Hydraulic turbine

Abstract

The utility model discloses a hydraulic turbine which comprises a shell, a turbine blade, a turbine blade and a driving device. The middle section of the rotor is arranged in the containing cavity, a first-stage impeller and a second-stage impeller are arranged on the rotor, and the first-stage impeller and the second-stage impeller are arranged in a mirror image mode; the first end cover is arranged at one end of the containing cavity, and the first end cover is close to one side of the first-stage impeller; the second end cover is arranged at the other end of the containing cavity, and the second end cover is close to one side of the secondary impeller; the diameters of the two ends of the containing cavity are larger than those of the first-stage impeller and the second-stage impeller. The internal structure of the hydraulic turbine can be arranged according to the small recovery power requirement, the structure is simple, the manufacturing difficulty and cost are reduced, and the economical efficiency is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to a liquid force recovery technical field especially relates to a liquid force turbine. BACKGROUND

[0002] In recent years, in response to the policy of energy conservation and environmental protection, green and sustainable development, in the petroleum chemical industry, such as: hydrocracking, large-scale synthetic ammonia, fertilizer manufacturing, seawater desalination, methanol synthesis, low-temperature methanol washing and other devices, the use of liquid force recovery turbine recovery process is widely implemented to recover the surplus pressure energy and convert it into mechanical energy to drive mechanical equipment, replacing the previous direct pressure relief with pressure relief valve, solving the practical problem of causing a large amount of energy waste.

[0003] In the related art, low-temperature methanol washing and similar processes are widely used, and most of them require small recovery power (≤100kW). If a multi-stage inner shell horizontal split structure or a multi-stage segmented liquid force turbine is used, it will cause a mismatch between supply and demand, resulting in complex equipment structure, high manufacturing difficulty, high cost, large cumulative loss between stages, low recovery efficiency and other drawbacks, and even there may be a problem of insufficient installation space for large structure size. If a single-stage structure liquid force turbine is used, the specific speed of the single stage will necessarily be reduced, and the recovery efficiency will be low. SUMMARY

[0004] The utility model aims at least to solve one of the technical problems existing in the prior art or related art.

[0005] Therefore, the utility model provides a liquid force turbine, wherein the liquid force turbine can set the internal structure of the liquid force turbine according to the small recovery power requirement, the structure is simple, the manufacturing difficulty and cost are reduced, and the economy is improved.

[0006] Specifically, the following technical scheme is included:

[0007] The utility model provides a liquid force turbine, which comprises:

[0008] A housing is provided with a containing cavity;

[0009] A rotor is provided with a first-stage impeller and a second-stage impeller, and the first-stage impeller and the second-stage impeller are mirror image arranged.

[0010] A first end cover is arranged at one end of the containing cavity, and the first end cover is close to one side of the first-stage impeller.

[0011] A second end cover is arranged at the other end of the containing cavity, and the second end cover is close to one side of the second-stage impeller.

[0012] The diameter of the accommodating cavity at both ends is greater than the diameter of the primary impeller and the secondary impeller.

[0013] Optionally, the shell is provided with a suction inlet and a discharge outlet, the suction inlet is communicated with the accommodating cavity through a primary suction chamber, the discharge outlet is communicated with the accommodating cavity through a secondary discharge chamber, and the medium passes through the primary suction chamber, a primary discharge chamber, a transition flow channel, a secondary suction chamber in sequence and then enters the secondary discharge chamber to flow out.

[0014] Optionally, the accommodating cavity is provided with a transition flow channel, the primary suction chamber, the primary discharge chamber, the transition flow channel, the secondary suction chamber and the secondary discharge chamber are integrally formed, and the primary discharge chamber, the transition flow channel and the secondary suction chamber are geometrically symmetrical structures.

[0015] Optionally, the hydraulic turbine further comprises:

[0016] A first bearing component is sleeved on the first end of the rotor, and the first bearing component is located on the side of the first end cover away from the primary impeller;

[0017] A second bearing component is sleeved on the second end of the rotor, and the second bearing component is located on the side of the second end cover away from the secondary impeller;

[0018] The second end of the rotor protrudes from the end of the second bearing component, and a shaft coupling is connected to the second end of the rotor.

[0019] Optionally, the first bearing component and the rotor are connected through a pair of thrust ball bearings, and the pair of thrust ball bearings are arranged back to back; the second bearing component and the rotor are connected through a deep groove ball bearing.

[0020] Optionally, the first bearing component is isolated from the outside through a first bearing isolator on the side close to the first end cover; the second bearing component is isolated from the outside through a second bearing isolator at both ends respectively, and the deep groove ball bearing is located between the two second bearing isolators.

[0021] Optionally, mechanical seals are respectively arranged between the first end cover and the rotor and between the second end cover and the rotor.

[0022] Optionally, the hydraulic turbine further comprises:

[0023] An inter-stage component comprises a shaft sleeve and a bushing, the shaft sleeve is fixedly connected with the rotor, the bushing is arranged in the accommodating cavity of the shell, and the inter-stage component is arranged between the primary impeller and the secondary impeller.

[0024] Optionally, the bushing is provided with a first helical groove on one side thereof facing the sleeve, and the sleeve is provided with a second helical groove on one side thereof facing the bushing, the first helical groove and the second helical groove have the same structural parameters and opposite rotation directions.

[0025] Optionally, the shell is integrally formed.

[0026] The hydraulic turbine provided by the embodiment of the utility model, comprising a shell, and a rotor arranged in the shell, a primary impeller and a secondary impeller are fixedly sleeved on the rotor, the shell is used for accommodating at least part of the rotor, the primary impeller and the secondary impeller, therefore the diameter of two ports of the accommodating cavity is greater than the diameter of the primary impeller and the secondary impeller, in working, the first end cover and the second end cover are closed, when overhauling, the primary impeller, the secondary impeller and the rotor can be taken down to overhaul and maintain only by dismounting the first end cover and the second end cover, quick dismounting and mounting are realized, hydraulic energy is converted into mechanical energy through two-stage single-suction impellers, the structure is simple, manufacturing difficulty and cost are reduced, and economy is improved.

[0027] The above description is only a summary of the technical scheme of the application, in order to more clearly understand the technical means of the application, the application can be implemented according to the content of the specification, and in order to make the above and other purposes, characteristics and advantages of the application more obvious and easy to understand, the following specific embodiments of the application are described. BRIEF DESCRIPTION OF DRAWINGS

[0028] In order to more clearly illustrate the technical scheme in the embodiment of the utility model, the following will briefly introduce the drawings needed to be used in the embodiment description, obviously, the drawings in the following description are only some embodiments of the utility model, and for those skilled in the art, other drawings can also be obtained according to these drawings without creating labor.

[0029] Figure 1 It is a sectional view of the hydraulic turbine according to one embodiment of the utility model;

[0030] Figure 2a It is a schematic view of the shell according to one embodiment of the utility model;

[0031] Figure 2b It is Figure 2a It is a rotating sectional view of A-A-A of the embodiment shown;

[0032] Figure 2c It is Figure 2a It is a top view of the embodiment shown;

[0033] Figure 3 It is a schematic view of the interstage component according to one embodiment of the utility model;

[0034] Figure 4 It isFigure 3 enlarged view of the primary impeller of the embodiment shown;

[0035] Figure 5 for Figure 1 enlarged view of the primary impeller and the secondary impeller of the embodiment shown.

[0036] wherein, Figures 1 to 5 The correspondence between the reference signs and the component names in the drawings is as follows:

[0037] 100 hydraulic turbine, 110 casing, 111 suction inlet, 112 primary suction chamber, 113 discharge outlet, 114 secondary discharge chamber, 115 transition flow passage, 116 primary discharge chamber, 117 secondary suction chamber, 120 rotor, 121 primary impeller, 122 secondary impeller, 130 first end cover, 131 first mechanical seal, 140 second end cover, 141 second mechanical seal, 150 first bearing component, 151 thrust ball bearing, 152 first bearing spacer, 160 second bearing component, 161 deep groove ball bearing, 162 second bearing spacer, 170 inter-stage component, 171 shaft sleeve, 1711 second helical groove, 172 bushing, 1721 first helical groove, 180 pressure relief pipe, 191 balance hole, 192 cooling water cavity, 193 impeller outlet, 194 impeller front cover plate, 195 impeller rear cover plate. DETAILED DESCRIPTION

[0038] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all the other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0039] Before the embodiments of the present application are described in further detail, the orientation terms such as “upper”, “lower”, “lateral” in the embodiments of the present application do not have the meaning of limiting the scope of protection of the present application.

[0040] In order to make the technical solutions and advantages of the present application clearer, the embodiments of the present application will be described in further detail below with reference to the drawings.

[0041] Figure 1 is a sectional view of a hydraulic turbine according to an embodiment of the present application; Figure 2a is a schematic view of a casing according to an embodiment of the present application; Figure 2b is Figure 2a is a rotational sectional view of A-A-A of the embodiment shown; Figure 2c is Figure 2aa top view of the illustrated embodiment; Figure 5 To Figure 1 The illustrated embodiment provides an enlarged schematic view at the primary impeller and the secondary impeller.

[0042] As Figures 1 to 2c The utility model discloses an embodiment provides a hydraulic turbine 100, the hydraulic turbine 100 includes:

[0043] The shell 110 is equipped with the accommodation cavity in the shell 110;

[0044] The rotor 120 is arranged in the accommodation cavity in the middle section of the rotor 120, and the primary impeller 121 and the secondary impeller 122 are arranged on the rotor 120, and the primary impeller 121 and the secondary impeller 122 are mirror image arrangement;

[0045] The first end cover 130 is arranged at one end of the accommodation cavity, and the first end cover 130 is close to the side of the primary impeller 121;

[0046] The second end cover 140 is arranged at the other end of the accommodation cavity, and the second end cover 140 is close to the side of the secondary impeller 122;

[0047] Among them, the diameter of the two ends of the accommodation cavity is greater than the diameter of the primary impeller 121 and the secondary impeller 122.

[0048] It should be noted that the hydraulic turbine 100 includes the shell 110, and the rotor 120 arranged in the shell 110, and the primary impeller 121 and the secondary impeller 122 are fixedly sleeved on the rotor 120, and the shell 110 is used for accommodating at least part of the rotor 120, the primary impeller 121 and the secondary impeller 122, so that the diameter of the two ports of the accommodation cavity is greater than the diameter of the primary impeller 121 and the secondary impeller 122, and during operation, the first end cover 130 and the second end cover 140 are closed, and during maintenance, the primary impeller 121, the secondary impeller 122 and the rotor 120 can be removed for maintenance by only removing the first end cover 130 and the second end cover 140, realizing quick disassembly, converting hydraulic energy into mechanical energy through two-stage single-suction impellers, simple structure, reducing manufacturing difficulty and cost, improving economy, and being more suitable for small recovery power (≤100kW) demand.

[0049] Specifically, the first end cover 130 and the second end cover 140 are fixedly connected with the shell 110 through bolts, when maintenance is required, the bolts are loosened, the first end cover 130 and the second end cover 140 are removed from the shell 110, the primary impeller 121 is taken out from the side of the first end cover 130, the secondary impeller 122 is taken out from the side of the second end cover 140, and after the primary impeller 121 and the secondary impeller 122 are taken out, the rotor 120 can also be taken out from the shell 110, realizing maintenance of the parts in the shell 110, improving disassembly efficiency, and simple structure.

[0050] It should be noted that, as shown in Figure 5 The first-stage impeller 121 and the second-stage impeller 122 are arranged in a mirror image of the impeller outlet 193, and combined with the balance hole 191, which can achieve more than 95% of the axial force self-balancing, and the residual axial force is borne by the thrust ball bearing 151 at one end of the first bearing part 150. The two-stage impeller is arranged in a mirror image of the impeller outlet 193, which not only can achieve the axial force self-balancing of the hydraulic turbine 100, but also can shorten the axial length of the over-flow channel arranged in series, thereby reducing the complexity of the flow channel structure, being conducive to protecting the precision of the over-flow part, improving the uniformity of the liquid flow in the hydraulic turbine 100, and thereby improving the efficiency of the hydraulic turbine. In addition, if the two-stage impeller (the first-stage impeller 121 and the second-stage impeller 122) is arranged in series, a balance device needs to be added, which will increase the axial length of the rotor and increase the risk of instability of the rotor 120. It can be understood that the mirror image arrangement of the impeller outlet 193 means that the first-stage impeller 121 and the second-stage impeller 122 are the same in structure, and the two-stage impeller is arranged face to face with respect to the outlet, which is different from the usual arrangement of the impellers in series.

[0051] In addition, the axial force mainly comes from the front cover plate 194 and the rear cover plate 195 of the impeller, which are asymmetric in structure, and the force directed to the outlet of the turbine impeller generated by the different pressure and direction. The two-stage impeller is mirror arranged, so that the axial force of the first-stage impeller 121 directed to the right side and the axial force of the second-stage impeller 122 directed to the left side can be offset. After the axial force is balanced in structure, the balancing device for balancing the axial force does not need to be additionally arranged in structure, so that the product structure is simple. The transition flow passage 115 between the two-stage impellers is a communication passage of the first-stage pressure-out chamber 116 of the first-stage impeller 121 and the second-stage suction chamber 117 of the second-stage impeller 122. If the discharge flow passage of the outlet of the second-stage impeller 122, i.e., the second-stage pressure-out chamber 114, is arranged in series, it needs to be arranged on the right side of the second-stage impeller 122, so that the axial length and the complexity of the flow passage are increased. The two-stage impellers are mirror arranged, and the outlet 113 and the second-stage pressure-out chamber 114 can be arranged in the middle of the two-stage impellers, so that the overall structure is more compact, and the length of the rotor 120 is relatively shorter than that of the series arrangement. The flow passage generally refers to all the components through which the medium flows. Corresponding to the product, the flow passage includes the shell and the impeller, and the shell includes the first-stage pressure-out chamber 116, the second-stage suction chamber 117, the first-stage suction chamber 112, the transition flow passage 115 and the second-stage pressure-out chamber 114 in the accommodation cavity. The balance hole 191 communicates the flow passage in the impeller with the rear sealing cavity of the impeller. The structures of the two-stage impellers are completely the same, but the energy of the medium working on the inlet of the two-stage impellers is slightly different, i.e., the pressure drop of the medium after passing through the first-stage impeller 121 is not completely the same as the pressure drop of the medium after passing through the second-stage impeller 122, so that the axial forces of the two-stage impellers are different in size. At this time, the balance hole 191 needs to be arranged to adjust the pressure of the flow passage in the impeller and the side of the second end cover 140, so that the axial forces of the two-stage impellers are basically the same in size and opposite in direction, and the self-balance of the axial force is realized.

[0052] For example, the sealing cavity and the first end cover 130 and the second end cover 140 are integrally cast, a canned mechanical seal is adopted, and a cooling water cavity 192 is arranged, for example, if the temperature of the conveying liquid medium exceeds 66°C, cooling water can be selected to be used for cooling, and if the conveying liquid medium needs to be kept warm, low-pressure steam or other heat preservation medium can be introduced. The first end cover 130 of the rotor 120 is provided with a pressure relief pipe 180, which is in communication with the outlet 113 of the hydraulic turbine 100, so as to reduce the pressure of the high-pressure side sealing cavity, solve the problem of short service life of the mechanical seal due to high pressure of the sealing cavity of the hydraulic turbine 100, that is, the reliability and stability of the pressure of the hydraulic turbine 100 during operation can be ensured, and the service life of the mechanical seal can be improved. It can be understood that because the first end cover 130 side belongs to the high-pressure side, in order to reduce the pressure of the sealing cavity and protect the mechanical seal, the pressure relief pipe 180 is arranged in communication with the outlet 113 of the hydraulic turbine 100, and the pressure of the outlet of the hydraulic turbine 100 is low, which plays a role in pressure relief.

[0053] Exemplarily, the first mechanical seal 131 is arranged between the first end cover 130 and the rotor 120, and the second mechanical seal 141 is arranged between the second end cover 140 and the rotor 120. The mechanical seals can improve the sealing performance of the first end cover 130 and the second end cover 140 and the rotor 120, reduce the liquid leakage, and ensure the efficiency of the hydraulic turbine 100.

[0054] In an available embodiment, the housing 110 is provided with the suction inlet 111 and the discharge outlet 113. The suction inlet 111 is communicated with the containing cavity through the primary suction chamber 112, and the discharge outlet 113 is communicated with the containing cavity through the secondary pressure outlet chamber 114. The medium flows out through the primary pressure outlet chamber 116, the transition flow passage 115, the secondary suction chamber 117, and then the secondary pressure outlet chamber 114 in sequence.

[0055] It should be noted that the housing is an integrated casting including the primary suction chamber 112, the primary pressure outlet chamber 116, the transition flow passage 115, the secondary suction chamber 117, and the secondary pressure outlet chamber 114. The medium directly enters the primary impeller through the primary suction chamber 112, and then flows out through the primary pressure outlet chamber 116, the transition flow passage 115, the secondary suction chamber 117, and then the secondary pressure outlet chamber 114 in sequence. Figure 2c It can be seen that the discharge outlet 113 and the suction inlet 111 are not coincident in the axial direction, and there is a certain offset distance.

[0056] The suction inlet 111 is communicated with the containing cavity through the primary suction chamber 112, and the suction inlet 111 is located at one end of the primary suction chamber 112 away from the containing cavity. The discharge outlet 113 is communicated with the containing cavity through the secondary pressure outlet chamber 114, and the discharge outlet 113 is located at one side of the secondary pressure outlet chamber 114 away from the containing cavity. The primary suction chamber 112 and the secondary pressure outlet chamber 114 are vertically arranged with the rotor 120. The suction inlet 111 and the discharge outlet 113 are connected with the system pipeline through the flanges, respectively.

[0057] It should be noted that the containing cavity of the housing 110 forms a flow passage, and the primary suction chamber 112 and the secondary suction chamber 117 are both symmetrical double-volute structures, which can realize the self-balancing of the radial force of the hydraulic turbine 100. When the rotor 120 is unevenly stressed in the circumferential direction, i.e., the radial force is generated in a certain direction in a certain area of the circumference, especially when the working condition deviates, the radial force is more prominent. For the turbine working condition, the medium flows into the rotor 120 from the primary suction chamber 112 to drive the rotor 120 to rotate, realizing the conversion of pressure energy into mechanical energy. The single-volute inlet structure is a circumferentially asymmetric geometric structure, which can cause high non-uniformity of the medium pressure and velocity in the circumferential direction of the impeller inlet. The rotor 120 needs to bear a large radial force. The use of the circumferentially symmetrical double-volute structure can greatly improve the uniformity of the medium pressure and velocity distribution in the circumferential direction of the impeller inlet. Under the optimal working condition, the radial force can be balanced, and under the non-optimal working condition, the radial force under the deviation of the working condition can be reduced.

[0058] In one possible implementation, as shown in Figure 2b The primary suction chamber 112, the primary discharge chamber 116, the transition flow passage 115, the secondary suction chamber 117 and the secondary discharge chamber 114 are integrally formed. The primary suction chamber 112, the primary discharge chamber 116, the transition flow passage 115 and the secondary suction chamber 117 are geometrically symmetrical structures.

[0059] The transition flow passage 115 is integrally formed by an internal flow passage, and the two branches are symmetrically distributed. The primary impeller 121 is axially installed into the housing 110 from the position of the first end cover 130, and the secondary impeller 122 is axially installed into the housing 110 from the position of the second end cover 140. The impellers are limited in the axial direction by the shaft shoulder and the shaft sleeve, and are connected in the radial direction by the key and the shaft, which will not be described again. In the internal flow passage, the medium passes through the primary suction chamber 112, the primary impeller 121 (in the primary discharge chamber 116), the transition flow passage 115, the secondary impeller 122 (in the secondary suction chamber 117) and the secondary discharge chamber 114 to form a continuous flow passage.

[0060] The primary suction chamber 112, the secondary discharge chamber 114 and the transition flow passage 115 on the housing 110 are integrally formed by casting. The casting process can pour molten metal into a casting mold that is adapted to the shape of the part, so that a complex-shaped part blank or part can be produced, which can ensure the accuracy of the transition flow passage 115 and is conducive to ensuring the efficiency of the hydraulic turbine 100. At the same time, since only one primary impeller 121 and one secondary impeller 122 are used to realize the function of the hydraulic turbine 100, the structure of the accommodation chamber is simpler, so that the difficulty of casting processing is reduced.

[0061] It should be noted that the integrally formed housing 110 can also avoid the fitting deviation of the combined housing, reduce the number of parts, thereby reducing the cumulative deviation between the parts, and reducing the processing procedures and working hours of the parts, thereby reducing the manufacturing cost of the hydraulic turbine 100, and also improving the running stability and flow uniformity of the hydraulic turbine 100.

[0062] Additionally, the cross-sectional area, the cross-sectional shape of the primary suction chamber 112 and the secondary suction chamber 117, the diffusion degree of the suction diffusion pipe, i.e. the starting angle of the tongue, and / or the change of the inlet blade angle of the impeller to match the outlet angle of the water inlet chamber can be optimized and improved, and the flow loss of the flow components can be minimized through multiple circulation iterations and multi-dimensional matching to ensure the high efficiency of the hydraulic turbine 100.

[0063] Wherein, the cross-sectional area and the cross-sectional shape refer to the cross-sectional area and the cross-sectional shape of the flow passage of the suction chamber (water inlet chamber). For the hydraulic turbine 100, the water inlet chamber is not only a through-flow component, but also a crucial functional component. The matching of the pressure, velocity, velocity direction, and outflow direction of the outlet medium of the water inlet chamber with the inlet of the impeller is a key factor determining the recovery performance of the hydraulic turbine 100. The size of the flow area will affect the flow velocity of the medium in the suction chamber. Different flow velocities and cross-sectional shapes will result in different losses of the medium in the suction chamber. Different parameters need to be matched according to the principle of minimum loss. The diffuser pipe is part of the suction chamber, which refers to the part from the flange of the suction inlet 111 to the tongue of the water inlet chamber. The diffuser degree refers to the degree of diffusion (degree of area change) from the inlet to the outlet of the diffusion section. The starting angle of the tongue refers to the angle between the position of the tongue and the eighth cross section of the suction chamber. The inlet angle of the impeller refers to the angle of the blade at the inlet of the impeller (the end away from the rotor 120). The water outlet angle of the suction chamber refers to the angle of the medium flowing out of the suction chamber and into the impeller. If the two angles are well matched, the medium flowing out of the suction chamber and into the impeller will be smooth, and the impact and vortex losses will be small, which is beneficial to improving the efficiency of the hydraulic turbine 100. These two angles need to be adjusted and matched in different working conditions by observing the CFD flow field state, and gradually approach the best matching state. Because there are several geometric parameters that affect the performance of the hydraulic turbine 100, such as the cross-sectional area of the suction chamber, the diffuser degree of the diffuser pipe, the starting angle of the tongue, the inlet angle of the impeller, the flow area of the impeller, and the blade profile, etc. all of which affect the performance of the hydraulic turbine 100, multiple parameters, i.e. multi-dimensional cross-circulation matching, are required to obtain the most suitable matching form. The flow component refers to all components through which the medium flows, such as the first-stage suction chamber 112, the first-stage impeller 121, the transition flow passage 115, the second-stage impeller 122, and the second-stage pressure outlet chamber 114.

[0064] In a feasible implementation, the hydraulic turbine 100 further comprises:

[0065] The first bearing component 150 is sleeved on the first end of the rotor 120, and the first bearing component 150 is located on the side of the first end cover 130 away from the first-stage impeller 121.

[0066] The second bearing component 160 is sleeved on the second end of the rotor 120, and the second bearing component 160 is located on the side of the second end cover 140 away from the second-stage impeller 122.

[0067] The second end of the rotor 120 protrudes from the end of the second bearing component 160, and the second end of the rotor 120 is connected with the shaft coupling.

[0068] The first bearing part 150 is arranged at the first end of the rotor 120 and located at the side of the first end cover 130 away from the primary impeller 121, and the first bearing part 150 is fixedly connected with the first end cover 130 through bolts. Similarly, the second bearing part 160 is arranged at the second end of the rotor 120 and located at the side of the second end cover 140 away from the secondary impeller 122, and the second bearing part 160 is fixedly connected with the second end cover 140 through bolts. The primary impeller 121 can be taken out from the accommodating cavity by first removing the first bearing part 150 and then removing the first end cover 130 at the first end of the rotor 120, and the secondary impeller 122 can be taken out from the accommodating cavity by first removing the second bearing part 160 and then removing the second end cover 140 at the second end of the rotor 120, and finally the rotor 120 can be removed from the casing 110, so that the convenience and efficiency of disassembly and assembly of the hydraulic turbine 100 are realized.

[0069] It should be noted that the second end of the rotor 120 passes through the second bearing part 160 away from the side of the second end cover 140, and the rotor 120 extending out of the second bearing part 160 is provided with a shaft coupling. The liquid enters the accommodating cavity through the suction port 111, drives the impeller to rotate and then drives the rotor 120 to rotate, the second end of the extended rotor 120 is connected with other components requiring rotary force, so as to realize the purpose of converting hydraulic energy into mechanical energy, and the driven liquid is discharged through the discharge port 113.

[0070] For example, in the embodiment, the first bearing part 150 and the second bearing part 160 adopt a cast steel structure, are fixed on the first end cover 130 and the second end cover 140 respectively by positioning and bolting, the first bearing part 150 adopts an oil slinger lubrication, and the outer sides of the first bearing part 150 and the second bearing part 160 are respectively cast with heat dissipation fins, so that the heat dissipation area is increased, the bearing temperature is reduced, and the service life of the bearing is prolonged.

[0071] In a feasible embodiment, the first bearing part 150 and the rotor 120 are connected through a pair of thrust ball bearings 151 arranged back to back, and the second bearing part 160 and the rotor 120 are connected through a deep groove ball bearing 161.

[0072] The thrust ball bearing 151 can bear axial load, the primary impeller 121 and the secondary impeller 122 adopt the structure form of mirror image arrangement of discharge ports, and in combination with the balance hole 191, more than 95% of axial force can be self-balanced, and the residual axial force is borne by the thrust ball bearing 151 at one end of the first bearing part 150; meanwhile, the thrust ball bearing 151 also has the aligning performance, can reduce the installation error, and improves the bearing capacity of the axial force. The second end of the rotor 120 needs to be connected with the shaft coupling, so the second bearing part 160 is needed to bear the axial and radial load, the deep groove ball bearing 161 can be adopted to meet the requirement, and the balanced load distribution can not only prolong the service life of the bearing, but also improve the efficiency and stability of the output rotary force.

[0073] It should be noted that the thrust ball bearing 151 and the deep groove ball bearing 161 are both lubricated by the oil slinger, and the lubrication can also play a certain heat dissipation effect.

[0074] In a possible implementation, the first bearing part 150 is isolated from the outside through the first bearing isolator 152 on the side close to the first end cover 130; the two ends of the second bearing part 160 are isolated from the outside through the second bearing isolator 162 respectively, and the deep groove ball bearing 161 is located between the two second bearing isolators 162.

[0075] The first end of the rotor 120 does not protrude from the first bearing part 150, so the first end of the first bearing part 150 close to the first end cover 130 is connected with the rotor 120 through a first bearing isolator 152, and the second end of the rotor 120 protrudes from the second bearing part 160, so the two ends of the second bearing part 160 in contact with the rotor 120 are connected with the rotor 120 through the second bearing isolator 162. The bearing isolator replaces the existing copper skeleton type oil seal, can avoid the situation that the oil seal causes the lubricating oil to overflow due to long-term dynamic and static friction, and thus improves the sealing performance of the hydraulic turbine 100, prolongs the service life of the bearing of the hydraulic turbine 100, and reduces the maintenance cost.

[0076] Figure 3 It is a schematic view of the inter-stage part according to an embodiment of the present application; Figure 4 It is a schematic view of the hydraulic turbine according to an embodiment of the present application. Figure 3 It is an enlarged schematic view of A in the embodiment shown.

[0077] In a possible implementation, as shown in Figure 3 and Figure 4 The hydraulic turbine 100 further comprises:

[0078] The inter-stage part 170 comprises a shaft sleeve 171 and a bushing 172, the shaft sleeve 171 is fixedly connected with the rotor 120, the bushing 172 is arranged in the accommodating cavity of the casing 110, and the inter-stage part 170 is arranged between the primary impeller 121 and the secondary impeller 122.

[0079] The inter-stage component 170 can isolate the primary impeller 121 and the secondary impeller 122, i.e., the sealing effect between the two stages, and limit the primary impeller 121 and the secondary impeller 122, thereby improving the stability and reliability of the primary impeller 121 and the secondary impeller 122.

[0080] In an available embodiment, the bushing 172 is provided with a first spiral groove 1721 on the side facing the shaft sleeve 171, and the shaft sleeve 171 is provided with a second spiral groove 1711 on the side facing the bushing 172, and the structural parameters of the first spiral groove 1721 and the second spiral groove 1711 are the same, and the rotation directions are opposite.

[0081] In the embodiment, the bushing 172 is provided with a first spiral groove 1721 on the side facing the shaft sleeve 171, and the shaft sleeve 171 is provided with a second spiral groove 1711 on the side facing the bushing 172, and the surfaces of the bushing 172 and the shaft sleeve 171 are surface-hardened with anti-seizure hard alloy steel. Such a design can effectively reduce the minimum radial gap between the shaft sleeve 171 and the bushing 172, reduce the leakage area, reduce the leakage between the two stages, and improve the efficiency of the hydraulic turbine 100. The first spiral groove 1721 and the second spiral groove 1711 can also prevent the shaft from being clamped due to the reduction of the radial gap. The surface-hardened anti-seizure hard alloy can reduce the probability of seizure.

[0082] It can be understood that seizure refers to the phenomenon that the rotating part and the static part are clamped, causing the rotor 120 to be unable to rotate normally. In the embodiment, the bushing 172 is considered as a static part, and the shaft sleeve 171 is considered as a rotating part. Under normal circumstances, there is a certain gap between the two, and they can rotate normally. During the operation of the hydraulic turbine 100, the medium flowing through the rotating and static parts will have a certain temperature rise, especially when high-temperature medium is transported. The heat of the medium will be transferred to the rotating and static parts. Due to differences in shape, material, and other factors, the parts will expand differently. At this time, if the gap between the two is less than the expansion amount, the two will be clamped, i.e., the shaft sleeve 171 and the bushing 172 will stick together, and the rotor 120 will not rotate normally, resulting in the phenomenon of shaft clamping. If the gap between the two is set to be large in order to prevent seizure, the leakage between the two stages will inevitably increase, the volumetric loss of the hydraulic turbine 100 will increase, and the efficiency will decrease.

[0083] Therefore, in the present application, a small gap design (to reduce the leakage) is adopted between the shaft sleeve 171 and the bushing 172, and anti-seizure hard alloy steel is surface-hardened on the outer circle of the shaft sleeve 172 and the inner circle of the bushing 171. On the one hand, the heat is not easy to expand, and on the other hand, it is not easy to stick together, thereby reducing the risk of shaft clamping.

[0084] It should be noted that the first spiral groove 1721 and the second spiral groove 1711 can also play a throttling role. When the hydraulic turbine 100 rotates clockwise from the shaft coupling end (the second end of the rotor 120), the inner hole of the bushing 172 is the first spiral groove 1721, and the rotation direction of the hydraulic turbine 100 is the same, and the second spiral groove 1711 on the surface of the shaft sleeve 171 is opposite to the rotation direction of the hydraulic turbine 100. The spiral groove structure parameters of the bushing 172 and the shaft sleeve 171 are the same, and the pumping effect generated when the shaft sleeve 171 rotates is used to achieve better sealing effect, which greatly reduces the influence of inter-stage leakage on the performance of the hydraulic turbine 100. The rotation direction of the hydraulic turbine 100 is the rotation direction of the rotor 120, and the shaft sleeve 171 and the rotor 120 rotate together. The spiral groove is machined on the outer surface of the shaft sleeve 171, and the spiral groove itself is stationary relative to the shaft sleeve 171. The spiral grooves are machined on the inner circle of the stationary part bushing 172 and the outer circle of the rotating part shaft sleeve 171, and the rotation directions of the two spiral grooves are opposite. When the shaft sleeve 171 rotates with the rotor 120, it is equivalent to a stationary spiral groove on the bushing 172 cooperating with a spiral groove on the shaft sleeve 171 in the opposite direction, and the two cooperate to seal and play a good joint throttling role. That is, the cooperation of the two opposite spiral grooves can better prevent the medium from leaking from the high-pressure side to the low-pressure side.

[0085] For example, through CFD analysis and calculation, the leakage of the first spiral groove 1721 and the second spiral groove 1711 of the present application can be reduced by 19.6% to 32.3% compared with the leakage of the inter-stage component 170. That is, the improvement of the inter-stage component 170 of the present application has obvious progress, which can efficiently improve the efficiency of the hydraulic turbine 100. CFD is the abbreviation of computational fluid dynamics, that is, the numerical simulation calculation. The gap between the shaft sleeve 171 and the bushing 172, that is, the fluid domain, is made into a three-dimensional model, and the three-dimensional model is made into a grid model. According to the actual parameters (such as pressure) and boundary conditions (such as rotation or static, given speed, etc.), the actual situation is simulated and calculated by using CFD calculation software numeca. The leakage under different conditions can be calculated and verified.

[0086] As can be seen from the above, the hydraulic turbine 100 of the present application can solve the problems of high investment cost, complex structure, small recovered energy and the like of the existing products, has the effects of compact structure, few parts, small installation size and low manufacturing cost, and greatly reduces the leakage, improves the liquid recovery efficiency and the efficiency of the hydraulic turbine 100.

[0087] In the present application, the terms "first" and "second" are only used for description purposes, and cannot be understood as indicating or implying relative importance. The term "a plurality of" means two or more, unless otherwise clearly limited.

[0088] Other embodiments of the present application will be apparent to those skilled in the art from consideration of the specification and practice of the application disclosed herein. It is intended that the present application cover any and all variations of the application that come within the scope of the general inventive concepts described herein and including all modifications, equivalent processes, and / or uses for which the present application pertains. The specification and examples are to be considered exemplary only.

[0089] The above merely preferred embodiments of the present application and are not intended to limit the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A hydraulic turbine, characterized in that The hydraulic turbine comprises: a shell, which is internally provided with a containing cavity; a rotor, a middle section of which is arranged in the containing cavity, and which is provided with a primary impeller and a secondary impeller, the primary impeller and the secondary impeller being arranged in mirror image; a first end cover, which is arranged at one end of the containing cavity and is close to one side of the primary impeller; a second end cover, which is arranged at the other end of the containing cavity and is close to one side of the secondary impeller; wherein the diameters of the two ends of the containing cavity are greater than the diameters of the primary impeller and the secondary impeller.

2. The hydraulic turbine according to claim 1, characterized in that The shell is provided with an inlet and an outlet, the inlet is communicated with the containing cavity through a primary suction chamber, the outlet is communicated with the containing cavity through a secondary pressure chamber, and the medium passes through the primary suction chamber, a primary pressure chamber, a transition flow channel, a secondary suction chamber in sequence and then enters the secondary pressure chamber to flow out.

3. The hydraulic turbine according to claim 2, characterized in that The primary suction chamber, the primary pressure chamber, the transition flow channel, the secondary suction chamber and the secondary pressure chamber are integrally formed, and the primary pressure chamber, the transition flow channel and the secondary suction chamber are all geometrically symmetrical structures.

4. The hydraulic turbine according to claim 1, characterized in that The hydraulic turbine further comprises: a first bearing component, which is sleeved on a first end of the rotor and is located on a side of the first end cover away from the primary impeller; a second bearing component, which is sleeved on a second end of the rotor and is located on a side of the second end cover away from the secondary impeller; the second end of the rotor extends out of an end of the second bearing component, and a coupling is connected to the second end of the rotor.

5. The hydraulic turbine according to claim 4, characterized in that The first bearing component and the rotor are connected through a pair of thrust ball bearings, and the pair of thrust ball bearings are arranged back to back; the second bearing component and the rotor are connected through a deep groove ball bearing.

6. The hydraulic turbine according to claim 5, characterized in that The first bearing component is isolated from the outside through a first bearing isolator on a side close to the first end cover; the second bearing component is isolated from the outside through a second bearing isolator on each end, and the deep groove ball bearing is located between the two second bearing isolators.

7. The hydraulic turbine according to claim 1, characterized in that A first mechanical seal is arranged between the first end cover and the rotor, and a second mechanical seal is arranged between the second end cover and the rotor.

8. The hydraulic turbine of claim 1, wherein, The hydraulic turbine further comprises: an inter-stage component, which comprises a shaft sleeve and a bushing, the shaft sleeve is fixedly connected with the rotor, and the bushing is arranged in the containing cavity of the shell, and the inter-stage component is arranged between the primary impeller and the secondary impeller.

9. The hydraulic turbine according to claim 8, characterized in that A first helical groove is arranged on a side of the bushing facing the shaft sleeve, a second helical groove is arranged on a side of the shaft sleeve facing the bushing, the structure parameters of the first helical groove and the second helical groove are the same, and the rotation directions thereof are opposite.

10. The hydraulic turbine according to any one of claims 1 to 9, characterized in that The shell is integrally formed.

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