A self-circulating anti-gas stagnation hydraulic turbine

Abstract

The present invention discloses a self-circulating anti-gas stagnation type hydraulic turbine, comprising a pump body, a main impeller and an outlet section. Sealing rings are arranged on the front and rear cover plates of the main impeller, a guide vane is arranged between the outlet section and the pump body, a jet hole is arranged on the rear cover plate of the guide vane, a jet guide vane is arranged at the rear cover plate of the guide vane, the jet guide vane is fixedly connected to the guide vane, a blade flow channel is arranged on the jet guide vane, the inlet width of the blade flow channel is greater than the outlet width, the outlet of the blade flow channel is butted with the inlet of the jet hole, a self-circulating impeller is arranged in the jet guide vane, and the self-circulating impeller is connected to the main impeller through a shaft. The present invention provides a self-circulating anti-gas stagnation type hydraulic turbine, which adds a jet guide vane and a self-circulating impeller at the guide vane outlet, and through the dual effects of self-circulating impeller suction and jetting from the jet hole, the gas phase at the guide vane outlet is no longer retained, thereby avoiding the problem of a significant decrease in turbine efficiency and operation reliability due to gas retention at the guide vane outlet.

Description

Technical Field

[0001] The invention relates to a hydraulic turbine, in particular to a self-circulating anti-gas stagnation type hydraulic turbine. Background Art

[0002] In the natural gas purification process, such as desulfurization, dehydration, tail gas treatment and sulfur recovery, a large amount of liquid residual pressure is usually generated, which has the potential for recycling. Taking the existing desulfurization device as an example, the liquid residual pressure difference between the absorption tower and the flash tank is as high as 6.0 MPa. The traditional operation mode is to reduce the pressure through devices such as pressure reducing valves and then transport, resulting in waste of residual pressure. However, hydraulic turbine technology can effectively recover the fluid residual pressure in these industrial processes, with significant energy-saving and emission reduction effects.

[0003] In practical applications, due to the high pressure and temperature difference of the residual pressure liquid between the absorption tower and the flash tank, gas precipitation often occurs at the impeller outlet. At the same time, due to the reverse pressure gradient in the tailwater pipe along the flow direction, the gas stagnates at the impeller outlet. Generally, the gas content is 15-25%. This gas phase stagnation phenomenon leads to a significant decrease in turbine efficiency and operating reliability. Summary of the invention

[0004] The technical task of the present invention is to provide a self-circulating anti-gas stagnation type hydraulic turbine in view of the above deficiencies in the prior art.

[0005] The technical solution adopted by the present invention to solve its technical problems is: a self-circulating anti-gas stagnation type hydraulic turbine, including a pump body, a main impeller and an outlet section, sealing rings are arranged on the front and rear cover plates of the main impeller, a guide vane is arranged between the outlet section and the pump body, a sealing ring is arranged between the guide vane and the main impeller, a jet hole is arranged on the rear cover plate of the guide vane, the outlet of the jet hole is inclined, a jet guide vane is arranged at the rear cover plate of the guide vane, the jet guide vane is fixedly connected to the guide vane, a blade flow channel is arranged on the jet guide vane, the inlet width of the blade flow channel is greater than the outlet width, the outlet of the blade flow channel is butted against the inlet of the jet hole, on the axial section of the jet guide vane, the blade flow channel is a right-angled trapezoid, and its right-angled side is located on the front cover plate of the jet guide vane, and the inlet and outlet area ratio of the blade flow channel is greater than the outlet width. , a1 is the inlet area of ​​the blade flow channel, a2 is the outlet area of ​​the blade flow channel, a self-circulation impeller is arranged in the jet guide vane, the self-circulation impeller is a semi-open impeller, the blades on the self-circulation impeller are forward curved blades, and the self-circulation impeller is connected to the main impeller through a shaft.

[0006] Further improvement: the inclination angle between the outlet of the jet hole and the rear cover of the guide vane .

[0007] Further improvement: The radius of the main impeller inlet is R1, and the radius from the sealing ring to the shaft center is , the inlet width of the main impeller , b2 is the outlet width of the volute; the outlet angle of the main blade on the main impeller , the component of the main impeller outlet absolute velocity in the circumferential velocity , the inlet angle of the guide vane on the guide vane , the outlet angle of the guide vane , where v m2 is the main impeller outlet axial velocity, u2 is the main impeller outlet circumferential velocity, v u1 is the component of the absolute velocity at the main impeller inlet in the circumferential velocity, R a It is the radius of the intersection of the main impeller outlet edge and the flow channel centerline.

[0008] Further improvement: outlet radius of the self-circulating impeller , the outlet width of the forward curved blade , the outlet angle of the forward curved blade .

[0009] Further improvement: the inlet width of the blade flow channel , the outlet width of the blade channel , the inlet radius of the jet guide vane , the exit radius of the jet guide vane .

[0010] Advantages of the present invention: The present invention provides a self-circulating anti-gas stagnation type hydraulic turbine, which adds a jet guide vane and a self-circulating impeller at the guide vane outlet. Through the dual effects of self-circulating impeller suction and jet hole jetting, the gas phase at the guide vane outlet is no longer retained, thereby avoiding the problem of a significant decrease in turbine efficiency and operating reliability caused by gas retention at the guide vane outlet. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Figure 1 It is a structural schematic diagram of the present invention.

[0012] Figure 2 It is a schematic diagram of the dimensions of the main impeller of the present invention.

[0013] Figure 3 It is a schematic diagram of the dimensions of the main blade of the present invention.

[0014] Figure 4 It is a schematic diagram of the axial section of the self-circulating impeller of the present invention.

[0015] Figure 5 It is a schematic structural diagram of the forward curved blades on the self-circulating impeller of the present invention.

[0016] Figure 6It is a schematic diagram of an axial section of the jet guide vane of the present invention.

[0017] Figure 7 It is a schematic cross-sectional view of the jet guide vane of the present invention.

[0018] Figure 8 It is a structural schematic diagram of the guide vane of the present invention.

[0019] Fig. 9 It is a schematic diagram of the structure of the jet hole of the present invention.

[0020] Fig.10 It is a schematic structural diagram of the guide vane of the present invention.

[0021] In the figure: outlet section 1, guide vane 2, jet hole 21, rear cover plate 22, guide vane 23, pump body 3, jet guide vane 4, front cover plate 41, blade channel 42, self-circulating impeller 5, forward curved blade 51, main impeller 6, sealing ring 61, main blade 62, shaft 7, sealing ring 8. DETAILED DESCRIPTION

[0022] The present invention is described in detail below with reference to the accompanying drawings.

[0023] like Figures 1 to 10 As shown, a self-circulating anti-gas stagnation type hydraulic turbine comprises a pump body 3, a main impeller 6 and an outlet section 1, sealing rings 61 are provided on the front and rear cover plates of the main impeller 6, a guide vane 2 is provided between the outlet section 1 and the pump body 3, a sealing ring 8 is provided between the guide vane 2 and the main impeller 6, a jet hole 21 is provided on the rear cover plate 22 of the guide vane 2, a jet guide vane 4 is provided at the outlet of the guide vane 2, the jet guide vane 4 is fixedly connected to the guide vane 2, a blade flow channel 42 is provided on the jet guide vane 4, the inlet width of the blade flow channel 42 is greater than the outlet width, the outlet of the blade flow channel 42 is butted against the inlet of the jet hole 21, a self-circulating impeller 5 is provided in the jet guide vane 4, and the self-circulating impeller 5 is connected to the main impeller 6 through a shaft 7.

[0024] Main impeller: Figure 2 , 3 As shown, the radius of the main impeller 6 at the inlet is R1, and the radius from the sealing ring 61 to the shaft center is , the inlet width of the main impeller 6 , b2 is the outlet width of the volute, and the outlet angle of the main blade 62 on the main impeller , the component of the main impeller's outlet absolute velocity in the circumferential velocity , which reduces the leakage of the front and rear cavities, reduces the volume loss, and improves the turbine efficiency; where v m2 is the main impeller outlet axial velocity, u2 is the main impeller outlet circumferential velocity, v u1is the component of the absolute velocity at the main impeller inlet in the circumferential velocity, R a is the radius of the intersection of the main impeller outlet edge and the flow channel centerline; when the main impeller is selected, v m2 、u2、v u1 , R a These parameters can be obtained based on the geometric parameters of the main impeller itself.

[0025] Guide vane: Figure 8 , 9 As shown in 10, the inlet angle of the guide vane 23 on the guide vane 2 , the outlet angle of the guide vane 23 The outlet of the jet hole 21 is inclined, and the inclination angle between the outlet of the jet hole 21 and the rear cover plate 22 of the guide vane 2 is Such a design can give the fluid at the guide vane outlet rotational kinetic energy, causing the gas medium to gather below the guide vane outlet.

[0026] Self-circulating impeller: Figure 4 , 5 As shown, the self-circulating impeller 5 is a semi-open impeller, the blades on the self-circulating impeller 5 are forward curved blades 51, and the outlet radius of the self-circulating impeller 5 is , the outlet width of the forward curved blade 51 , the outlet angle of the forward curved blade 53 , which can maximize the velocity of the fluid at the outlet of the self-circulating impeller 5 and help form the jet in the jet hole 21.

[0027] Jet guide vane: Figure 6 , 7 As shown, the inlet radius of the jet guide vane 4 , jet guide vane 4 outlet radius On the axial section of the jet guide vane 4, the blade flow channel 42 is a right-angled trapezoid, whose right-angled side is located on the front cover plate 41 of the jet guide vane 4, and the inlet width of the blade flow channel 42 is , the outlet width of the blade flow channel 42 , the inlet and outlet area ratio of the blade flow channel 42 is , a1 is the inlet area of ​​the blade flow channel, a2 is the outlet area of ​​the blade flow channel, and the fluid velocity at the outlet of the self-circulating impeller 5 is further increased, which further contributes to the formation of the jet in the jet hole 21.

[0028] Its working principle is: when high-pressure liquid enters from the hydraulic turbine inlet, it drives the main impeller 6 to rotate. During the rotation of the main impeller 6, gas is precipitated at the outlet of the main impeller 6. Driven by the spiral vortex at the outlet of the main impeller 6, the gas-liquid two-phase fluid is transported to the outlet of the guide vane 2. Since the outlet of the guide vane 2 has a circulation, the liquid rotation discharge process carries away part of the gas, while part of the gas is stagnant at the outlet of the guide vane 2. At the same time, the main impeller 6 drives the shaft 7 to rotate, and drives the self-circulation impeller 5 to rotate together.

[0029] The rotation of the self-circulating impeller 5 generates a suction effect, which sucks the stagnant gas at the outlet of the guide vane 2 into the jet guide vane 4. The blade flow channel 42 on the jet guide vane 4 is a gradually contracting flow channel, so that the gas-liquid two-phase fluid entering the jet hole 21 has a high velocity, and a jet is generated at the outlet of the guide vane 2. Under the dual effects of the suction of the self-circulating impeller 5 and the jet of the jet hole, the gas phase at the outlet of the guide vane 2 is no longer stagnant, and a part of the stagnant gas circulates in the outlet of the guide vane 2, the self-circulating impeller 5, and the jet hole 21, and a part of the stagnant gas is carried to the turbine outlet by the liquid after going out of the jet hole 21.

[0030] The above descriptions are merely embodiments of the present invention and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention specification and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A self-circulating anti-gas stagnation type hydraulic turbine, comprising a pump body, a main impeller and an outlet section, characterized in that: Sealing rings are provided on the front and rear covers of the main impeller, guide vanes are provided between the outlet section and the pump body, sealing rings are provided between the guide vanes and the main impeller, and jet holes are provided on the rear cover of the guide vanes. The outlet of the jet hole is inclined, and the inclination angle between the outlet of the jet hole and the rear cover of the guide vane is A jet guide vane is provided at the rear cover of the guide vane, the jet guide vane is fixedly connected to the guide vane, a blade flow channel is provided on the jet guide vane, the inlet width of the blade flow channel is greater than the outlet width, the outlet of the blade flow channel is butted with the inlet of the jet hole, and the inlet radius of the jet guide vane is , the exit radius of the jet guide vane is On the axial section of the jet guide vane, the blade flow channel is a right-angled trapezoid, whose right-angled side is located on the front cover plate of the jet guide vane, and the inlet width of the blade flow channel is , the outlet width of the blade channel is , the inlet and outlet area ratio of the blade flow channel A self-circulating impeller is arranged in the jet guide vane, the self-circulating impeller is connected to the main impeller through a shaft, the self-circulating impeller is a semi-open impeller, the blades on the self-circulating impeller are forward curved blades, and the outlet radius of the self-circulating impeller is , R1 is the radius of the main impeller at the inlet, and the outlet width of the forward curved blade is , the inlet width of the main impeller is , b2 is the volute outlet width, and the outlet angle of the forward curved blade is .

2. The self-circulating anti-gas stagnation type hydraulic turbine according to claim 1, characterized in that: The radius from the sealing ring to the center of the shaft is , the outlet angle of the main blades on the main impeller is , the component of the main impeller outlet absolute velocity in the circumferential velocity , the inlet angle of the guide vane on the guide vane is , the outlet angle of the guide vane is , where v m2 is the main impeller outlet axial velocity, u2 is the main impeller outlet circumferential velocity, v u1 is the component of the absolute velocity at the main impeller inlet in the circumferential velocity, R a It is the radius of the intersection of the main impeller outlet edge and the flow channel centerline.

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