41results about How to "Reduce secondary flow loss" patented technology

A first stage blade of a two-stage high pressure turbine includes an airfoil having a profile substantially in accordance with at least an intermediate portion of the Cartesian coordinate values of X, Y and Z set forth in Table 2. The X and Y values are distances, which when smoothly connected by an appropriate continuing curve, define airfoil profile sections at each distance Z. The profile sections at each distance Z are joined smoothly to one another to form a complete airfoil shape.

Provided is a turbine blade cascade endwall that is capable of suppressing a vortex generated on a suction surface of a turbine stator blade and that is capable of reducing secondary-flow loss due to this vortex. A turbine blade cascade endwall that is positioned on a tip side of a plurality of turbine stator blades arranged in a ring form is provided with a pressure gradient alleviating part that alleviates a pressure gradient generated in the blade height direction at a suction surface of the turbine stator blades due to a clearance leakage flow, leaking out of a gap between a tip of a turbine rotor blade located on the upstream side of the turbine stator blades and a tip endwall disposed facing the tip of this turbine rotor blade.

Provided is a turbine blade cascade endwall that is capable of reducing crossflow and is capable of reducing secondary-flow loss that occurs in association with the crossflow, therefore being capable of achieving enhanced turbine performance. A convex portion (11) that is gently swollen as a whole, that has an apex (P1) at a position of 0 to 20% pitch in a position of 5 to 25% Cax, that gently slopes from this apex (P1) toward a downstream side and a suction side surface of an adjacently disposed turbine stationary blade (B1) or turbine moving blade, and that slopes slightly steeply from the apex (P1) toward an upstream side is provided between one turbine stationary blade (B1) or turbine moving blade and another turbine stationary blade (B1) or turbine moving blade disposed adjacent to one turbine stationary blade (B1) or turbine moving blade.

Disclosed is a highly efficient turbine nozzle blade that reduces the number of blades in an axial-flow turbine while reducing secondary-flow loss. In the nozzle blade, when a differential pressure between a pressure side and a suction side of each blade, at the same axial chord position of the blade, is defined as a load of the blade, and a ratio between axial chord length “Cx” of the blade and an axial distance “xp” from a leading edge of the blade at a maximum load position that maximizes the blade load is defined as a maximum load relative position, Cx is greater at a hub and tip than at an intermediate vertical portion, and simultaneously a maximum load relative position at the hub and tip is set to be nearer to a trailing edge thereof than a maximum load relative position of the intermediate vertical portion of the blade.

The invention discloses a mixed-flow type water pump turbine. The mixed-flow type water pump turbine comprises a volute, fixed guide vanes, movable guide vanes, a turning wheel and an exhaust water pipe, wherein the turning wheel is located at the middle part inside the volute; the fixed guide vanes and the movable guide vanes are distributed inside the volute and are located near the turning wheel; the exhaust water pipe is connected to the middle part of the bottom of the volute; the turning wheel is mainly composed of an upper canopy, a lower ring and vanes; the vanes are located between the upper canopy and the lower ring and are distributed along the circumference of the lower ring in groups; each group of the vanes is composed of a long vane, an intermediate van and two short vanes; one short vane serves as a first short vane and is located between the long vane and the intermediate vane of the group of the vanes while the other short vane serves as a second short vane and is located between the intermediate vane of the group of the vanes and the long vane of the adjacent group of the vanes. The bending degree of the curve in an S region is reduced obviously, the secondary flow loss is lower, the flowing property of a flow field is improved, the running stability of a machine set is guaranteed, and the likelihood of occurrence of vibration of the machine set is reduced.

The invention provides a modeling method for an axis-asymmetric end wall of an annular blade grid of an air compressor or a turbine. The method comprises the following steps: firstly, zoning modeling zones of a convex part structure or a concave part structure; modeling a convex part control curve or a concave part control curve in the axial direction of the blade grid or the circumferential direction of the blade grid; and finally modeling a curved surface control function in the radial direction of the blade grid. The invention particularly provides a novel convex part or concave part control function. Through the adoption of the method, the axis-asymmetric end wall of the annular blade grid of the air compressor or the turbine can be modeled conveniently and flexibly; and through the adoption of the axis-asymmetric end wall, the pressure gradient in a passage can be reduced effectively, the airflow at the exit of the passage can be more uniform, the total pressure loss coefficient in the passage can be reduced considerably, the secondary flow loss in the passage can be reduced, and further the performance of the blade grid of the air compressor or the turbine can be improved.

The invention discloses a turbine disc cavity sealing structure with prewhirl air entraining. An inner supporting ring 1 is provided with a plurality of prewhirl air-entraining flow paths, the prewhirl air-entraining flow paths are formed by air entraining holes 2, air collecting cavities 3 and air outlet holes 4 in sequence, wherein the air entraining holes 2 are a plurality of round holes whichare evenly arranged in the circumferential direction, the air entraining holes 2 are arranged on the end surface of an outer ring of air inlet holes of the inner supporting ring, the air collecting cavities 3 are of a hollow cavity structure, and the range of angles formed between the air outlet holes 4 and a center line of a motor is 65 to 80 degree. According to the turbine disc cavity sealing structure with prewhirl air entraining, a rotary blade root part works in design conditions, the secondary flow loss of a rotary blade passage is decreased greatly, compared with the existing disc cavity sealing structure, the efficiency of the turbine can be increased by nearly 1% after adopting the turbine disc cavity sealing structure with prewhirl air entraining, and the turbine disc cavity sealing structure with prewhirl air entraining is simple in structure, can mostly borrow the existing disc cavity sealing structure, and is good in economy and realizability.

The invention discloses a turbine blade body structure. A two-dimension blade profile of a blade body is a crescent closed curve defined by an inner arc curve and a back arc curve; the blade body has a characteristic parameter chord length CH, and an axial width CX; the blade body is formed by twisting and superimposing multiple two-dimension blade profiles according to a certain rule, and has a characteristic parameter blade body height H; the chord length CH of the two-dimension blade profile accords with a parabolic distribution rule from the root area to the top area in the blade height direction; a trend is that the chord lengths of the root area and the top area of the blade body are high, and the chord length of the middle area of the blade body is low; and the axial width CX of the two-dimension blade profile substantially remains unchanged. The turbine blade body structure can allow the turbine blade to simultaneously give consideration to different main loss sources of the root area, the top area and the middle area, thereby effectively and reliably improving the aerodynamic performance of the turbine blade and reducing aerodynamic loss.

A centrifugal fluid machine is provided. In order to suppress the separation and slowdown of a flow in the vicinity of the front edge of a blade suction surface shroud of an impeller when the flow rate is reduced while reducing secondary flow loss within the impeller to thereby maintain the operating range of the impeller in a centrifugal fluid machine, the shroud side is inclined further backward with respect to a rotation direction than the hub side at the back edge of an impeller blade when the impeller is viewed from a suction direction that is the upstream direction of a rotating shaft. Moreover, in adjacent two impeller blades, the shroud side of a blade located behind in the rotation direction of the impeller overlaps, in the vicinity of the front edge of the blade, with a blade located in front in the rotation direction.

The invention discloses a low-noise device for a centrifugal compressor of a turbocharger, aiming at overcoming the defect of serious airflow turbulence after an air guide wheel air incoming re-circulating structure is adopted by a turbocharger with the lowest cost so as to lower noise and improve the efficiency of the compressor. The low-noise device has the following technical scheme that based on the prior art, a space is formed between a shell 4 of an air compressor and an air guide sleeve 3, and a flow guide cover 15 is arranged in the low-noise device so as to form secondary air inlet passages 7 and 14; and arc flow guide treatment is carried out at the turning of the channel of related parts, and the air guide sleeve 3 is provided with 3 grooves or 3-20 circular holes at the radial circumference corresponding to an impeller 1 of the air compressor. The low-noise device can be widely applied to compressors to lower the noise and has wide application prospect.

An axial compressor includes a plurality of stator vanes attached to an inner surface of a casing defining an annular flow path and a plurality of rotor blades attached to a rotating rotor defining the annular flow path. A flow path is defined between a pressure surface of a stator vane and a suction surface of a stator vane, the vanes being circumferentially adjacent to each other, or between a pressure surface of a rotor blade and a suction surface of a rotor blade, the blades being circumferentially adjacent to each other. The flow path is formed so that a throat portion at which a flow path width is minimized is provided on the upstream side of 50% of an axial chord length.

The invention belongs to the field of gas turbine engines, and relates to a turbine disk cavity sealing structure with bypass gas entraining. The turbine disk cavity sealing structure with bypass gasentraining comprises an inner support ring assembly provided with an inner support ring gas inlet hole, a front baffle plate assembly, a pre-rotation nozzle, a first gas passage for transferring a first path of cold gas output by the pre-rotation nozzle, a second gas passage for transferring a second path of cold gas output by the pre-rotation nozzle, and a third gas passage arranged between the inner support ring assembly and the front baffle plate assembly, wherein the third gas passage comprises a first sealing device arranged between the inner support ring assembly and the front baffle plate assembly, a sub gas passage and a bypass gas entraining passage; a third path of cold gas output by the pre-rotation nozzle flows into the sub gas passage and the bypass gas entraining passage through the first sealing device; and gas output by the third gas passage flows toward a high-pressure turbine movable blade.

Disclosed are contorted saber-shaped stationary blades for high, middle and low pressure cylinders of a supercritical steam turbine of 1000MW, which are composed of a blade root, a blade profile and a shroud ring; wherein, the blade has a contorted saber-shaped cross section, which is contorted at the circumferential direction; wherein, the sections along the length direction of the blade roots of contorted saber-shaped stationary blades for high and middle pressure cylinders are T-shaped while the section along the length direction of the blade root of the contorted saber-shaped stationary blade for the low pressure cylinder is L-shaped; a blade tip is in the form of an integral shroud ring structure. The stationary blades adopt latest compound leaned technology and processing technology, and on the basis of ensuring less damage to the blade profile, the blade is contorted in the blade root and the blade tip at the circumferential direction, which causes air flow to speed up slightly when passing through the blade root and the blade tip and reduces the flowing of the airflow at the end faces of the blade root and the blade tip.

The invention discloses a kW-grade supercritical carbon dioxide radial flow type turbine structure with the flow dividing blades. A volute, fixed blade grids, movable blade grids and the flow dividingblades are included, wherein the fixed blade grids, the movable blade grids and the flow dividing blades are arranged in the volute; each flow dividing blade is arranged between every two adjacent movable blade grids; each fixed blade grid flow channel is formed between every two adjacent fixed blade grids, and movable blade grid flow channels are formed between the movable blade grids and the flow dividing blades; in work, supercritical carbon dioxide work media enter the structure from the volute, the gas is uniformly allocated into the fixed blade grid flow channels by the volute, the pressure of the work media in the fixed blade grid flow channels is gradually lowered, and the flow speed is gradually increased; and then the supercritical carbon dioxide work media enter the movable blade grid flow channels, in the movable blade grid flow channels, the supercritical carbon dioxide work media push an impeller to rotate and output work, and finally discharging in the axial direction is achieved. In the kW-grade supercritical carbon dioxide radial flow type turbine structure with the flow dividing blades, due to the scheme of adding of the flow dividing blades and improvement of ageometrical angle of an impeller inlet, the pneumatic efficiency of the radial flow type turbine structure is substantially improved while the running safety is guaranteed, and important engineering significance and broad application prospects are achieved.

The invention discloses a design method of a twisted swept structure stator blade for a steam turbine, and relates to the technical field of steam turbine blades. The invention aims to solve the problem of flow loss of low-pressure last-stage long blades of an existing steam turbine. The method comprises the steps that a blade design foundation and a stacking rule are determined, wherein the blade design foundation is a straight blade without a bending and twisting structure, and the stacking rule is stacking along the circle center of a steam outlet circle; based on the basic straight blade and the stacking rule, bending, sweeping and twisting are conducted on the blade, and the static blade of the bending, twisting and sweeping structure is obtained; an initial stacking line is determined, and a stator blade geometric entity is obtained in combination with the typical section blade profile; importing the obtained geometric entity into a blade three-dimensional simulation calculation and optimization platform, and further performing blade pneumatic calculation and blade strength calculation; and obtaining an optimal stacking line according to a calculation result, and finally stacking each typical section along the optimal stacking line to obtain the bending-twisting-sweeping blade. The method is used for designing the steam turbine stator blade.

The invention particularly discloses a 302.24 mm penultimate-stage moving blade for a high-rotating-speed biomass power generation steam turbine. The 302.24 mm penultimate-stage moving blade for the high-rotating-speed biomass power generation steam turbine solves the problems that in the prior art, the safety of a high-rotating-speed biomass generator set cannot be achieved, the pneumatic performance of a penultimate-stage blade is low, and the penultimate-stage blade cannot adapt to a high-rotating-speed biomass power generation steam turbine are solved. The 302.24 mm penultimate-stage moving blade comprises a blade working part, a blade root and a shroud ring; the blade working part, the blade root and the shroud ring are forged into a whole from top to bottom, the molded line of the blade working part is a variable cross-section twisted blade, the adjacent cross sections are twisted relatively, the cross-section areas of the blade working part are gradually reduced from the root to the top, the height L of the blade working part is 302.24 mm, the axial width V of the root of the blade working part is 47.15 mm, the diameter of the root of the blade working part is phi 960.14 mm, and the exhaust area of the blade working part is 1.20 m<2>; and the blade root is a helical tooth fir tree type blade root, and the axial width W of the blade root is 64.12 mm. The 302.24 mm penultimate-stage moving blade is used for the field of turbine moving blades.

The invention aims to provide a gas compressor blade. Compared with an existing gas compressor blade, the gas compressor blade can obtain relatively better aerodynamic performance. The invention further aims to provide a gas compressor which comprises the gas compressor blade. In order to achieve the purpose, the gas compressor blade comprises a blade body and an edge plate connected with the blade top or the blade root of the blade body, the connecting position of the blade body and the edge plate is in transition through a rounded corner, the rounded corner adopts a small chamfer radius at the front edge of the blade body, and a chamfer radius is gradually increased from the front edge of the blade body to the tail edge of the blade body.

To provide an axial flow turbine that can reduce interference loss and secondary flow loss, and can reduce mixing loss. An axial flow turbine includes: stator blades provided on the inner-circumference side of a diaphragm outer ring; a diaphragm inner ring provided on the inner-circumference side of the stator blades; moving blades provided on the outer-circumference side of a rotor; a shroud provided on the outer-circumference side of the moving blades; a main flow path constituted by a flow path formed between an inner circumferential surface of the diaphragm outer ring and an outer circumferential surface of the diaphragm inner ring, and a flow path formed between an inner circumferential surface of the shroud and an outer circumferential surface of the rotor; and a cavity formed between the diaphragm inner ring and the rotor. The outer circumferential surface of the rotor has protruding portions and depressed portions. Each depressed portion extends along a relative flow direction of a working fluid passed through the stator blades in the main flow path.