1. A turbine, characterized by: comprises a seat body and a speed reducer, wherein the speed reducer comprises a primary transmission part, a secondary transmission part and a tertiary transmission part, the primary transmission part is in transmission connection with the secondary transmission part, the secondary transmission part is in transmission connection with the tertiary transmission part, the tertiary transmission part is arranged on the seat body,

the base body is internally provided with an outer impeller, the outer impeller comprises an outer impeller body and a hollow shaft, the outer impeller body is connected with the secondary transmission part through the hollow shaft, the outer impeller body comprises an upper impeller plate and a lower impeller plate, a plurality of outer impeller sheets are arranged at intervals along the circumferential edge of the outer impeller body, two ends of each outer impeller sheet are respectively connected with the upper impeller plate and the lower impeller plate, the upper impeller plate, the lower impeller plate and the outer impeller sheets are connected to form a fluid cavity, the fluid cavity is internally provided with an inner impeller, the inner impeller comprises an inner impeller body and an inner rotating shaft, the inner rotating shaft is coaxially arranged with the hollow shaft, the inner impeller body is connected with the primary transmission part through the inner rotating shaft, the inner impeller body comprises an inner impeller plate, a plurality of inner impeller sheets are arranged at intervals along the circumferential direction of the inner impeller plate, the lower impeller plate is provided with a discharge port, and the discharge port is positioned below the inner impeller body,

the outer impeller is provided with an annular nozzle, the annular nozzle is positioned between the outer impeller sheet and the inner impeller sheet and comprises a fluid inlet and a fluid outlet, the fluid inlet faces the outer impeller sheet, and the fluid outlet faces the inner impeller sheet.

2. The turbomachine of claim 1, wherein: the reduction gear is planetary reducer, planetary reducer install in the top of pedestal, one-level transmission portion is the sun gear, interior pivot with sun gear coaxial arrangement, second grade transmission portion includes planet carrier and two at least planet wheels, the planet wheel rotatory install in the planet carrier, the hollow shaft with the planet carrier is connected, the sun gear with planet wheel meshing transmission, tertiary transmission portion is interior ring gear, the planet through-hole has been seted up at the middle part of interior ring gear, second grade transmission portion install in the planet through-hole, the planet wheel with interior ring gear meshing installation, interior ring gear is fixed in the pedestal.

3. The turbomachine of claim 2, wherein: the pedestal includes seat shell and bearing base, the base installing port has been seted up at the top of seat shell, bearing base pass through the base installing port install in the seat shell, bearing base's upper end circumference is outstanding to be formed with the base fixed part, the base fixed part is fixed in the top of seat shell, the planet installation cavity has been seted up to bearing base's upper end, the planet carrier install in the planet installation cavity, bearing base downwardly extending forms logical axial region, logical axial region has seted up logical axle through-hole, lead to the axle through-hole with the planet installation cavity intercommunication, the hollow shaft passes through logical axle through-hole with the planet carrier is connected, interior ring gear suit in the outside of planet installation cavity, interior ring gear is fixed in bearing base.

4. The turbomachine of claim 1, wherein: the inner wheel piece is arranged on the outer wheel piece, the inner wheel piece is arranged on the inner rotating shaft, the outer end of the inner wheel piece faces the outer wheel piece and is an inner end, and the interval between the outer ends of the adjacent inner wheel pieces is larger than the interval between the inner ends.

5. The turbomachine of claim 1, wherein: the annular nozzle is disposed around an outer periphery of the inner wheel body, and the fluid inlet is larger than the fluid outlet.

6. The turbomachine of claim 5, wherein: the fluid inlet has a longitudinal cross-sectional area at least one time greater than a longitudinal cross-sectional area of the fluid outlet.

7. The turbomachine of claim 5, wherein: the inner peripheral area of the annular nozzle is at least twice as large as the area of the discharge port.

8. The turbomachine of claim 5, wherein: the diameter ratio of the outer diameter of the annular nozzle to the inner wheel body is 1.5-3.

9. The turbomachine of claim 1, wherein: the spacing distance between the outer wheel sheets is equal to the length of the outer wheel sheets in the radial direction of the outer wheel body, and the length of the outer wheel sheets in the radial direction of the outer wheel body is 5% -20% of the diameter of the outer wheel body.

10. The turbomachine of claim 1, wherein: the cross-sectional area of the discharge port accounts for 50% -60% of the cross-sectional area of the inner wheel body.

Background

Since the existing turbines drive the impeller by accelerating the direct impact of the fluid, the main disadvantage of this drive is that the fluid flow rate is much higher than the impeller speed to drive the impeller efficiently. When the rotating speed of the impeller is gradually close to the flowing speed of the fluid, the driving efficiency of the fluid driving to the impeller is also gradually reduced, particularly when the impeller is lightly loaded or unloaded, the driving energy of the fluid is greatly wasted without attack, which is a big common problem of various turbines, and solves the unreasonable output defect, the existing turbine usually needs to operate at a fixed rotating speed and needs a complex throttling device for assistance to achieve ideal benefits, so that systematic control is complicated, if the turbine works in an environment with complex load change, the ideal benefits are difficult to achieve, the driving mode of the turbine only utilizes the kinetic energy of the fluid as driving under any rotating speed and any load, and the potential energy and the pressure energy of the fluid are not flexibly utilized all the time, so the working efficiency of the turbine is naturally low, and the efficiency of the turbine is improved by a mode of connecting a plurality of stages of impellers or a plurality of machines, this undoubtedly makes it bulky, unresponsive and impractical to implement in terms of miniaturization, and these drawbacks indicate that the existing driving techniques are not suitable for high-speed operation, while the operation at low speed is subject to many constraints due to environmental requirements.

Disclosure of Invention

The purpose of the invention is: a turbine with low transmission efficiency loss and wide application range.

In order to achieve the above object, the present invention provides a turbine, including a base and a speed reducer, where the speed reducer includes a first-stage transmission part, a second-stage transmission part, and a third-stage transmission part, the first-stage transmission part is in transmission connection with the second-stage transmission part, the second-stage transmission part is in transmission connection with the third-stage transmission part, the third-stage transmission part is mounted on the base, an outer impeller is rotatably disposed in the base, the outer impeller includes an outer impeller body and a hollow shaft, the outer impeller body is connected with the second-stage transmission part through the hollow shaft, the outer impeller body includes an upper impeller plate and a lower impeller plate, a plurality of outer impeller pieces are disposed at intervals along a circumferential edge of the outer impeller body, two ends of each outer impeller piece are respectively connected with the upper impeller plate and the lower impeller plate, the upper impeller plate, the lower impeller plate and the outer impeller piece are connected to form a fluid chamber, and an inner impeller is disposed in the fluid chamber, interior impeller includes interior wheel body and interior pivot, interior pivot with hollow shaft coaxial arrangement, interior wheel body passes through interior pivot with one-level transmission portion connects, interior wheel body includes the interior wheel board, follows the circumference interval of interior wheel board sets up a plurality of interior wheel pieces, the discharge port has been seted up to the lower wheel board, the discharge port is located the corresponding below of interior wheel body, outer impeller is equipped with annular nozzle, annular nozzle is located outer wheel piece with between the interior wheel piece, annular nozzle includes fluid inlet and fluid outlet, fluid inlet orientation outer wheel piece, fluid outlet orientation inner wheel piece.

As a preferred scheme, the reduction gear is a planetary reduction gear, the planetary reduction gear is installed at the top of the base body, the first-stage transmission part is a sun gear, the inner rotating shaft is coaxially installed with the sun gear, the second-stage transmission part comprises a planet carrier and at least two planet gears, the planet gears are rotatably installed on the planet carrier, the hollow shaft is connected with the planet carrier, the sun gear is in meshing transmission with the planet gears, the third-stage transmission part is an inner gear ring, a planet through hole is formed in the middle of the inner gear ring, the second-stage transmission part is installed in the planet through hole, the planet gears are in meshing installation with the inner gear ring, and the inner gear ring is fixed on the base body.

According to the preferable scheme, the base body comprises a base shell and a bearing base, a base mounting opening is formed in the top of the base shell, the bearing base is mounted on the base shell through the base mounting opening, a base fixing portion is formed in the circumferential direction of the upper end of the bearing base in a protruding mode, the base fixing portion is fixed to the top of the base shell, a planet mounting cavity is formed in the upper end of the bearing base, the planet carrier is mounted in the planet mounting cavity, the bearing base extends downwards to form a through shaft portion, a through shaft through hole is formed in the through shaft portion and communicated with the planet mounting cavity, the hollow shaft is connected with the planet carrier through the through shaft through hole, the inner gear ring is sleeved on the outer side of the planet mounting cavity, and the inner gear ring is fixed to the bearing base.

Preferably, one end of the inner wheel piece facing the outer wheel piece is an outer end, one end of the inner wheel piece facing the inner rotating shaft is an inner end, and the interval between the outer ends of the adjacent inner wheel pieces is larger than the interval between the inner ends.

Preferably, the annular nozzle is disposed around the periphery of the inner wheel body, the fluid inlet being larger than the fluid outlet.

Preferably, the fluid inlet has a longitudinal cross-sectional area at least twice greater than the longitudinal cross-sectional area of the fluid outlet.

Preferably, the inner peripheral area of the annular nozzle is at least twice as large as the area of the discharge port.

Preferably, the diameter ratio of the outer diameter of the annular nozzle to the inner wheel body is 1.5-3.

Preferably, the distance between the outer wheel pieces is equal to the length of the outer wheel piece in the radial direction of the outer wheel body, and the length of the outer wheel piece in the radial direction of the outer wheel body is 5% to 20% of the diameter of the outer wheel body.

Preferably, the cross-sectional area of the discharge port accounts for 50% -60% of the cross-sectional area of the inner wheel body.

Compared with the prior art, the turbine provided by the embodiment of the invention has the beneficial effects that: the outer impeller is driven to rotate by fluid, when the outer impeller rotates, the fluid is pushed to enter the fluid cavity through the outer impeller blade to move centripetally to form rotating fluid, the pressure in the fluid cavity is increased along with the increase of the rotating fluid, when the rotating fluid passes through the annular nozzle, the annular nozzle further extrudes the rotating fluid to improve the flowing speed of the rotating fluid entering the inner impeller, the inner impeller is driven to rotate by the rotating fluid, the inner rotating shaft is driven to drive the first-stage transmission part through the rotation of the inner impeller, the second-stage transmission part is driven to drive the outer impeller to rotate, and the fluid entering from the edge of the outer impeller further drives the inner impeller to rotate by repeating the process. Eventually, the fluid flows out of the discharge port. The inner impeller and the outer impeller are connected through the speed reducer to form a mutual circulation driving structure, so that the energy loss of the outer impeller and the inner impeller in the energy transfer process is reduced, and the energy utilization rate of the fluid is improved. The annular nozzle converts the rotating fluid in centripetal motion into the driving force for tangentially driving the inner impeller, thereby realizing the purpose of converting kinetic energy into mechanical energy of the inner impeller. Different centrifugal potential energy is generated by different rotating speeds of the inner impeller, so that the purpose of automatic throttling can be realized according to the load condition.

Drawings

Fig. 1 is a schematic view of the overall structure of the embodiment of the present invention.

Fig. 2 is a schematic view of the internal structure of the embodiment of the present invention.

Fig. 3 is a schematic structural view of an outer impeller according to an embodiment of the present invention.

Fig. 4 is a schematic structural view of an inner impeller according to an embodiment of the present invention.

FIG. 5 is a schematic view of a bearing mount structure according to an embodiment of the invention.

In the figure:

10. a base body; 11. a seat shell; 12. a bearing base; 13. a base fixing portion; 14. a planet mounting cavity; 15. a through shaft portion; 16. a through shaft through hole;

20. a speed reducer; 21. a sun gear; 22. a planet carrier; 23. a planet wheel; 24. an inner gear ring;

30. an outer impeller; 31. an outer wheel body; 32. a hollow shaft; 33. an upper wheel plate; 34. a lower wheel plate; 35. an outer wheel sheet; 36. a fluid chamber; 37. a discharge port;

40. an inner impeller; 41. an inner wheel body; 42. an inner rotating shaft; 43. an inner wheel plate; 44. an inner wheel sheet;

50. an annular nozzle; 51. a fluid inlet; 52. a fluid outlet.

Detailed Description

The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.

In the description of the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. used herein are used to indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.

In the description of the present invention, it should be understood that the terms "connected," "fixed," and the like are used in a broad sense, and for example, the terms "connected," "connected," and "fixed" may be fixed, detachable, or integrated; the connection can be mechanical connection or welding connection; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

As shown in fig. 1 to 5, a turbine according to a preferred embodiment of the present invention includes a base 10 and a speed reducer 20, wherein the speed reducer 20 includes a first-stage transmission portion, a second-stage transmission portion and a third-stage transmission portion, the first-stage transmission portion is in transmission connection with the second-stage transmission portion, the second-stage transmission portion is in transmission connection with the third-stage transmission portion, the third-stage transmission portion is mounted on the base 10,

the base body 10 is provided with an outer impeller 30 in a rotating manner, the outer impeller 30 comprises an outer impeller body 31 and a hollow shaft 32, the outer impeller body 31 is connected with a secondary transmission part through the hollow shaft 32, the outer impeller body 31 comprises an upper impeller plate 33 and a lower impeller plate 34, a plurality of outer impeller sheets 35 are arranged at intervals along the circumferential edge of the outer impeller body 31, two ends of each outer impeller sheet 35 are respectively connected with the upper impeller plate 33 and the lower impeller plate 34, the upper impeller plate 33, the lower impeller plate 34 and the outer impeller sheets are connected to form a fluid chamber 36, an inner impeller 40 is arranged in the fluid chamber 36, the inner impeller 40 comprises an inner impeller body 41 and an inner rotating shaft 42, the inner rotating shaft 42 and the hollow shaft 32 are coaxially arranged, the inner impeller body 41 is connected with a primary transmission part through the inner rotating shaft 42, the inner impeller body 41 comprises an inner impeller plate 43, a plurality of inner impeller sheets 44 are arranged at intervals along the circumferential direction of the inner impeller plate 43, the lower impeller plate 34 is provided with a discharge port 37, the discharge port 37 is positioned below the inner impeller body 41,

the outer impeller 30 is provided with an annular nozzle 50, the annular nozzle 50 being located between the outer and inner blades 35, 44, the annular nozzle 50 comprising a fluid inlet 51 and a fluid outlet 52, the fluid inlet 51 being directed towards the outer impeller blades 35 and the fluid outlet 52 being directed towards the inner blade 44.

In the turbine of the present invention, the fluid drives the outer impeller 30 to rotate, when the outer impeller 30 rotates, the fluid is pushed by the outer impeller 35 to enter the fluid cavity 36 to move centripetally to form a rotating fluid, the pressure in the fluid cavity 36 increases with the increase of the rotating fluid, when the rotating fluid passes through the annular nozzle 50, the annular nozzle 50 further extrudes the rotating fluid to increase the flow speed of the rotating fluid entering the inner impeller 40, the inner impeller 40 is driven to rotate by the rotating fluid, the inner rotating shaft 42 is driven by the rotation of the inner impeller 40 to drive the primary transmission part, the primary transmission part drives the secondary transmission part, the secondary transmission part drives the outer impeller 30 to rotate, and the fluid entering from the edge of the outer impeller 30 repeats the above process again to further push the inner impeller 40 to rotate. Eventually, the fluid flows out of the discharge port 37. The inner impeller 40 and the outer impeller 30 are connected through the reducer 20 to form a mutual circulation driving structure, so that the energy loss of the outer impeller 30 and the inner impeller 40 in the energy transfer process is reduced, and the energy utilization rate of the fluid is improved. The rotating fluid moving centripetally is converted into the driving force driving the inner impeller 40 tangentially by the annular nozzle 50, thereby achieving the purpose of converting kinetic energy into mechanical energy for rotating the inner impeller 40. Different centrifugal potential energy is generated by different rotating speeds of the inner impeller 40, so that the purpose of automatic throttling can be realized according to the load condition.

Taking water as a fluid medium as an example, the diameter of the inner impeller 40 is 2.5cm, the working water pressure is 0.3mpa, and the speed ratio of the speed reducer 20 is 1: 3, the test is carried out under the condition that the water head jet speed of 0.3mpa pressure is 24.2m/s, the rotating speed of the inner impeller 40 reaches 291 revolutions per second, namely, the inner impeller 40 rotates at the speed of 22.8 m/s, which shows that the tangential speed of the fluid in the annular nozzle 50 can be more than 22.8 m/s to maintain the rotating speed of the inner impeller 40 at 291 revolutions per second, the rotating speed of the inner impeller 40 is almost close to the water head jet speed, the energy conversion rate of the fluid is high, the loss of the fluid in the transmission process is small, and therefore, the turbine has the characteristic of high operating efficiency at high speed and low torque.

The diameter of the inner impeller 40 is 3cm, and the rotating speed of the inner impeller 40 is tested to reach 235 rpm under the same environmental conditions, namely the inner impeller 40 rotates at the speed of 22.1 m/s in the circumferential direction, which is slightly lower than the above example, but the internal pressure can be balanced, so the power is not changed, and therefore the diameter size of the inner impeller 40 determines the rotating speed.

In the case where the diameter of the discharge port 37 is the same as the diameter of the inner impeller 40, the water velocity at the discharge port is only 0.8 m/s, which is only 4% of the jet velocity of the fluid head, so that the turbine of the present invention has a characteristic of extremely small flow rate at no load.

Under the condition of a steady-pressure environment, when the turbine is from no load to full load, the flow rate of the discharge port 37 is increased along with the increase of the load, the rotating speed of the inner impeller 40 is slightly reduced, but the torque is increased along with the increase of the flow rate, which shows that the tangential speed of the rotating fluid in the annular nozzle 50 is not influenced by the rotating speed of the inner impeller 40 and is always kept in a state close to a constant speed, so that the turbine has the characteristics of load characteristic close to the constant speed and high torque at the low rotating speed.

When the turbine of the invention is applied with frequency load, the jumping frequency of the fluid head at the discharge port 37 is sensitive without hysteresis, the response speed of the water flow is extremely high, and the mobility of the turbine is strong.

When the heavy load is applied to the turbine of the present invention, when the internal pressure of the fluid chamber 36 is reduced to 70%, the torque starts to gradually decrease, the inner wheel 44 of the inner impeller 40 is changed into the forward-curved type, and the fluid injection inlet is changed into the circumferential nozzle, the torque is not obviously increased, which indicates that the tangential angle of the fluid for pushing the inner wheel 44 is always perpendicular to the radial angle of the inner wheel 44 as the effective torque, and the effective range of the torque is determined under the environment condition of pressure stabilization.

Increasing the speed ratio of the reduction gear 20 to 1: at time 5, when the turbine is in no-load, the capability of balancing internal pressure is reduced, the flow of the discharge port 37 is increased, and the torque is enhanced, so that the speed ratio of the inner impeller 40 and the outer impeller 30 is controllable to the flow, the speed ratio is a key parameter for determining the use property of the rotor, and the wide applicability of the rotor to various environments is highlighted.

The hollow shaft 32 and the inner rotary shaft 42 can be used as output shafts, the inner rotary shaft 42 can be directly used as an output shaft of a turbine when the flow is abundant, the hollow shaft 32 can be used as an output shaft when the flow is insufficient, and a speed reducer 20 can be additionally arranged as necessary for assisting, so that the purpose of ensuring that the outer impeller 30 or the inner impeller 40 can work efficiently in a pressure stabilizing environment is achieved, and the flow is not lower than 10% of the actual flow of the pressure generally.

As shown in fig. 1 to 2, further, the speed reducer 20 is a planetary speed reducer 20, the planetary speed reducer 20 is installed on the top of the seat body 10, the first-stage transmission portion is a sun gear 21, the inner rotating shaft 42 is coaxially installed with the sun gear 21, the second-stage transmission portion includes a planet carrier 22 and at least two planet gears 23, the planet gears 23 are rotatably installed on the planet carrier 22, the hollow shaft 32 is connected with the planet carrier 22, the sun gear 21 is in meshing transmission with the planet gears 23, the third-stage transmission portion is an inner gear ring 24, a planet through hole is formed in the middle of the inner gear ring 24, the second-stage transmission portion is installed in the planet through hole, the planet gears 23 are in meshing installation with the inner gear ring 24, and the inner gear ring 24 is fixed on the seat body 10. Specifically, internal rotating shaft 42 and sun gear 21 coaxial arrangement, and then drive sun gear 21 rotatory, hollow shaft 32 and planet carrier 22 coaxial arrangement, because planet wheel 23 meshes the installation with sun gear 21 and internal tooth ring 24 respectively, sun gear 21 is rotatory and then drive hollow shaft 32 through planet wheel 23 and rotate, and then hollow shaft 32 drives outer impeller 30 rotatory, and then realize that inner impeller 40 and outer impeller 30 form the structure of mutual circulation drive through reduction gear 20, improve the conversion of fluid drive power, reduce the loss of fluid drive power in transmission process.

Further, as shown in fig. 5, the seat body 10 includes a seat shell 11 and a bearing base 12, a base mounting opening is opened at the top of the seat shell 11, the bearing base 12 is mounted on the seat shell 11 through the base mounting opening, a base fixing portion 13 is formed at the upper end of the bearing base 12 in a circumferential protruding manner, the base fixing portion 13 is fixed at the top of the seat shell 11, a planet mounting cavity 14 is opened at the upper end of the bearing base 12, the planet carrier 22 is mounted on the planet mounting cavity 14, the bearing base 12 extends downward to form a through shaft portion 15, the through shaft portion 15 is opened with a through shaft through hole 16, the through shaft through hole 16 is communicated with the planet mounting cavity 14, the hollow shaft 32 is connected with the planet carrier 22 through the through shaft through hole 16, the inner ring gear 24 is sleeved outside the planet mounting cavity 14, and the inner ring gear 24 is fixed on the bearing base 12. The mounting of the inner impeller 40 and the outer impeller 30 on the housing 11 is effected by the bearing base 12.

Further, as shown in fig. 4, one end of the inner wheel piece 44 facing the outer wheel piece 35 is an outer end, one end of the inner wheel piece 44 facing the inner rotating shaft 42 is an inner end, and the interval between the outer ends of the adjacent inner wheel pieces 44 is larger than the interval between the inner ends, so as to increase the impact area of the rotating fluid on the outer end of the inner wheel piece 44 and improve the transmission efficiency of the rotating fluid on the inner wheel piece 44. The inner wheel 44 is of a front-open radial structure, and can be a driving wheel or a starting wheel, and the installation direction of the inner wheel 44 is not in the same straight line with the flow direction of the rotating fluid sprayed from the annular nozzle 50. Preferably, the rotating fluid ejected from the annular nozzle 50 is directed perpendicularly to the outer end side surface of the outer wheel 35, and the pushing efficiency is high.

Further, as shown in FIG. 1, an annular nozzle 50 is disposed around the outer periphery of the inner wheel 41, with a fluid inlet 51 being larger than a fluid outlet 52. Specifically, the annular nozzle 50 is disposed around the inner wheel body 41 to increase the drive action inlet area of the inner impeller 40 by the rotating fluid ejected from the annular nozzle 50. The fluid inlet 51 is larger than the fluid outlet 52 so that the fluid entering from the outer impeller 30 is further compressed in the annular nozzle 50 to increase the flow velocity of the rotating fluid into the inner impeller 40, thereby increasing the drive velocity of the rotating fluid to the inner impeller 40 and increasing the drive efficiency of the rotating fluid to the inner impeller 40.

Further, as shown in fig. 1 to 2, the longitudinal sectional area of the fluid inlet 51 of the annular nozzle 50 is at least twice larger than the longitudinal sectional area of the fluid outlet 52, and the larger the longitudinal area of the fluid inlet 51 is larger than the radial area of the fluid outlet 52, the greater the fluid pressure in the annular nozzle, the faster the rotating fluid flows out through the annular nozzle 50, and the higher the driving efficiency of the rotating fluid to the inner impeller 40.

Further, the area of the inner circumference of the annular nozzle 50 is at least twice larger than the area of the discharge port 37, so that the acting time of the impeller 40 in the rotating fluid is prolonged, the transmission effect of the driving force in the rotating fluid on the impeller 40 is improved, and the loss of the rotating fluid in the power transmission process is reduced.

Further, the diameter ratio of the outer diameter of the annular nozzle 50 to the inner wheel body 41 is 1.5-3, and the diameter ratio of the outer diameter of the annular nozzle 50 to the inner wheel body 41 is greater than 1.5, so that the annular nozzle 50 can push the inner wheel body 41, and the larger the outer diameter of the annular nozzle 50 is, the more the fluid can be stored, and the larger the pushing force on the inner wheel body 41 is formed. Preferably, the diameter ratio of the outer diameter of the annular nozzle 50 to the inner wheel body 41 is 1.5, the outer diameter of the annular nozzle 50 to the inner wheel body 41 is too large, which may cause waste of fluid energy, the outer diameter of the annular nozzle 50 to the inner wheel body 41 is too small, the annular nozzle 50 has insufficient pushing force on the inner wheel body 41, which results in low pushing efficiency, and the diameter ratio of the outer diameter of the annular nozzle 50 to the inner wheel body 41 is set to 1.5, which not only ensures pushing efficiency, but also does not cause waste of resources.

Further, as shown in fig. 3, the distance between the outer ring segments 35 is equal to the length of the outer ring segments 35 in the radial direction of the outer ring body 31, and the length of the outer ring segments 35 in the radial direction of the outer ring body 31 is 5% to 20% of the diameter of the outer ring body 31. The outer impeller 35 is set to have a short length so that the fluid flowing in from the outside flows into the annular nozzle 50 as soon as possible, the acting time of the fluid flowing to the inner impeller 40 is shortened, and the acting efficiency of the fluid on the inner impeller 40 is improved. The inner impeller 40 and the outer impeller 30 do not have automatic starting capability and need to be started by the aid of external force, but once the inner impeller 40 and the outer impeller 30 are started, the inner impeller 40 and the outer impeller 30 simultaneously generate starting torque, so that the starting is easy, and the starting torque only needs to overcome the inertia force of the inner impeller 40 and the outer impeller 30. The outer impeller 30 has features compatible with prior art drive techniques when various external forces are used to provide the starting torque, such as a volute.

Further, the transverse cross-sectional area of the discharge port 37 accounts for 50% -60% of the cross-sectional area of the inner wheel body 41, so as to ensure the discharge of fluid and the normal operation of the inner wheel body 41.

The working process of the invention is as follows: the outer impeller 30 is driven to rotate by fluid, after the outer impeller 30 is started to rotate, the fluid is pushed to enter the fluid cavity 36 through the outer impeller sheet 35 to move centripetally to form rotating fluid, the pressure in the fluid cavity 36 is increased along with the increase of the rotating fluid, when the rotating fluid passes through the annular nozzle 50, the annular nozzle 50 further extrudes the rotating fluid to improve the flow speed of the rotating fluid entering the inner impeller 40, the inner impeller 40 is driven to rotate by the rotating fluid, the inner rotating shaft 42 is driven to rotate by the inner impeller 40 to drive the primary transmission part, the primary transmission part drives the secondary transmission part, the secondary transmission part drives the outer impeller 30 to rotate, and the fluid entering from the edge of the outer impeller 30 repeats the process again to further push the inner impeller 40 to rotate. Eventually, the fluid flows out of the discharge port 37.

In summary, embodiments of the present invention provide a turbine that has a very small flow rate at idle, has a high operating efficiency at high speed and low torque, and can be used in high-pressure and low-flow environmental conditions. The high-speed rotation of the rotating speed exceeding 10000r/min is easy to realize, the load characteristic close to the constant speed is realized under the condition of a stable pressure environment, and the characteristic of high torque is realized at the time of low rotating speed, so that the use requirements of most power systems can be met. The automatic throttling device has the characteristics of automatic throttling according to the load condition, high response speed, strong maneuverability, considerable economic benefit when working in an environment with complicated load change, and simplification of a control device. The single group of impellers has extremely high conversion efficiency, and a plurality of groups of impellers are not required to be connected for use or other auxiliary devices, so that the size is small, and the miniaturization is easy to implement. The starting stage can generate starting torque, has the characteristic of independent operation, can be compatible with the existing driving technology, such as a volute device, and can easily realize stepless speed change and non-rigid transmission. The device is suitable for various fluids as working media, has lower requirements on the provided environmental conditions, and can be suitable for both high-pressure low-flow and low-pressure high-flow, thereby having wide application. Can be in a high-speed standby state for a long time, has extremely low loss and is convenient to apply.

The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.