阅读说明：本技术 一种trt间隙调节方法 (TRT clearance adjusting method ) 是由 陈一峰 戴军 李锋辉 于 2021-04-30 设计创作，主要内容包括：本发明的一种TRT间隙调节方法,检测透平动叶和机组承缸之间的实时动静间隙值,将实时动静间隙值与预设动静间隙值进行对比,获取实时动静间隙值与预设动静间隙值的动静间隙实际差异值,判断所述动静间隙实际差异值是否大于预设差异值,若是,则推动TRT转子朝靠近或远离机组承钢的方向位移以减小所述动静间隙实际差异值,使所述动静间隙实际差异值小于所述预设差异值。本发明的一种TRT间隙调节方法,能够实时对透平动叶和机组承缸之间的动静间隙值进行调节,减少机组相邻两级之间的漏气损失,使机组达到更高的效率和功率,带来更大的经济效益。(The invention discloses a TRT (blast furnace Top gas recovery turbine) clearance adjusting method, which comprises the steps of detecting a real-time dynamic and static clearance value between a turbine movable blade and a unit bearing cylinder, comparing the real-time dynamic and static clearance value with a preset dynamic and static clearance value, obtaining a dynamic and static clearance actual difference value between the real-time dynamic and static clearance value and the preset dynamic and static clearance value, judging whether the dynamic and static clearance actual difference value is larger than the preset difference value, if so, pushing a TRT rotor to move towards a direction close to or far away from a unit bearing steel so as to reduce the dynamic and static clearance actual difference value, and enabling the dynamic and static clearance actual difference value to be smaller than the preset difference value. According to the TRT clearance adjusting method, the dynamic and static clearance values between the turbine movable blade and the unit bearing cylinder can be adjusted in real time, the air leakage loss between two adjacent stages of the unit is reduced, the unit achieves higher efficiency and power, and greater economic benefits are brought.)

1. A TRT clearance adjusting method is characterized by comprising the following steps: detect real-time sound clearance value between turbine movable blade and the unit holds the jar, contrast real-time sound clearance value with predetermineeing sound clearance value, acquire real-time sound clearance value and predetermine the sound clearance actual difference value of sound clearance value, judge whether sound clearance actual difference value is greater than predetermineeing the difference value, if, then promote the TRT rotor towards the direction displacement that is close to or keeps away from the unit and holds the steel in order to reduce sound clearance actual difference value makes sound clearance actual difference value is less than predetermineeing the difference value.

2. The TRT clearance adjusting method according to claim 1, wherein if the actual difference value of the dynamic and static clearances is less than or equal to the preset difference value, the real-time dynamic and static clearance value between the movable turbine blade and the bearing cylinder of the unit is continuously detected until the actual difference value of the dynamic and static clearances is greater than the preset difference value.

3. The TRT clearance adjusting method according to claim 1, wherein the detecting of the real-time dynamic and static clearance value between the turbine movable blade and the unit bearing cylinder comprises the following steps: and detecting a real-time dynamic and static clearance value between the turbine movable blade and the unit bearing cylinder through a radial displacement sensor arranged on the unit bearing cylinder.

4. The TRT gap adjusting method according to claim 1, wherein when determining whether the actual difference value between the dynamic gap and the static gap is greater than a preset difference value, the TRT gap adjusting method further comprises: judging whether the actual difference value of the dynamic and static gaps is a non-negative value or not, if so, pushing the TRT rotor to displace towards the direction close to the bearing steel of the unit until the actual difference value of the dynamic and static gaps is a preset difference value; if not, the TRT rotor is pushed to move towards the direction away from the bearing steel of the unit until the actual difference value of the dynamic and static gaps is a preset difference value.

5. The TRT clearance adjustment method according to claim 4, wherein pushing the TRT rotor to displace towards or away from a bearing steel of the unit comprises: two hydraulic pistons are respectively arranged on the working surface of the thrust bearing and the non-working surface opposite to the working surface, and the two hydraulic pistons push the TRT rotor to move towards the direction far away from or close to the bearing steel of the unit through the thrust bearing.

6. The TRT clearance adjustment method according to claim 4 or 5, wherein when the TRT rotor is pushed to displace towards the direction close to or away from the bearing steel of the unit, the TRT clearance adjustment method further comprises the following steps: detecting whether the axial displacement of the TRT rotor exceeds the maximum safe displacement, wherein the maximum safe displacement refers to the maximum displacement of the TRT rotor without dynamic and static rubbing with bearing steel of a unit.

7. The TRT clearance adjustment method according to claim 6, wherein detecting whether the axial displacement of the TRT rotor exceeds the maximum safe displacement amount includes: whether the axial displacement of the TRT rotor exceeds the maximum safe displacement amount is detected by an axial displacement sensor arranged on a displacement path of the TRT rotor.

8. The TRT clearance adjusting method according to claim 1, wherein a real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder meets the following formula:

if the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the unit bearing cylinder is a non-negative value,

if the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the bearing cylinder of the unit is a negative value,

in the above formula, a1 is the initial position of the TRT rotor in the axial direction thereof, a2 is the maximum safe displacement amount of the TRT rotor, and α is the included angle between the axial direction of the TRT rotor and the dynamic and static gaps between the turbine movable blade and the unit bearing cylinder.

9. The TRT clearance adjustment method according to claim 1, wherein a thrust force F that pushes the TRT rotor to displace toward or away from a bearing steel of the unit satisfies the following equation:

if the direction of the thrust F is the direction of pushing the TRT rotor to approach the bearing steel of the unit:

f is not less than Fn + Rj;

if the direction of the thrust F is the direction for pushing the TRT rotor to move away from the bearing steel of the unit:

f is not less than Fn-Rj;

in the above formula, Fn is a static friction force when the TRT rotor is displaced in its axial direction, and Rj is a wind resistance when the TRT rotor is displaced in its axial direction.

10. The TRT clearance adjusting method according to claim 1, wherein if the TRT rotor displaces in a direction away from bearing steel of the unit, a thrust F for pushing the TRT rotor to displace and a real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relation:

B＝|-kF+d|+C；

if the TRT rotor displaces towards the direction close to the bearing steel of the unit, the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relations:

B＝C-|kF+d|；

in the above equation, k and d are a correction coefficient and an empirical constant, respectively.

Technical Field

The invention belongs to the technical field of blast furnace top gas residual pressure recovery turbine power generation devices, and particularly relates to a TRT (blast furnace top gas recovery turbine) gap adjusting method.

Background

The TRT is a blast furnace gas residual pressure recovery turbine power generation device, and the TRT is a device which utilizes the pressure energy and the heat energy of blast furnace top gas to enable the gas to work through a turbine expansion machine to drive a generator to generate power and recover energy.

The TRT rotor is a rigid rotor and consists of movable blades, vane isolating blocks, a main shaft and the like. In the TRT starting process, the rising speed of the temperature of the movable blade is higher than that of the temperature of the cylinder, so that the expansion amount of the movable blade is obviously larger than that of the cylinder, and the phenomenon is more serious when the temperature of the working medium is higher. In order to prevent the friction between the movable blade and the cylinder, the condition of the most severe working condition change must be considered for the design value of the dynamic and static clearance. After the expansion amount of the movable blade reaches the maximum value, the cylinder still continues to expand, so that the dynamic and static gaps are gradually increased, and the TRT efficiency is reduced. Therefore, a certain clearance value is reserved in the design stage, but with the operation of the unit, because the parameter change of the blast furnace gas is severe, the dynamic clearance and the static clearance of the unit are larger than the design value after the unit operates for a short time, and the efficiency of the unit is obviously reduced.

In order to solve the problems, the patent of the invention is provided by CN202011077367.5 filed by patent application No. of patent application, inventor Power engineering Limited company of sending scientific energy, and is named as a multi-stage TRT stator blade inner housing, and the invention mainly adopts the multi-stage structure design to the stator blade inner housing, so that each stage of TRT stator blade has a matched expansion angle; through setting up the first circular arc section and the first-stage quiet leaf spherical surface cooperation of the first-stage section of admitting air, the second circular arc section and the quiet leaf spherical surface cooperation of second grade section of admitting air, and then solved the quiet leaf blade body of TRT and the too big problem in interior casing radial clearance. However, the technical scheme also has the following defects: firstly, the technical scheme adopts a method for matching the second arc section of the air inlet section with the spherical surface of the second-stage stationary blade, which is mainly designed aiming at the structure of the stationary blade and has the problem of processing difficulty; secondly, the technical scheme still can not avoid the problem of dynamic and static rub caused by severe change of blast furnace gas parameters, and the efficiency of the unit is not obviously improved along with the operation of the unit.

Disclosure of Invention

1. Technical problem to be solved by the invention

The invention aims to overcome the defects that the efficiency of a unit is obviously reduced because the ratio of dynamic and static clearances to a designed value is larger after a short time due to dynamic and static rubbing in the running process of the unit in the prior art, and provides a TRT clearance adjusting method.

2. Technical scheme

In order to achieve the purpose, the technical scheme provided by the invention is as follows:

a TRT clearance adjusting method comprises the steps of detecting a real-time dynamic and static clearance value between a turbine movable blade and a unit bearing cylinder, comparing the real-time dynamic and static clearance value with a preset dynamic and static clearance value, obtaining a dynamic and static clearance actual difference value between the real-time dynamic and static clearance value and the preset dynamic and static clearance value, judging whether the dynamic and static clearance actual difference value is larger than the preset difference value, if so, pushing a TRT rotor to move towards a direction close to or far away from unit bearing steel so as to reduce the dynamic and static clearance actual difference value, and enabling the dynamic and static clearance actual difference value to be smaller than the preset difference value.

The preferable technical scheme is as follows:

in the TRT gap adjusting method, if the actual difference value of the dynamic and static gaps is smaller than or equal to the preset difference value, the real-time dynamic and static gap value between the movable turbine blade and the bearing cylinder of the turbine unit is continuously detected until the actual difference value of the dynamic and static gaps is greater than the preset difference value.

According to the TRT clearance adjusting method, detecting the real-time dynamic and static clearance value between the turbine movable blade and the unit bearing cylinder includes: and detecting a real-time dynamic and static clearance value between the turbine movable blade and the unit bearing cylinder through a radial displacement sensor arranged on the unit bearing cylinder.

The TRT gap adjusting method described above, when determining whether the actual difference value between the dynamic gap and the static gap is greater than the preset difference value, further includes: judging whether the actual difference value of the dynamic and static gaps is a non-negative value or not, if so, pushing the TRT rotor to displace towards the direction close to the bearing steel of the unit until the actual difference value of the dynamic and static gaps is a preset difference value; if not, the TRT rotor is pushed to move towards the direction away from the bearing steel of the unit until the actual difference value of the dynamic and static gaps is a preset difference value.

In the TRT clearance adjusting method, the pushing the TRT rotor to displace towards the direction close to or away from the bearing steel of the unit includes: two hydraulic pistons are respectively arranged on the working surface of the thrust bearing and the non-working surface opposite to the working surface, and the two hydraulic pistons push the TRT rotor to move towards the direction far away from or close to the bearing steel of the unit through the thrust bearing.

When the TRT rotor is pushed to displace towards a direction close to or away from the bearing steel of the unit, the TRT clearance adjusting method further includes: detecting whether the axial displacement of the TRT rotor exceeds the maximum safe displacement, wherein the maximum safe displacement refers to the maximum displacement of the TRT rotor without dynamic and static rubbing with bearing steel of a unit.

In the TRT clearance adjusting method as described above, the detecting whether the axial displacement of the TRT rotor exceeds the maximum safe displacement amount includes: whether the axial displacement of the TRT rotor exceeds the maximum safe displacement amount is detected by an axial displacement sensor arranged on a displacement path of the TRT rotor.

According to the TRT clearance adjusting method, the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder meets the following formula:

if the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the unit bearing cylinder is a non-negative value,

then

If the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the bearing cylinder of the unit is a negative value,

in the above formula, a1 is the initial position of the TRT rotor in the axial direction thereof, a2 is the maximum safe displacement amount of the TRT rotor, and α is the included angle between the axial direction of the TRT rotor and the dynamic and static gaps between the turbine movable blade and the unit bearing cylinder.

According to the TRT clearance adjusting method, the thrust force F for pushing the TRT rotor to displace towards the direction close to or far away from the bearing steel of the unit meets the following formula:

if the direction of the thrust F is the direction of pushing the TRT rotor to approach the bearing steel of the unit:

f is not less than Fn + Rj;

if the direction of the thrust F is the direction for pushing the TRT rotor to move away from the bearing steel of the unit:

f is not less than Fn-Rj;

in the above formula, Fn is a static friction force when the TRT rotor is displaced in its axial direction, and Rj is a wind resistance when the TRT rotor is displaced in its axial direction.

According to the TRT clearance adjusting method, if the TRT rotor displaces towards the direction far away from the bearing steel of the unit, the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relation:

B＝|-kF+d|+C；

if the TRT rotor displaces towards the direction close to the bearing steel of the unit, the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relations:

B＝C-|kF+d|；

in the above equation, k and d are a correction coefficient and an empirical constant, respectively.

3. Advantageous effects

Compared with the prior art, the technical scheme provided by the invention has the following beneficial effects:

(1) according to the TRT clearance adjusting method, when the real-time dynamic and static clearance value caused by dynamic and static rubbing is larger than the preset dynamic and static clearance value or the real-time dynamic and static clearance value is smaller than the preset dynamic and static clearance value due to misoperation in the running process of the unit, the TRT rotor is pushed to move towards the direction close to or far away from the steel bearing of the unit so as to reduce the actual difference value of the dynamic and static clearances, and the actual difference value of the dynamic and static clearances is smaller than the preset difference value. The dynamic and static clearance values between the turbine movable blade and the unit bearing cylinder can be adjusted in real time, so that the air leakage loss between two adjacent stages of the unit is reduced, the unit achieves higher efficiency and power, and greater economic benefit is brought;

(2) according to the TRT clearance adjusting method, the range of the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder is limited, so that collision between the turbine movable blade and the unit bearing cylinder caused by excessive adjustment of the real-time dynamic and static clearance value B can be avoided; on the basis, a relation is established between a thrust F for pushing the TRT rotor to displace and a real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder, and further the possibility is provided for automatically controlling the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder by controlling the thrust F of the hydraulic piston or controlling the work of the hydraulic piston.

Drawings

Fig. 1 is a flow chart of a TRT gap adjustment method of the present invention;

FIG. 2 is a schematic view of the arrangement of the apparatus when a TRT gap adjusting method according to the present invention is applied;

100, turbine blades; 200. a unit bearing cylinder; 300. a TRT rotor; 400. a thrust bearing; 500. A hydraulic piston; 600. a hydraulic oil pump; 700. a radial displacement sensor; 800. an axial displacement sensor.

Detailed Description

In order to facilitate an understanding of the invention, the invention will now be described more fully hereinafter with reference to the accompanying drawings, in which several embodiments of the invention are shown, but which may be embodied in many different forms and are not limited to the embodiments described herein, but rather are provided for the purpose of providing a more thorough disclosure of the invention.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present; when an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present; the terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs; the terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention; as used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

In the TRT starting process, the rising speed of the temperature of the turbine movable vane is higher than that of the cylinder bearing cylinder, so that the expansion amount of the movable vane is obviously larger than that of the cylinder, and the phenomenon is more serious when the temperature of the working medium is higher. After the expansion amount of the movable blade reaches the maximum value, the cylinder still continues to expand, so that the dynamic and static gaps are gradually increased, and dynamic and static rubbing occurs between the turbine movable blade and the unit bearing cylinder.

On the other hand, if the TRT unit fails or operates incorrectly, a dynamic and static clearance between the TRT rotor and unit bearing steel may be small, and dynamic and static rubbing is also easily generated between the turbine movable blade and the unit bearing cylinder.

In view of the above problems, the present embodiment provides a TRT clearance adjusting method, as shown in fig. 1, which is mainly used for adjusting a real-time dynamic and static clearance value between the turbine rotor blade 100 and the unit bearing cylinder 200. The method specifically comprises the following steps: detecting a real-time dynamic and static clearance value between the turbine movable blade 100 and the unit bearing cylinder 200, comparing the real-time dynamic and static clearance value with a preset dynamic and static clearance value, acquiring a dynamic and static clearance actual difference value between the real-time dynamic and static clearance value and the preset dynamic and static clearance value, judging whether the dynamic and static clearance actual difference value is greater than the preset difference value, if so, pushing the TRT rotor 300 to displace towards a direction close to or far away from the unit bearing steel so as to reduce the dynamic and static clearance actual difference value, and enabling the dynamic and static clearance actual difference value to be smaller than the preset difference value; if the actual difference value of the dynamic and static gaps is smaller than or equal to the preset difference value, the real-time dynamic and static gap value between the turbine movable blade 100 and the unit bearing cylinder 200 is continuously detected until the actual difference value of the dynamic and static gaps is larger than the preset difference value.

Specifically, as shown in fig. 2, the TRT rotor 300 is a rigid rotor and is composed of turbine rotor blades 100 of different stages, a spacer block, a main shaft, and the like, wherein the main shaft is formed by high alloy steel integral forging and precision machining, the turbine rotor blades 100 are mounted on the main shaft, and the spacer block is mounted between the turbine rotor blades 100 of different stages. When the TRT works, blast furnace gas is led out to do work and is converted into kinetic energy to be applied to the turbine movable blade 100, so that the whole TRT rotor 300 rotates, and the rotor drives the engine to rotate together through the coupler to generate electricity.

When the real-time dynamic and static clearance value caused by dynamic and static rubbing is larger than the preset dynamic and static clearance value in the running process of the unit or the real-time dynamic and static clearance value is smaller than the preset dynamic and static clearance value due to misoperation, the method of the embodiment is adopted, the relative connection relation of the TRT rotor 300 and the turbine movable blade 100 is utilized, and the actual difference value of the dynamic and static clearances is reduced by pushing the TRT rotor 300 to move towards the direction close to or far away from the bearing steel of the unit, so that the actual difference value of the dynamic and static clearances is smaller than the preset difference value. And then can adjust the sound clearance value between turbine movable vane 100 and unit bearing cylinder 200 in real time, reduce the gas leakage loss between the adjacent two-stage of unit, make the unit reach higher efficiency and power, bring bigger economic benefits.

Specifically, detecting real-time dynamic and static clearance values between turbine movable blade 100 and unit bearing cylinder 200 includes: real-time dynamic and static clearance values between the turbine movable blade 100 and the unit bearing cylinder 200 are detected through a radial displacement sensor 700 arranged on the unit bearing cylinder 200.

In the above method, considering that the real-time dynamic and static clearance value between the turbine movable blade 100 and the unit bearing cylinder 200 is mainly detected, the radial displacement sensor 700 may be selected as a linear displacement sensor or a pull rope sensor in terms of the selection of the radial displacement sensor 700. The linear displacement sensor has the advantages of simple structure, good linear precision and stability, compact structure, long measuring stroke, small equipment space standard, high measuring precision, good reliability, long service life and less maintenance. In this embodiment, the radial displacement sensor 700 is a pull-cord sensor of 80M/WEP 70-1500-A1.

For real-time dynamic and static gaps, the dynamic and static gaps are influenced by dynamic and static rubbing, or a unit breaks down or is in misoperation, and the actual difference values of the dynamic and static gaps can be non-negative values or negative values. The direction of thrust on the TRT rotor 300 is also different with corresponding adjustment. In specific implementation, this embodiment is judging whether the actual difference value of dynamic and static gaps is greater than the preset difference value, and further includes: judging whether the actual difference value of the dynamic and static gaps is a non-negative value, if so, pushing the TRT rotor 300 to displace towards the direction close to the bearing steel of the unit until the actual difference value of the dynamic and static gaps is a preset difference value; if not, the TRT rotor 300 is pushed to move towards the direction away from the bearing steel of the unit until the actual difference value of the dynamic and static gaps is the preset difference value.

In the implementation of the above process in specific equipment, a thrust bearing 400 may be first provided, the thrust bearing 400 is fixedly connected to the TRT rotor 300, in the axial direction of the thrust bearing 400, the thrust bearing 400 includes a working surface and a non-working surface opposite to the working surface, two hydraulic pistons 500 are respectively provided on the working surface and the non-working surface of the thrust bearing 400, the two hydraulic pistons 500 are supplied with hydraulic lubricating oil by a hydraulic oil pump 600 to work outwards, the two hydraulic pistons 500 can push the TRT rotor 300 from two opposite directions through the thrust bearing 400, and the thrust directions of the two hydraulic pistons 500 are respectively along an intra-unit counter airflow direction and an intra-unit downwind direction, so that the TRT rotor 300 can be displaced in a direction away from or close to the intra-unit bearing steel, wherein the direction in which the intra-unit counter airflow displaces the TRT rotor 300 is defined as the main pushing direction of the hydraulic pistons 500, the direction in which the TRT rotor 300 is displaced along the airflow in the unit is defined as an auxiliary pushing direction of the hydraulic piston 500, and the main pushing direction and the secondary pushing direction are on the same horizontal line.

Although the above embodiments specifically consider the influence of the radial displacement of the TRT rotor 300 on the dynamic and static clearances between the turbine movable blade 100 and the unit bearing steel when the TRT rotor 300 is displaced, in the specific embodiments, it should be considered that the change of the lateral displacement of the TRT rotor 300 when the TRT rotor 300 is displaced may also cause dynamic and static rubbing between the TRT rotor 300 and the unit bearing steel, and therefore, on the premise of comprehensively considering the comprehensive adjustment of the dynamic and static clearances, it is also required to ensure that the axial displacement of the TRT rotor 300 cannot exceed the maximum displacement amount of the dynamic and static rubbing with the unit bearing steel. On the basis, the TRT gap adjustment method of the present embodiment further includes: when the TRT rotor 300 is pushed to move towards the direction close to or far away from the bearing steel of the unit, whether the axial displacement of the TRT rotor 300 exceeds the maximum safe displacement amount is detected, wherein the maximum safe displacement amount is the maximum displacement amount of the TRT rotor 300 without dynamic and static rubbing with the bearing steel of the unit.

In a specific method of detecting the axial displacement of the TRT rotor 300, detecting whether the axial displacement of the TRT rotor 300 exceeds the maximum safe displacement amount includes: an axial displacement sensor 800 is arranged on the displacement path of the TRT rotor 300, and whether the axial displacement of the TRT rotor 300 exceeds the maximum safe displacement amount is detected by the axial displacement sensor 800.

In the above method, it is considered that the axial displacement of the TRT rotor 300 is mainly detected, and therefore, the axial displacement sensor 800 may be selected from a linear displacement sensor and a pull-cord sensor in the selection of the axial displacement sensor 800. In this embodiment, the radial displacement sensor 700 is a pull-cord sensor of 80M/WEP 70-1500-A1.

By combining the technical scheme, the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder and the axial displacement of the TRT rotor respectively satisfy the following relations:

when the TRT rotor is in displacement, the real-time dynamic and static clearance value B is possibly larger than a preset dynamic and static clearance value C between the turbine movable blade and the unit bearing cylinder and is also possibly smaller than the preset dynamic and static clearance value C between the turbine movable blade and the unit bearing cylinder. Under any condition, the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder is larger than 0 so as to avoid collision between the turbine movable blade and the unit bearing cylinder;

the axial displacement of the TRT rotor should be less than its maximum displacement;

the maximum axial displacement of the TRT rotor is larger than the real-time dynamic and static clearance value between the turbine movable blade and the unit bearing cylinder.

On the basis of the above conception, in this embodiment, the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder satisfies the following formula:

if the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the unit bearing cylinder is a non-negative value,

then

If the actual difference value of the dynamic and static gaps between the real-time dynamic and static gap value B and the preset dynamic and static gap value C between the turbine movable blade and the bearing cylinder of the unit is a negative value,

in the above formula, a1 is the initial position of the TRT rotor in the axial direction thereof, a2 is the maximum safe displacement amount of the TRT rotor, and α is the included angle between the axial direction of the TRT rotor and the dynamic and static gaps between the turbine movable blade and the unit bearing cylinder.

By adopting the real-time dynamic and static clearance value B to satisfy the formula, the collision between the turbine movable blade and the unit bearing cylinder can be avoided when the real-time dynamic and static clearance value B is automatically and dynamically adjusted, and the stability of the whole TRT system is ensured.

Although the above formula establishes a satisfying formula when the real-time dynamic and static clearance value B is dynamically adjusted, the satisfying formula still cannot satisfy the requirement of automatic control adjustment of the real-time dynamic and static clearance value B. Because the real-time dynamic and static clearance value B is influenced by the displacement of the TRT rotor, and the displacement of the TRT rotor is related to the thrust for pushing the TRT rotor to displace towards the direction close to or far away from the bearing steel of the unit, the embodiment further introduces the thrust F for pushing the TRT rotor to displace towards the direction close to or far away from the bearing steel of the unit so as to seek to establish a relationship between the thrust F and the real-time dynamic and static clearance value B.

For the thrust force F for pushing the TRT rotor to displace towards the direction close to or away from the bearing steel of the unit, the TRT rotor receives the friction force of the TRT rotor and the bottom contact surface of the TRT rotor when moving. On the other hand, the forward and reverse of the airflow in the TRT unit can affect the displacement of the TRT rotor. In order to enable the TRT rotor to generate displacement at the thrust force F, in the present embodiment, the thrust force F to the TRT rotor is made to satisfy the following formula:

if the direction of the thrust F is the direction of pushing the TRT rotor to approach the bearing steel of the unit:

f is not less than Fn + Rj;

if the direction of the thrust F is the direction for pushing the TRT rotor to move away from the bearing steel of the unit:

f is not less than Fn-Rj;

in the above formula, Fn is a static friction force when the TRT rotor is displaced in its axial direction, and Rj is a wind resistance when the TRT rotor is displaced in its axial direction.

On the basis of the minimum limit of the thrust F in the formula, the TRT rotor can be ensured to generate displacement under the thrust F, and then the real-time dynamic and static clearance value B can be adjusted.

On the basis of the embodiment, because the real-time dynamic and static clearance value B and the formula satisfying the thrust F of the TRT rotor are found respectively, the dynamic regulation is carried out on the oil inlet and outlet quantity of the two hydraulic pistons, a plurality of groups of thrust F satisfying the formula satisfying the thrust F of the TRT rotor are arranged, the radial displacement sensor and the axial displacement sensor are utilized, the corresponding real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder under the conditions of different thrust F is determined, the straight line cluster between the real-time dynamic and static clearance value B and the thrust F under different thrust F is obtained, and the straight line cluster equation is determined:

if the TRT rotor displaces towards the direction far away from the bearing steel of the unit, the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relationship:

B＝|-kF+d|+C；

if the TRT rotor displaces towards the direction close to the bearing steel of the unit, the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the bearing cylinder of the unit meet the following relations:

B＝C-|kF+d|；

in the above formula, k and d are respectively a correction coefficient and an empirical constant obtained by performing linear analysis on the thrust F and the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder.

According to the technical scheme, a relation is established between the thrust F for pushing the TRT rotor to displace and the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder, and then the possibility is provided for automatically controlling the real-time dynamic and static clearance value B between the turbine movable blade and the unit bearing cylinder by controlling the thrust F of the hydraulic piston or controlling the acting of the hydraulic piston

The above-mentioned embodiments only express a certain implementation mode of the present invention, and the description thereof is specific and detailed, but not construed as limiting the scope of the present invention; it should be noted that, for those skilled in the art, without departing from the concept of the present invention, several variations and modifications can be made, which are within the protection scope of the present invention; therefore, the protection scope of the present patent shall be subject to the appended claims.