WO2010107146A1 - 반작용식 터빈 - Google Patents

반작용식 터빈 Download PDF

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Publication number
WO2010107146A1
WO2010107146A1 PCT/KR2009/001389 KR2009001389W WO2010107146A1 WO 2010107146 A1 WO2010107146 A1 WO 2010107146A1 KR 2009001389 W KR2009001389 W KR 2009001389W WO 2010107146 A1 WO2010107146 A1 WO 2010107146A1
Authority
WO
WIPO (PCT)
Prior art keywords
injection
chamber
turbine
housing
steam
Prior art date
Application number
PCT/KR2009/001389
Other languages
English (en)
French (fr)
Korean (ko)
Inventor
김기태
Original Assignee
Kim Ki-Tae
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kim Ki-Tae filed Critical Kim Ki-Tae
Priority to PCT/KR2009/001389 priority Critical patent/WO2010107146A1/ko
Priority to US13/257,213 priority patent/US20120009055A1/en
Priority to CN200980158196.4A priority patent/CN102356214B/zh
Priority to JP2012500700A priority patent/JP5592933B2/ja
Priority to EP09841930.2A priority patent/EP2410127A4/de
Publication of WO2010107146A1 publication Critical patent/WO2010107146A1/ko

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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
    • F01D1/32—Non-positive-displacement machines or engines, e.g. steam turbines with pressure velocity transformation exclusively in rotor, e.g. the rotor rotating under the influence of jets issuing from the rotor, e.g. Heron turbines
    • 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
    • F01D1/18—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means
    • F01D1/22—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means traversed by the working-fluid substantially radially
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings

Definitions

  • the present invention relates to a reaction turbine using steam, gas or compressed air.
  • the steam turbine is a type of prime mover that converts the thermal energy of steam into mechanical work.
  • the steam turbine is widely used as a main engine for thermal power generation and ships because of low vibration, good efficiency, and high speed and high horsepower.
  • the steam turbine ejects and expands the high temperature and high pressure steam generated by the boiler from a nozzle or a fixed blade to generate a high speed steam flow, and induces the high speed steam flow to a rotating turbine blade to form the turbine. It is designed to rotate the shaft by impulse or reaction that occurs when it strikes the wing.
  • the steam turbine includes a plurality of nozzles for converting thermal energy of steam into velocity energy, and a plurality of turbine blades arranged in parallel with the plurality of nozzles to convert velocity energy into mechanical work.
  • the high-pressure steam flows into the steam chamber from the boiler, expands, and rotates the turbine shaft coupled with the turbine blade while passing through each nozzle and the turbine blade of the steam chamber and moves to the exhaust chamber.
  • the steam moved to the exhaust chamber was introduced into the condenser, cooled, and then returned to the boiler by a feed pump or discharged to the atmosphere.
  • the force for rotating the turbine shaft is proportional to the momentum of steam incident on the turbine blades
  • the momentum of the steam is determined by various factors such as the number and surface area of the turbine blades, the angle of incidence of the steam.
  • the steam impinging on the blades of the turbine is different in both speed and direction, it is difficult to properly design the shape, angle, and the like in consideration of all of them, so there is a limit in producing a turbine having high efficiency.
  • the present invention solves the problems of the conventional steam turbine as described above, even if condensed water is generated in the steam can prevent damage to the components due to the collision with the condensate in advance, thereby facilitating the management of steam It is an object of the present invention to provide a reaction steam turbine that can be used as well as inexpensive materials and can simplify the assembly process to reduce the manufacturing cost.
  • an object of the present invention is to provide a reaction steam turbine that can simplify the determination of the momentum due to steam to easily manufacture a turbine of high efficiency.
  • an object of the present invention is to provide a reaction steam turbine that can reduce the pressure loss of steam to increase the thermal efficiency of the turbine.
  • the housing is provided with at least one injection chamber; At least one injection rotation unit installed in the housing and rotating in reaction to the injection of the steam while injecting steam in the circumferential direction; And a turbine shaft rotatably coupled to the housing or coupled to rotate together with the housing to rotate together with the injection rotation and transmit the rotational force to another device.
  • the reaction steam turbine of the present invention is configured to rotate the injection rotating part and the turbine shaft using the repulsive force generated when the steam is injected from the injection rotating part, so that the steam turbine is mixed even if condensed water is mixed. It can maintain the stability of and greatly reduce the manufacturing cost. In addition, it can significantly reduce the flow resistance of the steam or prevent pressure leakage and reduce the energy loss to obtain a low-cost and high efficiency turbine.
  • FIG. 1 is a perspective view showing an embodiment of the reaction steam turbine of the present invention broken
  • FIG. 2 is a longitudinal sectional view showing an embodiment of the steam turbine according to Figure 1,
  • FIG 3 is a perspective view showing another embodiment of the injection passage in the steam turbine according to Figure 1,
  • FIG 4 is a longitudinal sectional view showing another embodiment of the steam turbine according to Figure 1,
  • 5 and 6 are a perspective view showing a steam guide installed in the housing of the steam turbine according to FIG.
  • FIG. 7 and 8 are perspective views showing the injection flow path of the steam turbine according to Figure 1 broken;
  • FIGS. 7 and 8 are longitudinal cross-sectional views showing embodiments of the shape of the injection passages according to FIGS. 7 and 8;
  • FIGS. 12 and 13 are perspective views showing embodiments of the shape of the injection pipe according to FIGS. 10 and 11;
  • 14 to 18 are longitudinal cross-sectional views and perspective views showing other embodiments of the reaction steam turbine of the present invention.
  • the reaction steam turbine includes a housing 110 having at least one injection chamber 112 and an injection chamber 112 of the housing 110. At least one injection rotation part which is disposed to overlap at a predetermined interval from the inner side to the outer side and rotates in response to the injection of steam (for convenience, divided into the first, second and third injection rotation parts from the inside to the outside)
  • One turbine shaft 130 which rotates together with 120A, 120B and 120C and the respective injection rotation parts 120A, 120B and 120C and transmits the rotational force to an external device (not shown). It includes.
  • the housing 110 is formed in a cylindrical shape and the inlet 111 is supplied steam through a boiler (not shown), and the injection chamber 112 extending from the inlet 111 is formed in a cylindrical shape and
  • the guide part 113 extends to communicate with the injection chamber 112 and is formed in a substantially truncated cone shape, and the discharge part 114 extends to communicate with the guide part 113 and has a cylindrical shape.
  • the inlet 111 is formed on the same center line as the outlet 114, the outer peripheral surface is supported by a first bearing 141 to rotate the steam turbine.
  • the inlet 111 may be formed through one side of the injection chamber 112.
  • an extension part (not shown) extending from the first injection rotation part 120A may be supported by the first bearing 141 so as to be sealedly coupled through the inlet part 111.
  • the inner circumferential surface of the injection chamber 112 may be formed in a smooth tube shape, and the injection rotation parts 120A, 120B, and 120C to guide the movement of steam injected from the third injection rotation part 120C.
  • Steam guide portion may be formed in the forward direction with respect to the rotation direction of the.
  • the steam guide portion may be formed by grooves 112a at regular intervals in the circumferential direction as shown in FIG. 5, or may be formed by mounting the blades 112b at predetermined intervals in the circumferential direction as shown in FIG. 6. .
  • the guide part 113 has an inner circumferential surface of the guide part 113 so as to have a diameter smaller from the injection chamber 112 toward the discharge part 114 so that steam passing through the injection chamber 112 can be smoothly guided to the discharge part 114. It is formed to be inclined.
  • the guide portion 113 may be formed vertically so that a portion meeting the discharge portion 114 may be rounded or inclined.
  • the discharge portion 114 may be formed in a cylindrical shape as shown in Figure 2, in some cases may be formed through the end of the guide portion 113.
  • the injection rotating parts 120A, 120B, and 120C are formed in hollow cylinders whose both ends in the axial direction are sealed, and are arranged to radially expand (first, second, first, and second, for convenience.
  • the chambers 121, 122, and 123 are formed along the circumferential direction on the outer circumferential surfaces of the chambers 121, 122, and 123.
  • the chambers 121, 122, and 123 have the same volume of the inner spaces S1, S2, and S3, and have an inner circumferential surface in the shape of a smooth tube.
  • One side of the chambers 121, 122, and 123 may be sealed to one inner wall of the housing 110 while the other side of the chambers 121, 122, 123 may be welded to seal the turbine shaft 130.
  • Plates 127a and 127b are formed.
  • the flow blocking plates 127a and 127b may be formed to extend from the outer side of the inner chamber to the inner side of the outer chamber so that steam is injected from the inner chamber and guided smoothly to the injection passages 125 and 126 of the outer chamber. have.
  • the chambers 121, 122, and 123 may be formed to have different volumes of the internal spaces S1, S2, and S3.
  • the inner spaces S1, S2, and S3 of the chambers 121, 122, and 123 may be proportional to the total cross-sectional area of the corresponding injection passages 124, 125, and 126. You can increase or decrease the size.
  • Each of the injection passages 124, 125, and 126 may be formed in a plurality of circles at regular intervals along the axial direction as shown in FIG. 7, and one or more along the axial direction as shown in FIG. 8. It may be formed one by one in the shape of a long hole.
  • the injection passages 124, 125, and 126 may be formed at regular intervals along the circumferential direction as shown in FIGS. 2 and 9 to 11.
  • the injection passages 124, 125, 126 in the chambers 121, 122, 123 may have the same cross-sectional area in the axial direction, and in some cases, the axial direction. It may be formed differently along.
  • the injection flow paths 124, 125, and 126 are respectively formed from the inner chamber to the outer chamber so that the pressure of steam can be lowered through the chambers 121, 122, 123 as shown in FIG. 2.
  • the cross-sectional area can be formed wide.
  • the volume of each of the chambers 121, 122, 123 may be the same from the inner side to the outer side, or may be gradually widened.
  • the volume of each of the chambers 121, 122, 123 may be gradually reduced from the inner side to the outer side in consideration of the overall cross-sectional area of the injection passages 124, 125, 126.
  • the total injection flow path cross-sectional area of each of the chambers 121, 122, and 123 may be adjusted to have different cross-sectional areas of each injection flow path, but the number of injection flow paths of each of the chambers 121, 122, and 123 may be adjusted. Can be adjusted to be different from each other. For example, as shown in FIG. 2, the number of the injection passages 124, 125, 126 is gradually increased from the inner chamber to the outer chamber so that the entirety of each of the chambers 121, 122, 123 is increased.
  • the injection oil can enlarge the cross-sectional area.
  • the injection passages 124, 125, and 126 may be shaped in various ways.
  • the injection passages 124, 125, and 126 are circumferentially formed on the outer circumferential wall surfaces of the chambers 121, 122, and 123 as shown in FIGS. 1, 2, and 7 to 9. It may be formed to be obliquely simple through, and as shown in Figs. 3, 10 and 11, the injection holes 124a, 125a, 126a radially on the outer circumferential wall surface of the chambers 121, 122, 123.
  • the injection passages 124, 125, 126 may be formed to be rotated in a rotational direction with respect to the normal direction of the injection rotation parts.
  • the injection holes 124a, 125a and 126a are formed to be distorted in the rotational direction.
  • the injection holes 124a, 125a and 126a are radial.
  • the outlet end of the injection pipe 124b, 125b, 126b is bent or inclined in the rotational direction.
  • the injection holes 124a, 125a, 126a and the injection pipes 124b, 125b, 126b may be formed separately, respectively, as shown in FIGS. 12 and 13.
  • 124a, 125a and 126a and the injection pipes 124b and 125b and 126b may be elongated in the axial direction.
  • the internal flow paths 124c and 125c of the injection pipes 124b, 125b and 126b as shown in FIG. 126c may be formed in one long hole shape, or may be formed of a plurality of multi-holes as shown in FIG. 13.
  • the turbine shaft 130 penetrates the center of the housing 110 and the center of each of the injection rotating parts 120A, 120B, and 120C, and part of the turbine shaft 130 is each of the injection rotating parts 120A, 120B ( Welding to the chambers 121, 122, 123 of 120C.
  • One end of the turbine shaft 130 may be rotatably supported by the second bearing 142 so that the entire steam turbine including the turbine shaft 130 may rotate.
  • the diameter of the turbine shaft 130 is formed smaller than the diameter of the inlet 111 or outlet 114 of the housing 110 so that steam can flow to the outside of the turbine shaft 130.
  • reaction steam turbine according to the present invention as described above is operated as follows.
  • the steam generated in the boiler is supplied to the inlet 111 of the housing 110 through the pipe, the steam is introduced into the first chamber 121 of the first injection rotation unit 120A, The steam of the first chamber 121 is injected circumferentially through the first injection passages 124 and flows into the second chamber 122 of the second injection rotating part 120B.
  • the steam is injected in the circumferential direction through the second injection passages 125 of the second injection rotation unit 120B to the third chamber 123 of the third injection rotation unit 120C, and the 3 is injected in the circumferential direction through the third injection passages 126 of the rotary injection unit 120C is injected into the injection chamber 112 of the housing 110, the steam is guide portion ( 113 and the discharge unit 114 is discharged to the atmosphere or is returned to the condenser (not shown) is repeated a series of processes to be returned to the boiler.
  • the turbine shaft 130 passes through the housing 110 so that one side of the turbine shaft 130 is supported by the first bearing 141 and one side of the housing 110 is second. Although it was supported by the bearing 142, in this embodiment, as shown in FIG. 14, the turbine shaft 130 penetrates through the housing 110, and both sides of the turbine shaft 130 are respectively the first bearing 141. And is supported by the second bearing 142.
  • one side of the turbine shaft 130 may be supported by the first bearing 141 outside the discharge portion 114 of the housing, and in some cases between the discharge portion 114 of the housing 110. May be supported by the first bearing 141.
  • the discharge part 114 is formed in a cylindrical shape, but the first bearing 141 is disposed between the discharge part 114 and the discharge part 114.
  • the other side of the turbine shaft 130 may be supported by the second bearing 142 outside the inlet 111 of the housing 110, and in some cases with the inlet 111 of the housing 110.
  • the second bearing 142 may be supported by the second bearing 142 in between.
  • the inlet 111 is formed in a cylindrical shape, but the second bearing 142 is between the inlet 111.
  • the second bearing 142 When disposed in the ribs 111a may be formed radially on the inlet 111 so that steam may smoothly flow into the first injection rotation unit 120A.
  • the steam turbine of the present embodiment may be configured such that the housing 110 and the injection rotating parts 120A, 120B, 120C are in sliding contact with each other, as shown in FIG. 14, so that the housing 110 does not rotate. Only the injection rotation parts 120A, 120B, 120C and the turbine shaft 130 can rotate, so that more power can be transmitted to an external device, thereby increasing energy efficiency.
  • the turbine shaft 130 is supported by a bearing through the housing 110, but this embodiment has one side of the turbine shaft 130 as shown in FIG. 15.
  • the inside of the housing 110 is coupled to the injection rotating parts (120A, 120B, 120C) and only the other side is rotatably supported by the first bearing (141).
  • the inlet 111 is protruded from the other side of the housing 110 so that the inlet 111 is rotatably supported by the second bearing 142.
  • the turbine shaft 130 is provided separately from the housing 110 to be penetrated and coupled thereto.
  • the housing 110 and the turbine shaft 130 are as shown in FIG. 16. ) Is integrally formed.
  • the inlet part 111 and the outlet part 114 of the housing 110 are formed long, and the outlet part 114 of the housing 110 is coupled to an external device, and the injection rotation parts 120A, 120B, and 120C are connected to the external device.
  • the propulsion force generated from) is transmitted to the external device through the housing 110. That is, the housing 110 is to play the role of the turbine shaft 130 together.
  • the injection rotation parts are arranged to radially overlap one housing, but in this embodiment, the plurality of housings and the injection rotation parts are arranged at intervals in the axial direction. .
  • the steam turbine of the present embodiment includes a plurality of housings (first, second and third housings 210 for convenience, from the current side to the downstream side, as shown in FIGS. 17 and 18) to be spaced apart by a predetermined interval in the axial direction.
  • 220 and 230 are disposed, and the injection rotation parts 240 and 250 and 260 in the injection chambers 212, 222 and 232 of the housings 210, 220 and 230, respectively.
  • the plurality of injection rotating parts 240, 250, and 260 are welded to one turbine shaft 280 penetrating through the center thereof, and one side of the turbine shaft 280 is the third housing 230. ) Is rotatably supported by the fourth bearing 274, or rotatably supported by the fourth bearing 274 between the third housing 230 as shown in FIGS. 17 and 18.
  • the first to third housings 210, 220 and 230 have an inner circumferential surface of the downstream side injection rotation parts 250 and 260 on one side of the respective injection chambers 212,222 and 232.
  • the guides 213, 223, and 233 inclined toward the chambers 251 and 261 and the discharge part 234 to be described later are formed.
  • These guides 213, 223, 233 are chambers 251 of the downstream injection rotary parts 250, 260 in which steam is injected into the respective injection chambers 212, 222, 232. 261) or to be guided to the outside smoothly.
  • the inner wall surfaces of the first to third housings 210, 220, 230 may be formed in a smooth tube shape, but the steam injected from the respective injection rotation parts 240, 250, 260 may be formed.
  • An additional may be formed.
  • Each of the chambers 241, 251, 261 of the first to third injection rotation parts 240, 250, 260 may be formed in the same volume or in different volumes.
  • the volume of each of the chambers 241, 251, 261 is determined according to the ratio of the total cross-sectional area of the injection passages 242, 252, 262 provided in the chambers 241, 251, 261. Can be done.
  • the total cross-sectional area of each of the injection passages 242, 252, 262 is the current side, the downstream side, that is, It may be preferable that the pressure of the steam may be lowered step by step from the first injection rotation part 240 to the third injection rotation part 260.
  • each of the injection flow paths 240, 250, and 260 may be adjusted to have different cross-sectional areas of each of the injection flow paths, or may be adjusted by varying the number of the injection flow paths. For example, in FIGS. 17 and 18, the number of injection passages 242, 252, and 262 increases from the first injection rotation unit 240 to the third injection rotation unit 260.
  • the reaction steam turbine according to the present invention is to obtain the propulsion force by the reaction force while the steam delivered from the boiler is injected through the injection passage in each injection rotation part, even if condensed water is mixed in the steam delivered from the boiler There is no risk of damage to the steam turbine components due to condensate.
  • the stability of the steam turbine is not only greatly improved, there is no fear of damage to the steam turbine, and thus a relatively inexpensive material can be used and the assembly process can be simplified, thereby significantly reducing manufacturing costs.
  • conventional impeller turbines require precise design, fabrication and complex assembly of hundreds to thousands of impellers, and thus require a lot of advanced manpower and precision, whereas the present invention provides precision required for the design or fabrication of parts such as impellers. Highly low and highly efficient turbines can be obtained, which can be manufactured at significantly lower cost than current impeller turbines.
  • the steam turbine according to the present invention can not only reduce the size of the entire steam turbine as a plurality of injection rotational portions for radial stability, but also flow for steam between the injection rotational portions of the steam turbine. Since no resistance is generated, the efficiency of the steam turbine or the relative efficiency of the boiler can be greatly improved. It is possible to reduce the flow resistance of steam as the inclined guide portion is formed in the housing even when the injection rotation part is disposed in the axial direction, thereby improving the efficiency of the steam turbine and the relative efficiency of the boiler.
  • the steam turbine of the present invention utilizes the action and reaction, which is the third law of Newton's motion, and can reduce energy consumed to generate propulsion in the turbine as in the case of an impeller turbine (or a momentum transfer turbine).
  • the high efficiency steam turbine can be obtained.
  • the steam turbine of the present invention when the pressure of steam from the boiler is constant and the speed of steam injected from the injection rotating part is equal to the circumferential speed caused by the rotation of the injection rotating part, the steam is applied to the injection rotating part. At rest, only the injection rotor moves at the same speed as the steam's injection speed and moves in the opposite direction of the tangential, resulting in a theoretical energy transfer efficiency of 100% of the total momentum or total kinetic energy the steam had. Therefore, the steam turbine of the present invention can obtain a high efficiency that can not be reached theoretically in any impeller turbine.
  • reaction turbine according to the present invention can be similarly applied to an engine using a gas turbine, compressed air, or the like as well as the steam turbine described above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Nozzles (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
PCT/KR2009/001389 2009-03-18 2009-03-18 반작용식 터빈 WO2010107146A1 (ko)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/KR2009/001389 WO2010107146A1 (ko) 2009-03-18 2009-03-18 반작용식 터빈
US13/257,213 US20120009055A1 (en) 2009-03-18 2009-03-18 Reaction-type turbine
CN200980158196.4A CN102356214B (zh) 2009-03-18 2009-03-18 反作用式涡轮
JP2012500700A JP5592933B2 (ja) 2009-03-18 2009-03-18 反作用式タービン
EP09841930.2A EP2410127A4 (de) 2009-03-18 2009-03-18 Reaktionsturbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2009/001389 WO2010107146A1 (ko) 2009-03-18 2009-03-18 반작용식 터빈

Publications (1)

Publication Number Publication Date
WO2010107146A1 true WO2010107146A1 (ko) 2010-09-23

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PCT/KR2009/001389 WO2010107146A1 (ko) 2009-03-18 2009-03-18 반작용식 터빈

Country Status (5)

Country Link
US (1) US20120009055A1 (de)
EP (1) EP2410127A4 (de)
JP (1) JP5592933B2 (de)
CN (1) CN102356214B (de)
WO (1) WO2010107146A1 (de)

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JP2013154159A (ja) * 2011-11-04 2013-08-15 Toshiyuki Kamimura 吸引による推力回転装置
US20130318974A1 (en) * 2011-03-02 2013-12-05 Ki Tae Kim Gas turbine
US20140248124A1 (en) * 2011-09-30 2014-09-04 Hk Turbine Co., Ltd. Reactive turbine apparatus
JP2015505931A (ja) * 2011-12-07 2015-02-26 ジャレド ホールディングス リミテッド 機械仕事を生み出すための方法

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US20150082793A1 (en) * 2012-04-03 2015-03-26 Equitherm S.À R.L. Device for power generation according to a rankine cycle
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JP3182052U (ja) * 2012-12-14 2013-03-07 俊之 上村 吸引回転ブラシ掛け装置
KR101418345B1 (ko) * 2013-09-27 2014-07-10 최혁선 축류형 다단 터빈의 구조
KR101667386B1 (ko) * 2014-12-24 2016-10-19 포스코에너지 주식회사 축력 특성이 개선된 스팀 터빈
DE102015112569A1 (de) * 2015-07-30 2017-02-02 Sabine Hilpert Vorrichtung zur Energieumwandlung
US10519858B2 (en) * 2016-07-22 2019-12-31 Brent Wei-Teh LEE Engine, rotary device, power generator, power generation system, and methods of making and using the same
CN113217114B (zh) * 2021-05-31 2022-11-01 张龙 一种封闭旋转式环形涡喷蒸汽轮

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US20120009055A1 (en) 2012-01-12
EP2410127A1 (de) 2012-01-25
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