CN213775827U - Axial compressor bearing cylinder and axial compressor using same - Google Patents

Abstract

The utility model belongs to the technical field of axial compressor, a axial compressor who holds jar and use it is disclosed to axial compressor. 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

Axial compressor bearing cylinder and axial compressor using same

Technical Field

The utility model belongs to the technical field of axial compressor, concretely relates to axial compressor holds jar and uses its axial compressor.

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.

SUMMERY OF THE UTILITY MODEL

In order to solve the above-mentioned whole or partial problem, the utility model aims to provide an axial compressor holds jar to when can avoiding the movable vane to wipe the jar, improve boost capacity and efficiency, avoid the air current to take place from the too early separation of movable vane blade department and the unstable problem of rotation of movable vane blade.

The utility model discloses an 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 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 utility model also provides an axial compressor. According to the utility model discloses an axial compressor includes that above-mentioned axial compressor holds the jar.

Compared with the prior art, the utility model discloses an axial compressor holds jar has the following advantage in several respects:

1) compared with the solid wall without the annular groove, the inner peripheral wall surface of the conical inner through hole of the axial flow compressor bearing cylinder 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 ring groove, the inner peripheral wall surface of the conical inner through hole of the bearing cylinder of the axial flow compressor of the utility model can effectively reduce the influence of the 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 utility model discloses an axial compressor holds actual extension length of movable blade of jar and obtains increasing the linear velocity of the apex that makes the movable blade, and under the same rotational speed, the apex linear velocity of movable blade increases, and the ability reinforcing of doing work of movable blade, stall margin increase, actual surge point pressure ratio increase.

Drawings

Fig. 1 is a schematic structural view of a bearing cylinder of an axial flow 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

For better understanding, the purpose, structure and function of the present invention are described in detail below with reference to the accompanying drawings.

Fig. 1 and fig. 2 show the structure of the axial compressor bearing cylinder 100 according to the embodiment of the present invention, wherein fig. 1 is the structural schematic diagram of the axial compressor bearing cylinder 100 according to the embodiment of the present invention, and fig. 2 is a partial structural schematic diagram of the axial compressor bearing cylinder 100 shown 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.

According to the utility model discloses axial compressor holds jar 100 when using, as shown in fig. 1, quiet leaf holds jar 1 for quiescent condition, and movable vane rotor 2 is high-speed rotating state, and gaseous entering axial compressor holds jar 100 by the distolateral A of admitting air in, after the effect of quiet leaf 12 and movable vane 22, forms compressed gas and finally is located to discharge by exhaust end side B.

According to the utility model discloses axial compressor holds jar 100:

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 rotor 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 rotor blade 22 and the inner circumferential wall surface of the conical inner through hole 13, thereby effectively delaying the separation of the flow 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, compare with the jar that holds of different fluting, the utility model discloses axial compressor holds apex (tip 22a) of movable vane blade 22 of jar 100 and the internal face boundary layer position of corresponding conical interior through-hole 13 and changes, and under same benchmark, the influence of boundary layer factor reduces to can delay the too early separation of air current and rotatory unstable phenomenon effectively and take place.

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 utility model discloses, carry out three-dimensional simulation test through the proportion to the apex clearance, according to three-dimensional calculated result and relevant data, be 0.6% to 1.6% rather than the radial length of corresponding movable vane blade 22 through the radial dimension who restricts ring channel 3 for movable vane blade 22's apex (tip 22a) is suitable with ring channel 3's tank bottom clearance value, and like this, can reduce the air current loss that causes by movable vane blade 22's apex (tip 22a) radial gap leakage and secondary flow effectively through this setting, slows down the air current separation phenomenon and takes place.

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 combination 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.

Through the above arrangement, the axial compressor bearing cylinder 100 according to the present invention, including the above four embodiments, but not limited to the above four embodiments, can be specifically implemented to the structure of the annular groove 3 according to specific requirements, for example, the structure of the annular groove 3 can be specifically implemented by combining various factors such as the convenience of processing, the requirement of the boosting capacity, and the 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. Through this setting, can make the utility model discloses axial compressor holds jar 100 and adjusts quiet leaf blade 12 through crank 14, fixes the firm of movable vane 22 through movable vane tenon 23 simultaneously, thereby not only makes the utility model discloses axial compressor holds jar 100 quiet leaf blades 12 adjustable to satisfy multiple application demand, can also improve the utility model discloses axial compressor holds the stability that jar 100 used, prolongs its life.

The utility model also provides an axial compressor. According to the utility model discloses an axial compressor includes above-mentioned axial compressor and holds jar 100. In view of the above, the axial compressor of the present invention includes the above-mentioned axial compressor bearing cylinder 100, which can effectively improve the boosting capacity and efficiency when in use, and avoid the problem of the unstable rotation of the air flow from the premature separation of the movable blade and the movable 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 present invention belongs.

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 orientations and positional relationships indicated in the drawings for convenience in describing the present invention and for simplicity in 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 thus should not be construed as limiting the present 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; although the present invention has been described in detail with reference to the foregoing embodiments, it should 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 substantially depart from the scope of the embodiments of the present invention, and are intended to be covered by the claims and the specification. In particular, the technical features mentioned in the embodiments can be combined in any way as long as there is no structural conflict. The present invention is not limited to the particular embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the 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.

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