CN216554613U - Compressor guide vane adjusting and driving mechanism - Google Patents
Compressor guide vane adjusting and driving mechanism Download PDFInfo
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- CN216554613U CN216554613U CN202121711002.3U CN202121711002U CN216554613U CN 216554613 U CN216554613 U CN 216554613U CN 202121711002 U CN202121711002 U CN 202121711002U CN 216554613 U CN216554613 U CN 216554613U
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Abstract
The utility model discloses an adjusting driving mechanism of a guide vane of a gas compressor, which mainly comprises a main actuating cylinder, an auxiliary actuating cylinder and a connecting pipeline. The primary and secondary rams control movement of the piston by a high pressure air supply that is directed from the compressor case. The higher the rotating speed of the air compressor is, the larger the air entraining pressure of the adjustable guide vane adjusting and driving mechanism is, the larger the piston displacement of the actuating cylinder is, and the larger the rotating angle of the adjustable guide vane is. The parameters can quantitatively meet the regulation requirement of the compressor through the detailed design of the internal structure of the actuating cylinder. The guide vane adjusting and driving mechanism can adjust the angle of the guide vane by air bleed from the casing of the air compressor, and a hydraulic source or an air source does not need to be specially equipped for the guide vane adjusting and driving mechanism, so that the cost and the complexity of the guide vane adjusting and driving mechanism are reduced.
Description
Technical Field
The utility model belongs to the technical field of gas compressors, and relates to an adjusting and driving mechanism for adjustable guide vanes of a gas compressor, in particular to a self-air-entraining controlled adjusting and driving mechanism for guide vanes of the gas compressor. The utility model is also applicable to compressor sets with guide vane adjusting mechanisms.
Background
The core components of a gas turbine include a compressor, a combustor, and a turbine. The purpose of the compressor is to compress air to form high-pressure air, then the high-pressure air flows into the combustion chamber to be mixed and combusted with fuel to generate high-temperature high-pressure gas, and finally the high-temperature high-pressure gas pushes the turbine to rotate to work, so that the purpose of converting chemical energy into mechanical energy is achieved.
For medium-large gas turbines, the compressor generally adopts an axial flow compressor, that is, the air is forced to flow from the front end to the rear end of the compressor by the interaction of multi-stage rotor blades and stator blades, and the air pressure of the air in a flow channel is gradually increased. In order to improve the working coordination of the multistage blades and enable the compressor to stably work in a wider range, the stator blades of the compressor are required to have certain opening and closing capabilities frequently, so that the installation angle of the stator blades is adjusted. In engineering, a gas turbine is generally provided with an adjustable guide vane adjusting and driving mechanism of a gas compressor to drive the opening and closing angles of certain stages of stator blades.
The common adjustable guide vane adjusting system in the engineering at present adopts a driving structure formed by a main actuating cylinder and an auxiliary actuating cylinder to ensure that stator blades synchronously rotate to a specified angle. The working medium of the two actuating cylinders is generally fuel oil or an adjustable hydraulic oil source or a gas source provided by a test bed. For the gas turbine adopting fuel oil as fuel, the actuating cylinder can be controlled to act by expanding the functional module of the fuel oil adjusting device. However, for a gas turbine using natural gas as fuel, the compressor guide vane adjusting and driving mechanism is no longer suitable for using fuel oil as a working medium of the adjusting system driving mechanism, and a controllable hydraulic oil source or a controllable gas source needs to be separately provided for the actuating cylinder, which obviously increases the complexity and the cost of the gas turbine system and also increases the complexity of a gas turbine control system.
The patent provides a design scheme of extracting high-pressure air from a flow passage of a gas compressor to be used as a working medium of an actuating cylinder. Through the internal structure design of the actuating cylinder, the functional relation between the working state of the air compressor and the adjusting angle of the guide vane can be established, and hydraulic oil equipment or control air source equipment for providing working media for the blade adjusting mechanism in the original design is omitted.
SUMMERY OF THE UTILITY MODEL
In order to solve the problem of source of working media of a driving mechanism in a guide vane adjusting system of a gas compressor, the utility model provides the guide vane adjusting and driving mechanism of the gas compressor.
Specifically, the technical scheme adopted by the utility model for solving the technical problem is as follows:
a compressor guide vane adjusting and driving mechanism at least comprises a main actuating cylinder and an auxiliary actuating cylinder, and is characterized in that,
the main actuating cylinder at least comprises a main driving rod, a main actuating cylinder shell, an inner cylinder, a main bearing piston, a main rear end cover, a supporting bushing, a pull rod and a control piston, wherein,
the inner cylinder is arranged in the main actuating cylinder shell, the inner cylinder is a cylindrical cylinder with openings at two ends, a flange mounting edge is formed at the rear end of the cylindrical cylinder, and the flange mounting edge is fixedly connected with a connecting flange at the rear end of the main actuating cylinder shell;
the main bearing piston is arranged in the main actuating cylinder shell and comprises a cylindrical main body part and a hollow rod-shaped extension part formed at the front end of the cylindrical main body part; an annular flange part is formed at the rear end of the cylindrical main body part and can move back and forth along the inner wall of the main actuating cylinder shell; the inner cavity of the rod-shaped extension part is communicated with the inner cavity of the cylindrical main body part, and the rod-shaped extension part can move back and forth along the central hole at the front end of the actuating cylinder shell; the main driving rod is fixedly arranged at the front end of the rod-shaped extension part and is connected with a linkage ring of an adjustable guide vane of the gas compressor; a plug cover with a central hole is fixedly arranged at the front end of the inner cavity of the cylindrical main body part;
the main rear end cover comprises a plate-shaped cover body and a cylindrical extending portion formed on the front end face of the plate-shaped cover body, the plate-shaped cover body is fixedly arranged at the rear end of the inner cylinder through a connecting piece, the cylindrical extending portion is coaxially sleeved in the inner cavity of the inner cylinder, a switching sleeve is coaxially arranged at the front end of the cylindrical extending portion, the switching sleeve comprises a front-end large-diameter section and a rear-end small-diameter section, a step portion is formed between the front-end large-diameter section and the rear-end small-diameter section, the rear-end small-diameter section of the switching sleeve is inserted at the front end of the cylindrical extending portion, and the switching sleeve can move back and forth along the axial direction under the dual restraint of the cylindrical extending portion and the inner cylinder;
the control piston is arranged in the cylindrical extension part of the main rear end cover in a front-back sliding manner, an annular bulge is arranged on the inner wall of the inner cylinder close to the front end, a large spring is arranged between the annular bulge and the step part of the adapter sleeve, the support bushing is fixedly arranged on the front side of the annular bulge through a connecting piece arranged at the front end of the inner cylinder, and a small spring is arranged between the control piston and the support bushing;
the rear end of the pull rod is fixedly connected with the control piston, the main body part of the pull rod penetrates through the support bushing, a diameter reducing part is formed at the front end of the pull rod and penetrates through a central hole of a plug cover in the force bearing piston, a locking nut is fixedly arranged on the pull rod, the outer diameter of the diameter reducing part at the front end of the pull rod is smaller than the aperture of the central hole of the plug cover in the force bearing piston, and a gap is formed between the diameter reducing part and the central hole;
the main actuating cylinder forms R, S, T, W air chambers with 4 air chambers in total, wherein,
the air cavity R and the air cavity S are respectively positioned at two sides of the main force bearing piston, the space between the outer wall of the main force bearing piston and the inner wall of the main actuating cylinder shell forms the air cavity R, and the space enclosed by the inner wall of the main force bearing piston, the inner wall of the main actuating cylinder shell, the outer wall of the inner cylinder, the blanking cover and the support bushing forms the air cavity S; the air cavity T and the air cavity W are respectively positioned at two sides of the control piston, the air cavity T is formed by the space enclosed among the control piston, the inner cylinder, the cylindrical extension part of the main rear end cover, the adapter sleeve and the support bushing, and the space enclosed between the brake piston and the plate-shaped cover body of the main rear end cover is formed into the air cavity W;
a, B, C, D, E gas interfaces are arranged on the main actuating cylinder, a plate-shaped cover body of the main rear end cover is provided with a gas interface A communicated with the gas cavity W, an annular end cover of the inner cylinder is provided with a gas interface B communicated with the gas cavity T, the wall surface of the actuating cylinder shell is respectively provided with a gas interface C, D communicated with the gas cavity R, and the annular end cover of the inner cylinder is provided with a gas interface E communicated with the gas cavity S;
the auxiliary actuating cylinder at least comprises an auxiliary driving rod, an auxiliary actuating cylinder shell, an auxiliary bearing piston and an auxiliary rear end cover, wherein,
the auxiliary actuating cylinder shell is integrally a cylindrical shell part with an opening at the rear end and a closed front end, an annular connecting flange is formed at the rear end of the auxiliary actuating cylinder shell, a central through hole is formed on the front end surface of the auxiliary actuating cylinder shell,
the auxiliary rear end cover comprises a plate-shaped cover body and a columnar extension part formed on the front end surface of the plate-shaped cover body, the plate-shaped cover body is fixedly arranged on a rear end connecting flange of the auxiliary actuating cylinder shell, the columnar extension part is coaxially sleeved in the auxiliary actuating cylinder shell,
the auxiliary force bearing piston is coaxially sleeved in the auxiliary actuating cylinder shell and comprises a cylindrical main body part and a rod-shaped extension part formed at the front end of the cylindrical main body part, and the cylindrical main body part of the auxiliary force bearing piston can move back and forth along the outer wall of the cylindrical extension part of the auxiliary rear end cover; an annular flange part is formed at the rear end of the cylindrical main body part of the auxiliary bearing piston and can move back and forth along the inner wall of the auxiliary actuating cylinder shell; the rod-shaped extension part can move back and forth along the central through hole at the front end of the auxiliary actuating cylinder shell; the auxiliary driving rod is fixedly arranged at the front end of the rod-shaped extension part and is also connected with a linkage ring of an adjustable guide vane of the gas compressor;
m, N air cavities are formed in the auxiliary actuating cylinder, wherein the air cavity M and the air cavity N are respectively positioned at the front side and the rear side of the auxiliary bearing piston, the space between the outer wall of the auxiliary bearing piston and the inner wall of the auxiliary actuating cylinder shell is formed into the air cavity N, and the space enclosed by the inner wall of the auxiliary bearing piston, the inner wall of the auxiliary actuating cylinder shell and the auxiliary rear end cover is formed into the air cavity M;
the auxiliary actuating cylinder is provided with F, G, H, J gas interfaces with 4, wherein a plate-shaped cover body of the auxiliary rear end cover is provided with a gas interface F, J communicated with the gas cavity M, and the wall surface of the shell of the auxiliary actuating cylinder is respectively provided with a gas interface G, H communicated with the gas cavity N;
-leading out a high-pressure gas source from a compressor casing, introducing high-pressure air in a compressor flow channel, wherein the high-pressure gas source is respectively communicated with a gas interface A of the main actuating cylinder, a gas interface F of the auxiliary actuating cylinder and a gas interface H of the auxiliary actuating cylinder through pipelines; the gas interface E of the main actuating cylinder is connected with the gas interface J of the auxiliary actuating cylinder through a pipeline; the gas interface C of the main actuating cylinder is connected with the gas interface G of the auxiliary actuating cylinder through a pipeline; the gas interface B of the main actuating cylinder is communicated with the atmospheric environment in a design state; and the gas interface D of the main actuating cylinder is in a closed state in a working state.
The utility model relates to a compressor guide vane adjusting and driving mechanism which mainly comprises a main actuating cylinder, an auxiliary actuating cylinder and a connecting pipeline. The main actuating cylinder and the auxiliary actuating cylinder work synchronously to drive the linkage ring of the guide vane of the gas compressor together, so that the incongruity of the guide vane of the gas compressor along the circumferential direction can be avoided. The main actuating cylinder comprises a control piston and a force bearing piston, and the auxiliary actuating cylinder only comprises the force bearing piston and no control piston. The control piston in the main actuating cylinder determines whether the cavity pressure of the rodless cavity of the bearing piston can be established; the force bearing piston determines the displacement of the actuating cylinder driving rod. The connecting pipeline comprises a plurality of sections of pipelines, wherein a part of the pipelines guide a high-pressure air source from an interface on the casing of the compressor to be used by the two actuating cylinders; the other part of pipeline connects the rod cavities of the bearing pistons in the two actuating cylinders and simultaneously connects the two rodless cavities. For the two actuating cylinders of the main actuating cylinder and the auxiliary actuating cylinder, high-pressure air led from a casing of the compressor can jointly control the displacement of a control piston in the main actuating cylinder in combination with a spring, so that whether a rodless cavity of a bearing piston can build pressure or not is controlled, and the displacement of the bearing piston and a driving rod is further controlled.
Preferably, an adjusting ring is arranged between the support bushing in the main actuating cylinder and the annular boss in the inner cylinder, an adjusting pad is arranged between the small spring and the control piston, and the pre-pressure of the small spring is changed by adjusting the thickness of the adjusting ring and/or the adjusting pad. That is, the relationship between the displacement of the control piston in the main ram and the bleed air pressure of the compressor case is fine-tunable. Specifically, the pre-pressure of the small spring can be changed by adjusting the thickness of an adjusting pad and/or an adjusting ring at the end of the spring, so that the air pressure critical value for controlling the piston to start moving is changed; the force balance of the control piston can also be changed in special cases by supplying air to the air chamber where the spring is located.
In addition, the air pressure of the force bearing piston rod cavity and the air pressure of the force bearing piston rodless cavity of the main actuating cylinder and the auxiliary actuating cylinder are both derived from the bleed air of the casing of the secondary compressor, and the cavity pressures of the two cavities are close to each other. The force of the force bearing piston mainly depends on the cavity pressure acting area in the rod cavity and the rodless cavity, and meanwhile, the cavity pressure can be finely adjusted on the throttling elements of the air inlet interfaces of the rod cavity and the rodless cavity.
Preferably, the main driving rod is fixedly connected with the main bearing piston, and the main driving rod and the main bearing piston move synchronously; the auxiliary driving rod is fixedly connected with the auxiliary bearing piston, and the auxiliary driving rod and the auxiliary bearing piston move synchronously.
Preferably, a sealing ring is arranged between an annular flange part of the cylindrical main body part of the main force bearing piston and the inner wall of the main actuating cylinder shell, a sealing ring is arranged between the rod-shaped extension part of the main force bearing piston and a central hole at the front end of the main actuating cylinder shell, a sealing ring is arranged between the annular bulge in the inner cylinder and the support bushing, a sealing ring is arranged between the central rod of the control piston and the support bushing, a sealing ring is arranged between the annular end cover at the rear end of the inner cylinder and the connecting flange at the rear end of the main actuating cylinder shell, and a sealing ring is arranged between the main rear end cover and the rear end of the inner cylinder, so that the sealing performance of the air cavity R, S, T, W is ensured.
Preferably, the rear end small-diameter section of the adapter sleeve is in large clearance fit with the cylindrical extension part of the main rear end cover, and the front end large-diameter section of the adapter sleeve is in large clearance fit with the inner cylinder. Preferably, in the non-operating state, the air pressure in the air chamber W, T, S, R is ambient air pressure, the control piston stops at the rearmost end (leftmost side) under the pre-pressure of a small spring, and the force bearing piston stops at the rearmost end (leftmost side) along with the control piston.
Preferably, a step part for controlling the axial movement of the piston in a serial mode is limited on the pull rod, a gap Y is formed between the rear side surface B of the plug cover in the main force bearing piston and the step part of the pull rod, and the air cavity S is communicated with the atmospheric environment through the gap Y, a gap between the diameter reducing part of the pull rod and the central hole of the plug cover of the main force bearing piston and a gap between the rod-shaped extension part of the main force bearing piston and the main driving rod.
Further, when the air pressure in the air cavity W rises enough to overcome the pre-pressure of the small spring, the control piston starts to move forward (right), when the moving distance reaches the value of the gap Y, the gap Y is blocked, the air cavity S is no longer communicated with the atmosphere, and the air pressure in the air cavity S starts to be determined by the air pressure of the air introduced from the air interface E.
Further, as the air pressure in the air chamber W further rises, the control piston continues to move forward (right), and the large spring starts to be compressed when the control piston moves to a position where it presses the adapter sleeve.
Preferably, sealing rings are arranged between the plate-shaped cover body of the auxiliary rear end cover and the connecting flange at the rear end of the auxiliary actuating cylinder shell, between the annular flange part at the rear end of the cylindrical main body part of the auxiliary force bearing piston and the auxiliary actuating cylinder shell, and between the rod-shaped extension part of the auxiliary force bearing piston and the central through hole at the front end of the actuating cylinder shell, so as to jointly ensure the sealing performance of the air cavity M, N.
In addition to the above features and advantages, the present invention has other objects, features and advantages. The present invention will be described in further detail below with reference to the drawings.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the utility model and, together with the description, serve to explain the utility model and not to limit the utility model. In the drawings:
FIG. 1 is a schematic diagram of a compressor vane adjustment drive mechanism in accordance with a preferred embodiment of the present invention;
fig. 2 is a schematic view of the internal structure of the primary ram of the preferred embodiment of the present invention;
FIG. 3 is an enlarged fragmentary view of region A of the main ram of the present invention showing the rodless chamber open to atmosphere;
FIG. 4 is an enlarged fragmentary view of region A of the main ram of the present invention showing the rod chamber open to atmosphere;
fig. 5 is a schematic view showing the internal structure of the auxiliary ram according to the preferred embodiment of the present invention;
figure 6 is a schematic representation of the change in air pressure within each air chamber of the present invention as a function of the bleed air source pressure.
The reference numerals are explained below:
1-a main drive rod; 2-sealing ring; 3-supporting the bushing; 4-a small spring; 5-a nut; 6-inner cylinder; 7-main bearing piston; 8-main actuating cylinder shell; 9-large spring; 10-a sealing ring; 11-adjusting the cushion; 12-a primary rear end cap; 13-a pull rod; 14-a control piston; 15-sealing ring; 16-an adapter sleeve; 17-a sealing ring; 18-an adjustment ring; 19-a sealing ring; 20-blocking the cover; 21-auxiliary driving rod; 22-auxiliary actuating cylinder housing; 23-auxiliary bearing piston; 24-a sealing ring; 25-auxiliary rear end cap; 26-sealing ring.
Detailed Description
In order to make the implementation objects, technical solutions and advantages of the present invention clearer, the technical solutions in the embodiments of the present invention will be described in more detail below with reference to the accompanying drawings in the embodiments of the present invention. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The described embodiments, which are part of the present invention, are not all embodiments, and are intended to be illustrative of the present invention and should not be construed as limiting the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The utility model particularly relates to an adjustable guide vane adjusting and driving mechanism of a gas compressor. The adjustable guide vane adjusting and driving mechanism of the air compressor provided by the utility model adopts air introduced from an air compressor flow passage as a working medium for driving the actuating cylinder. Fig. 1 shows a schematic diagram of an adjustable guide vane adjusting driving mechanism of a compressor used in the present invention, fig. 2 to 4 show schematic diagrams of an internal structure of a main actuator cylinder, fig. 5 shows a schematic diagram of an internal structure of an auxiliary actuator cylinder, and fig. 6 shows a schematic diagram of a relationship between a change in air pressure in each air chamber and a pressure of a bleed air source.
Constitution and principle of adjustable guide vane adjusting and driving mechanism
As shown in fig. 1, the adjustable vane adjusting driving mechanism of the present invention mainly includes a main actuator cylinder 100, an auxiliary actuator cylinder 200, and a connecting pipeline.
The main ram 100 contains A, B, C, D, E with 5 air ports and R, S, T, W with 4 air chambers.
The internal structure of the auxiliary ram 200 is different from the internal structure of the main ram and includes F, G, H, J with 4 air ports, two air chambers: air cavity M and air cavity N.
The source of the external pipeline is connected to the casing of the compressor and introduces high-pressure air in the flow channel of the compressor. The high-pressure air introduced through the pipeline is divided into three paths:
(a) the first path is connected to the air interface A of the main actuating cylinder and provides high-pressure air for the air cavity W;
(b) the second path is connected to an air interface F of the auxiliary actuating cylinder and provides high-pressure air for the air cavity M;
(c) the third path is connected to the air interface H of the auxiliary actuating cylinder to provide high-pressure air for the air cavity N.
In order to make the main actuating cylinder and auxiliary actuating cylinder retain their coordination, two pipelines are additionally provided to make the air pressures in front and rear air cavities of main force-bearing piston in the main actuating cylinder and in front and rear air cavities of auxiliary force-bearing piston in the auxiliary actuating cylinder retain identical. Namely:
(a) connecting a gas interface E of the main actuating cylinder with a gas interface J of the auxiliary actuating cylinder by adopting a pipeline so as to ensure that the pressure of a gas cavity S in the main actuating cylinder is equal to the pressure of a gas cavity M in the auxiliary actuating cylinder;
(b) a pipeline is adopted to connect the gas interface C of the main actuating cylinder with the gas interface G of the auxiliary actuating cylinder, so that the pressure of the gas cavity R in the main actuating cylinder is equal to the pressure of the gas cavity N in the auxiliary actuating cylinder.
In addition, the air interface B of the main actuating cylinder is connected with the air cavity T, and the air interface B is open in the design state, so that the air pressure in the air cavity T is ensured to be constant environmental air pressure, and the air pressure in the air cavity T can be changed through the air interface B under necessary conditions. The air interface D needs to be blocked in the working state, and can be connected with external air pressure under the necessary condition.
Internal structure of main actuating cylinder
The internal structure of the primary ram 100 is shown in fig. 2-4. The main actuating cylinder 100 comprises a main driving rod 1, a main actuating cylinder shell 8, an inner cylinder 6, a main bearing piston 7, a main rear end cover 12, a supporting bush 3, a pull rod 13 and a control piston 14, wherein,
the inner cylinder 6 is arranged in the main actuating cylinder shell 8, the inner cylinder 6 is a cylindrical cylinder with openings at two ends, a flange mounting edge is formed at the rear end of the cylindrical cylinder, and the flange mounting edge is fixedly connected with a flange at the rear end of the main actuating cylinder shell 8 through a connecting piece;
the main bearing piston 7 is arranged in the main actuating cylinder shell 8, the main bearing piston 7 comprises a cylindrical main body part and a rod-shaped extension part formed at the front end of the cylindrical main body part, the inner diameter of the cylindrical main body part of the main bearing piston 7 is matched with the outer diameter of the cylindrical cylinder of the inner cylinder 6, and the cylindrical main body part of the main bearing piston 7 can be tightly attached to the outer wall of the inner cylinder 6 to move back and forth; an annular flange part is formed at the rear end of the cylindrical main body part, and the outer diameter of the annular flange part is matched with the inner diameter of the main actuator cylinder shell 8, so that the annular flange part can be attached to the inner wall of the main actuator cylinder shell 8 to move back and forth; the rod-shaped extension part is of a hollow structure, the inner cavity of the rod-shaped extension part is communicated with the inner cavity of the cylindrical main body part, and the outer diameter of the rod-shaped extension part is matched with the aperture of the central hole in the front end of the main actuator cylinder shell 8, so that the rod-shaped extension part can move back and forth along the central hole in the front end of the main actuator cylinder shell 8; the main driving rod 1 is fixedly arranged at the front end of the rod-shaped extension part, and the main driving rod 1 is connected with a linkage ring of an adjustable guide vane of the gas compressor; the front end of the inner cavity of the cylindrical main body part is fixedly provided with a plug cover 20 with a central hole through a connecting piece;
the main rear end cap 12 includes a plate-shaped cap body and a cylindrical extension portion formed on a front end surface of the plate-shaped cap body, the plate-shaped cover body is fixedly arranged at the rear end of the inner cylinder 6 through a connecting piece, the cylindrical extension part is arranged in the inner cavity of the inner cylinder 6, and the front end of the cylindrical extension part is coaxially provided with an adapter sleeve 16, the adapter sleeve 16 comprises a front large-diameter section and a rear small-diameter section, a step part is formed between the front end large diameter section and the rear end small diameter section, the rear end small diameter section of the adapter sleeve 16 is matched with the inner diameter of the cylindrical extension part of the main rear end cover 12 and is inserted at the front end of the cylindrical extension part, the outer diameter of the front large-diameter section of the adapter sleeve 16 is matched with the inner diameter of the inner cylinder 6, the adapter sleeve 16 can move back and forth along the axial direction under the double restraint of the cylindrical extension and the inner cylinder 6;
the control piston 14 is arranged in the cylindrical extension part of the main rear end cover 12 in a back and forth sliding way, an annular bulge is arranged on the inner wall of the inner cylinder 6 near the front end, a large spring 9 is arranged between the annular bulge and the step part of the adapter sleeve 16, the support bush 3 is fixedly arranged at the front side of the annular bulge through a connecting piece arranged at the front end of the inner cylinder 6, and a small spring 4 is arranged between the control piston 14 and the support bush 3;
the rear end of the pull rod 13 is fixedly connected with the control piston 14, the main body part of the pull rod 13 penetrates through the support bushing 3, a diameter reducing part is formed at the front end of the pull rod 13 and penetrates through a central hole of the plug cover 20 in the main bearing piston 7, then a locking nut is fixedly arranged, the outer diameter of the diameter reducing part at the front end of the pull rod 13 is smaller than the aperture of the central hole of the plug cover 20 in the main bearing piston 7, and a gap is formed between the diameter reducing part and the central hole;
the main ram 100 has R, S, T, W formed therein for a total of 4 air chambers, wherein,
the air cavity R and the air cavity S are respectively positioned at two sides of the main force bearing piston 7, the space between the outer wall of the main force bearing piston 7 and the inner wall of the main actuating cylinder shell 8 forms the air cavity R, and the space enclosed between the inner wall of the main force bearing piston 7 and the inner wall of the main actuating cylinder shell 8, the outer wall of the inner cylinder 6, the blanking cover 20 and the support bush 3 forms the air cavity S; the air cavity T and the air cavity W are respectively positioned at two sides of the control piston 14, the air cavity T is formed by the space enclosed among the control piston 14, the inner cylinder 6, the cylindrical extension part of the main rear end cover 12, the adapter sleeve 16 and the support bush 3, and the air cavity W is formed by the space enclosed among the plate-shaped cover bodies of the control piston 14 and the main rear end cover 12;
a, B, C, D, E gas interfaces are arranged on the main actuating cylinder 100, the plate-shaped cover body of the main rear end cover 12 is provided with a gas interface A communicated with the gas cavity W, the annular end cover of the inner cylinder 6 is provided with a gas interface B communicated with the gas cavity T, the wall surface of the actuating cylinder shell 8 is respectively provided with a gas interface C, D communicated with the gas cavity R, and the annular end cover of the inner cylinder 6 is provided with a gas interface E communicated with the gas cavity S;
the driving rod 1 is connected with a linkage ring of an adjustable guide vane of the gas compressor. The stroke of the main driving rod 1 determines the rotation of the linkage ring, so that the adjustable guide vanes of the gas compressor of the relevant level are driven to rotate in an angle mode. The main driving rod 1 and the main bearing piston 7 are connected together and move synchronously.
The air cavity R and the air in the air cavity S jointly act to control the movement of the main bearing piston 7. The cavity between the main bearing piston 7 and the main actuating cylinder shell 8 together forms an air cavity R in the figure 1, and the sealing ring 2 and the sealing ring 10 together ensure the sealing performance of the air cavity R. The other side of the main bearing piston 7 is an air cavity S which is mainly enclosed by the main bearing piston 7, the blanking cover 20, the actuating cylinder shell 8, the inner cylinder 6 and the support bush 3; and meanwhile, the sealing rings 10, 17 and 19 jointly ensure the sealing performance of the air cavity S.
The air cavity T and the air cavity W are respectively positioned at two sides of the control piston 14, and the air cavity T mainly comprises an inner cylinder 6, a main rear end cover 12, the control piston 14 and a support bushing 3. The sealing rings 15,17,19 together ensure the tightness of the air chamber T. The adapter sleeve 16 in the air cavity T is in large clearance fit with the sleeves of the inner cylinder 6 and the end cover 12, and the internal air pressure distribution is not influenced. Air chamber W is formed by end cap 12 and control piston 14.
Under the non-working state, the air pressures in the air cavity W, the air cavity T, the air cavity S and the air cavity R are all the ambient air pressures, and the control piston 14 stops at the leftmost side under the action of the pre-pressure force of the small spring 4. The magnitude of the pre-pressure of the small spring can be adjusted by grinding the thicknesses of the adjusting pad 11 and the adjusting ring 18. The pull rod 13 connects the blanking cap 20 and the control piston 14 together; the screw on the blanking cover 20 connects the blanking cover 20 and the main bearing piston 7 together. Therefore, in the non-working state, the main bearing piston 7 is stopped at the leftmost side along with the control piston 14. A small gap Y is ensured to exist between the end cover 20 and the boss on the pull rod 13 in a non-working state by grinding the left side surface B of the blanking cover 20. Through the small gap Y, the central vent hole at the right end of the pull rod 13 and the central vent hole on the driving rod 1, the air cavity S can be ensured to be communicated with the atmosphere when the small gap Y is opened.
When the air pressure in the air chamber W rises enough to overcome the pre-pressure of the small spring 4, the control piston 14 starts to move rightwards, when the moving distance reaches the value of the gap Y, the gap Y is blocked, the air chamber S is no longer communicated with the atmosphere, and the air pressure in the air chamber S starts to be determined by the air pressure of the air introduced by the air interface E. As the air pressure in the air chamber W further rises, the control piston 14 continues to move rightward. When the control piston 14 is moved to a position where it presses against the adapter sleeve 16, the large spring 9 starts to be compressed.
Internal structure of auxiliary actuating cylinder
The internal structure of the auxiliary actuator cylinder is simpler than that of the main actuator cylinder. As shown in fig. 5, the auxiliary ram 200 includes a drive rod 21, an auxiliary ram housing 22, an auxiliary force-bearing piston 23, and an auxiliary rear end cap 25, wherein,
the auxiliary actuator cylinder housing 22 is a cylindrical housing member with an open rear end and a closed front end, an annular connecting flange is formed at the rear end of the auxiliary actuator cylinder housing 22, a central through hole is formed at the front end surface of the auxiliary actuator cylinder housing 22,
the auxiliary rear end cap 25 includes a plate-shaped cap body and a cylindrical extension portion formed on a front end surface of the plate-shaped cap body, the plate-shaped cap body is fixedly disposed on the rear end connecting flange of the auxiliary actuator cylinder housing 22 through a connecting member, the cylindrical extension portion is coaxially sleeved in the auxiliary actuator cylinder housing 22,
the auxiliary force bearing piston 23 is coaxially sleeved in the auxiliary actuating cylinder shell 22, the auxiliary force bearing piston 23 comprises a cylindrical main body part and a rod-shaped extension part formed at the front end of the cylindrical main body part, the inner diameter of the cylindrical main body part of the auxiliary force bearing piston 23 is matched with the outer diameter of the columnar extension part of the auxiliary rear end cover 25, and the cylindrical main body part of the auxiliary force bearing piston 23 can tightly cling to the outer wall of the columnar extension part of the auxiliary rear end cover 25 to move back and forth; an annular flange part is formed at the rear end of the cylindrical main body part of the auxiliary bearing piston 23, and the outer diameter of the annular flange part is matched with the inner diameter of the auxiliary actuating cylinder shell 22, so that the annular flange part can be attached to the inner wall of the auxiliary actuating cylinder shell 22 to move back and forth; the outer diameter of the rod-like extension part is matched with the aperture of the central through hole at the front end of the auxiliary actuating cylinder shell 22, so that the rod-like extension part can move back and forth along the central through hole at the front end of the actuating cylinder shell; the auxiliary driving rod 21 is fixedly arranged at the front end of the rod-shaped extension part, and the auxiliary driving rod 21 is also connected with a linkage ring of an adjustable guide vane of the gas compressor;
m, N air cavities are formed in the auxiliary actuator cylinder 200, wherein the air cavity M and the air cavity N are respectively located at the front side and the rear side of the auxiliary force bearing piston 23, a space between the outer wall of the auxiliary force bearing piston 23 and the inner wall of the auxiliary actuator cylinder shell 22 forms the air cavity N, and a space enclosed by the inner wall of the auxiliary force bearing piston 23, the inner wall of the auxiliary actuator cylinder shell 22 and the auxiliary rear end cover 25 forms the air cavity M;
the auxiliary actuator cylinder 200 is provided with F, G, H, J gas ports, wherein a plate-shaped cover body of the auxiliary rear end cover 25 is provided with a gas port F, J communicated with the gas cavity M, and the wall surface of the auxiliary actuator cylinder shell 22 is provided with a gas port G, H communicated with the gas cavity N.
In general, the auxiliary drive rod 21, auxiliary ram housing 22, auxiliary apply piston 23, seal 24 and seal 26 of the auxiliary ram 200 are similar in function and structure to those of the main ram. The main difference is the secondary rear end cap 25. The auxiliary rear end cap 25 of the auxiliary ram 200 is used only to form the air chamber M; the main actuator cylinder 100 controls the chamber pressure in the air chamber S through the main rear end cap 12, the control piston 14, the small spring 4, the large spring 9, and other structural components.
The auxiliary actuating cylinder 200 is provided with two air cavities M, N, an air cavity M on the left side of the auxiliary bearing piston 23 is composed of an auxiliary rear end cover 25 and the auxiliary bearing piston 23, and the sealing rings 24 at the 3 positions jointly ensure the sealing performance of the air cavities M. The air cavity N on the right side (rear side) of the auxiliary bearing piston 23 is composed of the auxiliary bearing piston 23 and an auxiliary actuating cylinder shell 22, and a sealing ring 26 and a sealing ring 24 at the position 2 are used for ensuring the sealing performance of the air cavity N. The air cavity M is connected with an air source through an air interface F and is connected with the air cavity S of the main actuating cylinder through an air interface J. The air chamber N is connected to an air source through an air port H and to an air chamber R of the main actuator cylinder 100 through an air port G.
Working process of adjustable guide vane adjusting and driving mechanism
When the compressor starts to work, the rotating speed of the compressor is gradually increased, and the air pressure in the flow channel of the compressor is also gradually increased. The adjustable guide vane adjusting and driving mechanism selects which stage of the air compressor to bleed air according to the guide vane adjusting requirement of the air compressor and the internal structure size of the actuating cylinder. The air-entraining position can meet the condition that when the guide vane of the air compressor needs to rotate, an air source provided by the air-entraining position can overcome the pre-pressure of the small spring 4 of the main actuating cylinder and the moving resistance of the control piston 14.
According to the schematic diagram shown in fig. 1, a high-pressure gas source led out from a casing of a compressor is respectively injected into a gas cavity M and a gas cavity N through a gas interface F and a gas interface H of an auxiliary actuating cylinder. Orifices are arranged in the gas interface F and the gas interface H, and the air pressure of a rod cavity (an air cavity N and an air cavity R) and a rodless cavity (the air cavity S and the air cavity M) of the actuating cylinder can be adjusted by adjusting the size of the orifices. Through the communication of the pipes, the cavity pressures of the rod cavity and the rodless cavity of the main actuating cylinder 100 and the auxiliary actuating cylinder 200 can be respectively synchronized. In addition, a high-pressure air source led out from the compressor casing is connected to the air cavity W of the main ram 100 through a pipe.
The working process of the adjustable guide vane adjusting driving mechanism is shown in fig. 6, and the specific stages are described as follows:
first stage (rodless chamber deflation): after the compressor is started, the pressure in the rod cavities (air cavities N and R) of the auxiliary actuating cylinder and the main actuating cylinder is gradually increased along with the increase of the working rotating speed of the compressor, and the pressure in the rodless cavities (air cavities M and S) is basically not established because the rodless cavities are communicated with the outside atmosphere due to the existence of the initial gap Y. At the moment, the force bearing pistons of the two actuating cylinders stop at the leftmost side under the action of pressure difference of a rod cavity (air cavity N, air cavity R) and a rodless cavity (air cavity S and air cavity M), and the displacement of the driving rod is zero.
Second phase (gap Y closed, gap X open): the working speed of the compressor is continuously increased, and the pressure of an air source led out from a casing of the compressor is also continuously increased. The pressure in the air chamber W of the main actuator rises to a threshold value, causing the air pressure P on the left side of the control piston 14W cavity×A1Beyond the rightThe resultant force of (a). This resultant force comprises the pre-stress F of the small spring 4PrepressingPressure P of gas in the chamber TT-shaped cavity×A2And the resistance F to movement of the control piston 14Friction of. Where A is1And A2Respectively, the air pressure bearing areas in the chamber W and the chamber T acting on the control piston 14. Is formulated as follows:
Pw cavity-critical×A1≥FPrepressing+FFriction of+PT-shaped cavity×A2… … … … … … … … formula (1)
Following the pressure P of the air chamber WW cavityFurther increase in control piston 14 moves right until gap Y closes and gap X opens. The rodless chambers (chambers S and M) of the ram begin to build pressure and the rod chambers (chambers R and N) are in communication with the outside atmosphere. Theoretically, the existence of the gap Y is a switch device for controlling the cavity pressure of the rodless cavity of the bearing piston, so the arrangement of the gap Y is not suitable to be overlarge. The adjustment of the closing point of time of the gap Y can be fine-tuned by thinning the thickness of the adjusting pad 11 and adjusting ring 18 in the main actuator cylinder. In special cases it is also possible to supply the chamber T with a closing time point of the air pressure change gap Y.
Third stage (force bearing piston extension): after the gap Y is closed, the pressure of the rodless cavities (cavity S and cavity M) continues to increase with the compressor case bleed air pressure. When the gap Y is closed, the gap X is naturally opened, and the rod cavities (cavity R and cavity N) are decompressed to the external atmospheric environment through the vent hole V and the vent hole U. Is formulated as follows, where Δ PThrottle hole FThe pressure loss due to the orifices in the gas connection H and the gas connection F.
PN cavity＝PR cavity＝PAtmosphere (es)… … … … … … … … … … … … formula (2)
PM cavity＝PS cavity＝PAir entraining agent-ΔPThrottle F… … … … … … … … formula (3)
For the auxiliary actuator, the condition for the force-bearing piston 23 to start moving is as follows:
Pm cavity×A3＞PN cavity×A4+FFriction of+FDrive the… … … … … … … … formula (4)
Wherein A is3And A4The air pressure bearing areas of the air cavity M and the air cavity N acting on the bearing piston 23 are respectively. FFriction ofThe friction force which needs to be overcome for the movement of the force bearing piston. FDrive theThe reaction force fed back to the driving rod 21 by the compressor adjustable mechanism comprises the friction force of the linkage mechanism, the pneumatic resistance on the compressor guide vane and the like. The reaction force in the adjusting process of the gas turbine compressor guide vane is shared by the driving rod of the main actuating cylinder and the auxiliary actuating cylinder. Where FFriction ofAnd FDrive theAre all determined by objective conditions, A3And A4Are not changeable after the ram configuration is determined. The fine adjustment of this stage is therefore effected primarily by adjusting the size of the orifice in the gas connection F, so that Δ P is changedThrottle hole F。
The movement conditions of the force bearing piston 7 for the main actuator are similar to the force bearing piston 23 in the auxiliary actuator. The difference is that the control piston 14 in the main actuating cylinder also has a pushing effect on the force bearing piston 7. However, under the counteracting action of the elasticity of the small spring 4 and the stress balance condition of the force bearing piston, the pushing force of the control piston 14 to the force bearing piston 7 is smaller.
Under the pressure action of the rodless cavity, the force bearing piston can move to the maximum stroke position of the force bearing piston after meeting the cavity pressure condition formula (4) theoretically. In fact, once the displacement of the force-bearing piston 7 is greater than that of the control piston 14, the gap Y is opened, the rodless chamber is deflated, and the force-bearing piston returns to the position corresponding to the displacement of the control piston again under the action of the chamber pressure of the rod chamber. It can be seen that the displacement of the driving rod is consistent with that of the bearing piston, and the displacement of the bearing piston needs to be consistent with that of the control piston. The force condition of the control piston 14 becomes formula (5) after the gap Y is closed. Wherein FSpringThe spring force of the small spring 4 and the large spring 9 on the control piston 14, FForce bearing pistonThe force of the force bearing piston 7 on the control piston 14 through the pull rod 13.
PW cavity×A1＞FPrepressing+FFriction of+PT-shaped cavity×A2+FSpring+FForce bearing piston… … … formula (5)
Because FForce bearing pistonIt is not easy to calculate, so there is formula (6) for the whole of the control piston and the force bearing piston in the main actuating cylinder as the force bearing analysis object.
PW cavity×A1+PS cavity×A3＞FPrepressing+FSpring+PT-shaped cavity×A2+PR cavity×A4+FFriction of+FDrive the… … formula (6)
The main ram moves following equation (6) until the load reaches the maximum stroke of the force piston.
Two springs, a small spring 4 and a large spring 9, are used here in order to meet the requirements of the gas turbine for FSpringAnd the force bearing piston displacement. The angle change rate of the guide vane of the gas compressor is smoother under the high state of the gas turbine.
Fourth stage (force-bearing piston return): when the air compressor is ready to stop from a high state, the rotating speed is gradually reduced, and the air pressure of air introduced from a casing of the air compressor is gradually reduced. The pressure in the chamber W of the primary ram also decreases and the control piston 14 starts to move to the left under the influence of the spring force, thereby opening the gap Y and closing the gap X. After the gap Y is opened, the rodless cavities (the cavity M and the cavity S) are communicated with the atmosphere, and the cavity pressure is reduced; and after the gap X is closed, the rod cavity (cavity N and cavity R) is communicated with the bleed air at the outlet of the compressor, and cavity pressure is gradually built up. After the pressure of the rodless cavity is reduced, under the action of the cavity pressure of the rod cavity (cavity N and cavity R), the force bearing pistons of the two actuating cylinders drive the driving rod to move leftwards. The correspondence between the air pressure level of the chamber W and the spring force is as in equation (7). Wherein FSmall springAnd FBig springIs the spring force of the spring on the control piston 14, the magnitude of the spring force depending on the displacement d of the control piston, i.e. equation (8), where k is the spring constant of the spring, L0Is the amount of precompression for the spring. After the adapter sleeve 16 is restored to the initial position, the elastic force F of the large springBig springInitially equal to zero.
PW cavity×A1+FFriction of＝FSmall spring+FBig spring+PT-shaped cavity×A2… … … … formula (7)
FSpring＝k·(L0+ d) … … … … … … formula (8)
As the pressure of the chamber W is continuously reduced, the force-bearing piston moves to the leftmost position, i.e., stops moving after contacting the C-surface of the inside cylinder 6.
From the above analysis, it can be seen that the air pressure of the bleed air of the compressor casing determines the displacement of the control piston and further determines the displacement of the drive rod through the bleed action of the gap X or the gap Y.
The object of the present invention is fully effectively achieved by the above embodiments. It will be appreciated by those skilled in the art that the present invention includes, but is not limited to, those illustrated in the accompanying drawings and described in the foregoing detailed description. While the utility model has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the utility model is not to be limited to the disclosed embodiment, but on the contrary, is intended to cover various modifications within the spirit and scope of the appended claims.
Claims (10)
1. A compressor guide vane adjusting and driving mechanism at least comprises a main actuating cylinder and an auxiliary actuating cylinder, and is characterized in that,
the main actuating cylinder at least comprises a main driving rod, a main actuating cylinder shell, an inner cylinder, a main bearing piston, a main rear end cover, a supporting bushing, a pull rod and a control piston, wherein,
the inner cylinder is arranged in the main actuating cylinder shell, the inner cylinder is a cylindrical cylinder with openings at two ends, a flange mounting edge is formed at the rear end of the cylindrical cylinder, and the flange mounting edge is fixedly connected with a connecting flange at the rear end of the main actuating cylinder shell;
the main bearing piston is arranged in the main actuating cylinder shell and comprises a cylindrical main body part and a hollow rod-shaped extension part formed at the front end of the cylindrical main body part; an annular flange part is formed at the rear end of the cylindrical main body part and can move back and forth along the inner wall of the main actuating cylinder shell; the inner cavity of the rod-shaped extension part is communicated with the inner cavity of the cylindrical main body part, and the rod-shaped extension part can move back and forth along the central hole at the front end of the actuating cylinder shell; the main driving rod is fixedly arranged at the front end of the rod-shaped extension part and is connected with a linkage ring of an adjustable guide vane of the gas compressor; a plug cover with a central hole is fixedly arranged at the front end of the inner cavity of the cylindrical main body part;
the main rear end cover comprises a plate-shaped cover body and a cylindrical extending portion formed on the front end face of the plate-shaped cover body, the plate-shaped cover body is fixedly arranged at the rear end of the inner cylinder through a connecting piece, the cylindrical extending portion is coaxially sleeved in the inner cavity of the inner cylinder, a switching sleeve is coaxially arranged at the front end of the cylindrical extending portion, the switching sleeve comprises a front-end large-diameter section and a rear-end small-diameter section, a step portion is formed between the front-end large-diameter section and the rear-end small-diameter section, the rear-end small-diameter section of the switching sleeve is inserted at the front end of the cylindrical extending portion, and the switching sleeve can move back and forth along the axial direction under the dual restraint of the cylindrical extending portion and the inner cylinder;
the control piston is arranged in the cylindrical extension part of the main rear end cover in a front-back sliding manner, an annular bulge is arranged on the inner wall of the inner cylinder close to the front end, a large spring is arranged between the annular bulge and the step part of the adapter sleeve, the support bushing is fixedly arranged on the front side of the annular bulge through a connecting piece arranged at the front end of the inner cylinder, and a small spring is arranged between the control piston and the support bushing;
the rear end of the pull rod is fixedly connected with the control piston, the main body part of the pull rod penetrates through the support bushing, a diameter reducing part is formed at the front end of the pull rod and penetrates through a central hole of a plug cover in the force bearing piston, a locking nut is fixedly arranged on the pull rod, the outer diameter of the diameter reducing part at the front end of the pull rod is smaller than the aperture of the central hole of the plug cover in the force bearing piston, and a gap is formed between the diameter reducing part and the central hole;
the main actuating cylinder forms R, S, T, W air chambers with 4 air chambers in total, wherein,
the air cavity R and the air cavity S are respectively positioned at two sides of the main force bearing piston, the space between the outer wall of the main force bearing piston and the inner wall of the main actuating cylinder shell forms the air cavity R, and the space enclosed by the inner wall of the main force bearing piston, the inner wall of the main actuating cylinder shell, the outer wall of the inner cylinder, the blanking cover and the support bushing forms the air cavity S; the air cavity T and the air cavity W are respectively positioned at two sides of the control piston, the air cavity T is formed by the space enclosed among the control piston, the inner cylinder, the cylindrical extension part of the main rear end cover, the adapter sleeve and the support bushing, and the space enclosed between the brake piston and the plate-shaped cover body of the main rear end cover is formed into the air cavity W;
a, B, C, D, E gas interfaces are arranged on the main actuating cylinder, a plate-shaped cover body of the main rear end cover is provided with a gas interface A communicated with the gas cavity W, an annular end cover of the inner cylinder is provided with a gas interface B communicated with the gas cavity T, the wall surface of the actuating cylinder shell is respectively provided with a gas interface C, D communicated with the gas cavity R, and the annular end cover of the inner cylinder is provided with a gas interface E communicated with the gas cavity S;
the auxiliary actuating cylinder at least comprises an auxiliary driving rod, an auxiliary actuating cylinder shell, an auxiliary bearing piston and an auxiliary rear end cover, wherein,
the auxiliary actuating cylinder shell is integrally a cylindrical shell part with an opening at the rear end and a closed front end, an annular connecting flange is formed at the rear end of the auxiliary actuating cylinder shell, a central through hole is formed on the front end surface of the auxiliary actuating cylinder shell,
the auxiliary rear end cover comprises a plate-shaped cover body and a columnar extension part formed on the front end surface of the plate-shaped cover body, the plate-shaped cover body is fixedly arranged on a rear end connecting flange of the auxiliary actuating cylinder shell, the columnar extension part is coaxially sleeved in the auxiliary actuating cylinder shell,
the auxiliary force bearing piston is coaxially sleeved in the auxiliary actuating cylinder shell and comprises a cylindrical main body part and a rod-shaped extension part formed at the front end of the cylindrical main body part, and the cylindrical main body part of the auxiliary force bearing piston can move back and forth along the outer wall of the cylindrical extension part of the auxiliary rear end cover; an annular flange part is formed at the rear end of the cylindrical main body part of the auxiliary bearing piston and can move back and forth along the inner wall of the auxiliary actuating cylinder shell; the rod-shaped extension part can move back and forth along the central through hole at the front end of the auxiliary actuating cylinder shell; the auxiliary driving rod is fixedly arranged at the front end of the rod-shaped extension part and is also connected with a linkage ring of an adjustable guide vane of the gas compressor;
m, N air cavities are formed in the auxiliary actuating cylinder, wherein the air cavity M and the air cavity N are respectively positioned at the front side and the rear side of the auxiliary bearing piston, the space between the outer wall of the auxiliary bearing piston and the inner wall of the auxiliary actuating cylinder shell is formed into the air cavity N, and the space enclosed by the inner wall of the auxiliary bearing piston, the inner wall of the auxiliary actuating cylinder shell and the auxiliary rear end cover is formed into the air cavity M;
the auxiliary actuating cylinder is provided with F, G, H, J gas interfaces with 4, wherein a plate-shaped cover body of the auxiliary rear end cover is provided with a gas interface F, J communicated with the gas cavity M, and the wall surface of the shell of the auxiliary actuating cylinder is respectively provided with a gas interface G, H communicated with the gas cavity N;
-leading out a high-pressure gas source from a compressor casing, introducing high-pressure air in a compressor flow channel, wherein the high-pressure gas source is respectively communicated with a gas interface A of the main actuating cylinder, a gas interface F of the auxiliary actuating cylinder and a gas interface H of the auxiliary actuating cylinder through pipelines; the gas interface E of the main actuating cylinder is connected with the gas interface J of the auxiliary actuating cylinder through a pipeline; the gas interface C of the main actuating cylinder is connected with the gas interface G of the auxiliary actuating cylinder through a pipeline; the gas interface B of the main actuating cylinder is communicated with the atmospheric environment in a design state; and a gas interface D of the main actuating cylinder is in a closed state in a working state.
2. The compressor guide vane adjustment drive mechanism as claimed in claim 1, characterized in that an adjustment ring is arranged between the support bushing in the main cylinder and the annular projection in the inner cylinder, an adjustment pad is arranged between the small spring and the control piston, and the pre-pressure of the small spring is changed by adjusting the thickness of the adjustment ring and/or the adjustment pad.
3. The compressor guide vane adjustment driving mechanism as claimed in claim 1, wherein the main driving rod is fixedly connected with the main bearing piston, and the main driving rod and the main bearing piston move synchronously; the auxiliary driving rod is fixedly connected with the auxiliary bearing piston, and the auxiliary driving rod and the auxiliary bearing piston move synchronously.
4. The compressor guide vane adjusting and driving mechanism as claimed in claim 1, wherein a sealing ring is disposed between the annular flange of the cylindrical main body of the main force bearing piston and the inner wall of the main actuating cylinder housing, a sealing ring is disposed between the rod-like extension of the main force bearing piston and the central hole of the front end of the main actuating cylinder housing, a sealing ring is disposed between the annular protrusion in the inner cylinder and the support bushing, a sealing ring is disposed between the center rod of the control piston and the support bushing, a sealing ring is disposed between the annular end cover of the rear end of the inner cylinder and the connecting flange of the rear end of the main actuating cylinder housing, and a sealing ring is disposed between the main rear end cover and the rear end of the inner cylinder.
5. The compressor vane adjustment drive mechanism of claim 1, wherein the rear small diameter section of the adapter sleeve and the cylindrical extension of the main rear end cap, and the front large diameter section of the adapter sleeve and the inner cylinder are in large clearance fit.
6. The compressor vane adjustment drive mechanism as claimed in claim 1, characterized in that in the non-operating state, the air pressure in the air chamber W, T, S, R is ambient air pressure, the control piston stops at the rearmost end under the pre-pressure of a small spring, and the force bearing piston stops at the rearmost end together with the control piston.
7. The compressor guide vane adjusting and driving mechanism as claimed in claim 1, wherein the pull rod limits the step part of the control piston in axial movement, a gap Y is provided between the rear side surface B of the plug in the main force bearing piston and the step part of the pull rod, and the air chamber S is communicated with the atmosphere through the gap Y, the gap between the diameter reduction part of the pull rod and the central hole of the plug of the main force bearing piston, and the gap between the rod-shaped extension part of the main force bearing piston and the main driving rod.
8. The compressor vane adjustment drive according to claim 7, characterized in that the control piston starts to move forward when the air pressure in the air chamber W rises sufficiently to overcome the pre-pressure of the small spring, and when the movement distance reaches the value of the gap Y, the gap Y is blocked, the air chamber S is no longer open to the atmosphere, and the air pressure in the air chamber S starts to be determined by the air pressure of the air introduced by the air connection E.
9. The compressor vane adjustment drive mechanism of claim 8, wherein the control piston continues to move forward as the air pressure in the air cavity W further increases, the large spring begins to be compressed when the control piston moves to a position to compress the adapter sleeve.
10. The compressor guide vane adjusting and driving mechanism as claimed in claim 1, wherein sealing rings are disposed between the plate-shaped cover body of the auxiliary rear end cover and the connecting flange at the rear end of the auxiliary actuating cylinder housing, between the annular flange portion at the rear end of the cylindrical main body portion of the auxiliary force bearing piston and the auxiliary actuating cylinder housing, and between the rod-shaped extension portion of the auxiliary force bearing piston and the central through hole at the front end of the actuating cylinder housing.
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