WO2020235754A1

WO2020235754A1 - Jig for testing rotating body, and method for designing jig for testing rotating body

Info

Publication number: WO2020235754A1
Application number: PCT/KR2019/013794
Authority: WO
Inventors: 양성진
Original assignee: 한화에어로스페이스 주식회사
Priority date: 2019-05-17
Filing date: 2019-10-21
Publication date: 2020-11-26
Also published as: KR20200132379A

Abstract

The present invention relates to a method for designing a jig for testing a rotating body. A method for designing a jig for testing a rotating body according to one embodiment of the present invention, which is a method for designing a jig that connects a rotating body mounted on a gas turbine and test equipment for testing the strength of the rotating body, comprises: a specification analysis step of analyzing specifications of the test equipment; an initial jig design step of designing an initial form of the jig in consideration of the specifications of the test equipment analyzed in the specification analysis step; a rotor dynamic analysis step of analyzing the jig, designed through the initial jig design step, by applying a rotor dynamic analysis; and a change step of changing the form of the jig or changing a design value of the rotor dynamic analysis if the jig does not satisfy a reference value through the analysis result in the rotor dynamic analysis step, wherein the rotor dynamic analysis step comprises a static analysis step, a natural frequency analysis step, and a balancing analysis step.

Description

Jig for rotating body test and design method of jig for rotating body test

The present invention relates to a jig for testing a rotating body and a method for designing a jig for testing a rotating body. Specifically, the present invention relates to a jig for connecting a rotating body mounted on a gas turbine and a test equipment for testing the strength of the rotating body, and a method of designing the same.

In general, a turbine is a mechanical device that obtains rotational force by impulsive force or reaction force by using a flow of a compressible fluid such as steam or gas, and includes a steam turbine using steam and a gas turbine using high temperature combustion gas.

Among them, the gas turbine is largely composed of a compressor, a combustor and a turbine. The compressor is provided with an air inlet for introducing air, and a plurality of compressor vanes and compressor blades are alternately arranged in a compressor casing.

The combustor supplies fuel to the compressed air compressed by the compressor and ignites it with a burner, thereby generating high-temperature and high-pressure combustion gas.

In the turbine, a plurality of turbine vanes and turbine blades are alternately arranged in a turbine casing. In addition, a rotor is disposed so as to pass through the center of the compressor, combustor, turbine and exhaust chamber.

Both ends of the rotor are rotatably supported by bearings. Further, a plurality of disks are fixed to the rotor, each blade is connected, and a drive shaft such as a generator is connected to an end of the exhaust chamber side.

Since these gas turbines do not have a reciprocating mechanism such as a piston of a four-stroke engine, there is no mutual friction part such as a piston-cylinder, so the consumption of lubricating oil is extremely small, and the amplitude, characteristic of a reciprocating machine, is greatly reduced, and high-speed motion is possible. There is an advantage.

Briefly explaining the operation of the gas turbine, the compressed air in the compressor is mixed with fuel and combusted to produce a high-temperature combustion gas, and the resulting combustion gas is injected into the turbine side. The injected combustion gas passes through the turbine vane and the turbine blade to generate a rotational force, thereby rotating the rotor.

In the turbine used as described above, stress is concentrated in a specific position due to vibrations generated in the radial direction as the blades rotate, which causes a problem of causing cracks and fatigue failure.

Therefore, if the rotor (compressor/turbine) is damaged during operation, it has a fatal effect on the entire gas turbine system, so it is necessary to check the strength of the rotor in advance.

The Spin (or over speed) test is a test that tests the centrifugal strength of a material by rotating at least 120% of the rated speed. It must be performed and checked before mass production. Dedicated equipment is required for the spin test, but even if a dedicated equipment is equipped, the design of a jig for high speed rotation, that is, an arbor and rotor, must be reviewed in advance and a test must be performed.

At this time, since the jig is designed based on experience, there is a problem in that excessive vibration of the rotating body occurs, so that the target rotational speed is not reached and the test cannot be performed.

In this case, since the jig must be redesigned, there is a problem in that time, productive and economic losses occur.

An object of the present invention is to design a jig by applying a rotor dynamic analysis to the design process of a jig to prevent excessive vibration of a rotating body that may occur during a spin test of a gas turbine rotating body.

In the method of designing a jig for testing a rotating body according to an embodiment of the present invention, in the method of designing a jig connecting a rotating body mounted on a gas turbine and a test equipment for testing the strength of the rotating body, the specification of the test equipment A specification analysis step of analyzing the data; An initial jig design step of designing an initial shape of the jig in consideration of the specifications of the test equipment analyzed in the specification analysis step; A rotor dynamic analysis step of analyzing the jig designed through the initial jig design step by applying a rotor dynamic analysis; And a change step of changing a shape of the jig or changing a design value of the rotor dynamic analysis when the jig is not satisfied with the reference value through the analysis result in the rotor dynamic analysis step, wherein the rotor dynamic analysis step It includes a static analysis step, a natural frequency analysis step, and a balancing analysis step.

In an embodiment, in the static analysis step, it may be determined whether the twist angle of the jig satisfies a reference angle value.

In an embodiment, in the step of analyzing the natural frequency, it may be determined whether a difference between the natural frequency of the jig and the rated speed of the rotating body satisfies a reference margin ratio.

In an embodiment, in the balancing analysis step, it may be determined whether a vibration tolerance value of the jig satisfies a reference vibration value.

In one embodiment, the changing step may change the shape of the jig when the jig is not satisfied with the reference value through the analysis result of the static analysis step or the natural frequency analysis step.

In an embodiment, in the changing step, when the jig is not satisfied with the reference value through the analysis result of the balancing analysis step, the design value of the rotor dynamic analysis may be changed.

A jig for testing a rotating body according to an embodiment of the present invention is a jig for testing a rotating body, wherein the jig is designed by the method of designing a jig for testing a rotating body.

In one embodiment, the jig may be inserted into a through hole formed in the rotating body.

In one embodiment, a fastening groove into which a fastening member can be inserted may be formed at one side of the jig.

In one embodiment, the jig may be formed to be elastically deformed when the fastening member is inserted into the fastening groove.

In a jig for testing a rotation body according to another embodiment of the present invention, in a jig for testing a rotation body including an arbor and a rotor, the jig is designed by the method of designing a jig for testing a rotation body.

In one embodiment, the arbor may have an insertion hole into which the rotor is inserted, and the insertion hole may be formed to have a predetermined diameter with respect to a central axis of the arbor.

In one embodiment, a fixing groove for fixing the arbor and the rotor may be formed on an outer circumferential surface of the arbor.

In one embodiment, a plurality of fasteners for fixing the rotor may be formed on the inner circumferential surface of the arbor.

The present invention is effective in blocking excessive vibration of a rotating body that may occur during a spin test of a gas turbine rotating body by designing a jig by applying a rotor dynamic analysis to the design process of a jig.

Therefore, the present invention has the effect of blocking time, productive, and economic losses due to the redesign of the jig.

1 is a block diagram of a jig designing equipment for a rotating body test for designing a jig for testing a rotating body.

2 is a flowchart sequentially showing a method of designing a jig for testing a rotating body according to an embodiment of the present invention.

3 and 4 are views exemplarily showing a process of applying a rotor dynamic analysis in a method of designing a jig for testing a rotor according to an embodiment of the present invention.

5 is a diagram showing a connection relationship between a rotating body, a test equipment, and a jig for testing a rotating body.

6 is a view showing a jig for testing a rotating body according to the first embodiment of the present invention.

7 is a view showing a jig for testing a rotating body according to a second embodiment of the present invention.

8 is a diagram showing a connection relationship between a rotating body, a test equipment, and a jig for testing a rotating body according to a third embodiment of the present invention.

9 is a cross-sectional view of a jig for testing a rotating body according to a third embodiment of the present invention.

Advantages and features of the present invention, and a method of achieving them will become apparent with reference to the embodiments described below in detail with the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, but may be implemented in a variety of different forms, and only these embodiments make the disclosure of the present invention complete, and are common knowledge in the technical field to which the present invention pertains. It is provided to completely inform the scope of the invention to those who have, and the invention is only defined by the scope of the claims. The same reference numerals refer to the same components throughout the specification.

Unless otherwise defined, all terms (including technical and scientific terms) used in the present specification may be used as meanings that can be commonly understood by those of ordinary skill in the art to which the present invention belongs. In addition, terms defined in a commonly used dictionary are not interpreted ideally or excessively unless explicitly defined specifically.

The terms used in the present specification are for describing exemplary embodiments and are not intended to limit the present invention. In this specification, the singular form also includes the plural form unless specifically stated in the phrase. As used in the specification, “comprises” and/or “comprising” do not exclude the presence or addition of one or more other elements other than the mentioned elements.

Hereinafter, a method of designing a jig for testing a rotating body according to an embodiment of the present invention will be described with reference to the drawings.

On the other hand, since the jig (10, 40) is designed based only on experience, excessive vibration of the rotating body is generated in the jig (10, 40) during the strength test of the rotating body (30, 60) using the test equipment (20, 50). In this case, there is a problem that the strength test of the

rotating bodies

30 and 60 cannot be performed. Accordingly, there is a need to design the

jig

10 and 40 through a systematic method rather than an empirical design.

Referring to FIG. 1, the jig design equipment 100 includes an input unit 101, a control unit 103 and a design unit 105.

The input unit 101 receives parameter values for designing the

jigs

10 and 40 from the user. For example, the input unit 101 may receive a value for the diameter of the rotor 13 of the

jigs

10 and 40 from the user. However, this is only an example, and the parameter value input by the input unit 101 from the user includes all parameters necessary for designing the

jig

10 and 40.

The input unit 101 transfers parameter values for designing the

jigs

10 and 40 received from the user to the control unit 103.

The control unit 103 controls the design unit 105 to design the shape of the

jig

10 and 40 according to the parameter values for designing the

jig

10 and 40 received from the input unit 101.

For example, the control unit 103 is a design unit to design the diameter of the rotor 13 of the

jig

10 and 40 according to the value for the diameter of the rotor 13 of the

jig

10 and 40 received from the input unit 101. 105) can be controlled.

The design unit 105 designs the

jigs

10 and 40 according to the control command of the control unit 103. Specifically, the design unit 105 designs the shapes of the

jigs

10 and 40 according to the control command of the control unit 103.

2, first, the control unit 103 analyzes the specifications of the test equipment (20, 50) (S101). Specifically, the control unit 103 analyzes the specifications of the

test equipment

20 and 50 by grasping the characteristics of the spindle 21, which is a component included in the

test equipment

20 and 50, the bearing position, and the like.

Thereafter, the design unit 105 designs the shape of the

jig

10 and 40 in consideration of the specifications of the

test equipment

20 and 50 analyzed in step S101 (S103). Specifically, the design unit 105 designs the shape of the

jig

10 and 40 by receiving a control command from the control unit 103. Meanwhile, the

jigs

10 and 40 designed in step S103 refer to the

jigs

10 and 40 designed without a rotor dynamics analysis.

Thereafter, the test equipment (20, 50) applies the rotor dynamic analysis to the jig (10, 40) designed in step S103 (S105, S107, S109, S111, S115, S117, S119). That is, the test equipment (20, 50) sequentially applies static analysis, natural frequency analysis, and balancing analysis to the jig (10, 40).

First, the test equipment (20, 50) applies a static analysis of the rotor dynamic analysis to the jig (10, 40) (S107, S109). The static analysis refers to an analysis that analyzes the deflection, inclination, and twist angle of the

jig

10 and 40.

Specifically, the test equipment (20, 50) applies a static analysis to the jig (10, 40) to determine whether the twist angle (sag angle or inclination) of the jig (10, 40) satisfies the reference angle value. The reference angle value refers to an angle value used as a reference for determining whether the degree of twisting of the

jigs

10 and 40 is within a normal range.

Thereafter, as a result of determination in step S109, when the twist angle of the

jig

10 and 40 satisfies the reference angle value, the

test equipment

20 and 50 applies the natural frequency analysis to the jig 10 and 40 (S111, S115). The natural frequency analysis means an analysis comparing the natural frequencies of the

jigs

10 and 40 with the rated speeds of the

rotating bodies

30 and 60.

Specifically, the test equipment (20, 50) applies the natural frequency analysis to the jig (10, 40) so that the difference between the natural frequency of the jig (10, 40) and the rated speed of the rotating body (30, 60) is the reference margin ratio. Determine whether you are satisfied. The reference margin rate refers to a margin rate that is a reference for determining whether the difference between the natural frequency of the

jig

10 and 40 and the rated speed of the

rotating bodies

30 and 60 is within a normal range.

For example, the test equipment (20, 50) is the natural frequency of the jig (10, 40) and the rotating body (30) as a result of applying the Campbell Diagram analysis when the rated speed of the rotating bodies (30, 60) is 90000 (rpm). , It can be determined whether the difference between the rated speeds of 60) has a resonance margin ratio of 20% or more.

3, the frequency at which the frequency (a) of the jig (10, 40) and the rotational speed (b) of the rotating bodies (30, 60) meet when the test equipment (20, 50) applies Campbell Diagram analysis to test That is, it can be confirmed that the natural frequency is 92361 (rpm). Since the rated speed of the

rotors

30 and 60 is 90000 (rpm), the difference between the natural frequency of the

jig

10 and 40 and the rated speed of the

rotors

30 and 60 is about 5%, making the margin less than 20%. You can see what it represents. Accordingly, in the case of FIG. 3, it is necessary to change the shape of the

jig

10 and 40. This is because, as described above, the

test equipment

20 and 50 rotates the

rotating bodies

30 and 60 at a speed of 120% or more of the rated speed to test the centrifugal strength of the materials of the

rotating bodies

30 and 60. .

4, the frequency at which the frequency (a) of the jig (10, 40) and the rotational speed (b) of the rotating bodies (30, 60) meet when the test equipment (20, 50) applies Campbell Diagram analysis to test. That is, it can be seen that the natural frequency is 108660 (rpm). Since the rated speed of the

rotors

30 and 60 is 90000 (rpm), it can be seen that the difference between the natural frequency of the

jig

10 and 40 and the rated speed of the

rotors

30 and 60 represents a margin rate of 20% or more. . Accordingly, in the case of FIG. 4, the test can be continued without changing the shape of the

jigs

10 and 40.

At this time, when applying the Campbell Diagram analysis, the test equipment (20, 50) applied a relatively low stiffness value of 1x10 ⁷ N/m to the ball bearing included in the test equipment (20, 50) and applied a damping of 10%. Premise. In addition, the test equipment (20, 50) in the case of the bushing (bush) bearing included in the test equipment (20, 50), the spindle 21 and the radial clearance is set to 0.5 mm or more, rather than the bearing role of the spindle (21). It is intended to play only the role of limiting excessive vibration of Therefore, it is assumed that 5x10 ³ N/m and 1.5x10 ³ Ns/m are applied to the stiffness and damping for the bushing bearing, respectively.

In addition, the test equipment (20, 50) applies Critical Speed Map analysis or Mode analysis to determine whether the difference between the natural frequency of the jig (10, 40) and the rated speed of the rotating body (30, 60) satisfies the standard margin rate. You can judge. However, it goes without saying that the

test equipments

20 and 50 can perform natural frequency analysis on the

jigs

10 and 40 even through methods other than the illustrated analysis method.

On the other hand, as a result of the determination in step S109, when the twist angle of the

jig

10 and 40 is not satisfied with the reference angle value, the design unit 105 changes the shape of the jig 10 and 40 (S113).

For example, the design unit 105 may change the shape of the

jig

10 and 40 by increasing or decreasing the diameter of the rotor 13 so that the twist angle of the

jig

10 and 40 satisfies the reference angle value. Alternatively, the design unit 105 may change the shape of the

jig

10 and 40 by increasing or decreasing the length of the rotor 13.

However, when the diameter of the

rotating bodies

30 and 60 is R, the design unit 105 may change the shape of the

jig

10 and 40 so that the length of the

jig

10 and 40 does not exceed the 2R range. In addition, the design unit 105 may change the shapes of the

jigs

10 and 40 so that the diameters of the

jigs

10 and 40 are within the range of 0.25R to 0.5R. This is because the length of the jig (10, 40) is as short as possible, and the weight of the jig (10, 40) should be designed to be as light as possible, which is advantageous for rotor dynamic analysis.

Thereafter, as a result of determination in step S115, if the difference between the natural frequency of the

jig

10 and 40 and the rated speed of the

rotating bodies

30 and 60 satisfies the reference margin rate, the

test equipment

20 and 50 is ) To apply the balancing analysis (S117, S119). The balancing analysis means performing the analysis by setting the left and right masses of the

jigs

10 and 40 differently according to the reference mass imbalance. At this time, the reference mass imbalance refers to a value indicating how unbalanced the left and right masses are to be set based on the central plane of the jig (10, 40), and in the present invention, the reference mass imbalance amount is ISO 1940-1. It is premised to apply within the range of G2.5~5 (2 times).

Specifically, the test equipment (20, 50) selects a reference mass imbalance, sets the left and right masses of the jig (10, 40) differently according to the reference mass imbalance, applies a balancing analysis, and applies the analysis result jig (10). , It is determined whether the vibration of 40) satisfies the reference vibration value. In this case, the reference vibration value means a value that is a reference for determining whether the vibration of the

jig

10 and 40 is within a normal range.

Thereafter, when the vibration of the

jig

10 and 40 is not satisfied with the reference vibration value as a result of the determination in step S119, the

test equipment

20 and 50 reselects the reference mass imbalance amount to the reselected reference mass imbalance amount. Set the left and right masses of the jig (10, 40) differently accordingly, and apply the balancing analysis again. At this time, the

test equipment

20 and 50 selects the reselected reference mass imbalance as a value that is relaxed compared to the previous reference mass imbalance.

That is, the test equipment (20, 50) applies the balancing analysis to the jig (10, 40) until the vibration of the jig (10, 40) satisfies the reference vibration value.

On the other hand, if the difference between the natural frequency of the

jig

10 and 40 and the rotational speed of the

rotating bodies

30 and 60 is unsatisfied with the reference margin rate as a result of the determination in step S115, the design unit 105 determines the shape of the

jig

10 and 40 To change (S113).

Hereinafter, with reference to FIGS. 5 to 9, a jig for testing a rotating body designed according to a method of designing a jig for testing a rotating body according to an embodiment of the present invention will be described.

5 is a diagram showing a connection relationship between a rotating body, a test equipment, and a jig for testing a rotating body. In this case, in FIG. 5, it is assumed that the jig 10 and the rotating body 30 are integrally formed.

Referring to FIG. 5, it can be seen that the jig 10 is disposed between the test equipment 20 and the rotating body 30 to connect the test equipment 20 and the rotating body 30.

The jig 10 is composed of an arbor 11 and a rotor 13. The arbor 11 is connected to the flange 23 of the test equipment 20, and the rotor 13 is connected to the rotating body 30. At this time, a specific structure of the jig 10 will be described later with reference to FIGS. 6 and 7.

The test equipment 20 is an equipment that tests the strength of the rotating body 30, and tests the centrifugal strength of the material of the rotating body 30 by rotating the rotating body 30 at a speed of 120% or more of the rated speed. At this time, in FIG. 5, it is shown that the test equipment 20 is composed of a spindle 21 and a flange 23 to briefly display only the configuration connected to the jig 10, but the test equipment 20 is shown in FIG. It is composed of other components besides the one that has been set.

The rotating body 30 is connected to the jig 10 and means a test target product whose strength is measured through the test equipment 20. For example, the rotor 30 may mean a specimen that simulates a compressor and a turbine. Alternatively, the rotating body 30 may mean a compressor and a turbine that are actually mounted on a gas turbine.

6 is a view showing a jig for testing a rotating body according to the first embodiment of the present invention. In this case, FIG. 6 (a) is a view showing a state before the arbor 111 and the rotor 131 are coupled, and FIG. 6 (b) is a view showing a state in which the arbor 111 and the rotor 131 are coupled. .

Referring to FIG. 6, the jig for testing a rotating body according to the first embodiment of the present invention includes an arbor 111 and a rotor 131.

The arbor 111 has an insertion hole 1111 into which the rotor 131 can be inserted. In this case, the insertion hole 1111 is formed to have a predetermined diameter based on the central axis of the arbor 111. The predetermined diameter corresponds to the diameter of the rotor 131.

In addition, fixing

grooves

1113 and 1115 for fixing the arbor 111 and the rotor 131 are formed on the outer peripheral surface of the arbor 111. In this case, the fixing

grooves

1113 and 1115 may be formed at symmetrical positions on the outer peripheral surface of the arbor 111, respectively. As shown in FIG. 6, fixing

grooves

1113 and 1115 are formed on the outer circumferential surface of the arbor 111, so that the arbor 111 and the rotor 131 can be fixed using a spanner or a general tool without the need for a separate jig. There is an effect to be able to. Accordingly, there is an effect of preventing damage or shape change due to the fixing of the arbor 111 and the rotor 131.

7 is a view showing a jig for testing a rotating body according to a second embodiment of the present invention. At this time, Figure 7 (a) is a cross-sectional view showing a state before the arbor 112 and the rotor 132 are coupled, Figure 7 (b) is a cross-sectional view showing the state in which the arbor 112 and the rotor 132 are coupled. .

Referring to FIG. 7, a jig for testing a rotating body according to a second embodiment of the present invention includes an arbor 112 and a rotor 132.

The arbor 112 has an insertion hole 1121 into which the rotor 132 can be inserted. At this time, the insertion hole 1121 is formed to have a predetermined diameter with respect to the central axis of the arbor 112. The predetermined diameter corresponds to the diameter of the rotor 132.

In addition, a plurality of fasteners 1123 for fixing the rotor 132 are formed on the inner circumferential surface of the arbor 112, and a fixing groove is coupled to the plurality of fasteners 1123 formed on the arbor 112 on the outer circumferential surface of the rotor 132 (1321) is formed.

Specifically, on the inner circumferential surface of the arbor 112, a plurality of fasteners 1123 are arranged at regular intervals along the diameter of the inner circumferential surface of the arbor 112 as shown in FIG. 7 (a), and the rotor 132 On the outer circumferential surface, it can be seen that the fixing groove 1321 is formed along the diameter of the outer circumferential surface of the rotor 132 as shown in FIG. 7 (a). Accordingly, as shown in FIG. 7 (b), when the rotor 132 is inserted into the arbor 112, it can be seen that the plurality of fasteners 1123 are coupled to the fixing groove 1321.

In addition, the

second fastening members

80 and 90 are coupled to the

second fastening grooves

1125 and 1127 of the arbor 112, respectively, so that the coupling force between the arbor 112 and the rotor 132 may be improved.

8 is a diagram showing a connection relationship between a rotating body, a test equipment, and a jig for testing a rotating body according to a third embodiment of the present invention. In this case, in FIG. 8, it is assumed that the jig 40 and the rotating body 60 pass through. In addition, unlike the jig 10 shown in FIGS. 5 to 7, the jig 40 shown in FIG. 8 will be described on the premise that it is an integral type without distinction between an arbor and a rotor.

Referring to FIG. 8, the jig 40 is inserted into a through hole formed in the rotating body 60. In this case, the through hole is formed to have a size corresponding to the diameter of the jig 40 with respect to the central axis of the rotating body 60. In addition, the jig 40 has a first fastening groove 41 into which the first fastening member 70 can be inserted. A process of inserting the first fastening member 70 into the first fastening groove 41 of the jig 40 will be described later with reference to FIG. 9.

The test equipment 50 is an equipment for testing the strength of the rotating body 60, and tests the centrifugal strength of the material of the rotating body 60 by rotating the rotating body 60 at a speed of 120% or more of the rated speed. At this time, in FIG. 8, it is illustrated that the test equipment 50 is composed of a spindle 51 and a flange 53 to briefly display only the configuration connected to the jig 40, but the test equipment 20 is shown in FIG. It is composed of other components besides the one that has been set.

The rotating body 60 is connected to the jig 40 and means a test target product whose strength is measured through the test equipment 50. For example, the rotor 60 may mean a specimen that simulates a compressor and a turbine. Alternatively, the rotating body 60 may mean a compressor and a turbine that are actually mounted on a gas turbine.

9 is a cross-sectional view of a jig for testing a rotating body according to a third embodiment of the present invention. At this time, Figure 9 (a) is a cross-sectional view of a state before the fastening member is coupled to the jig for testing a rotating body according to the third embodiment of the present invention, and Figure 9 (b) is a circuit according to the third embodiment of the present invention. It is a cross-sectional view of a state in which the fastening member is coupled to the entire test jig.

Referring to FIG. 9 (a), it can be seen that a first fastening groove 41 into which the first fastening member 70 can be inserted is formed in the jig 40 as described above. At this time, the diameter of the first fastening groove 41 is formed smaller than the diameter of the first fastening member (70).

Referring to FIG. 9B, it can be seen that the first fastening member 70 is inserted into the first fastening groove 41. At this time, since the jig 40 is composed of an elastic material, even if the diameter of the first fastening groove 41 is smaller than the diameter of the first fastening member 70, the first fastening member 70 is in the first fastening groove 41. It can be inserted in a force-fitting state. That is, the jig 40 is elastically deformed when the first fastening member 70 is inserted into the first fastening groove 41. Therefore, the jig 40 for testing a rotation body according to the third embodiment of the present invention is fastened through the first fastening member 70 without fastening the jig 40 to the rotation body 60 by shrink fit, so that strength There is an effect that it is easy to disassemble the jig 40 and the rotating body 60 after testing such as.

Those of ordinary skill in the art to which the present invention pertains will appreciate that the present invention can be implemented in other specific forms without changing the technical spirit or essential features thereof. Therefore, it should be understood that the embodiments described above are illustrative in all respects and not limiting. The scope of the present invention is indicated by the claims to be described later rather than the detailed description, and all changes or modified forms derived from the meaning and scope of the claims and their equivalent concepts should be interpreted as being included in the scope of the present invention. do.

Claims

In the method of designing a jig connecting a rotating body mounted on a gas turbine and a test equipment for testing the strength of the rotating body,

A specification analysis step of analyzing specifications of the test equipment;

An initial jig design step of designing an initial shape of the jig in consideration of the specifications of the test equipment analyzed in the specification analysis step;

A rotor dynamic analysis step of analyzing the jig designed through the initial jig design step by applying a rotor dynamic analysis; And

In the rotor dynamic analysis step, if the jig is not satisfied with the reference value through the analysis result, a change step of changing the shape of the jig or changing the design value of the rotor dynamic analysis,

The rotor dynamics analysis step includes a static analysis step, a natural frequency analysis step, and a balancing analysis step.
The method of claim 1,

The static analysis step is a method for designing a jig for testing a rotating body to determine whether the twist angle of the jig satisfies a reference angle value.
The method of claim 1,

The natural frequency analysis step is a method for designing a jig for testing a rotating body to determine whether a difference between the natural frequency of the jig and the rated speed of the rotating body satisfies a reference margin ratio.
The method of claim 1,

The balancing analysis step is a method for designing a jig for testing a rotating body to determine whether or not a vibration tolerance of the jig satisfies a reference vibration value.
The method of claim 1,

In the changing step, if the jig is not satisfied with the reference value through the analysis result of the static analysis step or the natural frequency analysis step, the jig design method for a rotating body test is changed.
The method of claim 1,

In the changing step, if the jig is not satisfied with the reference value through the analysis result of the balancing analysis step, the design value of the rotor dynamic analysis is changed.
In the jig for testing the rotating body,

The jig is a jig for testing a rotation body designed by the jig design method for testing a rotation body according to claim 1.
The method of claim 7,

The jig is a jig for testing a rotating body inserted into a through hole formed in the rotating body.
The method of claim 8,

The jig is a jig for testing a rotating body in which a fastening groove into which a fastening member can be inserted is formed on one side.
The method of claim 9,

The jig is a jig for testing a rotating body that is formed to be elastically deformed when the fastening member is inserted into the fastening groove.
In the jig for testing a rotating body including an arbor and a rotor,

The jig is a jig for testing a rotation body designed by the jig design method for testing a rotation body according to claim 1.
The method of claim 11,

The arbor has an insertion hole into which the rotor can be inserted,

The insertion hole is a jig for testing a rotating body formed to have a predetermined diameter with respect to the central axis of the arbor.
The method of claim 12,

A jig for testing a rotating body having a fixing groove for fixing the arbor and the rotor formed on the outer circumferential surface of the arbor.
The method of claim 12,

A jig for testing a rotating body having a plurality of fasteners for fixing the rotor formed on the inner circumferential surface of the arbor.