CN214035792U - Impeller suitable for megawatt-level differential pressure power generation turboexpander - Google Patents
Impeller suitable for megawatt-level differential pressure power generation turboexpander Download PDFInfo
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- CN214035792U CN214035792U CN202120081694.1U CN202120081694U CN214035792U CN 214035792 U CN214035792 U CN 214035792U CN 202120081694 U CN202120081694 U CN 202120081694U CN 214035792 U CN214035792 U CN 214035792U
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Abstract
The utility model relates to an impeller suitable for megawatt level differential pressure electricity generation turboexpander belongs to the impeller field, is to the impeller that does not have the megawatt level differential pressure electricity generation turboexpander yet to propose, include: the impeller comprises a hub and impeller blades, an air passage is formed between every two adjacent impeller blades, the linear type of the impeller blades is variable cross-section twisted blades, the number of the impeller blades is prime, the inlet radius of the impeller blades, the outlet root radius of the impeller blades, the outlet top radius of the impeller blades, the inlet blade height of the impeller blades and the axial length of the impeller blades are limited, and the included angles between the linear type and the axial direction of the inlet area and the outlet area of the impeller blades in the meridian plane are an inlet inclination angle and an outlet inclination angle. The invention adopts radial impeller design software, analyzes the performance of the impeller through one-dimensional thermodynamic calculation, and adjusts the meridian flow channel design, the blade thickness distribution and the angle division of the impeller through three-dimensional modeling, thereby optimizing the blade profile distribution and meeting the structural strength requirement.
Description
The technical field is as follows:
the utility model belongs to the technical field of the impeller, concretely relates to impeller suitable for megawatt level differential voltage power generation turbo expander.
Background art:
with the construction of natural gas pipe networks, the current general trend of gas transmission pipelines in the world is as follows: long distance, large caliber, high pressure and networking. The high-pressure natural gas transmitted by the high-pressure gas transmission main line is required to be depressurized according to the gas supply pressure requirement of downstream users at the natural gas receiving door stations and the pressure regulating stations of all cities, and then the high-pressure natural gas can be supplied to ordinary users for use, so the pressure regulating stations are arranged behind the natural gas receiving door stations or the receiving door stations of all cities. The high-pressure natural gas can generate great pressure drop in the pressure regulating process, and a great amount of energy is released. If the mode of a turboexpander can be adopted to recycle the pressure energy, the utilization rate of energy and the economical efficiency of the operation of a natural gas pipeline network can be improved to a great extent. The turbo expander is used for recovering pressure energy, relatively advanced technology is available abroad, and only the turbo expander with low power grade is researched at present at home, but the turbo expander is not suitable for the actual situation of a natural gas pipeline network. The impeller is a key part of the turboexpander, and the impeller needs to have good profile distribution, meet the requirements on the structural strength in the thickness design, have good pneumatic performance and can realize high-efficiency operation under wider working conditions. Therefore, research and development of an impeller which can be applied to a megawatt differential pressure power generation turboexpander and can provide technical support for localization of units with the same power level are urgently needed.
The invention content is as follows:
the utility model discloses a solve that it is good that the pneumatic performance is not had yet domestically, can be applicable to megawatt level differential pressure generation turboexpander's impeller again, provide an impeller suitable for megawatt level differential pressure generation turboexpander, through the molded lines distribution of adjustment impeller, optimize blade thickness distribution and angle graduation, can realize the high efficiency operation under the broad operating mode condition.
The utility model discloses a technical scheme lie in: an impeller suitable for a megawatt differential pressure power generation turboexpander, comprising: the impeller comprises a hub and a plurality of impeller blades uniformly and circumferentially arranged on the surface of the hub, an air passage is formed between every two adjacent impeller blades, the hub and the impeller blades are of an integral structure, the linear shape of the impeller blades is a variable-section twisted blade, the sectional area of the impeller blades is gradually reduced from the root to the top, relative torsion exists between every two adjacent sections, the blade profile curve of each section is a space curve, the number of the impeller blades is prime, the inlet radius R1 of the impeller blades is 160mm, the outlet root radius R2 of the impeller blades is 60mm, and the outlet top radius R3 of the impeller blades is 140 mm; the inlet blade height Z1 of the impeller blade is 30mm, the axial length Z2 of the impeller blade is 155mm, the included angles between the molded lines of the inlet area and the outlet area of the impeller blade in the meridian plane and the axial direction are an inlet inclination angle alpha 1 and an outlet inclination angle alpha 2, the inlet inclination angle alpha 1 is 90 degrees, and the outlet inclination angle alpha 2 is 0 degree; the included angle between the inlet area of the impeller blade and the tangential direction of the circumferential line A on the air inlet side of the hub is an inlet blade angle beta 1, the value range of the beta 1 is 80-90 degrees, the included angle between the outlet area of the impeller blade and the tangential direction of the circumferential line B on the air outlet side of the hub is an outlet blade angle beta 2, the blade root section of the impeller blade is defined as a section o-o, the section with 20% of blade height is defined as a section a-a, the section with 40% of blade height is defined as a section B-B, the section with 60% of blade height is defined as a section c-c, the section with 80% of blade height is defined as a section D-D, the blade tip section is defined as a section e-e, the value range of the beta 2 is 0-75 degrees along with the change of the section height from the section o-o to the section e-e, and the change range of the chord.
Preferably, the blade root section 0-0 has an inlet blade angle β 11 of 90 °, an outlet blade angle β 21 of 0 ° and a chord length D1 of 224.7 mm.
Preferably, the inlet vane angle β 12 at the 20% vane height section a-a is 88 °, the outlet vane angle β 22 is-2 °, and the chord length D2 is 214.1 mm.
Preferably, the inlet blade angle β 13 at the 40% blade height section b-b is 86 °, the outlet blade angle β 23 is-14 °, and the chord length D3 is 204.2 mm.
Preferably, the inlet vane angle β 14 at the 60% vane height section c-c is 84 °, the outlet vane angle β 24 is-37 °, and the chord length D4 is 195.1 mm.
Preferably, the inlet blade angle β 15 at the 80% blade height section D-D is 82 °, the outlet blade angle β 25 is-60 °, and the chord length D5 is 185.9 mm.
Preferably, the inlet blade angle β 16 at the tip section e-e is 80 °, the outlet blade angle β 26 is-75 °, and the chord length D6 is 179.2 mm.
Preferably, the thickness of the impeller blade is tapered in the radial direction from the hub to the casing.
Preferably, the impeller blade adopts a structure that the front edge is square and the tail edge of the blade is arc-shaped.
Preferably, the thickness of the vane at the front edge of the vane of the impeller is the same, and the thickness of the vane at the tail edge of the vane is in a range of 3-8 mm.
The utility model has the advantages that:
the invention adopts radial impeller design software, analyzes the performance of the impeller through one-dimensional thermodynamic calculation, adjusts the meridian flow channel design, the thickness distribution and the angle graduation of the impeller through three-dimensional modeling, optimizes the profile distribution of the blades, leads the thickness design of the blades to be ideal, has the characteristics of meeting the structural strength requirement, low torsional stress of the blades, good strength performance and high efficiency of gas work performance, can efficiently operate under variable working conditions, and provides technical support for the localization development of the differential pressure power generation turboexpander. The invention realizes the localization of megawatt natural gas turbo-expander impeller products and enriches the design of high-pressure natural gas turbo-expander impellers.
Description of the drawings:
fig. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic meridional profile of an impeller blade;
FIG. 3 is a profile plot of different blade heights of an impeller blade;
FIG. 4 is a thickness profile of each interface of an impeller blade;
wherein: 1 hub and 2 impeller blades.
The specific implementation mode is as follows:
as shown in fig. 1 to 4, the utility model relates to an impeller suitable for megawatt level differential pressure power generation turbo expander, impeller adopt five-axis machining center to mill, and it includes: the impeller comprises a hub 1 provided with a central through hole and a plurality of impeller blades 2 uniformly and circumferentially arranged on the surface of the hub 1, an air passage is formed between every two adjacent impeller blades 2, the hub 1 and the impeller blades 2 are of an integral structure, the overall efficiency of an impeller, the load and stress distribution of the impeller blades 2 and the influence of wall surface resonance are considered, the number of the impeller blades 2 is prime, and the number of the impeller blades 2 is preferably 17. The linear type of the impeller blade 2 is a variable cross-section twisted blade, the sectional area of the variable cross-section twisted blade is gradually reduced from the root to the top, relative twisting is arranged between two adjacent cross sections, and the blade profile curve of each cross section is a space curve.
The radius R1 of the inlet of the impeller blade 2 is 160mm, the radius R2 of the outlet root of the impeller blade 2 is 60mm, and the radius R3 of the outlet top of the impeller blade 2 is 140 mm; the inlet blade height Z1 of the impeller blade 2 is 30mm, the axial length Z2 of the impeller blade 2 is 155mm, the included angle between the molded line of the inlet area and the outlet area of the impeller blade 2 in the meridian plane and the axial direction is an inlet inclination angle alpha 1 and an outlet inclination angle alpha 2, the inlet inclination angle alpha 1 is 90 degrees, the outlet inclination angle alpha 2 is 0 degree, and the linear distance between the top end and the tail end of the blade is a chord length D; the included angle between the inlet area of the impeller blade 2 and the tangential direction of the circumferential line A at the air inlet side of the hub 1 is an inlet blade angle beta 1, the included angle between the inlet area of the impeller blade 2 and the tangential direction of the circumferential line A at the air outlet side of the hub 1 is mainly considered to be 80-90 degrees if the inlet is flush with the front end part when the impeller blade is close to a casing, the value range of the inlet blade angle beta 1 from the hub 1 to the casing side is 80-90 degrees, the included angle between the outlet area of the impeller blade 2 and the tangential direction of the circumferential line B at the air outlet side of the hub 1 is an outlet blade angle beta 2, the blade root section of the impeller blade 2 is defined as a section o-o, the 20% blade height section is defined as a section a-a, the 40% blade height section is defined as a section B-B, the 60% blade height section is defined as a section c-c, the 80% blade height section is defined as a section d-d, the blade tip section is defined as a section e-e, and the section varies with the section height from the section o-o to the section e-e, the value range of the outlet blade angle beta 2 from the hub 1 to the side of the engine case is 0-75 degrees, and the variation range of the chord length D is 179.2-224.7 degrees.
In the use of the radial turbine, the impeller blade 2 is usually designed to be thicker near the hub 1 side, mainly because the impeller is used as a working component to bear larger impact load and centrifugal load, the maximum thickness of the hub 1 is located in the middle of 0.65-0.75, and the maximum thickness is deviated to the outlet section, mainly considering structural strength and the like. The thickness distribution of the impeller blade 2 close to the casing side is approximately uniform, and the middle section is slightly thicker. In the embodiment, the impeller blade 2 adopts a structure that the front edge is square and the tail edge is arc-shaped, the thickness of the blade is gradually reduced from the hub 1 to the casing side along the radial direction, on the hub 1, the impeller blade 2 is firstly increased and then reduced from an inlet area to an outlet area, the minimum thickness is 3mm, the maximum thickness is 13.5mm, and the maximum thickness point is at the position of 70% of the chord length; on the side of the casing, the thickness variation is not large, the minimum thickness is 3mm, the maximum thickness is 3.5mm, and the maximum thickness point is at the position of 50% of the chord length. From the hub 1 to the casing, the thickness of the blades at the front edge point is the same and is 3mm, and the thickness of the tail edge is 3mm to 8 mm.
Further, the inlet blade angle β 11 at the blade root section 0-0 is 90 °, the outlet blade angle β 21 is 0 °, and the chord length D1 is 224.7 mm.
Further, the inlet vane angle β 12 at the 20% vane height section a-a is 88 °, the outlet vane angle β 22 is-2 °, and the chord length D2 is 214.1 mm.
Further, the inlet blade angle β 13 at the 40% blade height section b-b is 86 °, the outlet blade angle β 23 is-14 °, and the chord length D3 is 204.2 mm.
Further, the inlet blade angle β 14 at the 60% blade height section c-c is 84 °, the outlet blade angle β 24 is-37 °, and the chord length D4 is 195.1 mm.
Further, the inlet blade angle β 15 at the 80% blade height section D-D is 82 °, the outlet blade angle β 25 is-60 °, and the chord length D5 is 185.9 mm.
Further, the inlet blade angle β 16 at the tip section e-e is 80 °, the outlet blade angle β 26 is-75 °, and the chord length D6 is 179.2 mm.
The above description is only the preferred embodiments of the present invention, and these embodiments are all based on the present invention, and the protection scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention should be covered by the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (10)
1. An impeller suitable for a megawatt differential pressure power generation turboexpander, comprising: the impeller is characterized in that the number of the impeller blades (2) is prime number, the impeller blades (2) are uniformly and circumferentially arranged on the surface of the hub (1), an air passage is formed between every two adjacent impeller blades (2), the hub (1) and the impeller blades (2) are of an integral structure, the linear type of the impeller blades (2) is a variable cross-section twisted blade, the sectional area of the variable cross-section twisted blade is gradually reduced from the root to the top, the relative twisting is arranged between every two adjacent cross sections, the blade profile curve of each cross section is a space curve,
the radius R1 of the inlet of the impeller blade (2) is 160mm, the radius R2 of the outlet root of the impeller blade (2) is 60mm, and the radius R3 of the outlet top of the impeller blade (2) is 140 mm; the inlet blade height Z1 of the impeller blade (2) is 30mm, the axial length Z2 of the impeller blade (2) is 155mm, the included angles between the molded lines of the inlet area and the outlet area of the impeller blade (2) in the meridian plane and the axial direction are an inlet inclination angle alpha 1 and an outlet inclination angle alpha 2, the inlet inclination angle alpha 1 is 90 degrees, and the outlet inclination angle alpha 2 is 0 degree; the included angle between the inlet area of the impeller blade (2) and the tangential direction of the circumferential line A at the air inlet side of the hub (1) is an inlet blade angle beta 1, the value range of the beta 1 is 80-90 degrees, the included angle between the air outlet area of the impeller blade (2) and the tangential direction of the circumferential line B at the air outlet side of the hub (1) is an outlet blade angle beta 2, the blade root section of the impeller blade (2) is defined as a section o-o, the blade height section of 20 percent is defined as a section a-a, the blade height section of 40 percent is defined as a section B-B, the blade height section of 60 percent is defined as a section c-c, the blade height section of 80 percent is defined as a section d-d, and the blade top section is defined as a section e-e, and the value range of beta 2 is 0 to-75 degrees along with the height change of the section from the section o-o to the section e-e, and the change range of the chord length D is 179.2 to 224.7.
2. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle β 11 at the blade root section 0-0 is 90 °, the outlet blade angle β 21 is 0 °, and the chord length D1 is 224.7 mm.
3. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle beta 12 at the section a-a of the 20 percent blade height is 88 degrees, the outlet blade angle beta 22 is-2 degrees, and the chord length D2 is 214.1 mm.
4. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle beta 13 at the section b-b of the 40 percent blade height is 86 degrees, the outlet blade angle beta 23 is-14 degrees, and the chord length D3 is 204.2 mm.
5. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle beta 14 at the section c-c of the 60 percent blade height is 84 degrees, the outlet blade angle beta 24 is-37 degrees, and the chord length D4 is 195.1 mm.
6. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle beta 15 at the position of the 80 percent blade height section D-D is 82 degrees, the outlet blade angle beta 25 is-60 degrees, and the chord length D5 is 185.9 mm.
7. The impeller of claim 1, adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the inlet blade angle beta 16 at the blade tip section e-e is 80 deg., the outlet blade angle beta 26 is-75 deg., and the chord length D6 is 179.2 mm.
8. An impeller suitable for use in a megawatt differential pressure generating turboexpander according to any one of claims 1 to 7 wherein: the thickness of the impeller blade (2) is gradually reduced from the hub (1) to the casing along the radial direction.
9. The impeller of claim 8, wherein said impeller is adapted for use in a megawatt differential pressure power generation turboexpander, and wherein: the impeller blade (2) adopts a structure that the front edge is square and the tail edge is arc-shaped.
10. The impeller of claim 9 adapted for use in a megawatt differential pressure power generation turboexpander, wherein: the thickness of the blade at the front edge of the impeller blade (2) is the same, and the thickness of the blade at the tail edge of the blade ranges from 3mm to 8 mm.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202120081694.1U CN214035792U (en) | 2021-01-13 | 2021-01-13 | Impeller suitable for megawatt-level differential pressure power generation turboexpander |
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| CN202120081694.1U CN214035792U (en) | 2021-01-13 | 2021-01-13 | Impeller suitable for megawatt-level differential pressure power generation turboexpander |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113833675A (en) * | 2021-09-16 | 2021-12-24 | 势加透博洁净动力如皋有限公司 | Impeller and air compressor with same |
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- 2021-01-13 CN CN202120081694.1U patent/CN214035792U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113833675A (en) * | 2021-09-16 | 2021-12-24 | 势加透博洁净动力如皋有限公司 | Impeller and air compressor with same |
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