WO2010107276A2 - Turbine multi-etage a ecoulement axial - Google Patents

Turbine multi-etage a ecoulement axial Download PDF

Info

Publication number
WO2010107276A2
WO2010107276A2 PCT/KR2010/001712 KR2010001712W WO2010107276A2 WO 2010107276 A2 WO2010107276 A2 WO 2010107276A2 KR 2010001712 W KR2010001712 W KR 2010001712W WO 2010107276 A2 WO2010107276 A2 WO 2010107276A2
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
fluid
housing
guide groove
front impeller
Prior art date
Application number
PCT/KR2010/001712
Other languages
English (en)
Korean (ko)
Other versions
WO2010107276A3 (fr
Inventor
최혁선
Original Assignee
Choi Hyuck Sun
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 Choi Hyuck Sun filed Critical Choi Hyuck Sun
Publication of WO2010107276A2 publication Critical patent/WO2010107276A2/fr
Publication of WO2010107276A3 publication Critical patent/WO2010107276A3/fr

Links

Images

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
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/04—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially axially
    • 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

Definitions

  • the present invention relates to an axial multistage turbine, and more particularly, to an axial multistage turbine that generates power by converting a linear motion of a fluid into a rotary motion.
  • Turbines are machines that convert the energy of fluids such as liquids and gases into useful mechanical work.
  • the turbine is to generate a rotational power by using the kinetic energy of the fluid flowing in a straight line, by planting a plurality of vanes or wings in the rotating body and by generating steam or gas to rotate the high speed to generate power.
  • the gas turbine compresses air, supplies it into a closed container, and injects fuel to inject the combustion gas of high temperature and high pressure into the blade of the turbine which is a rotating body to obtain rotational force.
  • the gas turbine has a disadvantage of low thermal efficiency, high fuel consumption, and complicated structure and large size of the rotating body, which requires a large space in the axial direction and thus is not easy to install.
  • Korean Patent Publication No. 10-0550366 discloses an axial multistage turbine.
  • the axial multi-stage turbine is a turbine impeller coupled with a circular cylindrical wheel formed at a diagonal angle in one direction from the fluid inlet at the front to the fluid outlet at the rear by drilling concentric circles adjacent to the circular plate body centered on the rotating shaft. It is provided.
  • the axial flow type multistage turbine does not affect the rotational force of the rotating body because the fluid introduced into the through hole of the circular plate is discharged to the rear of the circular plate instead of rotating the circular plate. Since the nozzle plate is fixed and the fluid is injected to the rear circular plate body, as the rotational speed of the circular plate body increases, the force of the fluid is inversely proportional to the rotational speed.
  • the axial multistage turbine is required to change the position of the through holes in multiple stages so as to interfere with the fluid passing through the through holes in order to increase the amount of power generated, so that a large number of circular plates are required, resulting in a large manufacturing cost and manpower. This is required, and the manufacturing process is complicated because each circular plate must be matched according to the moving direction of the fluid. There is a disadvantage in that it reduces the power production efficiency.
  • the present invention was devised to solve the above problems, and is easy to install or manufacture, and minimizes the loss and pressure drop of the fluid flowing into the housing, and the fluid hits the rotating body perpendicularly to the rotational direction of the rotating body. It is an object of the present invention to provide an axial multi-stage turbine that maximizes the power generation efficiency of a turbine.
  • the axial flow type multi-stage turbine includes a housing in which an inlet and an outlet are formed to allow fluid to flow therein, a rotating shaft rotatably installed in the housing, and installed in the rotating shaft.
  • a front impeller formed with a plurality of through holes penetrated to guide the fluid to the rear through the fluid, and fixed to the rotation shaft behind the front impeller, and rotating the fluid to rotate the rotation shaft.
  • At least one guide groove is formed to guide in the direction, the fluid flowing horizontally along the guide groove at the end of the guide groove perpendicularly hit the wall formed in the guide groove, discharge the fluid to the rear to generate a rotational force
  • At least one rear impeller having a rear outlet is formed.
  • the front impeller is fixed to the inside of the housing to rotatably support the rotating shaft, the through hole of the front impeller is in communication with the vertical portion and the vertical portion formed in parallel in the axial direction, the guide groove of the rear impeller It is preferable to have an inclined portion formed to be bent to guide the fluid.
  • the guide groove of the rear impeller is characterized in that formed in a plurality of branches along the circumferential direction.
  • the rear impeller further includes a plurality of airtight holding protrusions protruding on the outer circumferential surface so as to maintain the airtightness between the outer circumferential surface of the rear impeller and the housing, and the rear impeller installed on the rotating shaft at a position adjacent to the outlet is the rear outlet It further comprises a plurality of discharge guide protrusions protruded to guide the fluid discharged through the discharge port of the housing.
  • the front impeller according to another embodiment of the present invention for achieving the above object is fixed to the rotating shaft to rotate with the rotating shaft, the through hole of the front impeller is a vertical portion formed in parallel in the axial direction, the vertical It is in communication with the portion, and provided with an inclined portion formed to be bent to rotate the rotary shaft.
  • the front impeller may further include a plurality of resistance grooves or resistance protrusions formed along the circumferential direction on the upper surface of the front impeller so as to generate a rotational force by interfering with the fluid introduced into the housing.
  • the front impeller further includes at least one fluid guide groove for guiding the fluid flowing into the housing to the through hole of the front impeller.
  • the front impeller further includes a plurality of first outflow prevention protrusions protruding in a closed circuit along the circumferential direction on the upper edge of the front impeller so as to prevent the fluid flowing into the housing from leaking to the outer circumferential surface.
  • the axial flow type multi-stage turbine according to the present invention is easy to manufacture and install, thereby reducing the cost, and minimizing the pressure drop and the flow rate loss of the flowing fluid by maintaining the airtight inside the housing.
  • the fluid in the rotating body is perpendicular to the direction of rotation of the rotating body to increase the rotational force It provides the advantage of improving the power generation efficiency of the turbine.
  • FIG. 1 is a cross-sectional view of an axial multistage turbine according to a first embodiment of the present invention
  • Figure 2 is an exploded view of the axial multistage turbine of Figure 1
  • FIG. 3 is a partial cross-sectional view in the circumferential direction of the front impeller and the rear impeller of the axial multistage turbine of FIG.
  • FIG. 5 is a cross-sectional view of an axial multistage turbine according to a third embodiment of the present invention.
  • FIG. 6 is a perspective view of the front impeller of the axial multistage turbine according to the fourth embodiment of the present invention.
  • FIG. 7 is a perspective view of the front impeller of the axial multistage turbine according to the fifth embodiment of the present invention.
  • FIG. 8 is a partial cross-sectional perspective view of the front impeller of the axial multistage turbine according to the sixth embodiment of the present invention.
  • FIG. 9 is a partial perspective view of a rear impeller of an axial multistage turbine according to a seventh embodiment of the present invention.
  • FIG. 10 is a partial perspective view of a rear impeller of an axial multistage turbine according to an eighth embodiment of the present invention.
  • FIG. 11 is a perspective view of a rear impeller of an axial multistage turbine according to a ninth embodiment of the present invention.
  • FIG. 12 is a perspective view of a rear impeller of an axial multistage turbine according to a tenth embodiment of the present invention
  • FIG. 13 is a perspective view of a rear impeller of an axial multistage turbine according to an eleventh embodiment of the present invention.
  • FIG. 14 is a perspective view of a rear impeller of an axial multistage turbine according to a twelfth embodiment of the present invention.
  • 15 is a partial cross-sectional view in the circumferential direction of the front impeller of the axial multistage turbine according to the thirteenth embodiment of the present invention.
  • FIG. 16 is a partial perspective view of a rear impeller of an axial multistage turbine according to a fourteenth embodiment of the present invention.
  • FIG. 17 is a partial perspective view of a rear impeller of an axial multistage turbine according to a fifteenth embodiment of the present invention.
  • FIG. 18 is a partial perspective view of a rear impeller of an axial multistage turbine according to a sixteenth embodiment of the present invention.
  • FIG. 19 is a partial cross-sectional perspective view of a rear impeller of an axial multistage turbine according to a seventeenth embodiment of the present invention.
  • interference hole 99 vortex blocker 244: front guide groove
  • resistance groove 456 airtight holding projection 460: fluid bypass
  • interference projection member 557 discharge guide target 610: first leakage preventing projection
  • FIGS. 1-10 An axial multistage turbine 10 according to an embodiment of the present invention is shown in FIGS.
  • the axial flow type multi-stage turbine 10 includes a housing 20 formed to allow fluid to flow therein, a rotation shaft 30 rotatably installed inside the housing 20, and a rotation shaft 30.
  • the front impeller 40 formed with a plurality of through holes 41 through which the fluid passes, and the rear impeller 50 fixed to the rotating shaft 30 to be located behind the front impeller 40 guide the flow of the fluid. Generate rotational force.
  • the housing 20 has a cylindrical body 22 having both sides open to allow a fluid, which is a gas or a liquid, to be introduced into the housing 20, and an inlet 24 through which the fluid is introduced into the housing 20.
  • the front cover 21 which covers the front of the 22, and the rear cover 23 is formed to cover the lower portion of the body 22, the discharge port 25 through which the fluid inside the housing 20 is discharged.
  • the housing 20 configured as described above will be described in more detail as follows.
  • the front cover 21 and the rear cover 23 is formed in a disc shape having an outer diameter corresponding to the outer diameter of the housing 20.
  • the through hole is formed in the center of the front cover 21 and the rear cover 23 so that the rotating shaft 30 can be inserted.
  • the through hole of the front cover 21 and the rear cover 23 is preferably provided with a bearing 26 so that the rotating shaft 30 can be easily rotated.
  • Edges of the front cover 21 and the rear cover 23 is formed with a plurality of through holes to be coupled to the housing 20 by a bolt.
  • the body 22 has a receiving space for accommodating the front impeller 40 and the plurality of rear impeller 50 therein.
  • the inner circumferential surface of the front end of the body 22 has an impeller fixing groove 27 for fixing the front impeller 40.
  • the rotating shaft 30 is formed in an annular bar shape, and both ends of the rotating shaft 30 are rotatably supported by the front cover 21 and the rear cover 23 covering both sides of the housing 20.
  • the front impeller 40 is formed in a disk-like structure, and since the inflow fluid may be in a high temperature and high pressure state, it is preferable that the front impeller 40 is formed of a heat resistant material. Although not shown in the drawings, the edge of the front impeller 40 is fixed to the impeller fixing groove 27 inside the housing 20 by fixing bolts.
  • the central part of the front impeller 40 is formed with a through hole so that the rotation shaft 30 can be rotatably supported.
  • the through hole of the front impeller 40 is preferably provided with a bearing 26 so that the rotating shaft 30 can be easily rotated.
  • the front impeller 40 passes through the fluid introduced into the housing 20 to pass through the front impeller 40 to be inclined to guide the guide groove 51 of the rear impeller 50 to be described later.
  • a sphere 41 is formed.
  • the through-hole 41 of the above-mentioned front impeller 40 will be described in detail as follows.
  • the through hole 41 of the front impeller 40 is a vertical portion 42 formed vertically in the interior from the front side of the front impeller 40, the vertical portion 42 is in communication with the guide groove of the rear impeller 50 A bent portion 43 bent to correspond to the position of 51 is provided.
  • the through hole 41 of the front impeller 40 is not divided into a vertical portion 42 and a bent portion 43, but is integrally formed with the rotation shaft 30. It may be formed to be inclined in a direction corresponding to the rotation direction.
  • the through holes 41 of the front impeller 40 are formed in one row along the circumferential direction, but the number of the arrangement of the through holes 41 to be applied is not limited to the illustrated example. Depending on the flow rate and pressure of the fluid may be formed in a plurality of rows.
  • front impeller 40 is further provided between the front impeller 40 and the rear impeller 50 is further provided with an auxiliary impeller member 700 for passing the fluid passing through the front impeller 40 to generate a rotational force.
  • the auxiliary impeller member 700 will be described in detail with reference to FIG. 4 as follows.
  • the auxiliary impeller member 700 is fixed to the rotation shaft 30 so as to rotate together with the rotation shaft 30, and is formed in a disc shape.
  • the auxiliary impeller member 700 includes a plurality of through holes 710 formed so that the fluid passing through the front impeller 40 fixed inside the housing 20 can be introduced therein.
  • the through hole 710 of the auxiliary impeller member 700 is formed in the same configuration as the through hole 41 of the front impeller 40, a detailed description thereof will be omitted.
  • the through holes 710 are formed in plural in the circumferential direction. The fluid passing through the front impeller 40 is discharged through the through hole 710 of the auxiliary impeller member 700 to press the bent portion of the through hole 710 to increase the rotational force of the rotary shaft (30).
  • FIG. 5 Another embodiment of the front impeller 140 is shown in FIG. 5.
  • the front impeller 140 is formed in a disk-like structure, is fixed to the rotary shaft 30 is installed to rotate with the rotary shaft 30.
  • the front impeller 140 has a plurality of through-holes 41 formed to obliquely penetrate the front impeller 140 so as to pass the fluid introduced into the housing 20 to rotate the rotation shaft 30.
  • the through-hole 41 of the front impeller 140 is in communication with the vertical portion 42 and the vertical portion 42 formed perpendicularly to the inside from the front side of the front impeller 40 in the rotational direction of the rotation shaft 30 A bent portion 43 correspondingly bent is provided.
  • the fluid flowing into the through hole 41 strongly strikes the walls of the vertical portion 42 and the bent portion 43 to provide an increase in rotational force to the front impeller 140. Since the front impeller 140 is fixed to the rotation shaft 30, the fluid rotates the rotation shaft 30.
  • the fluid that is not guided to the rear is discharged through the fluid bypass 460, the fluid bypass 460 is not counted to the outside of the rotor like the existing turbine, but because the fluid is guided to the outside of the central axis of the rotor fluid The area to be counted is greatly reduced, and the flow loss is also greatly reduced.
  • the through hole 41 of the front impeller 140 is not formed by being divided into the vertical portion 42 and the bent portion 43, but integrally with the rotating shaft 30. It may be formed to be inclined in a direction corresponding to the rotation direction.
  • FIG. 6 Another embodiment of the front impeller 240 is shown in FIG. 6.
  • a front guide groove 244 is formed on the front surface of the front impeller 240 to guide the fluid introduced into the housing 20 to the through hole 41 of the front impeller 240.
  • the front guide groove 244 is formed to be curved along the circumferential direction.
  • the width of the front guide groove 244 is uniformly formed to the through hole 41 of the front impeller 240, the width of the front guide groove 244 at the position where the through hole 41 is formed is the through hole 41 It has a size corresponding to the inner diameter of.
  • front guide groove 244 is covered with a whole except for the first part of the fluid flows to the through hole so that the introduced fluid flows out only through the through hole 41 and does not flow out of the front guide groove 244. It is configured not to.
  • the fluid introduced into the front guide groove 244 is guided only through the through hole 41 and cannot flow out of the front guide groove 244. Can be prevented.
  • the front impeller 240 has been described with a structure in which three front guide grooves 244 are formed along the circumferential direction, but the number of the front guide grooves 244 to be applied is not limited to the illustrated example. It is preferable to be formed to correspond to the number of guide grooves 51 of the rear impeller 50 to be described later.
  • the fluid injected through the inlet 24 of the housing 20 is guided to the through-hole 41 of the front impeller 240 by the front guide groove 244, and the front impeller 240 while passing through the through-hole 41. To generate torque.
  • the fluid generating a rotational force in the front impeller 240 while passing through the through-hole 41 is determined by the structure in which the front guide groove 244 is formed.
  • FIG. 3 Another embodiment of the front impeller 340 is shown in FIG.
  • the front impeller 340 has a plurality of resistance grooves 344 formed in the radial direction to generate a rotational force to interfere with the fluid introduced into the housing 20 on the front.
  • the resistance groove 344 is formed between the through holes 41 of the front impeller 340, and is formed in a concave structure in the rotation direction of the front impeller 340. Fluid introduced into the housing 20 impinges on the inner wall of the resistance groove 344 formed on the front surface of the front impeller 340 to rotate the front impeller 340.
  • the shape of the through-hole 41 is a spherical shape of the inlet is circular and the inner diameter gradually decreases as it enters the inside, while the fluid flowing into the through-hole 41 passes through the narrow interior It is the structure that a pressure rises.
  • the front impeller 340 forwards to the front of the front impeller 340 to interfere with the fluid introduced into the housing 20 instead of the resistance groove 344. It may be provided with a protrusion formed protrusion.
  • FIG. 8 Another embodiment of the front impeller is shown in FIG. 8.
  • the front impeller forms a closed circuit along the circumferential direction on the upper edge of the front impeller so as to prevent the fluid flowing into the housing 40 from leaking to the outer circumferential surface of the front impeller.
  • the prevention protrusion 610 is provided.
  • the front cover 21 forms a closed circuit along the circumferential direction of the front cover 21 at a position opposite to the first leakage preventing protrusion 610 so as to be inserted between the first leakage preventing protrusion 610. Protruding to form a second leakage preventing projection 620 for sealing the space between the front cover 21 and the front impeller.
  • first and second outflow prevention protrusions 610 and 620 are formed to be spaced apart from each other at predetermined intervals so that the front impeller 40 can easily rotate along the second outflow prevention protrusion 620. .
  • the fluid introduced into the housing 20 does not flow out between the outer circumferential surface of the front impeller and the inner wall of the housing. It flows into the through hole 41 of the front impeller. Accordingly, the flow rate loss and the pressure drop due to the outflow of the fluid can be reduced by the first and second outflow prevention protrusions 610 and 620.
  • first and second leakage preventing protrusions 610 and 620 are not formed only between the front cover 21 and the front impeller, but the front impeller is inside the housing 20.
  • fixing to the lower surface of the front impeller and the upper surface of the rear impeller 50 may be formed respectively to prevent the fluid flowing between each impeller flows through the outer peripheral surface of the impeller may reduce the pressure loss.
  • the rear impeller 50 is fixed to the rotation shaft 30 behind the front impeller 40 and is formed in a disk structure.
  • the front side of the rear impeller 50 is formed with a guide groove 51 for guiding the fluid in the rotational direction of the rotation shaft 30 to rotate the rotation shaft 30, the guide groove 51 at the end of the guide groove 51
  • a rear discharge port 55 is formed to obliquely penetrate the rear impeller 50 so as to discharge the fluid flowing along the 51 to the rear of the rear impeller 50.
  • the guide groove 51 of the rear impeller 50 is formed along the circumferential direction on the upper side of the rear impeller 50 at a position corresponding to the through hole 41 of the front impeller 40.
  • the guide groove 51 may be formed to have a size corresponding to the flow rate of the fluid to accommodate the fluid introduced into the housing 20.
  • the fluid passing through the through hole 41 is moved along the guide groove 51 of the rear impeller 50 in the rotational direction of the rotation shaft 30. At this time, the fluid rotates the rear impeller 50.
  • the fluid moving along the guide groove 51 is discharged to the rear of the rear impeller 50 through the rear discharge port 55 formed at the end.
  • the rotational force is further increased because the rear discharge port 55 vertically presses the bent portion of the rear impeller 50 while being discharged through the rear discharge port 55.
  • FIG. 9 Another embodiment of the rear impeller 150 is illustrated in FIG. 9.
  • the rear impeller 150 is formed to protrude upward in the guide groove 51, and further includes a plurality of resistance blades 52 for generating rotational force by interfering with the fluid flowing along the guide groove 51. Equipped.
  • the resistance blade 52 is formed in a streamlined cross section so that fluid introduced into the guide groove 51 can smoothly flow between the plurality of resistance blades 52, and is preferably formed to be inclined toward the rear side of the fluid flow.
  • the fluid passing through the through hole 41 is moved by the guide groove 51 in the rotational direction of the rotation shaft 30, at which time the fluid impinges on the resistance blade 52 formed along the guide groove 51 to impart a rear impeller. Rotate 150.
  • the structure of the plurality of resistance blades 52 formed along the guide grooves 51 are inclined in the same direction, but the direction of the applied resistance blades 52 is not limited to the illustrated example. It may be formed zigzag.
  • FIG 10 shows another embodiment of the rear impeller 250.
  • the rear impeller 250 has resistance blades 53 protruding from both sides of the guide groove 51 along the guide groove 51.
  • the resistance blade 53 has a front side formed in a streamlined shape so that fluid flowing along the guide groove 51 can move smoothly between the plurality of resistance blades 53, and flows into the guide groove 51.
  • the rotational force is further increased by hitting the resistor blades 53 perpendicularly.
  • each resistance blade 53 is preferably formed in a zigzag on both sides of the guide groove (51).
  • FIG. 11 Another embodiment of the rear impeller 350 is illustrated in FIG. 11.
  • the rear impeller 350 is formed with a guide groove 51 branched in three directions along the circumferential direction.
  • Each branched guide groove 54 is formed with a plurality of resistance blades 52 for generating a rotational force by interfering with the fluid flowing along the guide groove 54.
  • the guide groove branched in three directions widens the contact area with the fluid so that the fluid easily rotates the rear impeller 350.
  • the guide groove 54 may be formed by branching in two directions or a plurality of branches instead of branching in three directions.
  • FIG. 12 Another embodiment of the rear impeller 450 of the axial multistage turbine 10 according to the invention is shown in FIG. 12.
  • the rear impeller 450 includes a plurality of airtight holding protrusions 456 protruding from the outer circumferential surface to maintain the airtightness between the outer circumferential surface of the rear impeller 450 and the housing 20.
  • the airtight holding protrusion 456 is formed to be inclined in the rotational direction of the rear impeller 450 so as to raise the fluid flowing out between the edge of the rear impeller 450 and the inner wall of the housing 20 to the upper surface of the rear impeller 450. desirable.
  • FIG. 13 Another embodiment of the rear impeller 460 is shown in FIG. 13.
  • the rear impeller 460 is a through-hole 41 of the front impeller 40 or the rear outlet of the rear impeller 50 so as to generate a rotational force to interfere with the fluid flowing into the guide groove 51 55 is provided with an interference protrusion member 461 protruding upward from a lower surface of the guide groove 51 at a position corresponding to 55).
  • the interference protrusion member 461 is formed at a predetermined height so as not to block the flow of the fluid on the lower surface of the guide groove 51, and the front side of the interference protrusion member 461 has a fluid flowing along the guide groove 51. It is formed to be inclined to interfere.
  • the fluid discharged to the through hole 41 of the front impeller 40 or the rear discharge port 55 of the rear impeller 50 pressurizes the interference projecting member 461 formed on the flow path of the fluid to rotate the rear impeller 460. Let's do it.
  • FIG. 14 Another embodiment of the rear impeller 550 is shown in FIG. 14.
  • a fluid discharged through the rear outlet 55 of the rear impeller 550 is disposed on the rear surface of the rear impeller 550 installed on the rotation shaft 30 adjacent to the outlet 25 of the housing 20.
  • a plurality of discharge guide targets 557 are formed to protrude so as to be guided to the discharge port 25 of the 20.
  • the discharge guide target 557 is formed convexly in the rotational direction of the rear impeller 550.
  • the fluid discharged through the rear discharge port 55 is guided to the edge of the rear impeller 550 by the discharge guide target 557, and the outside of the housing 20 through the discharge port 25 formed at the edge of the rear cover 23. To be discharged.
  • the number of the rear impellers 50 to be applied is not limited to the illustrated example. Alternatively, a plurality of rear impellers 50 may be installed.
  • the through hole 41 of the front impeller 40 is the front impeller 40.
  • a vertical portion 42 vertically formed therein from the front side of the front side, and a bent portion 43 communicating with the vertical portion 42 and bent to correspond to the position of the guide groove 51 of the rear impeller 50.
  • the fluid introduced into the housing 20 passes through the through-hole 41 formed in the front impeller 40, the fluid introduced into the through-hole 41 is a vertical portion of the through-hole 41 ( 42) and a strong impact on the connecting portion of the bent portion 43 generates a strong rotational force, the fluid is discharged to the rear of the front impeller (40).
  • FIG. 16 is a partial perspective view of a rear impeller of an axial multistage turbine according to a fourteenth embodiment of the present invention
  • FIG. 17 is a partial perspective view of a rear impeller of an axial multistage turbine according to a fifteenth embodiment of the present invention.
  • FIG. 18 is a partial perspective view of a rear impeller of an axial multistage turbine according to a sixteenth embodiment of the present invention
  • FIG. 19 is a partial perspective view of a rear impeller of an axial multistage turbine according to a seventeenth embodiment of the present invention.
  • FIG. 9 a further embodiment of the rear impeller 150 shown in FIG. 9 is illustrated.
  • a rectangular resistance blade 52 is illustrated, but FIGS. The resistance blade 52 of the shape is shown.
  • the rear impeller 150 is formed to protrude upward in the guide groove 51, so that the triangular pillar-shaped resistance blade 52 interferes with the fluid flowing along the guide groove 51 to generate rotational force.
  • an eddy current prevention device 99 connected to a vertex of the resistance blade 52.
  • FIG. 17 illustrates a semi-circular pillar-shaped resistance blade 52 and a rear impeller 150 further provided with a vortex prevention tool 99 connected to the resistance blade 52
  • FIG. 18 illustrates a rhombus pillar-shaped resistor.
  • the rear impeller 150 is further provided with a blade 52 and a vortex breaker 99.
  • the resistance blades 52 of the various shapes are preferably formed to be inclined so that the fluid passing through the guide groove 51 to generate a rotational force and the fluid flow smoothly to the rear side of the resistance blade (52).
  • FIG. 19 is a partial cross-sectional perspective view of the front impeller of the axial multistage turbine according to the eighteenth embodiment of the present invention.
  • the front impeller 350 is a front impeller (fluid flowing into the housing 40).
  • a plurality of first outflow prevention projections 610 are formed in the circumferential direction to the upper edge of the front impeller in the circumferential direction, wherein the front cover 21 is The front cover 21 is formed in a closed circuit along the circumferential direction and protrudes downward in the front cover 21 at a position opposite to the first leakage preventing protrusion 610 so as to be inserted between the first leakage preventing protrusions 610.
  • a second outflow prevention protrusion 620 for sealing a space between the front impeller 350 and the front impeller 350.
  • first and second outflow prevention protrusions 610 and 620 are formed to be spaced apart from each other at predetermined intervals so that the front impeller 40 can easily rotate along the second outflow prevention protrusion 620.
  • the difference from the partial cross-sectional perspective view of the front impeller shown in FIG. 8 is that the first and second outflow prevention protrusions 610 and 620 are formed close to the rotation shaft 30, and the structure can minimize fluid loss.
  • the high pressure fluid is injected into the housing 20 through the inlet 24 of the front cover 21.
  • the fluid introduced into the housing 20 passes through the through hole 41 formed in the front impeller 40.
  • the fluid introduced into the through hole 41 of the front impeller 40 hits the connection portion between the vertical part 42 and the bent part 43 of the through hole 41 and is discharged to the rear of the front impeller 40.
  • the fluid discharged through the through hole 41 flows into the guide groove 51 of the rear impeller 50 installed at the rear of the front impeller 40. Fluid introduced into the guide groove 51 moves along the guide groove 51. At this time, the fluid strikes the resistance blade 52 protruding along the guide groove 51, thereby rotating the rear impeller 50.
  • Fluid flowing along the guide groove 51 is discharged to the rear of the rear impeller 50 through the rear discharge port 55 formed at the end of the guide groove 51.
  • the rear discharge port 55 is formed to be inclined to correspond to the rotational direction of the rotation shaft 30
  • the fluid is discharged to the rear of the rear impeller 50 while rotating the rear impeller 50, at which time, the rear located at the end Behind the impeller the fluid is discharged in the opposite direction of rotation.
  • the axial multistage turbine 10 is installed such that the front impeller 40 and the plurality of rear impellers 50 are in close contact with each other, and the airtight holding protrusions 456 and the first and the outer circumferential surfaces of the rear impeller 50 are provided.
  • the second outflow prevention protrusions 610 and 620 are formed to prevent the fluid from flowing out between the impellers, thereby preventing the pressure loss caused by the outflow of the fluid.
  • each impeller forms a fluid flow path by the through-hole 41 and the guide groove 51 to allow the fluid to pass through the inside of each impeller, each passage has a resistance groove 344 or a resistance blade ( By providing a fluid interference means as shown in 52) to generate a rotational force in the entire section of the fluid flow path to provide the advantage of improving the output of the turbine, and because each impeller rotates at high speed, the fluid flowing inside each impeller Pressing the inner wall of each impeller by the centrifugal force to generate a rotational force to increase the generating power of the axial flow multi-stage turbine (10).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Turbines (AREA)

Abstract

La présente invention concerne une turbine multi-étage à écoulement axial, comportant : un carter définissant un orifice d'admission et un orifice d'évacuation pour y permettre la circulation de fluide ; et un arbre rotatif installé pour être entraîné en rotation installé dans le carter ; une roue avant installée sur l'arbre rotatif et perforée pour définir une pluralité d'ouvertures traversantes pour guider l'écoulement et le retour de fluide à travers celles-ci ; et au moins une roue arrière fixée sur l'arbre rotatif derrière la roue avant, et définissant au moins une rainure de guidage pour guider le fluide dans une direction de rotation de l'arbre rotatif pour faire tourner l'arbre rotatif, et comprenant un orifice de sortie arrière à une extrémité de la rainure de guidage pour générer une force de rotation par la décharge vers l'arrière du fluide circulant le long de la rainure de guidage. La turbine multi-étage à écoulement axial selon la présente invention est facile à installer et à fabriquer, permettant une réduction des coûts d'installation, et de minimiser la perte de fluide circulant dans le carter pour procurer l'avantage d'une efficacité accrue de production d'énergie de la turbine.
PCT/KR2010/001712 2009-03-20 2010-03-19 Turbine multi-etage a ecoulement axial WO2010107276A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020090023951A KR101033324B1 (ko) 2009-03-20 2009-03-20 축류형 다단터빈
KR10-2009-0023951 2009-03-20

Publications (2)

Publication Number Publication Date
WO2010107276A2 true WO2010107276A2 (fr) 2010-09-23
WO2010107276A3 WO2010107276A3 (fr) 2010-12-09

Family

ID=42740144

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2010/001712 WO2010107276A2 (fr) 2009-03-20 2010-03-19 Turbine multi-etage a ecoulement axial

Country Status (2)

Country Link
KR (1) KR101033324B1 (fr)
WO (1) WO2010107276A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101647421B1 (ko) * 2016-03-24 2016-08-10 동원펌프주식회사 다단식 원심펌프

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101184877B1 (ko) 2011-04-05 2012-09-26 최혁선 축류형 터빈의 개량구조
JP6002227B2 (ja) 2011-10-04 2016-10-05 チェ，ヒョック ソンＣＨＯＩ，Ｈｙｕｋ Ｓｕｎ 軸流型タービン
KR101272820B1 (ko) * 2012-04-26 2013-06-11 써클파워 주식회사 제트 터빈
KR101332613B1 (ko) * 2013-08-09 2013-11-25 이재본 방사형 임펠러가 결합된 다단터빈
KR101418345B1 (ko) 2013-09-27 2014-07-10 최혁선 축류형 다단 터빈의 구조
KR20160053684A (ko) * 2014-11-05 2016-05-13 이만숙 독립형 날개의 충동식 터빈 시스템
KR102034700B1 (ko) 2017-12-28 2019-10-21 김주섭 발전용 충동-반동 복합 터빈 장치
KR102054004B1 (ko) 2019-05-17 2019-12-09 백종빈 고 효율 축류 터빈
KR102486265B1 (ko) 2020-11-11 2023-01-10 박방림 고 효율 축류 터빈의 개량구조
KR20240031744A (ko) 2022-09-01 2024-03-08 박영석 기능이 개선된 고 효율 축류 터빈

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6692232B1 (en) * 2001-03-16 2004-02-17 Guy Louis Letourneau Rotor assembly for disc turbine
KR100531264B1 (ko) * 2003-07-30 2005-11-28 이재본 유체운동을 회전동력으로 전환하는 축류형 다단터빈
KR100550366B1 (ko) * 2004-03-17 2006-02-13 이재본 축류형 다단터빈
US20060233647A1 (en) * 2005-04-14 2006-10-19 Saunders Robert D Slotted bladeless turbine disc

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3448145B2 (ja) * 1995-11-24 2003-09-16 三菱重工業株式会社 熱回収式ガスタービンロータ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6692232B1 (en) * 2001-03-16 2004-02-17 Guy Louis Letourneau Rotor assembly for disc turbine
KR100531264B1 (ko) * 2003-07-30 2005-11-28 이재본 유체운동을 회전동력으로 전환하는 축류형 다단터빈
KR100550366B1 (ko) * 2004-03-17 2006-02-13 이재본 축류형 다단터빈
US20060233647A1 (en) * 2005-04-14 2006-10-19 Saunders Robert D Slotted bladeless turbine disc

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101647421B1 (ko) * 2016-03-24 2016-08-10 동원펌프주식회사 다단식 원심펌프

Also Published As

Publication number Publication date
KR20100105103A (ko) 2010-09-29
WO2010107276A3 (fr) 2010-12-09
KR101033324B1 (ko) 2011-05-09

Similar Documents

Publication Publication Date Title
WO2010107276A2 (fr) Turbine multi-etage a ecoulement axial
WO2016195238A1 (fr) Structure de refroidissement de turbo-soufflante du type à entraînement direct
KR100551523B1 (ko) 원심 압축기
WO2017039108A1 (fr) Structure de refroidissement de turbosoufflante double du type à entraînement direct
KR100413754B1 (ko) 가스터빈용압축기회전자냉각시스템
EP2009248B1 (fr) Agencement de turbine et procédé de refroidissement d'un anneau situé au bout d'une aube de turbine
US5290144A (en) Shroud ring for an axial flow turbine
CA2464414C (fr) Ouie de refroidissement pour aube de turbine haute pression
WO2012030052A2 (fr) Turbine à réaction
EP2715069B1 (fr) Bague d'étanchéité de piston
WO2010107146A1 (fr) Turbine du type à réaction
CN103775135B (zh) 燃气涡轮和用于这样的燃气涡轮的涡轮叶片
CN108060979B (zh) 燃气轮机及其旋流装置
CN1705203B (zh) 带有增压装置的气体冷却电机
JP6118018B2 (ja) シュラウド漏洩カバー
CN1380487A (zh) 燃气轮机
WO2018182272A1 (fr) Appareil de turbine centripète comprenant des buses à l'intérieur d'une turbine scellée
WO2016167456A1 (fr) Carter de volute et machine tournante le comportant
WO2015108353A1 (fr) Dispositif de refroidissement de turbine
WO2015108354A1 (fr) Appareil de scellement d'extrémité de pale pour turbine à gaz
WO2013058500A1 (fr) Turbine du type à réaction
WO2018199708A1 (fr) Appareil de propulsion de pale d'hélice d'arbre vertical pour navire à propulsion électrique
WO2023095964A1 (fr) Structure pour améliorer l'efficacité d'un moteur à aimant permanent d'une turbosoufflante
WO2019139199A1 (fr) Compresseur
CN217233829U (zh) 一种轴流式风机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10753726

Country of ref document: EP

Kind code of ref document: A2

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 19/01/2012)

122 Ep: pct application non-entry in european phase

Ref document number: 10753726

Country of ref document: EP

Kind code of ref document: A2