of the rectifier rib (2) perpendicular to the radial direction of the inlet shaft (1) is arc-shaped.

5. The runner device of a novel water turbine according to claim 1, characterized in that: Multiple rectifier ribs (2) are arranged in a ring around the water inlet shaft (1) to form a rectifier layer. Multiple rectifier layers are provided in the flow guide cavity. The spacing between each rectifier layer is 10~40mm. The spacing between adjacent rectifier ribs (2) in the same rectifier layer is 5~20mm.

6. The runner device of a novel water turbine according to claim 1 or 4, characterized in that: The width of the rectifier rib (2) is 1 / 15 to 1 / 5 of its length, and the thickness of the rectifier rib (2) is 1 / 10 to 1 / 3 of its width.

7. The runner device of a novel water turbine according to claim 4, characterized in that: The included angle at the end of the cross section of the rectifier rib (2) is 15° to 60°, and the included angle at the end is the angle between the tangent of the arc side and the adjacent side side.

8. The runner device of a novel water turbine according to claim 1, characterized in that: The reverse guide vane structure ring (3) includes an upper structure ring (301) and a lower structure ring (302). The upper structure ring (301) and the lower structure ring (302) are connected by a sealing solid ring section (303). The sealing solid ring section (303) is evenly arranged along the circumferential direction. Several reverse guide vanes (304) are also arranged between the upper structure ring (301) and the lower structure ring (302), and a reverse outlet (305) is formed between adjacent reverse guide vanes (304).

9. The runner device of a novel water turbine according to claim 8, characterized in that: The angle between the tangents of the reverse guide vane (304) and the inner side of the reverse guide vane structure ring (3) is 20° to 45°.

10. The runner device of a novel water turbine according to claim 1, characterized in that: An upper ring hoop (9), a lower ring hoop (10), and a wheel flange plate (4) are provided on the outside of the reverse guide vane structure ring (3). A reverse water outlet channel (11) is formed between the upper ring hoop (9), the lower ring hoop (10), the wheel flange plate (4), and the reverse guide vane structure ring (3). The upper ring hoop (9) and the lower ring hoop (10) are both made of multiple ring hoops welded together. The upper ring hoop (9) and the lower ring hoop (10) are respectively fixedly connected to the two cover plates and the reverse guide vane structure ring (3). The wheel flange plate (4) is fixedly connected between the upper ring hoop (9) and the lower ring hoop (10). A baffle (6) is sealed at one end of the reverse water outlet channel (11), and a backflush nozzle (5) is sealed at the other end of the reverse water outlet channel (11).

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