CN112360816A - Axial compressor bearing cylinder and axial compressor using same - Google Patents
Axial compressor bearing cylinder and axial compressor using same Download PDFInfo
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- CN112360816A CN112360816A CN202011423569.0A CN202011423569A CN112360816A CN 112360816 A CN112360816 A CN 112360816A CN 202011423569 A CN202011423569 A CN 202011423569A CN 112360816 A CN112360816 A CN 112360816A
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- 230000002093 peripheral effect Effects 0.000 claims abstract description 24
- 230000003068 static effect Effects 0.000 claims abstract description 16
- 238000000926 separation method Methods 0.000 description 7
- 230000002028 premature Effects 0.000 description 4
- 239000007787 solid Substances 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005272 metallurgy Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention belongs to the technical field of axial flow compressors and discloses an axial flow compressor bearing cylinder and an axial flow compressor using the same. This axial compressor holds jar includes: the static blade bearing cylinder comprises a bearing cylinder body and static blade blades which are arranged on the bearing cylinder body at intervals, and a conical inner through hole is formed in the bearing cylinder body; and the movable blade rotor comprises a rotating shaft and movable blade blades, the rotating shaft is coaxially arranged in the conical inner through hole, the movable blade blades are arranged on the rotating shaft at intervals, and the movable blade blades and the static blade blades are alternately distributed between the inner peripheral wall surface of the conical inner through hole and the outer peripheral wall surface of the rotating shaft. A gap is formed between the radial end part of the static blade and the outer wall surface of the rotating shaft, the length of the movable blade extending from the axis of the rotating shaft along the radial direction is equal to the size of the corresponding inner section radius of the conical inner through hole, a plurality of annular grooves coaxial with the conical inner through hole are formed on the inner peripheral wall of the conical inner through hole at intervals, and the annular grooves correspond to the positions of the movable blade.
Description
Technical Field
The invention belongs to the technical field of axial flow compressors, and particularly relates to a bearing cylinder of an axial flow compressor and the axial flow compressor using the bearing cylinder.
Background
At present, the existing axial flow compressors (or axial flow fans) applied to the fields of metallurgy, petrifaction and pharmacy all adopt the traditional fixed blade adjustable axial flow compressor, and the most important characteristic is that the air volume and the air pressure required by production can be met. The bearing cylinder adopted by the axial flow compressor comprises a stationary blade bearing cylinder and a movable blade rotor which is coaxial with the stationary blade bearing cylinder and is rotatably arranged in the stationary blade bearing cylinder, the stationary blade bearing cylinder is of a stepped annular cylinder structure with certain taper, the inner conical surface of the stepped annular cylinder structure is a conical surface, stationary blade blades are fixed at equal intervals, and the taper range of the inner conical surface is usually 2-5 degrees. The movable vane rotor is a cylinder with movable vane blades and is arranged in the inner conical surface. The static blades and the movable blades are alternately arranged to form an airflow compression section.
The axial flow compressor in the prior art usually considers the problem of avoiding the movable blade rubbing cylinder, therefore, a certain gap is usually reserved between the inner conical surface of the stationary blade bearing cylinder and the end part of the movable blade in the radial direction of the movable blade rotor, which causes the following problems in the compression process of the airflow due to the existence of the radial gap when the axial flow compressor in the prior art is in use: 1) the compressed airflow flows back in the axial direction of the rotor blade rotor to the inlet direction of the airflow through the radial gap, and the high static pressure airflow on the pressure surface side of the rotor blade also flows down to the suction surface of the rotor blade, thereby reducing the pressure boosting capability and the efficiency; 2) the radial clearance also tends to cause premature separation of the flow from the bucket blades, while also tending to cause rotational instability problems of the bucket blades.
Disclosure of Invention
In order to solve all or part of the above problems, an object of the present invention is to provide a bearing cylinder for an axial flow compressor, which can prevent a moving blade from rubbing against the cylinder, improve pressure boosting capability and efficiency, and prevent problems of premature separation of an air flow from the moving blade and unstable rotation of the moving blade.
The axial compressor bearing cylinder of the invention comprises: the static blade bearing cylinder comprises a bearing cylinder body and static blade blades which are arranged on the bearing cylinder body at intervals, and a conical inner through hole is formed in the bearing cylinder body; and the movable blade rotor comprises a rotating shaft and movable blade blades, the rotating shaft is coaxially arranged in the conical inner through hole, the movable blade blades are arranged on the rotating shaft at intervals, and the movable blade blades and the static blade blades are alternately distributed between the inner peripheral wall surface of the conical inner through hole and the outer peripheral wall surface of the rotating shaft. A gap is formed between the radial end part of the static blade and the outer wall surface of the rotating shaft, the length of the movable blade extending from the axis of the rotating shaft in the radial direction is equal to the size of the corresponding inner section radius of the conical inner through hole, a plurality of annular grooves coaxial with the conical inner through hole are formed on the inner peripheral wall of the conical inner through hole at intervals, and the annular grooves correspond to the positions of the movable blade in a one-to-one mode.
Further, the radial dimension of the annular groove is 0.6% to 1.6% of the radial length of the bucket blade corresponding thereto.
Further, the axial dimension of the annular groove is 109% to 115% of the chord length dimension formed by the projection of the end of the corresponding movable blade along the axial direction.
Further, the two side surfaces of the annular groove in the axial direction are equal in distance from the intake end side and the exhaust end side of the corresponding rotor blade.
Further, the groove of the annular groove is a rectangular groove, two opposite side surfaces of the rectangular groove are connected with the bottom surface through arc surfaces, and one ends, far away from the bottom surface, of the two opposite side surfaces of the rectangular groove are connected with the inner peripheral wall of the conical inner through hole through the arc surfaces.
Further, the groove of the annular groove is configured as an arc-shaped groove, and the edge of the arc-shaped groove is connected with the inner peripheral wall of the conical inner through hole through an arc surface.
Further, the groove of the annular groove is a triangular groove, and the edge of the triangular groove is connected with the inner peripheral wall of the conical inner through hole through an arc surface.
Further, the recess of ring channel includes relative vertical face and the arc bottom surface of connecting two vertical faces, and two vertical faces are connected through the arc surface with the arc bottom surface, and the one end of keeping away from the arc bottom surface of two vertical faces is passed through the arc surface and is linked to each other with the interior perisporium of conical interior through-hole.
Further, the movable blade is fixed on the rotating shaft through a movable blade tenon, and the static blade is fixed on the cylinder bearing body through a crank.
The invention also provides an axial flow compressor. The axial flow compressor comprises the bearing cylinder of the axial flow compressor.
Compared with the prior art, the axial flow compressor bearing cylinder has the following advantages:
1) compared with the solid wall without the annular groove, the inner peripheral wall surface of the conical inner through hole of the bearing cylinder of the axial flow compressor provided by the invention, which is provided with the annular groove, can effectively avoid the problem of abrasion caused by no clearance between the end part of the movable blade and the inner peripheral wall surface of the conical inner through hole;
2) compared with the solid wall without the annular groove, the inner peripheral wall surface of the conical inner through hole of the bearing cylinder of the axial flow compressor provided by the invention can effectively reduce the influence of gap loss (leakage, backflow and undercurrent) between the end part of the movable blade and the inner peripheral wall surface of the conical inner through hole, thereby effectively delaying the separation of the blade back airflow and reducing the loss;
3) the actual extension length of the movable blade of the bearing cylinder of the axial flow compressor is increased, so that the linear speed of the blade tip of the movable blade is increased, the linear speed of the blade tip of the movable blade is increased under the same rotating speed, the working capacity of the movable blade is enhanced, the stall margin is increased, and the actual surge-to-point pressure ratio is increased.
Drawings
FIG. 1 is a schematic structural view of a bearing cylinder of an axial compressor according to an embodiment of the present invention;
fig. 2 is a partial structural view of a bearing cylinder of the axial flow compressor shown in fig. 1.
Detailed Description
In order to better understand the purpose, structure and function of the present invention, a bearing cylinder of an axial flow compressor according to the present invention will be described in further detail with reference to the accompanying drawings.
Fig. 1 and 2 illustrate a structure of an axial compressor bearing cylinder 100 according to an embodiment of the present invention, wherein fig. 1 is a schematic structural view of the axial compressor bearing cylinder 100 according to the embodiment of the present invention, and fig. 2 is a schematic partial structural view of the axial compressor bearing cylinder 100 illustrated in fig. 1. As shown in fig. 1 and 2, an axial compressor bearing cylinder 100 according to an embodiment of the present invention includes: the static blade bearing cylinder 1 is characterized in that the static blade bearing cylinder 1 comprises a bearing cylinder body 11 and static blade blades 12 arranged on the bearing cylinder body 11 at intervals, and a conical inner through hole 13 is formed in the bearing cylinder body 11; and the movable blade rotor 2, the movable blade rotor 2 includes a rotating shaft 21 coaxially arranged in the conical inner through hole 13 and movable blade blades 22 arranged on the rotating shaft 21 at intervals, and the movable blade blades 22 and the stationary blade blades 12 are alternately distributed between the inner peripheral wall surface of the conical inner through hole 13 and the outer peripheral wall surface of the rotating shaft 21. A gap is formed between the radial end 12a of the stationary blade 12 and the outer wall surface of the rotating shaft 21, the length of the movable blade 22 extending in the radial direction from the axis of the rotating shaft 21 is equal to the size of the corresponding inner cross-sectional radius of the conical inner through hole 13, a plurality of annular grooves 3 coaxial with the conical inner through hole 13 are formed on the inner peripheral wall of the conical inner through hole 13 at intervals, and the positions of the annular grooves 3 and the positions of the movable blades 22 are in one-to-one correspondence.
When the axial compressor bearing cylinder 100 according to the embodiment of the present invention is used, as shown in fig. 1, the stationary blade bearing cylinder 1 is in a stationary state, the rotor blade rotor 2 is in a high-speed rotating state, and the gas enters the axial compressor bearing cylinder 100 from the intake end side a, is subjected to the action of the stationary blade 12 and the rotor blade 22, forms compressed gas, and is finally discharged from the exhaust end side B.
The axial compressor bearing cylinder 100 according to the embodiment of the present invention:
first, a gap is formed between the radial end 12a of the stationary blade 12 and the outer wall surface of the rotating shaft 21, so that when the movable blade rotor 2 rotates at a high speed, the problem that the stationary blade 12 and the outer wall of the rotating shaft 21 are easily rubbed can be effectively avoided, and the abrasion between the stationary blade 12 and the outer wall of the rotating shaft 21 can be effectively avoided;
secondly, the length of the bucket blade 22 extending radially from the axis of the shaft 21, i.e. the radial distance of the axis of the shaft 21 from the end 22a of the bucket blade 22, is equal to the size of the corresponding inner cross-sectional radius of the conical inner through hole 13, which is longer than the clearance remaining in the prior art for the radial length of the bucket blade 22. Meanwhile, a plurality of annular grooves 3 are formed in the inner circumferential wall of the conical inner through hole 13 at positions corresponding to the respective moving blade blades 22. With this arrangement, compared with the solid wall surface having no annular groove 3, the inner circumferential wall surface of the conical inner through hole 13 having the annular groove 3 formed therein can effectively avoid the problem of wear due to the clearance between the end 22a of the moving blade 22 and the inner circumferential wall surface of the conical inner through hole 13, and can effectively reduce the influence of the loss of the clearance (leakage, backflow, and underflow) between the end 22a of the moving blade 22 and the inner circumferential wall surface of the conical inner through hole 13, thereby effectively delaying the flow separation of the blade back and reducing the loss; on the other hand, the actual extension length of the rotor blade 22 is increased so that the linear velocity of the tip (end portion 22a) of the rotor blade 22 is increased, and at the same rotational speed, the linear velocity of the tip of the rotor blade 22 is increased, the workability of the rotor blade 22 is enhanced, the stall margin is increased, and the actual surge-to-pressure ratio is increased.
Therefore, compared with the bearing cylinder with different grooves, the blade tip (end portion 22a) of the moving blade 22 of the axial flow compressor bearing cylinder 100 according to the embodiment of the present invention and the position of the boundary layer of the inner wall surface of the corresponding conical inner through hole 13 are changed, and the influence of the boundary layer factors is reduced under the same reference, so that the phenomena of the premature separation of the air flow and the unstable rotation can be effectively delayed.
It should be noted that "axial" referred to herein should be understood as a direction of the axis of the rotating shaft 21, and "radial" should be understood as a direction perpendicular to the axis of the rotating shaft 21.
In a preferred embodiment, the radial dimension of the annular groove 3 may be 0.6% to 1.6% of the radial length of the bucket blade 22 corresponding thereto. According to the invention, through carrying out a three-dimensional simulation test on the proportion of the blade tip clearance, and according to a three-dimensional calculation result and related data, the radial dimension of the annular groove 3 is limited to be 0.6-1.6% of the radial length of the movable blade 22 corresponding to the radial dimension, so that the blade tip (end part 22a) of the movable blade 22 and the groove bottom clearance of the annular groove 3 are appropriate in value, and thus, through the arrangement, the air flow loss caused by the radial clearance leakage and secondary flow of the blade tip (end part 22a) of the movable blade 22 can be effectively reduced, and the occurrence of the air flow separation phenomenon can be slowed down.
Also preferably, the axial dimension of the annular groove 3 may be 109% to 115% of the chord length dimension formed by the projection of the end 22a of the bucket blade 22 corresponding thereto in the axial direction. Further preferably, both side surfaces of the annular groove 3 in the axial direction may be equal in distance from the intake end side a and the exhaust end side B of the rotor blade 22 corresponding thereto, respectively. With this arrangement, the axial ratio is selected taking into account the smooth transition of the airflow flow, taking a certain ratio of the axial projection lengths of the blades in relation to the axial clearance of the front and rear blade rows, thus giving the above ratios.
It should be noted that, in conjunction with the above description, the data range defined in the present invention also takes into consideration the influence of factors such as manufacturing and installation in actual engineering, and therefore, the optimal gap value range is theoretically relatively narrower.
In the first preferred embodiment shown in fig. 1 and 2, the groove of the annular groove 3 may be configured as a rectangular groove, opposite side surfaces of which may be connected to the bottom surface by an arc surface, and ends of the opposite side surfaces of which, which are away from the bottom surface, may be connected to the inner circumferential wall of the conical inner through-hole 13 by an arc surface. In a second preferred embodiment, the groove of the annular groove 3 may be configured as an arc-shaped groove, and the edge of the arc-shaped groove may be connected to the inner circumferential wall of the conical inner through-hole 13 by an arc surface. In a third preferred embodiment, the groove of the annular groove 3 may be configured as a triangular groove, and the edge of the triangular groove may be connected to the inner circumferential wall of the conical inner through-hole 13 by a circular arc surface. In a fourth preferred embodiment, the groove of the annular groove 3 may include two opposite vertical surfaces and an arc bottom surface connecting the two vertical surfaces, the two vertical surfaces may be connected with the arc bottom surface through an arc surface, and one ends of the two vertical surfaces far away from the arc bottom surface may be connected with the inner peripheral wall of the conical inner through hole 13 through the arc surface.
With the above arrangement, including the four embodiments, but not limited to the axial compressor bearing cylinder 100 according to the present invention of the four embodiments, the structure of the annular groove 3 can be implemented according to specific requirements, for example, the structure of the annular groove 3 can be implemented by combining various factors such as convenience of processing, requirement of pressure boosting capability, and pressure boosting efficiency.
Preferably, the moving blade 22 may be fixed to the rotating shaft 21 by a moving blade tenon 23, and the stationary blade 12 may be fixed to the cylinder receiving body 11 by a crank 14. With the arrangement, the axial flow compressor bearing cylinder 100 according to the embodiment of the present invention can adjust the stationary blade 12 through the crank 14, and at the same time, the movable blade 22 is firmly fixed through the movable blade tenon 23, so that the axial flow compressor bearing cylinder 100 according to the embodiment of the present invention can not only adjust the stationary blade 12 to meet various application requirements, but also improve the stability of the use of the axial flow compressor bearing cylinder 100 according to the embodiment of the present invention, and prolong the service life thereof.
The invention also provides an axial flow compressor. The axial compressor according to the present invention includes the above axial compressor bearing cylinder 100. As can be seen from the above description, the axial compressor of the present invention including the bearing cylinder 100 of the axial compressor can effectively improve the pressure boosting capability and efficiency when in use, and avoid the problems of premature separation of the airflow from the moving blade and unstable rotation of the moving blade.
It is to be noted that, unless otherwise specified, technical or scientific terms used herein shall have the ordinary meaning as understood by those skilled in the art to which the invention pertains.
In the description of the present application, it is to be understood that the terms "length," "inner," "axial," "radial," and the like are used in the positional or orientational relationships shown in the drawings to facilitate the description of the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be construed as limiting the invention.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention, and they should be construed as being included in the following claims and description. In particular, the technical features mentioned in the embodiments can be combined in any way as long as there is no structural conflict. It is intended that the invention not be limited to the particular embodiments disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (10)
1. The utility model provides an axial flow compressor bearing cylinder which characterized in that includes:
the static blade bearing cylinder comprises a bearing cylinder body and static blade blades arranged on the bearing cylinder body at intervals, and a conical inner through hole is formed in the bearing cylinder body; and
the movable blade rotor comprises a rotating shaft and movable blade blades, the rotating shaft is coaxially arranged in the conical inner through hole, the movable blade blades and the fixed blade blades are arranged on the rotating shaft at intervals, and the movable blade blades and the fixed blade blades are alternately distributed between the inner peripheral wall surface of the conical inner through hole and the outer peripheral wall surface of the rotating shaft;
a gap is formed between the radial end of the stationary blade and the outer wall surface of the rotating shaft, the length of the movable blade extending from the axis of the rotating shaft in the radial direction is equal to the size of the corresponding inner section radius of the conical inner through hole, a plurality of annular grooves coaxial with the conical inner through hole are formed on the inner peripheral wall of the conical inner through hole at intervals, and the annular grooves correspond to the positions of the movable blades one by one.
2. The axial compressor bearing cylinder according to claim 1, wherein the radial dimension of the annular groove is 0.6% to 1.6% of the radial length of the bucket blade corresponding thereto.
3. The axial compressor bearing cylinder according to claim 2, wherein the axial dimension of the annular groove is 109% to 115% of a chord length dimension formed by a projection of the end of the bucket blade corresponding thereto in the axial direction.
4. The axial compressor bearing cylinder according to claim 3, wherein both side surfaces in the axial direction of the annular groove are equal in distance from the intake end side and the exhaust end side of the rotor blade corresponding thereto, respectively.
5. The axial compressor bearing cylinder according to any one of claims 1 to 4, wherein the groove of the annular groove is configured as a rectangular groove, two opposite side surfaces of the rectangular groove are connected with the bottom surface through arc surfaces, and one ends of the two opposite side surfaces of the rectangular groove, which are far away from the bottom surface, are connected with the inner peripheral wall of the conical inner through hole through arc surfaces.
6. The axial compressor bearing cylinder according to any one of claims 1 to 4, wherein the groove of the annular groove is configured as an arc-shaped groove, and an edge of the arc-shaped groove is connected with an inner peripheral wall of the conical inner through hole by an arc surface.
7. The axial compressor bearing cylinder according to any one of claims 1 to 4, wherein the groove of the annular groove is configured as a triangular groove, and an edge of the triangular groove is connected to an inner peripheral wall of the conical inner through hole by a circular arc surface.
8. The axial compressor bearing cylinder according to any one of claims 1 to 4, wherein the groove of the annular groove comprises opposite vertical surfaces and an arc-shaped bottom surface connecting the two vertical surfaces, the two vertical surfaces are connected with the arc-shaped bottom surface through arc surfaces, and one ends of the two vertical surfaces far away from the arc-shaped bottom surface are connected with the inner peripheral wall of the conical inner through hole through arc surfaces.
9. Bearing cylinder for axial compressors according to any of the claims 1 to 4, characterized in that said moving blades are fixed on said shaft by means of moving blade tenons and said stationary blades are fixed on said bearing cylinder body by means of cranks.
10. An axial compressor characterized by comprising the axial compressor bearing cylinder according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011423569.0A CN112360816A (en) | 2020-12-08 | 2020-12-08 | Axial compressor bearing cylinder and axial compressor using same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011423569.0A CN112360816A (en) | 2020-12-08 | 2020-12-08 | Axial compressor bearing cylinder and axial compressor using same |
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| Publication Number | Publication Date |
|---|---|
| CN112360816A true CN112360816A (en) | 2021-02-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011423569.0A Pending CN112360816A (en) | 2020-12-08 | 2020-12-08 | Axial compressor bearing cylinder and axial compressor using same |
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| Country | Link |
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| CN (1) | CN112360816A (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB857800A (en) * | 1957-04-29 | 1961-01-04 | Gen Electric | Improvements in compressor |
| GB907373A (en) * | 1960-06-14 | 1962-10-03 | Daimler Benz Ag | Improvements relating to means for adjusting guide vanes in gas turbines, rotary compressors or like rotary bladed flow machines |
| US4238170A (en) * | 1978-06-26 | 1980-12-09 | United Technologies Corporation | Blade tip seal for an axial flow rotary machine |
| EP0194957A2 (en) * | 1985-03-11 | 1986-09-17 | United Technologies Corporation | Compressor blade tip seal |
| US4645417A (en) * | 1984-02-06 | 1987-02-24 | General Electric Company | Compressor casing recess |
| JPH07247996A (en) * | 1994-03-11 | 1995-09-26 | Ishikawajima Harima Heavy Ind Co Ltd | Passage form of compressor |
| WO2006137696A1 (en) * | 2005-06-23 | 2006-12-28 | Korea Ocean Research And Development Institute | Impulse turbine with rotor blade for prevention clearance flow loss |
| JP2016044567A (en) * | 2014-08-20 | 2016-04-04 | 三菱重工業株式会社 | Rotary machine |
| US20160348530A1 (en) * | 2013-12-19 | 2016-12-01 | Scnema | Turbine engine compressor, in particular of an aeroplane turboprop or turbofan |
| CN213775827U (en) * | 2020-12-08 | 2021-07-23 | 成都成发科能动力工程有限公司 | Axial compressor bearing cylinder and axial compressor using same |
-
2020
- 2020-12-08 CN CN202011423569.0A patent/CN112360816A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB857800A (en) * | 1957-04-29 | 1961-01-04 | Gen Electric | Improvements in compressor |
| GB907373A (en) * | 1960-06-14 | 1962-10-03 | Daimler Benz Ag | Improvements relating to means for adjusting guide vanes in gas turbines, rotary compressors or like rotary bladed flow machines |
| US4238170A (en) * | 1978-06-26 | 1980-12-09 | United Technologies Corporation | Blade tip seal for an axial flow rotary machine |
| US4645417A (en) * | 1984-02-06 | 1987-02-24 | General Electric Company | Compressor casing recess |
| EP0194957A2 (en) * | 1985-03-11 | 1986-09-17 | United Technologies Corporation | Compressor blade tip seal |
| JPH07247996A (en) * | 1994-03-11 | 1995-09-26 | Ishikawajima Harima Heavy Ind Co Ltd | Passage form of compressor |
| WO2006137696A1 (en) * | 2005-06-23 | 2006-12-28 | Korea Ocean Research And Development Institute | Impulse turbine with rotor blade for prevention clearance flow loss |
| US20160348530A1 (en) * | 2013-12-19 | 2016-12-01 | Scnema | Turbine engine compressor, in particular of an aeroplane turboprop or turbofan |
| JP2016044567A (en) * | 2014-08-20 | 2016-04-04 | 三菱重工業株式会社 | Rotary machine |
| CN213775827U (en) * | 2020-12-08 | 2021-07-23 | 成都成发科能动力工程有限公司 | Axial compressor bearing cylinder and axial compressor using same |
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