CN219452279U - Pipeline type water pump water turbine - Google Patents
Pipeline type water pump water turbine Download PDFInfo
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- CN219452279U CN219452279U CN202320603733.9U CN202320603733U CN219452279U CN 219452279 U CN219452279 U CN 219452279U CN 202320603733 U CN202320603733 U CN 202320603733U CN 219452279 U CN219452279 U CN 219452279U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
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Abstract
The utility model discloses a pipeline type water pump water turbine, which belongs to the field of hydroelectric generation and aims to solve the problem of frequency fluctuation in a micro-grid because water flows to an impeller of the water pump water turbine through turning. The device comprises a high-pressure section, a rotating part assembly, an impeller cavity section and a low-pressure section; the high-pressure section comprises an outer pressure bearing piece and an inner pressure bearing piece which are coaxially sleeved, and an annular flow channel is formed between the inner pressure bearing piece and the outer pressure bearing piece; the high-pressure section, the impeller cavity section and the low-pressure section are sequentially connected rightward, the high-pressure section comprises an outer pressure bearing part and an inner pressure bearing part which are coaxially sleeved, the outer pressure bearing part is a hollow revolving body which axially and continuously changes, the inner pressure bearing part is a right opening hollow revolving body which axially and continuously changes, and the rotating part assembly comprises an impeller and a main shaft; the main shaft rotates and sets up in the interior pressure-bearing piece, and the main shaft links to each other with the impeller, and the impeller is located the impeller chamber section. The utility model has the characteristic of flowing along the rotation axis of the impeller, so that the flow velocity of water flow is uniform and no rotation exists, and the stability of the water pump turbine is improved.
Description
Technical Field
The utility model belongs to the field of hydroelectric generation, and particularly relates to a pipeline type water pump turbine.
Background
The micro-grid is a small power generation and distribution system consisting of a distributed power generation system, an energy storage system, related loads and a monitoring protection system. The micro-grid can be operated in parallel with other grids, and can also be independently operated. Compared with the traditional wide-area power system, in the power supply structure of the novel local power system represented by the micro-grid, the novel energy source duty ratio of photovoltaic, wind power and the like is gradually improved, so that the micro-grid has obvious randomness, volatility and intermittence characteristics, and the difficulty of realizing the flexible controllable and safe and stable operation requirements of the micro-grid due to the reduction of the inertia of the grid system is further improved.
The system inertia of the power grid is determined by the number and capacity of the on-grid synchronous motors, and the overall kinetic energy of the system synchronous units is determined. Generally, the larger the capacity of the power grid, the more synchronous rotation inertial devices, the larger the system inertia of the power grid, and the stronger the frequency modulation capability of the power grid. One prominent feature of micro-grids is that the grid capacity is small and the new and renewable energy source occupancy is much larger than traditional wide area grids. The new energy sources such as photovoltaic power generation and wind power generation have higher occupation ratio in the micro-grid and do not provide system inertia for the grid, accordingly, the total capacity and the occupation ratio of the synchronous generator in the micro-grid are reduced, the system inertia of the micro-grid is reduced, and the frequency modulation capability of the micro-grid is directly influenced.
The system inertia of the grid is typically expressed in terms of the kinetic energy stored as the synchronous generator rotor rotates and thus describes the energy change caused by the change in rotational speed of the synchronous generator set as a power imbalance disturbance occurs in the grid system. For the micro-grid, because the capacity and the system inertia of the grid are small and the self-regulation capacity is limited, after a new energy unit suddenly drops off or the power demand suddenly increases and the power shortage occurs, the system inertia of the grid shows the trend of releasing the stored kinetic energy, the electromagnetic power of a synchronous generator unit in the micro-grid system is suddenly changed, the mechanical power of the synchronous generator unit is unchanged, a rotor is changed according to a rotor motion equation under the action of unbalanced torque, and the rotational speed is reduced to release the kinetic energy, so that the frequency of the micro-grid system is obviously reduced; after the new energy unit suddenly increases power generation or the power consumption demand suddenly decreases and power surplus occurs, the system inertia of the power grid presents a trend of absorbing energy, and the electromagnetic power of the synchronous generator unit in the micro-grid system can accumulate the surplus energy as the rotation potential energy of the unit, so that the rotation speed of the synchronous generator unit is suddenly increased, and the frequency of the micro-grid system is obviously increased. The micro-grid can cause the change of system frequency when power unbalance disturbance occurs due to the limitation of capacity and system inertia, and the power supply power quality of the micro-grid is directly affected.
The power imbalance of the micro-grid system can cause the frequency of the whole grid to change, and the fluctuation change of the input/output energy of the pumped storage unit with the functions of generating power and loading is one of the main reasons for the frequency change of the system during the operation process. Because of the limitation of the structure of the traditional water pump turbine, the incoming flow direction of the traditional water pump turbine is perpendicular to the direction of the rotation axis of the unit, and the water flow enters the impeller of the water pump turbine after a 90-degree sharp turn no matter in the power generation working condition or the pumping working condition. The water energy converted by the water pump hydroturbine presents a fluctuation state, and finally, the electric energy input/output by the generator motor to the micro-grid also fluctuates correspondingly, so that the frequency fluctuation in the micro-grid is caused.
Disclosure of Invention
The utility model aims to provide a pipeline type water pump turbine so as to solve the problem that the frequency in a micro-grid fluctuates due to the fact that water flow flows to an impeller of the water pump turbine after turning and the water energy converted by the water pump turbine shows a fluctuation state. The technical scheme adopted by the utility model is as follows:
a pipeline type water pump water turbine comprises a high-pressure section, a rotating part assembly, an impeller cavity section and a low-pressure section;
the high-pressure section comprises an outer pressure bearing piece and an inner pressure bearing piece, the outer pressure bearing piece and the inner pressure bearing piece are coaxially sleeved through a plurality of fixed guide vanes, and an annular flow passage is formed between the inner pressure bearing piece and the outer pressure bearing piece;
the outer pressure bearing piece, the impeller cavity section and the low-pressure section are sequentially connected to the right to form a hollow revolving body with axial continuous change, the outer pressure bearing piece comprises an inlet pipe section, a straight pipe section and a contracted pipe section which are sequentially connected to the right, the inlet pipe section is monotonously changed along the axial direction, the contracted pipe section is monotonously converged to the right, and the low-pressure section is monotonously diffused to the right;
the inner pressure bearing piece is a right-opening hollow revolving body with an axial continuous change and comprises a rectifying shell section, a straight shell section, a first shrinkage shell section, a conical shell section and a second shrinkage shell section which are sequentially connected rightward, wherein the rectifying shell section is monotonously diffused rightward, the first shrinkage shell section, the conical shell section and the second shrinkage shell section are monotonously converged rightward, and the annular flow passage area at the rectifying shell section is monotonously reduced rightward;
the rotating part assembly comprises an impeller, a main shaft and a generator rotor; the main shaft rotates and sets up in the interior pressure bearing piece, has cup jointed the generator rotor on the main shaft, and the right-hand member of main shaft links to each other with the impeller, is provided with sealedly between impeller or main shaft and the interior pressure bearing piece, is equipped with a plurality of blades on the impeller, and the top of a plurality of blades links to each other through the ring, and a plurality of blades are located the impeller chamber section.
Further, the inlet pipe section is one of a straight pipe, a tapered pipe which converges monotonically to the right, or a tapered pipe which converges monotonically to the left.
Further, the number of the fixed guide vanes is more than or equal to 2.
Further, the number of the blades is 2 or more.
Further, the two ends of the main shaft are respectively connected with the inner pressure-bearing piece through a bearing A and a bearing B.
Further, the straight tube section is omitted, and the inlet tube section is connected with the contracted tube section.
Further, the straight shell section is omitted, and the rectifying shell section is connected with the first shrinkage shell section.
Further, the cone shell section is omitted and the first shrink shell section is connected with the second shrink shell section.
Further, the second shrink wrap section is omitted.
Compared with the prior art, the utility model has the beneficial effects that:
1. the pipeline type water pump water turbine disclosed by the utility model has the characteristic of flowing along the axis of the impeller rotation shaft under two working conditions of the water turbine and the water pump, so that the water flow can flow uniformly and non-rotatably to the impeller as much as possible, the stability of the water pump water turbine is improved to the greatest extent, and the frequency fluctuation in a micro-grid is avoided.
2. The uniformity of the incoming flow velocity of the water turbine of the water pump turbine and the working condition of the water pump is improved;
3. the tangential speed of the incoming flow of the working condition of the water turbine of the water pump turbine is obviously reduced, and the rotation degree of the incoming flow is greatly reduced;
4. the secondary reflux condition of the incoming flow of the water pump working condition of the water pump turbine is improved.
Drawings
FIG. 1 is a front view of the present utility model;
FIG. 2 is a schematic diagram of the flow of water under the working condition of a conventional pump turbine;
FIG. 3 is a schematic diagram of the flow of water inside the volute under the working condition of a conventional pump turbine;
FIG. 4 is a schematic diagram of the flow of the incoming water under the working condition of a conventional pump turbine;
FIG. 5 is a schematic diagram of the flow of water under the working condition of a water pump of a conventional water pump turbine;
FIG. 6 is a diagram showing the flow of water from a conventional pump turbine under a pump condition;
FIG. 7 is a schematic diagram of the flow of water under turbine operating conditions according to the present utility model;
FIG. 8 is a schematic diagram of the water flow under the working condition of the water pump according to the present utility model;
FIG. 9 is a schematic diagram of the rectangular coordinate system set in the present utility model;
FIG. 10 is a cross-sectional view of the high pressure section of the present utility model;
fig. 11 shows a looped impeller.
In the figure: 1-high pressure section, 11-outer bearing, 111-inlet pipe section, 112-straight pipe section, 113-contracted pipe section, 12-inner bearing, 121-rectifying shell section, 122-straight shell section, 123-first contracted shell section, 124-cone shell section, 125-second contracted shell section, 13-fixed guide vane, 2-rotating part assembly, 21-impeller, 211-blade, 212-ring, 22-seal, 23-bearing A, 24-main shaft, 25-generator rotor, 26-bearing B, 3-impeller cavity section, 4-low pressure section, 5-volute, 6-draft tube.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present utility model more apparent, the present utility model is described below by means of specific embodiments shown in the accompanying drawings. It should be understood that the description is only illustrative and is not intended to limit the scope of the utility model. In addition, in the following description, descriptions of well-known structures and techniques are omitted so as not to unnecessarily obscure the present utility model.
The connection mentioned in the utility model is divided into fixed connection and detachable connection, wherein the fixed connection is a conventional fixed connection mode such as folding connection, rivet connection, bonding connection, welding connection and the like, the detachable connection comprises a conventional detachable mode such as bolt connection, buckle connection, pin connection, hinge connection and the like, and when a specific connection mode is not limited, at least one connection mode can be found in the conventional connection mode by default to realize the function, and the person skilled in the art can select the function according to the needs. For example: the fixed connection is welded connection, and the detachable connection is bolted connection.
The present utility model will be described in further detail below with reference to the accompanying drawings, the following examples being illustrative of the present utility model and the present utility model is not limited to the following examples.
Embodiment one: as shown in fig. 1 to 11, a pipeline type water pump turbine comprises a high-pressure section 1, a rotating part assembly 2, an impeller cavity section 3 and a low-pressure section 4;
the high-pressure section 1 comprises an outer pressure bearing piece 11 and an inner pressure bearing piece 12, wherein the outer pressure bearing piece 11 and the inner pressure bearing piece 12 are coaxially sleeved through a plurality of fixed guide vanes 13, and an annular flow passage is formed between the inner pressure bearing piece 12 and the outer pressure bearing piece 11;
the outer pressure bearing part 11, the impeller cavity section 3 and the low pressure section 4 are sequentially connected rightward to form a hollow revolving body with axial continuous change, the outer pressure bearing part 11 comprises an inlet pipe section 111, a straight pipe section 112 and a contracted pipe section 113 which are sequentially connected rightward, the inlet pipe section 111 is monotonously changed along the axial direction, the contracted pipe section 113 is monotonously converged rightward, the middle part of the impeller cavity section 3 is inwardly converged, and the low pressure section 4 is monotonously diffused rightward;
the inner pressure-bearing piece 12 is a right-opening hollow revolving body with continuously changing axial direction and comprises a rectifying shell section 121, a straight shell section 122, a first shrinkage shell section 123, a cone shell section 124 and a second shrinkage shell section 125 which are sequentially connected rightward, wherein the rectifying shell section 121 is monotonically diffused rightward, the first shrinkage shell section 123, the cone shell section 124 and the second shrinkage shell section 125 are monotonically converged rightward, and the annular flow passage area at the rectifying shell section 121 is monotonically reduced rightward;
the rotating part assembly 2 comprises an impeller 21, a main shaft 24 and a generator rotor 25; the main shaft 24 is rotatably arranged in the inner pressure bearing piece 12, the main shaft 24 is sleeved with the generator rotor 25, the right end of the main shaft 24 is connected with the impeller 21, a seal 22 is arranged between the impeller 21 or the main shaft 24 and the inner pressure bearing piece 12, a plurality of blades 211 are arranged on the impeller 21, the top ends of the blades 211 are connected through a ring 212, and the blades 211 are positioned in the impeller cavity section 3.
The inlet pipe section 111 is one of a straight pipe, a tapered pipe that converges monotonically to the right, or a tapered pipe that converges monotonically to the left.
The number of the fixed guide vanes 13 is 2 or more.
The number of the blades 211 is 2 or more.
The two ends of the main shaft 24 are respectively connected with the inner pressure-bearing member 12 through a bearing A23 and a bearing B26.
When the device is used as a water turbine, water flow flows from a high-pressure section 1 to a low-pressure section 4, the water energy is converted into mechanical energy to generate electricity, and when the device is used as a water pump, a magnetic field generated by an electromagnetic coil is used for driving a generator rotor 25 to rotate, so that an impeller 21 is driven to rotate, and the water flow is pumped from the low-pressure section 4 to the high-pressure section 1. The water turbine working condition of the water pump turbine is to convert the water energy into the mechanical energy, and the water pump working condition is to convert the mechanical energy into the water energy. The water energy of the water turbine through the water pump can be expressed as follows:
wherein:
E h : the unit of water energy passing through the water pump turbine is W;
ρ: density of water in kg/m 3 ；
g: acceleration of gravity in m/s 2 ；
p u : the pressure of the flow section is Pa;
and z: potential energy of unit position, the unit is m;
alpha: the kinetic energy non-uniformity coefficient is free of units;
v: the average flow velocity of the flow section is m/s;
the water flow velocity vector of the flow section is in m/s;
a: the area of the overcurrent is m 2 。
The water-pumping energy storage unit is a device for converting water energy into electric energy/electric energy into water energy, and the conversion relation between the water energy and the output/input force of the water-pumping energy storage unit is as follows:
for the power generation working condition of the pumped storage unit, namely the working condition of a water turbine of the water pump and the water turbine, the relation between the water energy and the output force of the pumped storage unit is as follows:
E G ＝η T ·E h (2)
wherein:
E G : the output of the pumped storage unit is W;
η T : the efficiency of the water turbine is unit-free.
For the pumping working condition of the pumped storage unit, namely the water pump working condition of the water pump turbine, the relation between the water energy and the inlet force of the pumped storage unit is as follows:
wherein:
E S : the unit of the force of the pumped storage unit is W;
η P : the efficiency of the water pump is not unit.
The relation between the unit output force of the pumped storage unit and other variables under the power generation working condition can be obtained by the combined type (1) and the formula (2):
the combination formula (1) and the formula (3) can obtain the relation between the set-in force of the pumped storage set and other variables under the pumping working condition:
the change rule of the micro-grid system frequency along with the load fluctuation of the pumped storage unit is as follows:
wherein:
j: the total inertia of the system is MWs/Hz;
Δf (t): the system frequency changes in Hz;
d: the load damping ratio is 1/Hz;
D ML : synchronous motor type load, the unit is MW;
the unit capacity variable quantity capable of providing frequency modulation service for the system is MW;
ΔE E : the load of the pumped storage unit fluctuates in MW.
If the load fluctuation delta E of the pumped storage unit E For inputting energy into the micro-grid, "±" in equation (6) is taken as "+"; if the load fluctuation delta E of the pumped storage unit E To output energy from micro-gridThe "±" in the formula (6) is "-".
Compared with the traditional water pump turbine, the pipeline type water pump turbine disclosed by the utility model has the following characteristics:
the pipeline type water pump water turbine disclosed by the utility model ensures that the center lines of incoming flow and outgoing flow of water flow are coincident with the center line of the impeller, and ensures that the water flow can flow uniformly and non-rotatably to the impeller 21 to the greatest extent, thereby improving the stability of the water pump water turbine to the greatest extent, and reducing the output/input force fluctuation of a pumped storage unit to the greatest extent. In the conventional pump turbine, under the working condition of the turbine, as shown in fig. 2, water flows from the high-pressure end into the volute 5 and then flows out from the draft tube 6 to the low-pressure side through the impeller 21. The water flow before it flows to the impeller 21 can be split into tangential flow in the volute 5 and axial flow formed by a 90 ° turn in the horizontal direction, as shown in fig. 3 and 4. Tangential flow within the volute 5 necessarily causes a significant amount of swirl to be generated in the water flowing into the impeller 21, while axial flow from a 90 ° turn in the horizontal direction causes severe non-uniformity in the water flow rate in addition to secondary flow, exacerbating swirl generation. The superposition of the above two negative effects causes the flow velocity of the water flowing to the impeller 21 under the working condition of the conventional water pump turbine to be seriously uneven and have a large number of eddies, and is reflected in the formula (4), the flow velocity vector is represented by the reduction of the uneven coefficient alpha of kinetic energy and the flow cross sectionSince the state exhibits unstable characteristics varying with time, the kinetic energy non-uniformity coefficient alpha decreases and the flow velocity vector of the flow cross section +.>Also the fluctuations of (a) show a trend over time, which leads to the output E of the final pumped-storage unit G Also along with the reduction of the kinetic energy non-uniformity coefficient alpha and the water flow velocity vector of the flow cross sectionIs significantly varied by the fluctuation of (c). Under the working condition of a water pump of a conventional water pump turbine, as shown in fig. 5, water flows into an impeller 21 from a low-pressure side draft tube 6 and flows out to a high-pressure side through a volute 5. As shown in fig. 6, the axial flow of the water flow before flowing to the impeller 21, which is formed by turning 90 ° in the horizontal direction, causes a secondary flow, and also causes serious flow velocity unevenness, in addition to the generation of swirl. This causes the flow velocity of the water flowing to the impeller 21 under the condition of the conventional water pump turbine to be severely uneven and to have a large number of eddies, and is reflected in equation (5), the flow velocity vector representing the reduction of the kinetic energy unevenness coefficient alpha and the flow cross section +.>Since the state exhibits unstable characteristics varying with time, the kinetic energy non-uniformity coefficient alpha decreases and the flow velocity vector of the flow cross section +.>Also the fluctuations of (a) show a trend over time, which leads to an inflow E of the final pumped-storage unit S Also along with the reduction of the kinetic energy non-uniformity coefficient alpha and the water flow velocity vector of the flow cross section +.>Is significantly varied by the fluctuation of (c).
The fluctuation of the output/input force of the pumped storage unit, which is generated by the uneven flow of water, of the traditional water pump turbine can obviously influence the frequency of the micro-grid system. According to formula (6), factors influencing the frequency change of the micro-grid system mainly comprise the total inertia J of the system, the load damping ratio D and the load D of the synchronous motor ML Unit capacity variable quantity capable of providing frequency modulation service for systemAnd load fluctuation delta E of pumped storage unit E . For a particular micro-grid system, the load damping ratio D can be considered to be known, and the total inertia J of the system and the load D of the synchronous motor class ML And a unit capacity variation amount capable of providing a frequency modulation service to the system +.>The larger the value of (2), the smaller the frequency variation of the system; load fluctuation delta E of pumped storage unit E The larger the frequency change of the system is, the larger the frequency change of the system is. Because the duty ratio of new energy sources such as photovoltaic and wind power generation in the micro-grid is very high, the total inertia J of the system and the load D of the synchronous motor are realized ML And a unit capacity variation amount capable of providing a frequency modulation service to the system +.>The factors which are used as factors for delaying the frequency change of the micro-grid are much lower in the grid than the traditional wide-area power system, which results in load fluctuation delta E of a pumped-storage unit which does not affect the frequency of the grid in the traditional wide-area power system E Relatively severe frequency fluctuations occur in the micro-grid system.
Aiming at the problems, the pipeline type water pump turbine disclosed by the utility model fundamentally solves the problem of fluctuation of the micro-grid frequency caused by load fluctuation of the pumped storage unit due to uneven flow of the water pump turbine. The specific measures are as follows: firstly, the pipeline type structure determines that the central lines of the water pump and the water turbine from the high pressure section 1 to the low pressure section 4 are coincident through the rotating part assembly 2 and the impeller cavity section 3, the water flow condition is obviously improved, the water flow presents a state of uniform flow speed and no tangential flow, namely, for the working condition of the water turbine, as shown in fig. 7, the water does not need to flow to the impeller 21 after passing through tangential flow in the volute 5 and turning 90 degrees horizontally like the traditional water pump and the water turbine, but directly flows from the high pressure side to the low pressure side, the central lines of the whole-process water pump and the water turbine are all unique, namely, the serious non-uniformity of the flow speed of the water flow to the impeller 21 in the working condition of the traditional water pump and the water turbine is solved in principle, and a large amount of vortexes are caused, and the reduction of the non-uniform coefficient alpha of kinetic energy and the flow speed vector of the flow cross section are causedExhibits a trend over time and ultimately leads to the output E of the pumped-storage unit G Also along with the reduction of the kinetic energy non-uniformity coefficient alpha and the water flow velocity vector of the flow cross section +.>A problem that the fluctuation of the (C) is obviously changed; for the water pump working condition, as shown in fig. 8, the water flow does not need to turn 90 degrees in the horizontal direction and then flows to the impeller 21 like the traditional water pump turbine, but flows from the low pressure side to the high pressure side directly, the central lines of the flow channels of the whole-course water pump turbine are the same, the water flow condition is obviously improved, the water flow presents a state with uniform flow speed and no tangential flow, namely, the water flow speed severely uneven and with a large amount of vortexes in the water pump working condition of the traditional water pump turbine is solved in principle, the reduction of the kinetic energy uneven coefficient alpha and the water flow speed vector of the flow cross section are caused>Exhibits a trend with time and ultimately leads to an inflow E of the pumped-storage unit S Also along with the reduction of the kinetic energy non-uniformity coefficient alpha and the water flow velocity vector of the flow cross section +.>The fluctuation of (3) is significantly changed. Secondly, the structure of the pipeline type water pump turbine is convenient for arranging the water pump turbine water diversion pressure pipeline, and the pipeline type water pump turbine disclosed by the utility model has the advantages that the water flow channels at the high pressure side and the low pressure side of the pipeline type water pump turbine are in a straight state without turning, and the water diversion pressure pipeline is easier to arrange in a straight state, so that the water flow inlets at the high pressure side and the low pressure side of the water pump turbine are provided with enough long straight pipe sections, and the water flow inlet is closer to the incoming flow assumption of the potential flow of the water pump turbine at the infinity, the stable state of the water flow entering the water pump turbine is further ensured, and the output E of a water pump energy storage unit is further improved G Force E S Is stable.
Build up with the centre of the fairing section 121And the vertex is an origin, the axial lead of the water pump turbine is an X-axis, the high-pressure section 1 and the low-pressure section 4 are plane rectangular coordinates in the positive direction, and the overflow area between the outer pressure bearing piece 11 and the inner pressure bearing piece 12 is calculated in the coordinates. The area of the flow through at the fairing section 121 is calculated as follows: the coordinates of any point M on the contour shape curve of the inner pressure receiving member 12 are set to (x) 1 ,y 1 ) The coordinates of the nearest N points on the outer pressure receiving member 11 to the M point are (x) 2 ,y 2 ) And the annular area formed by the rotation of the straight line formed by the point M and the point N around the X axis is the overflow area of the water pump turbine at the point M. When x is 1 ≠x 2 When the overcurrent area a is calculated as follows:
when x is 1 ＝x 2 When the overcurrent area a is calculated as follows:
A＝2·π·(y 2 2 -y 1 2 ) (8)
in addition, in order to avoid secondary backflow of water flow and change of flow velocity distribution caused by non-monotonic change of the overflow area, the utility model discloses a pipeline type water pump water turbine, which is characterized in that after pressure water flow enters an overflow channel between an outer pressure bearing piece 11 and an inner pressure bearing piece 12 of the water pump water turbine under the working condition of the water turbine, the overflow area between the outer pressure bearing piece 11 and the inner pressure bearing piece 12 is designed to be a monotonically reduced change trend along the water flow direction, so that the stability of the water flow of the working condition of the water turbine when flowing to an impeller 21 is ensured; under the working condition of the water pump, the shrinkage tube section 113 before the water flows to the impeller 21 is also designed to be of a monotonically decreasing structure along the water flow direction, and meanwhile, the shrinkage gradient is reasonably designed, so that the stability of the water flow to the impeller 21 under the working condition of the water pump is ensured.
The outer pressure bearing part 11 forming the high-pressure side runner of the pipeline type water pump water turbine is in a revolving body structure and is composed of three sections: the inlet pipe section 111 is a portion connected with the pressure pipe, the straight pipe section 112 is a connecting transition section, and the contracted pipe section 113 is a diversion portion before the water flows to the impeller 21. In order to ensure that the water flow does not generate secondary flow and change of speed distribution, the shrinkage gradient of the shrinkage tube section 113 along the pressure reduction direction is reasonably designed, and if the profile curve of the shrinkage tube section 113 is expressed as a function f (x) in a rectangular plane coordinate system shown in fig. 9, the first derivative and the second derivative of the function f (x) are respectively expressed as f '(x) and f "(x), and the function has the property that f' (x) < 0 and f" (x) < 0.
The inner pressure bearing piece 12 forming the high-pressure side runner of the pipeline type water pump water turbine is in a revolving body structure and is composed of five sections: the rectifying casing section 121 forms a diversion part of the high-pressure water flow through reasonable arrangement of the diffusion gradient, and if the contour curve of the rectifying casing section 121 is expressed by a function f (x) in a plane rectangular coordinate system shown in fig. 9, the function has the properties of f' (x) > 0 and f "(x) < 0 at the same time, the straight casing section 122 is a cylindrical connection transition section, and the first shrinkage casing section 123 and the cone casing section 124 jointly form the diversion part before the water flow flows to the impeller 21. In order to ensure that the water flow does not generate secondary flow and change of speed distribution, the shrinkage gradient of the first shrinkage shell section 123 along the pressure reduction direction is reasonably designed, if the profile curve of the first shrinkage shell section 123 is expressed as a function f (x) in a rectangular plane coordinate system shown in fig. 9, the function has the property that f '(x) < 0 and f "(x) < 0, while in order to better guide the water flow into the impeller 21, the cone shell section 124 is a transition section, a cone cylinder structure is adopted, the second shrinkage shell section 125 is in a concave structure, and in the rectangular plane coordinate system shown in fig. 9, if the profile curve of the second shrinkage shell section 125 is expressed as a function f (x), the function has the property that f' (x) < 0 and f" (x) > 0, so that the diffusion gradient along the pressure reduction direction can be more reasonable.
The outer pressure bearing member 11 and the inner pressure bearing member 12 are coaxially sleeved, water flows into the pipeline type water pump turbine from the high-pressure end, and the annular flow passage formed between the outer pressure bearing member 11 and the inner pressure bearing member 12 flows to the impeller 21. As shown in fig. 10, the radial cross-sectional view of the axial line of the annular flow passage and the impeller 21 is concentric with each other, and the flow passage surface is uniformly distributed.
The number of the fixed guide vanes 13 is 2 or more. The fixed guide vane 13 connects the large-size pressure bearing piece 11 and the small-size pressure bearing piece 12 together to form the high-pressure section 1. The fixed guide vane 13 also has the effect of reducing the secondary flow and improving the uniformity of the flow velocity distribution.
The impeller cavity section 3 is a revolution body. The impeller chamber section 3 is located between the high-pressure section 1 and the low-pressure section 4, and forms a rotary sealing pair together with the impeller 21 as a fixed part.
The number of blades 211 on the impeller 21 is 2 or more. The blades 211 on the impeller 21 allow a design in which the working angle can be adjusted. It also allows the addition of rings 212 to the blades 211 of the impeller 21 to increase rigidity,
embodiment two: straight tube section 112 is omitted and inlet tube section 111 is connected to convergent tube section 113.
Embodiment III: to ensure that the water flow does not produce secondary flow and changes in velocity profile, the straight shell section 122 may be omitted for the inner bearing 12 and the fairing section 121 connected directly to the first converging shell section 123.
Embodiment four: to ensure that the water flow does not produce secondary flow and velocity profile changes, the cone housing section 124 is omitted for the inner bearing 12 and the first convergent housing section 123 is directly connected to the second convergent housing section 125.
Fifth embodiment: the second shrink wrap section 125 is omitted.
The pipeline type water pump water turbine disclosed by the utility model has the characteristic of flowing along the axis of the impeller rotation shaft under two working conditions of the water turbine and the water pump, so that the water flow can flow uniformly and non-rotatably to the impeller as much as possible, the stability of the water pump water turbine is improved to the greatest extent, and the frequency fluctuation in a micro-grid is avoided.
The uniformity of the incoming flow velocity of the water turbine of the water pump turbine and the working condition of the water pump is improved;
the tangential speed of the incoming flow of the working condition of the water turbine of the water pump turbine is obviously reduced, and the rotation degree of the incoming flow is greatly reduced;
the secondary reflux condition of the incoming flow of the water pump working condition of the water pump turbine is improved.
The above embodiments are only illustrative of the present utility model and do not limit the scope thereof, and those skilled in the art may also make modifications to parts thereof without departing from the spirit of the utility model.
Claims (9)
1. A pipeline type water pump turbine is characterized in that: comprises a high-pressure section (1), a rotating part assembly (2), an impeller cavity section (3) and a low-pressure section (4);
the high-pressure section (1) comprises an outer pressure-bearing piece (11) and an inner pressure-bearing piece (12), the outer pressure-bearing piece (11) and the inner pressure-bearing piece (12) are coaxially sleeved through a plurality of fixed guide vanes (13), and an annular flow channel is formed between the inner pressure-bearing piece (12) and the outer pressure-bearing piece (11);
the outer pressure bearing piece (11), the impeller cavity section (3) and the low-pressure section (4) are sequentially connected rightward to form a hollow revolving body with axial continuous change, the outer pressure bearing piece (11) comprises an inlet pipe section (111), a straight pipe section (112) and a contracted pipe section (113) which are sequentially connected rightward, the inlet pipe section (111) is monotonously changed along the axial direction, the contracted pipe section (113) is monotonously converged rightward, and the low-pressure section (4) is monotonously diffused rightward;
the inner pressure-bearing piece (12) is a right-opening hollow revolving body with an axial continuous change and comprises a rectifying shell section (121), a straight shell section (122), a first shrinkage shell section (123), a conical shell section (124) and a second shrinkage shell section (125) which are sequentially connected rightward, wherein the rectifying shell section (121) is in monotonous diffusion rightward, and the first shrinkage shell section (123), the conical shell section (124) and the second shrinkage shell section (125) are in monotonous convergence rightward, so that the annular flow passage area at the rectifying shell section (121) is in monotonous reduction rightward;
the rotating part assembly (2) comprises an impeller (21), a main shaft (24) and a generator rotor (25); the main shaft (24) rotates and sets up in interior pressure-bearing piece (12), has cup jointed generator rotor (25) on main shaft (24), and the right-hand member of main shaft (24) links to each other with impeller (21), is provided with seal (22) between impeller (21) or main shaft (24) and interior pressure-bearing piece (12), is equipped with a plurality of blades (211) on impeller (21), and the top of a plurality of blades (211) links to each other through ring (212), and a plurality of blades (211) are located impeller chamber section (3).
2. A pipeline pump turbine according to claim 1, wherein: the inlet pipe section (111) is one of a straight pipe, a tapered pipe that converges monotonically to the right, or a tapered pipe that converges monotonically to the left.
3. A pipeline pump turbine according to claim 1, wherein: the number of the fixed guide vanes (13) is more than or equal to 2.
4. A pipeline pump turbine according to claim 1, wherein: the number of the blades (211) is 2 or more.
5. A ducted pump turbine according to any one of claims 1 to 4, wherein: the two ends of the main shaft (24) are respectively connected with the inner pressure-bearing piece (12) through a bearing A (23) and a bearing B (26).
6. A pipeline pump turbine according to claim 5, wherein: the straight tube section (112) is omitted, and the inlet tube section (111) is connected with the contracted tube section (113).
7. A pipeline pump turbine according to claim 5, wherein: the straight shell section (122) is omitted, and the rectifying shell section (121) is connected with the first shrinking shell section (123).
8. A pipeline pump turbine according to claim 5, wherein: the cone shell section (124) is omitted and the first shrink shell section (123) is connected to the second shrink shell section (125).
9. A pipeline pump turbine according to claim 5, wherein: the second shrink wrap section (125) is omitted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320603733.9U CN219452279U (en) | 2023-03-24 | 2023-03-24 | Pipeline type water pump water turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320603733.9U CN219452279U (en) | 2023-03-24 | 2023-03-24 | Pipeline type water pump water turbine |
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| Publication Number | Publication Date |
|---|---|
| CN219452279U true CN219452279U (en) | 2023-08-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202320603733.9U Active CN219452279U (en) | 2023-03-24 | 2023-03-24 | Pipeline type water pump water turbine |
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| Country | Link |
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| CN (1) | CN219452279U (en) |
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2023
- 2023-03-24 CN CN202320603733.9U patent/CN219452279U/en active Active
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