CN114165290B - Turbine and vibrator applying same - Google Patents
Turbine and vibrator applying same Download PDFInfo
- Publication number
- CN114165290B CN114165290B CN202111484973.3A CN202111484973A CN114165290B CN 114165290 B CN114165290 B CN 114165290B CN 202111484973 A CN202111484973 A CN 202111484973A CN 114165290 B CN114165290 B CN 114165290B
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- Prior art keywords
- cambered surface
- arc
- turbine
- concave
- convex
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
- F01D1/34—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The turbine provided by the invention comprises a wheel body, wherein a plurality of gear teeth are circumferentially arranged on the circumferential side of the wheel body, each gear tooth comprises a convex cambered surface and a concave cambered surface, and the convex cambered surfaces and the concave cambered surfaces are connected and combined into a fin shape; along the circumferential direction of the wheel body, between two adjacent gear teeth, the convex cambered surface tail end of one gear tooth is connected with the concave cambered surface tail end of the other gear tooth. Compared with the prior art, the turbine has better performance in rotating speed, acceleration, exciting force and vibration frequency. The invention also provides a vibrator applying the turbine, and compared with the prior art, the vibrator has larger exciting force and higher vibration frequency.
Description
Technical Field
The invention relates to the technical field of turbine vibrators, in particular to a turbine and a vibrator applying the turbine.
Background
In the prior art, the turbine generally uses straight teeth like gear teeth, gas backflow is difficult to form when gas flows through, and the turbine cannot well utilize power brought by gas flow, so that the performance of the turbine such as rotating speed, acceleration, exciting force, vibration frequency and the like is poor, the utilization rate of kinetic energy of the turbine is low, and finally energy waste is caused.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a turbine.
The turbine comprises a wheel body, wherein a plurality of gear teeth are circumferentially arranged on the peripheral side of the wheel body, each gear tooth comprises a convex cambered surface and a concave cambered surface, and the convex cambered surfaces and the concave cambered surfaces are connected and combined to form a fin shape; the convex cambered surface tail end of one gear tooth is connected with the concave cambered surface tail end of the other gear tooth along the circumferential direction of the wheel body, wherein the convex cambered surface tail end of one gear tooth is arranged between two adjacent gear teeth; the convex cambered surface and the concave cambered surface are arranged in an arc shape.
Through the arrangement, when the air flow pushes the turbine, the corresponding air flow is input to the connection position of the convex cambered surface and the concave cambered surface of the corresponding gear teeth, part of the air flow flows back in the opposite direction under the guide of the concave cambered surface and forms confluence with the newly input air, so that the position of the concave cambered surface is formed with a rotary air flow form, and work is continuously done on the concave cambered surface; the other part of air flow forms an arc flow direction to the other gear tooth under the guidance of the convex cambered surface, so that the front collision of the air flowing back to the concave cambered surface in the other gear tooth is avoided, and the kinetic energy loss of the rotary air flow in the corresponding concave cambered surface can be reduced; therefore, the rotating speed of the turbine is effectively propelled, the acceleration of the turbine is further improved, and higher vibration frequency and excitation force are generated.
Specifically, each gear tooth is uniformly distributed on the circumferential side of the wheel body in the circumferential direction, and each gear tooth is arranged in an end-to-end connection manner on the circumferential side of the wheel body along the circumferential direction of the wheel body. Through the arrangement, the stress on the periphery of the wheel body is more uniform, the reflux quantity of gas can be increased, the rotating speed and the acceleration of the turbine are further increased, and higher vibration frequency and excitation force are generated.
Specifically, the arc angle range of the convex arc surface is 44 ° or less and 34 ° or more.
Specifically, the arc angle range of the concave arc surface is less than or equal to 181 degrees and more than or equal to 156 degrees.
Specifically, the arc angle of the convex arc surface is set to 40 °, and/or the arc angle of the concave arc surface is set to 171 °.
Specifically, between two adjacent gear teeth, the end of the convex cambered surface of one gear tooth is connected with the end of the concave cambered surface of the other gear tooth in a circular arc transition manner. After the convex cambered surface of the previous gear tooth through which the gas flows, the gas can flow to the concave cambered surface of the next gear tooth to the greatest extent due to the arrangement of arc transition connection, so that the thrust force born by the concave cambered surface is increased, the rotating speed and the acceleration of the turbine are further increased, and higher vibration frequency and excitation force are generated.
Specifically, in the same gear tooth, the convex cambered surface and the concave cambered surface of the gear tooth are connected in a flat angle transition manner. Through the setting that the flat angle transition links to each other, gas is difficult to flow to the protruding cambered surface of same teeth of a cogwheel from the concave cambered surface of same teeth of a cogwheel, and gas can flow back to a greater extent to with the gas of new input converging each other, continue to do work to concave cambered surface, make rotational speed, the acceleration of turbine further increase, and make the vibratory force, the vibration frequency of turbine improve.
Specifically, the arc length corresponding to the convex arc surface is greater than the arc length corresponding to the concave arc surface. The foregoing arrangement is more conducive to backflow of gas.
Specifically, a first angle difference exists between a tangent line of the convex cambered surface and a circumferential tangent line of the wheel body; and/or a second angle difference exists between the angular bisector of the arc angle of the concave cambered surface and a straight line from the axis of the wheel body to the circle center corresponding to the concave cambered surface. The foregoing arrangement is more advantageous for directing the gas back flow.
Specifically, the extending directions of the convex cambered surface and the concave cambered surface are the same as the axial direction of the wheel body. Through the arrangement, the stress of the gear teeth is more average, and the phenomenon that the wear of different positions of the gear teeth caused by uneven stress is inconsistent is avoided, so that the service life of the turbine is influenced.
Specifically, a plurality of through holes are uniformly distributed on the end face of the wheel body, and the through holes extend along the axial direction of the wheel body. Through setting up the through-hole, set up the weight spare in the through-hole to balancing moment, the demand when adaptation actual application.
The invention also provides a vibrator applied with the turbine.
A vibrator comprising a housing with an inner cavity in which a turbine is arranged for use as described above.
Through setting up this turbine in the pedestal, the vibration frequency of this vibrator can be higher, exciting force can be bigger, plays better vibration effect.
The invention has the beneficial effects that:
1. through the arrangement, when the air flow pushes the turbine, the corresponding air flow is input to the connection position of the convex cambered surface and the concave cambered surface of the corresponding gear teeth, part of the air flow flows back in the opposite direction under the guide of the concave cambered surface and forms confluence with the newly input air, so that the position of the concave cambered surface is formed with a rotary air flow form, and work is continuously done on the concave cambered surface; the other part of air flow forms an arc flow direction to the other gear tooth under the guidance of the convex cambered surface, so that the front collision of the air flowing back to the concave cambered surface in the other gear tooth is avoided, and the kinetic energy loss of the rotary air flow in the corresponding concave cambered surface can be reduced; therefore, the rotating speed of the turbine is effectively propelled, the acceleration of the turbine is further improved, and higher vibration frequency and excitation force are generated.
2. Through setting up this turbine in the pedestal, the vibration frequency of this vibrator can be higher, exciting force can be bigger, plays better vibration effect.
Drawings
FIG. 1 is a schematic view of a turbine in accordance with the present invention;
FIG. 2 is an enlarged view of FIG. 1 at A;
FIG. 3 is a side view of the turbine of the present invention;
fig. 4 is a schematic view of a vibrator according to the present invention.
Reference numerals illustrate:
the wheel body 1, a tangent line 101 of a convex cambered surface, a circumferential tangent line 102 of the wheel body, an angular bisector 103 of the arc angle of a concave cambered surface, a straight line 104 from the axle center of the wheel body to the corresponding circle center of the concave cambered surface, the wheel teeth 11, the convex cambered surface 111, the concave cambered surface 112, the mounting hole 12, the through hole 13, the counterweight 14, the seat body 2, the inner cavity 20, the air inlet hole 21, an axis 210 of an air inlet channel, an air inlet channel 211, an air outlet hole 22, an axis 220 of an air outlet channel, an air outlet channel 221 and a fixing hole 23.
Detailed Description
In order to make the technical scheme, the purpose and the advantages of the invention more clear, the invention is further explained below with reference to the drawings and the embodiments.
Example 1 as shown in fig. 1 to 3:
the turbine comprises a wheel body 1, a plurality of gear teeth 11 are circumferentially arranged on the circumferential side of the wheel body 1, the gear teeth 11 comprise a convex cambered surface 111 and a concave cambered surface 112, and the convex cambered surface 111 and the concave cambered surface 112 are connected and combined into a fin shape; along the circumferential direction of the wheel body 1, between two adjacent gear teeth 1, the tail end of a convex cambered surface 111 of one gear tooth 1 is connected with the tail end of a concave cambered surface 112 of the other gear tooth 1; the convex arc surface 111 and the concave arc surface 112 are arranged in an arc shape.
Through the arrangement, when the air flow pushes the turbine, the corresponding air flow is input to the connection position of the convex cambered surface 111 and the concave cambered surface 112 of the corresponding gear tooth 11, part of the air flow flows back towards the opposite direction under the guide of the concave cambered surface 112, and forms confluence with the newly input air, so that the position of the concave cambered surface 112 is formed with a rotary air flow form, and work is continuously done on the concave cambered surface 112; the other part of air flow is guided by the convex cambered surface 111 to form an arc flow direction for the other gear tooth, so that the air flow is prevented from being in front collision with the air flowing back by the concave cambered surface 112 in the other gear tooth 1, and the kinetic energy loss of the rotary air flow in the corresponding concave cambered surface 112 can be reduced; therefore, the rotating speed of the turbine is effectively propelled, the acceleration of the turbine is further improved, and higher vibration frequency and excitation force are generated.
Each gear tooth 11 is uniformly distributed on the circumferential side of the wheel body 1, and each gear tooth 11 is arranged in an end-to-end connection on the circumferential side of the wheel body 1 along the circumferential direction of the wheel body 1. Through the arrangement, the stress on the periphery of the wheel body 1 is more uniform, the reflux quantity of gas can be increased, the rotating speed and the acceleration of the turbine are further increased, and higher vibration frequency and excitation force are generated.
Based on the actual application scenario, the working pressure is set to be 0.2MPa, and based on the actual processing requirement, the angle corresponding to the convex cambered surface 111 takes 2 ° as a processing gradient unit, and the angle corresponding to the concave cambered surface 112 takes 5 ° as a processing gradient unit, so that the turbine after each processing is tested and the turbine in the prior art, and test data shown in the following table 1 are obtained:
TABLE 1
As shown in table 1, when the arc angle range of the convex arc surface 111 is 44 ° or less and 34 ° or more and the arc angle range of the concave arc surface 112 is 181 ° or less and 156 ° or more, the turbine has remarkable effect progress in rotation speed, acceleration, excitation force, vibration frequency under the working pressure of 0.2MPa compared with the turbine of the prior art; when the arc angle of the convex arc surface 111 is 46 degrees and the arc angle of the concave arc surface 112 is 186 degrees, the rotation speed, acceleration, exciting force and vibration frequency of the turbine are obviously reduced and are lower than those when the arc angle of the convex arc surface 111 is 34 degrees and the arc angle of the concave arc surface 112 is 156 degrees, so that 34 degrees to 44 degrees are selected as the preferable processing range of the arc angle of the convex arc surface 111, and 156 degrees to 181 degrees are selected as the preferable processing range of the arc angle of the concave arc surface 112.
Preferably, the arc angle of the convex arc surface 111 is set to 40 °, and the arc angle of the concave arc surface 112 is set to 171 °. As shown in table 1, when the arc angle of the convex arc surface 111 is 40 ° and the arc angle of the concave arc surface 112 is 171 °, the rotation speed, acceleration, excitation force, and vibration frequency of the turbine reach the maximum value under the working pressure of 0.2MPa, so 40 ° is selected as the preferred machining value of the angle corresponding to the convex arc surface 111, and 171 ° is selected as the preferred machining value of the angle corresponding to the concave arc surface 112.
Between two adjacent gear teeth 11, the end of the convex arc surface 111 of one gear tooth 11 is connected with the end of the concave arc surface 112 of the other gear tooth 11 in an arc transition. After the gas flows through the convex cambered surface 111 of the previous gear tooth 11, the gas can flow to the concave cambered surface 112 of the next gear tooth 11 to the greatest extent due to the arrangement of arc transition connection, so that the thrust force born by the concave cambered surface 112 is increased, the rotating speed and the acceleration of the turbine are further increased, and higher vibration frequency and excitation force are generated.
As shown in fig. 2, in the same gear tooth 11, its convex cambered surface 111 and its concave cambered surface 112 are connected in a flat angle transition. Through the setting that the flat angle transition links to each other, gas is difficult to flow from the concave cambered surface 112 of same teeth of a cogwheel 11 to the convex cambered surface 111 of same teeth of a cogwheel 11, and gas can flow back to a greater extent to with the gas of new input mutually converging, continue to do work to concave cambered surface 112, make rotational speed, the acceleration of turbine further increase, and make vibration force, the vibration frequency of turbine improve.
The arc length corresponding to the convex arc surface 111 is longer than the arc length corresponding to the concave arc surface 112; a first angle difference b exists between the tangent line 101 of the convex arc surface 111 and the circumferential tangent line 102 of the wheel body 1; a second angle difference c exists between the angular bisector 103 of the arc angle of the concave cambered surface 112 and the straight line 104 from the axis of the wheel body 1 to the circle center corresponding to the concave cambered surface 112. The foregoing arrangement is more advantageous for directing the gas back flow.
The extending directions of the convex cambered surface 111 and the concave cambered surface 112 are the same as the axial direction of the wheel body 1. Through the arrangement, the stress of the gear teeth 11 is more average, and the phenomenon that the wear of different positions of the gear teeth 11 caused by uneven stress is inconsistent and influences the service life of the turbine is avoided.
The end face of the wheel body 1 is uniformly provided with a plurality of through holes 13, and the through holes 13 extend along the axial direction of the wheel body 1. Through the arrangement of the through holes 13, the weight pieces 14 are arranged in the through holes 13 to balance moment, so that the requirements of practical application are met.
The center of the end face of the wheel body 1 is provided with a mounting hole 12 for penetrating through the rotating shaft to be mounted in the vibrator.
Example 2 as shown in fig. 4:
the vibrator comprises a housing 2 with an inner cavity 20, in which inner cavity 20 a turbine is arranged, which is applied as described in example 1.
By arranging the turbine in the seat body 2, the vibration frequency of the vibrator can be higher, the exciting force can be larger, and better vibration effect is achieved.
The seat body 2 is provided with the air inlet 21 and the air outlet 22 which are communicated with the inner cavity 20, the air vent 21 is communicated with the inner cavity 20 through the air inlet channel 211, the air outlet 22 is communicated with the inner cavity 20 through the air outlet channel 221, the width of the air inlet channel 211 is smaller than that of the air outlet channel 221, and the width of the air inlet channel 211 is smaller than that of the air inlet 21, so that the effect of compressed gas is achieved, and the thrust of the gas is further improved.
Preferably, the air inlet holes 21 and the air outlet holes 22 are all upward, and the axis 210 of the air inlet channel 211 and the axis 220 of the air outlet channel 221 are tangential to the circumferential side of the wheel body 1, so that the wheel teeth 11 utilize the thrust of the air flow to the greatest extent, and further improve the rotation speed and the acceleration of the wheel body 1, thereby increasing the exciting force and the vibration frequency of the vibrator and playing a better role in vibration.
The two sides of the seat body 2 are also provided with fixing holes 23 for installation and fixation in practical application.
The foregoing is merely a preferred embodiment of the present invention, and modifications of the embodiments described above can be made by those skilled in the art without departing from the implementation principles of the present invention, and the corresponding modifications should also be considered as the protection scope of the present invention.
Claims (6)
1. The turbine is characterized by comprising a wheel body, wherein a plurality of gear teeth are circumferentially arranged on the circumferential side of the wheel body, each gear tooth comprises a convex cambered surface and a concave cambered surface, and the convex cambered surfaces and the concave cambered surfaces are connected and combined to form a fin shape; the convex cambered surface tail end of one gear tooth is connected with the concave cambered surface tail end of the other gear tooth along the circumferential direction of the wheel body, wherein the convex cambered surface tail end of one gear tooth is arranged between two adjacent gear teeth; the arc angle range of the convex arc surface is 44 degrees or less and 34 degrees or more, and the arc angle range of the concave arc surface is 181 degrees or less and 156 degrees or more; the arc length corresponding to the convex arc surface is longer than the arc length corresponding to the concave arc surface; a first angle difference is formed between a tangent line of the convex cambered surface and a circumferential tangent line of the wheel body; the angular bisector of the arc angle of the concave cambered surface and the straight line from the axis of the wheel body to the circle center corresponding to the concave cambered surface have a second angle difference.
2. The turbine of claim 1, wherein each of said gear teeth is circumferentially and uniformly disposed about a periphery of said wheel body, and wherein each of said gear teeth is disposed end-to-end about said periphery of said wheel body in a circumferential direction of said wheel body.
3. The turbine of claim 1, wherein the arc angle of the convex arc surface is set to 40 ° and/or the arc angle of the concave arc surface is set to 171 °.
4. The worm gear of claim 1, wherein between two adjacent gear teeth, the convex cambered surface end of one gear tooth is connected with the concave cambered surface end of the other gear tooth in a circular arc transition.
5. The turbine of claim 1 wherein said convex arcuate surface and said concave arcuate surface are connected in a flat angle transition in the same said tooth.
6. Vibrator, characterized in that it comprises a housing with an internal cavity in which a turbine is arranged for use according to any of claims 1-5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111484973.3A CN114165290B (en) | 2021-12-07 | 2021-12-07 | Turbine and vibrator applying same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111484973.3A CN114165290B (en) | 2021-12-07 | 2021-12-07 | Turbine and vibrator applying same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114165290A CN114165290A (en) | 2022-03-11 |
| CN114165290B true CN114165290B (en) | 2023-07-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111484973.3A Active CN114165290B (en) | 2021-12-07 | 2021-12-07 | Turbine and vibrator applying same |
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| Country | Link |
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| CN (1) | CN114165290B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1930394A (en) * | 2004-03-18 | 2007-03-14 | 弗兰克·丹尼尔·洛特里翁特 | Turbine and rotor therefor |
| CN102171413A (en) * | 2008-08-12 | 2011-08-31 | 西门子能源公司 | Canted outlet for transition in a gas turbine engine |
| CN103796762A (en) * | 2011-11-04 | 2014-05-14 | 日本精工株式会社 | Spindle device and electrostatic coating device |
| CN106015517A (en) * | 2016-07-20 | 2016-10-12 | 方年学 | Curvilinear-tooth point-line meshing gear and processing method thereof |
| CN109477417A (en) * | 2016-12-21 | 2019-03-15 | 三菱重工发动机和增压器株式会社 | The nozzle vane and turbine of turbocharger, turbocharger |
| CN111102063A (en) * | 2019-11-15 | 2020-05-05 | 车行天下网络科技股份有限公司 | Dual drive turbine |
| CN112523809A (en) * | 2020-11-30 | 2021-03-19 | 北京动力机械研究所 | Method for inhibiting unsteady airflow excitation force of turbine rotor blade |
| CN113339075A (en) * | 2021-06-15 | 2021-09-03 | 深圳朴坂科技有限公司 | Bladeless turbine with low input requirement and disc body thereof |
-
2021
- 2021-12-07 CN CN202111484973.3A patent/CN114165290B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1930394A (en) * | 2004-03-18 | 2007-03-14 | 弗兰克·丹尼尔·洛特里翁特 | Turbine and rotor therefor |
| CN102171413A (en) * | 2008-08-12 | 2011-08-31 | 西门子能源公司 | Canted outlet for transition in a gas turbine engine |
| CN103796762A (en) * | 2011-11-04 | 2014-05-14 | 日本精工株式会社 | Spindle device and electrostatic coating device |
| CN106015517A (en) * | 2016-07-20 | 2016-10-12 | 方年学 | Curvilinear-tooth point-line meshing gear and processing method thereof |
| CN109477417A (en) * | 2016-12-21 | 2019-03-15 | 三菱重工发动机和增压器株式会社 | The nozzle vane and turbine of turbocharger, turbocharger |
| CN111102063A (en) * | 2019-11-15 | 2020-05-05 | 车行天下网络科技股份有限公司 | Dual drive turbine |
| CN112523809A (en) * | 2020-11-30 | 2021-03-19 | 北京动力机械研究所 | Method for inhibiting unsteady airflow excitation force of turbine rotor blade |
| CN113339075A (en) * | 2021-06-15 | 2021-09-03 | 深圳朴坂科技有限公司 | Bladeless turbine with low input requirement and disc body thereof |
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| Publication number | Publication date |
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| CN114165290A (en) | 2022-03-11 |
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