WO1997040259A1 - Turbine a vapeur sans pales - Google Patents

Turbine a vapeur sans pales Download PDF

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Publication number
WO1997040259A1
WO1997040259A1 PCT/CN1997/000029 CN9700029W WO9740259A1 WO 1997040259 A1 WO1997040259 A1 WO 1997040259A1 CN 9700029 W CN9700029 W CN 9700029W WO 9740259 A1 WO9740259 A1 WO 9740259A1
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WO
WIPO (PCT)
Prior art keywords
steam
stator
rotor
holes
exhaust
Prior art date
Application number
PCT/CN1997/000029
Other languages
English (en)
Chinese (zh)
Inventor
Quangui Shen
Original Assignee
Quangui Shen
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=5118222&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO1997040259(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Quangui Shen filed Critical Quangui Shen
Priority to AU25024/97A priority Critical patent/AU2502497A/en
Publication of WO1997040259A1 publication Critical patent/WO1997040259A1/fr

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Classifications

    • 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
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • the present invention relates to a steam turbine, in particular to a bladeless steam turbine that converts thermal energy into a mechanical energy device.
  • the vane turbine following the piston steam engine has been widely used in industrial production.
  • the existing back pressure type, extraction type, condensing type, intermediate reheating type, etc. but their basic structure is generally the same, all are equipped with Multi-pressure stage device composed of moving blades and stationary blades, relying on steam
  • Vane turbines mainly include intake chambers, nozzles, moving blades, stationary blades, rotors, stators, main shafts, sliding bearing exhaust chambers, bolts and heat insulation layers, etc., except for the blades, rotors and stators of the main structure. Except that the pressure angles of the two pressure stages are the same, most of the dynamic and static blades of the pressure stages are from the root (axial) 15. ⁇ 30. Start at blade tip (axial) 70. ⁇ 85. The structure of the twisted and unrolled shape from thick to thin, the geometry of all the blades is very complicated.
  • the purpose of the present invention is to provide a bladeless turbine that significantly improves the power and effective thermal efficiency of a power machine, which mainly works by condensing and shrinking the volume of steam (working medium).
  • Bladeless steam turbine including stator, rotor, end cover, main shaft, bearings, inlet chamber, exhaust chamber, bolts, tripods and strong ribs, the shaft and rotor use a shaft key to cooperate statically, and the two ends of the shaft are connected to the bearing to move
  • the mating and end caps are bolted and screwed, and are characterized by: 1) the stator is made of a double-layered inner shell with a tapered sleeve, and the outer shell is a cooling water chamber; the cooling water chamber is provided with an inlet and a drainage pipe; The inner shell has a frustoconical shape, and the axial taper of the inner surface is 3 to 30 X.
  • the circumferential direction of the inner shell is provided with air holes and exhaust holes with equal intervals of 6 to 20 levels.
  • the holes are radially spaced at a circumferential angle of 4-30 °, and the holes are in the same direction and are 35 ° to 65 ° from the radial center perpendicular.
  • the inclination angle H3 ⁇ 4 is perpendicular to the axial centerline.
  • Each exhaust hole is connected to the next-stage intake hole, while the first-stage intake hole is connected to the intake chamber, and the last-stage exhaust hole is connected to the exhaust hole.
  • the chambers are connected, each pair of adjacent intakes
  • the rotor also has a frustoconical shape and is sleeved in the stator inner shell.
  • the rotor and the stator have a dynamic fit with a taper, that is, the axial inclination angle outside the rotor cone is the same as the axial inclination angle of the tapered inner surface of the stator inner shell.
  • the number of inlet and exhaust steam stages set in the axial direction of the rotor is the same as the number of steam holes in the stator.
  • the cavities distributed around the rotor are evenly spaced in the radial direction, and the interval angle of the cavities is 2. ⁇ 25.
  • the radial directions of the cavities are all the same and are consistent with the direction of the steam holes of the stator.
  • the backward inclination angle of the rear steam cavity surface in the radial direction is 20. -45 °, the two parallel axial spacers of the cavities are perpendicular to the central axis.
  • the rotor and the stator use the same taper, and self-phase running-in can be achieved after finishing. High concentricity can be achieved.
  • the axial movement can be adjusted to compensate the gap caused by the thermal expansion of the metal. Adjusted to the critical gap, because the above gap is small, the fluid on the rotor surface forms a vapor film seal, because the gap seal between the stator and the rotor can improve the efficiency of the machine by 3%-5%.
  • the present invention can improve the effective thermal efficiency by about 20% to 38% compared with the existing bladed steam turbine.
  • the above-mentioned thermal efficiency improvement radius is different.
  • the general trend of improving the thermal efficiency of the steam turbine of the present invention is no doubt.
  • FIG. 1 is a radial sectional view of a vaneless steam turbine according to the present invention
  • FIG. 2 is an axial half-section view of a vaneless steam turbine according to the present invention.
  • FIG. 3 is a schematic diagram of a radial working principle of a vaneless steam turbine according to the present invention.
  • Figure 4 is the axial working principle diagram of the vaneless turbine of the present invention.
  • FIG. 1 and 2 show an embodiment of a vaneless steam turbine according to the present invention, which includes a stator
  • the stator (1) is formed by nesting an inner shell (5) and an outer shell (6).
  • the inner shell (5) is frusto-conical to form a double-layered tapered stator (1).
  • the inner layer and the outer layer are The cooling water chamber (23), the cooling water flows from the water inlet pipe (21) into the cooling water chamber (23), and flows out from the drainage pipe (22).
  • the inner shell is provided with a 12-stage radial deflection angle 45.
  • the steam inlet holes (3) and steam exhaust holes (4) are evenly spaced symmetrically, and the circumference angle of the space is 10.
  • the 12-stage steam holes are evenly spaced along the axis to form 36 groups of holes spaced in and out in the circumferential direction.
  • Each steam hole is perpendicular to the axis in the axial direction, and the radial angle of the steam holes is uniformly eccentrically inclined. Angle 45.
  • the exhaust hole of the upper stage is connected with the intake hole of the next stage, the steam inlet of the first stage is connected with the steam inlet chamber (2), and the exhaust pipe of the last stage is connected with the exhaust chamber (8).
  • the steam inlet of the steam chamber (2) is provided with a steam inlet flange (19), and the steam outlet of the exhaust chamber (8) is provided with a steam exhaust flange (20).
  • Each group of steam inlets on the outer circumferential surface of the inner shell A steam hole cover (7) is provided on the hole and the steam exhaust hole.
  • the rotor (10) also has a truncated cone and is sleeved on the inner shell of the stator to form the same taper dynamic fit of the rotor and the stator.
  • the axial inclination angle of the outer surface of the rotor periphery is consistent with the inclination of the inner surface of the stator shell, and its inclination design Into 3 ⁇ 30.
  • a 12-stage small cavities (9) are set on the rotor, and the circumferential angle of the radial interval between the cavities is 8.
  • the radial direction in the small steam cavity is the same and is consistent with the stator steam hole direction, and the rear inclination angle of the rear steam cavity surface (subject to the rotor's turning) is 35.
  • the backward tilt angle of the front steam cavity surface is 5 °
  • the axial direction of the small steam cavity is parallel to the vertical center axis of the two surfaces.
  • the main shaft (12) and the rotor (10) are statically fitted with a shaft chain (11).
  • the sliding or rolling bearing (16) is placed at the center of 18), and the bearing cover (14) is fastened to the two ends of the stator with bolts (15) during assembly.
  • the foot frame (24) is provided with ground screw holes ( 25).
  • auxiliary devices such as axial seals, couplings, centrifugal automatic governors, steam control valves and steam control levers, and related systems are added to the heat insulation layer and related systems to form a complete set of Blade turbine equipment.
  • the working medium enters the steam inlet chamber (2) in the upper part of the stator (1) in the direction of arrow A, so that all the nozzles (steam inlets) of the entire first pressure stage have uniform pressure, and high-pressure steam is in the first stage nozzle. (3) is accelerated in the channel to generate kinetic energy, that is, the impact energy of steam, high-speed steam impacts the small steam cavity in the rotor (10), and the generated kinetic energy is transmitted to the shaft to perform external work.
  • the steam in the first pressure stage moves radially with the rotor (10) forward (see Figure 1), and flows out through the steam outlet (4) of the first pressure stage. The steam enters the first pressure stage, Once the first kinetic energy transfer is completed, the first work is performed.
  • the steam discharged from the first pressure stage flows axially along the steam hole cover (7) and enters the second pressure stage nozzle (3) to accelerate and impact the small steam cavity again.
  • the steam enters and exits for the second time, and the kinetic energy generated by the second pressure stage is transmitted again through the shaft to perform work.
  • the steam flows from the high pressure to the low pressure in this order and works repeatedly, and the pressure drops gradually, and the steam
  • the final work is performed through the nozzle (3) of the last stage (twelfth stage), and the exhaust chambers of the exhaust holes (4) of the last stage are merged and then exhausted.
  • FIG 3 is a schematic diagram of the rotational torque force due to the centrifugal pressure of the steam.
  • the rotational torque force is generated by the eccentric inertial impact caused by the high-speed steam flowing out of the mouth of the mouth.
  • stator inner shell (5) is processed in the circumferential direction of the nozzle (3) and the exhaust (4), the same method of inclined eccentric hole machining is used.
  • the inclined eccentric angle of the hole is formed with the center vertical line of the stator (1). 35. -65.
  • the inclination and eccentricity are directly proportional to the magnitude of the torque force.
  • the steam in the passage of the steam hole cover of the stator (1) produces a stepwise decompression and acceleration axial movement, and the expansion of the steam hole cover (7) produces the function of storing energy, so that the next pressure stage has sufficient quality improvement.
  • High steam transfer energy mass is proportional to energy in motion). Increasing the mass of working medium step by step is another special option for this structure.
  • the present invention mainly uses condensing steam to reduce the pressure of the steam flow and accelerate the volume to reduce the pressure. It is completely opposite to the working principle of the expansion expansion and drag reduction and acceleration of the vane steam turbine, which chooses to shrink the working medium.
  • the working principle of non-expansion can effectively recover the waste heat of the steam and play a regeneration cycle.
  • the stator (1) uses an inner shell (5) and an outer shell (6).
  • the sleeve structure sealing device uses cooling water (23) as a coolant. It plays two roles, one is to cool the high-temperature steam to reduce the volume and generate a pressure drop, so as to reduce the flow resistance and accelerate the fluid. The second is that the high-temperature steam passes through the inner shell (5) and the steam hole cover (7).
  • the large-area heat conduction and radiation of metal produce heat exchange, so that the waste heat of steam can be recycled and the utilization rate can be increased by 30% to 40%.
  • the torque generated by the device is the sum of the eccentric pressure of the steam from all the inclined eccentric holes of the device, and the power generated by the rotor is the sum of the energy chapters of the high-velocity impact and reaction kinetic energy generated by the high pressure of steam.
  • the inner surface of the inner shell (5) of the stator (1) is consistent with the outer surface of the rotor (10), and is processed into a conical structure with the same taper.
  • the function of the same taper is that the taper can be adjusted to optimize the seal after a single match. Clearance to eliminate misalignment errors caused by machining and assembly tolerances. Inclined taper is conducive to adjusting sealing clearance and improving sealing performance. Due to the multi-stage (6-20) structure, the utilization of the exhaust steam excess speed energy is fully improved Therefore, the output (rated power) is increased.
  • the porous structure of the stator is required to increase the eccentric pressure and capacity. Without affecting the welding hole cover, the circumferential distribution angle of the inlet and exhaust holes should be 3-30.
  • the (axial) centerline of the steam holes of each pressure stage on the outer circumferential surface of the stator inner shell is consistent.
  • the nozzle steam holes and the central vertical line form an inclined slope of 35. ⁇ 65. Eccentric angle (see Figure 3).
  • the rotor (10) adopts multiple small cavities (9), which increases the effective force area and increases the power.
  • the pressure stages of the small cavities (9) should be the same as the pressure stages of the stator (1). Each pressure There is no limit to the number of small cavities (single and even) in each stage.
  • the (axial) centerline of the cavities between each stage does not have to be aligned, which can increase the distribution of torque.
  • the diameter of the small cavities (9) in each pressure stage The distribution angle is 2-25. It is uniformly distributed in the circumferential direction.
  • the axial two parallel planes of each small air cavity are perpendicular to the axis, and the backward inclination angle of the rear steam cavity surface in the radial direction is 20 to 45.
  • the backward tilt angle of the front steam cavity surface in the radial direction is 5-15 °. This angle is favorable for receiving steam impact force and reducing the effect of centrifugal force generated when the rotor (10) is running.
  • cooling water and steam convection improves the heat exchange rate and cooling effect, and increases the water temperature, reduces the steam temperature, and increases the value of waste heat utilization.
  • the capacity of the cross-sectional area of the steam hole cover (7) is 2 to 10 times larger than the capacity of the cross-sectional area of the inlet and exhaust holes (14), which is conducive to the accelerated flow of steam in the axial direction and the energy accumulation and storage function. It can expand the heat dissipation area and increase the cooling effect.
  • Both the stator (1) and the rotor (10) adopt a monolithic structure, and its role is to improve the tensile and shear strength of the metal under thermal stress and improve the mechanical properties of the metal.
  • the stator (1) and the rotor (10) adopt non-friction Dynamic cooperation, so that the main body of the device does not wear, which is beneficial to improve the service life.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Cette invention concerne une turbine à vapeur sans pales, laquelle comprend un stator, un rotor, un arbre d'entraînement, une chambre d'admission et d'évacuation, des caches latéraux, un support, une base et des tendeurs. Le stator se compose de boîtiers interne et externe coniques qui sont reliés l'un à l'autre. Une chambre de refroidissement à eau sépare le stator du rotor. Le rotor conique et mobile est monté à l'intérieur du boîtier interne qui possède une même forme conique. Le stator comprend des orifices d'admission et d'évacuation qui forment un agencement incliné sur le plan radial, et qui sont recouverts par des caches. De nombreuses cavités sont réparties régulièrement en réseau et selon un angle de 2 à 25° à la surface du rotor, lesquelles cavités correspondent tant par leur nombre que par leur direction à celles des orifices du stator. Ce système permet d'accroître la puissance ainsi que l'efficacité thermique.
PCT/CN1997/000029 1996-04-18 1997-04-08 Turbine a vapeur sans pales WO1997040259A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU25024/97A AU2502497A (en) 1996-04-18 1997-04-08 A non-blade steam turbine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN96103835A CN1056435C (zh) 1996-04-18 1996-04-18 无叶汽轮机
CN96103835.7 1996-04-18

Publications (1)

Publication Number Publication Date
WO1997040259A1 true WO1997040259A1 (fr) 1997-10-30

Family

ID=5118222

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN1997/000029 WO1997040259A1 (fr) 1996-04-18 1997-04-08 Turbine a vapeur sans pales

Country Status (3)

Country Link
CN (1) CN1056435C (fr)
AU (1) AU2502497A (fr)
WO (1) WO1997040259A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012122940A1 (fr) * 2011-03-16 2012-09-20 Shi Jian Turbine de tesla

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100366871C (zh) * 2004-03-19 2008-02-06 刘富清 冲击式发动机
CN103835768B (zh) * 2012-11-22 2019-01-11 芜湖文青机械设备设计有限公司 一种汽轮机
CN105464878B (zh) * 2015-12-16 2017-11-07 山东新阳光机械制造有限公司 一种液压马达
CN106917640B (zh) * 2017-05-12 2020-05-22 陈晓兵 一种汽轮机无叶片叶轮、转子及多通道汽轮机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2888240A (en) * 1956-03-07 1959-05-26 Allis Chalmers Mfg Co Fluid cooled barrel cylinder for turbines
EP0349518A2 (fr) * 1988-05-05 1990-01-03 Johann Lukatsch Turbine à impulsion avec chambre de combustion avec tube à flamme
EP0625629A1 (fr) * 1993-05-21 1994-11-23 Shu Ping Chen Turbine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2047306U (zh) * 1989-04-04 1989-11-08 吴伯南 小型无叶片汽轮机组
US5344281A (en) * 1990-04-03 1994-09-06 Osoboe Konstruktorskoe Bjuro Po Konstruirovaniju, Issledovaniju I Vnedreniju Glubinnykh Besshtangovykh Nasosov Rotary vortex machine
RU2065978C1 (ru) * 1994-05-20 1996-08-27 Вячеслав Семенович Муравин Паросиловая двигательная установка

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2888240A (en) * 1956-03-07 1959-05-26 Allis Chalmers Mfg Co Fluid cooled barrel cylinder for turbines
EP0349518A2 (fr) * 1988-05-05 1990-01-03 Johann Lukatsch Turbine à impulsion avec chambre de combustion avec tube à flamme
EP0625629A1 (fr) * 1993-05-21 1994-11-23 Shu Ping Chen Turbine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012122940A1 (fr) * 2011-03-16 2012-09-20 Shi Jian Turbine de tesla

Also Published As

Publication number Publication date
CN1056435C (zh) 2000-09-13
CN1153864A (zh) 1997-07-09
AU2502497A (en) 1997-11-12

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