Patent Application
20170315036
The invention pertains to the field of nickel-based bolts, and relates to a design method for resistance to fracture of nickel-based bolts at high temperature, more particularly to a design method of bolts using nickel-based alloys with high strength and low resistance to fracture at high temperature, such as nickel-based high-temperature bolts, studs, nuts, etc.
In compliance with the principles of energy saving, consumption reduction, high efficiency and environmental protection, higher temperature, higher pressure and longer service life represent a developmental trend of devices in the fields of electric power, refining and chemicals, metallurgy, aviation, etc. For example, a single ultra-supercritical generator unit in a power plant has a power of 1000 MW or more, operating parameters of 600-650° C./32-35 MPa, and a design life of 30 years. An advanced turbine of an aero-engine has a front inlet temperature of up to 1980-2080° C., a thrust weight ratio of 15-20 or more, and a maximum service life of more than 40000 hours. The 700° C. thermal power and 4th generation nuclear power technologies under development with great efforts nowadays are also based on high temperature and pressure parameters and a long design life. With increasing promotion of the operating parameters of the devices, heat resisting materials such as ferrite steels, martensite steels and austenite steels cannot continue to meet the operating requirements of the various components. The effectuation of these process devices entails substantial use of nickel-based alloys with higher strength and better creep characteristics at high temperature.
Nickel-based high-temperature bolt, using nickel-based alloys as raw materials, is the generic term for all types of mechanical parts used to fasten and connect two or more elements as a whole at high-temperature environment. They mainly include bolts, studs, nuts, etc., widely used in the fields of energy, refining and chemicals, metallurgy, aviation, etc.
The current design methods for nickel-based high-temperature bolts are based on strength theories, and have the following general procedure: acquiring operating parameters; selecting a material; determining the pretension force; determining an arrangement and dimension of the bolts; analyzing the stress applied on the bolts; and checking the strength under various working conditions (considering the influence of relaxation).
However, fracture incidents of nickel-based high-temperature bolts occur from time to time. For example, some steam turbine bolts made of GH4145 alloy fractured in Jingyuan Second Power Co., Ltd. (2011); and a batch of bolts composed of Inconel 783 alloy cracked in several ultra-supercritical power generation units (2012); etc. Such incidents caused shutdown or production halt, leading to enormous economic loss. The main reason is that fracture toughness is specifically related to time and significantly reduces after a long time service of the nickel-based alloys at high temperature, although the nickel-based alloys has better high-temperature strength and anti-relaxation property. Hence, the critical point in design is to ensure that a nickel-based high-temperature bolt will not fracture in its service life. For this kind of materials with such properties, although, the conventional design methods for bolts based on strength theories appear to provide perfect safety factor, a decisive factor of the materials' fracture property is not taken into consideration in the design process, so the safe operation of a device cannot be guaranteed.
Therefore, the conventional design methods for bolts are not suitable for nickel-based bolts with superior strength and inferior resistance to fracture at high temperature. Thus, in this field, it is urgent to develop a new design method for resistance to fracture of nickel-based bolts at high temperature.
In view of the features of high strength and low resistance to fracture of nickel-based alloys at high temperature, a new design method is proposed for resistance to fracture of a nickel-based bolt at high-temperature environment, and a new strength design process is provided for bolts. Thus, the existing problem is solved in conventional method.
The invention provides a design method of high-temperature nickel-based bolts based on damage tolerance theory, comprising the following steps:
S1: acquiring operating parameters for the design, wherein the parameters include: the design temperature T; the environmental medium; the prospective operating life; the designation, structure and size of the material to be fastened; and the force P needed to fulfill the fastening function;
S2: selecting a material for bolts according to the design temperature T and the environmental medium in step S1;
S3: acquiring mechanical properties of the materials, including: linear expansion coefficients αb and αv of the material for bolts and the material to be fastened, respectively; the elastic modulus E, tensile property, stress relaxation property, and crack propagation threshold Kth of the bolt material at design temperature;
S4: determining a pretension stress σp of a single bolt according to the selected material in step S2, the pretension stress can be given as σp=0.50 σy, where σy represents the yield strength of the bolt material;
S5: determining the residual stress σr after stress relaxation in the design life at the design temperature T in step S1, wherein σr is obtained by referring to a database of material properties, or by extrapolating or interpolating a relaxation curve obtained by a high-temperature relaxation test and plotted by using Origin software, Excel software or by hand; calculating a thermal stress σt under the steady state according to σt=E(αv−αb)T; and determining a service stress σs under the steady state, wherein σs is the smaller one between σr and the larger one of σp+σt and σp;
S6: determining the number n, the effective cross-section area A and the distribution of bolts;
S7: determining a maximum allowable crack dimension according to the specification for nondestructive examination on bolts;
S8: calculating the maximum allowable service stress σth using the crack propagation threshold Kth at design temperature by assuming that the growth direction of the crack determined in step S7 is perpendicular to the loaded direction of the bolt. The σth can be represented by σth=Kth/(√{square root over (πa)}FI), where FI is obtained by referring to a handbook of stress intensity factors or by finite element calculation, and a is a length of the crack;
S9: comparing the service stress σs in step S5 and the maximum allowable service stress Σth in step S8, if σs is smaller than σth, then step S10 is performed; otherwise, return to step S4 and reduce the pretension stress σp; and
S10: after confirming that the crack does not propagate, and the bolts are safe during the design life, setting out the bolt material, the number n, the effective cross-section area A and the distribution of the bolts.
In a preferred embodiment, in step S3, the mechanical properties of the materials are obtained by referring to a database of material properties; or if this way fails, tests should be carried out.
In another preferred embodiment, the linear expansion coefficients are obtained using a thermal dilatometer; the elastic modulus E is obtained using a dynamic thermomechanical analysis; the tensile property is obtained by tensile tests at the design temperature; the stress relaxation property is obtained by relaxation testing at the design temperature; crack propagation threshold Kth at the design temperature is obtained as follows: crack growth tests are carried out using compact tensile specimens to obtain a curve of initial stress intensity factor vs. crack initiation time, and the curve is extrapolated or interpolated to obtain crack propagation threshold Kth in the design life.
In another preferred embodiment, the crack propagation threshold Kth in the design life is obtained from short-time crack growth tests at the design temperature. The curve of initial stress intensity factor vs. crack initiation time can be fitted using K=Btiφ, where K is stress intensity factor, ti represents crack initiation time, B and φ are material parameters obtained by fitting the test results. The stress intensity factor K calculated by putting the design life into the fitted equation is the crack propagation threshold Kth.
In another preferred embodiment, in step S6, the number n, the effective cross-section area A and the distribution of the bolts are designed according to P=nAσs, using the service stress σs obtained in step S5 in view of the size of the sealing face and the force P.
In another preferred embodiment, in step S7, the maximum allowable crack dimension is determined by balancing the minimum detectable size of defects by the nondestructive examination technique, the examination cost and the manufacture cost.
In another preferred embodiment, the nondestructive examination technique includes visual examination, magnetic powder examination and ray examination.
Beneficial Effects:
As the conventional design methods for bolts cannot ensure integrity of the nickel-based high-temperature bolts with high strength and low resistance to fracture, the inventors have developed a design method of high-temperature nickel-based bolts based on damage tolerance theory, and provide a new strength design process for bolts.
The accompanying drawings are provided for better understanding of the invention. They constitute a part of the specification for further explanation of the invention without limiting the invention.
The invention provides a design method of high-temperature nickel-based bolts based on damage tolerance theory, comprising the following steps:
S1: acquiring operating parameters for the design, such as the design temperature T; the environmental medium; the prospective operating life; the designation, structure and size of the material to be fastened; and the force (sealing force) P needed to fulfill the fastening function;
S2: selecting a material for bolts according to the design temperature and the environmental medium in step S1;
S3: acquiring mechanical properties of the materials, such as linear expansion coefficients αb andαv of the material for the bolt and the material to be fastened, respectively; elastic modulus E, tensile property, stress relaxation property, and crack propagation threshold Kth of the material for the bolt at the design temperature;
S4: determining a pretension σp for a single bolt according to the selected material in step S2, which can be given as σp=0.5 σy, where σy represents the yield strength of the bolt material;
S5: determining the residual stress σr after stress relaxation in the design life at the design temperature T in step S1; calculating the thermal stress σt under the steady state according to σt=E(αv−αb)T; and determining a service stress σs under the steady state;
S6: determining the number n, the effective cross-section area A and the distribution of bolts;
S7: determining a maximum allowable crack dimension according to the specification for nondestructive examination on bolts;
S8: calculating a maximum allowable service stress σth according to the following formula using the high-temperature crack propagation threshold Kth by assuming that the growth direction of the crack determined in step S7 is perpendicular to the loaded direction of the bolt
σth=Kth/(√{square root over (πa)}FI)
where FI is obtained by referring to a handbook of stress intensity factors or by finite element calculation, and a is the length of the crack;
S9: comparing the service stress σs in step S5 and the maximum allowable service stress σth in step S8, if σs is smaller than σth, then step S10 is performed; otherwise, return to step S4 and reduce the pretension stress σp;
S10: after confirming that crack will not propagate, and bolts are safe during the design life, setting out the bolt material, the number n, the effective cross-section area A and the distribution of the bolts.
According to the invention, in step S3, the mechanical properties of the materials are obtained by referring to a database of material properties; or if this way fails, tests should be carried out.
Preferably, the linear expansion coefficients may be obtained using a thermal dilatometer; the elastic modulus may be obtained using a dynamic thermomechanical analysis; the tensile property is obtained by tensile tests at the design temperature; the stress relaxation property is obtained by relaxation testing at the design temperature; crack propagation threshold Kth at the design temperature is obtained as follows: crack growth tests are carried out using compact tensile specimens to obtain a curve of initial stress intensity factor vs. crack initiation time, and the curve is extrapolated or interpolated to obtain crack propagation threshold value in the design life.
Preferably, the curve of initial stress intensity factor vs. crack initiation time may be plotted using Origin software, Excel software or by hand; and can be fitted using K=Btiφ, where K is stress intensity factor, ti is crack initiation time, B and φ are material parameters obtained by fitting the test results. The stress intensity factor K calculated by putting the design life into the fitted equation is the crack propagation threshold Kth.
Preferably, in step S5, σr may be obtained by referring to a database of material properties; if this way fails, it may be obtained by extrapolating or interpolating a relaxation curve obtained by a high-temperature relaxation test and plotted using Origin software, Excel software or by hand. Wherein σs is the smaller one between σr and the larger one of σp+σt and σp.
Preferably, the number n, the effective cross-section area A and the distribution of the bolts are designed according to P=nAσs using the service stress σs obtained in step S5 in view of the size of the sealing face, the force P and other factors.
Preferably, in step S7, the maximum allowable crack dimension may be determined by balancing the minimum detectable size of defects by a nondestructive examination technique such as visual examination, magnetic powder examination and ray examination, the examination cost and the manufacture cost.
Reference will be now made to the accompanying drawings.
S101: acquisition of operating parameters: acquiring operating parameters for the design according to the design conditions such as the design temperature; the environmental medium; the prospective operating life; the designation, structure and size of the material to be fastened; and the force (sealing force) P needed to fulfill the fastening function;
S102: material selection: selecting a material for bolts according to the design temperature and the environmental medium in step S101;
S103: acquisition of the material properties: acquiring linear expansion coefficients a of the material for the bolt and the material to be fastened; elastic modulus E, tensile property such as yield strength σy, stress relaxation property, crack propagation threshold Kth of the material for the bolt at the design temperature;
S104: determination of a pretension stress σp: determining a pretension stress for a single bolt according to the selected material in step S102, wherein σp=0.5 σy in general;
S105: determination of the steady service stress σs: determining the residual stress σr after stress relaxation at the design temperature in the design life, wherein σr may be obtained by referring to a database of material properties; if this way fails, it may be obtained by extrapolating or interpolating a relaxation curve obtained by high-temperature relaxation tests and plotted using Origin software, Excel software or by hand;
Calculating a temperature stress σt under the steady state according to σt=E(αv−αb)T, wherein E is the elastic modulus, αv is the linear expansion coefficient of the material to be fastened, αb is the linear expansion coefficient of the material for the bolt, and T is the design temperature;
Determining the service stress σs under the steady state, which is the smaller one between σr and the larger one of σp+σt and σp;
S106: determination of the number and size of the bolts: determining the number n, the effective cross-section area A and the distribution of the bolts according to P=nAσs using the service stress σs under working states obtained in step S105 in view of the size of the sealing face, the force P and other factors;
S107: determination of a maximum allowable crack dimension: determining a maximum allowable crack dimension according to the specification for nondestructive examination on bolts;
S108: determination of the maximum allowable service stress σth: calculating the maximum allowable service stress σth using the high-temperature crack propagation threshold Kth by assuming that the growth direction of the crack determined in step S107 is perpendicular to the loaded direction of the bolt, wherein the maximum allowable service stress σth can be calculated according to the following formula:
σth=Kth/(√{square root over (πa)}FI)
where FI can be obtained by referring to a handbook of stress intensity factors or by finite element calculation, and a is the length of the crack determined in step S107;
S109: comparing the service stress σs in step S105 and the maximum allowable service stress σth in step S108, wherein if σs is smaller than σth, then step S110 is performed; otherwise, the pretension stress σp is reduced and steps S105 to S110 are performed until σs<σth; and
S110: report of the design results after confirmation of the safety of the bolts: cracks will not propagate, and the bolts are safe during the design life; the bolt material, the number n, the effective cross-section area A and the distribution of the bolts determined in steps S102 and S106 are the design results of this run.
The invention will be further illustrated with reference to the following specific examples. It should be understood that these examples are only intended to exemplify the invention without limiting the scope of the invention. The test methods in the following examples for which no specific conditions are indicated will be carried out generally under conventional conditions or under those conditions suggested by the manufacturers. Unless otherwise specified, all percentages and copies are measured by weight.
High-temperature steam valve of a steam turbine needed to design the valve bolts. The design temperature for the bolt was 560° C., environment was atmospheric air, the design life was 100000 hours; the sealing force needed by the valve was 8500000 N; the valve material was GX12CrMoWVNbN10-1-1; the outer diameter of the sealing face of the valve was 1695 mm, and the inner diameter was 1085 mm.
The process flow was as follows:
I. Operating parameters were acquired. The design temperature T for the bolts was 560° C.; the valve material was GX12CrMoWVNbN10-1-1; the outer diameter of the sealing face of the valve was 1695 mm, and the inner diameter was 1085 mm; and the sealing force P needed by the valve was 8500000 N.
II. Inconel 783 alloy was selected as the material for the bolts based on the design temperature of 560° C.
III. The linear expansion coefficient αb of the Inconel 783 alloy at 560° C. was 1.22 E-5 1/° C., and the linear expansion coefficient αv of the GX12CrMoWVNbN10-1-1 steel at 560° C. was 1.24 E-5 1/° C. as determined using a thermal dilatometer (Netzsch, Germany). The elastic modulus E was 144 GPa at 560° C. as determined by static testing. Round bar tensile testing was conducted at 560° C., and the yield strength (0.2% offset) σy was 630 MPa. Stress relaxation tests were conducted at 560° C. to obtain stress relaxation performances at various loads. Curves of residual stress σ vs. time t were plotted using Origin software as shown in
IV. The pretension stress of a single bolt was determined as σp=0.5 σy=0.5×630 MPa=315 MPa.
V. The stress relaxation curves of the Inconel 783 alloy at 560° C. and various loads were extrapolated to 100000 hours to obtain a residual stress σr of 300 MPa. The thermal stress under the steady state was calculated as σt=E(αv−αb)T=144000×(1.24 E-5-1.22 E-5)×560=16 MPa. The service stress under the steady state was determined as σs=[(σp+σt, σp)max, σr]min=[(315+16, 315)max, 300]min=300 MPa.
VI. Considering the size of the sealing face, the sealing force P and other factors, according to P=nAσs, the number of the bolts was determined to be 24, and the effective cross-section area of the bolts was 1180 mm2. With the requirements of construction and the like taken into account, the outer diameter Do of the bolts was designed to be 46 mm, and the inner diameter Di was 25 mm, as shown in
VII. According the specification of nondestructive examination, the maximum allowable crack size was 1 mm which was the depth of plane defect.
VIII. The most dangerous conditions would occur when the growth direction of the crack is perpendicular to the loaded direction of the bolt, as shown in
σth=Kth/(√{square root over (πa)}FI)
where FI was available from a handbook of stress intensity factors, and FI of the cracks in both the inner and outer surfaces was 1.19. The maximum allowable service stress σth was 156 MPa.
IX. Obviously, the service stress σs under the steady state was larger than the maximum allowable service stress σth. Thus, the pretension stress σp was reduced to 140 MPa. The analysis from steps V to IX was performed, as detailed below:
9-5. The service stress under the steady state was determined as σs=[(σp+σt, σp)max, σr]min=[(140+16, 140)max, 300]min=156 MPa;
9-6. The number of the bolts was determined to be 24; the effective cross-section area of the bolts was 2280 mm2; the outer diameter Do of the bolts was 60 mm, and the inner diameter Di was 25 mm;
9-7. According to the specification of nondestructive examination, the maximum allowable crack size was 1 mm which was the depth of plane defect;
9-8. The most dangerous conditions would occur when the growth direction of the crack is perpendicular to the loaded direction of the bolt. With reference to the high-temperature crack propagation threshold Kth, the maximum allowable service stress σth was calculated as follows:
σth=Kth/(√{square root over (πa)}FI)
where FI was available from a handbook of stress intensity factors, and FI of the cracks in both the inner and outer surfaces was 1.16. The maximum allowable service stress σth was 160 MPa.
9-9. The service stress σs under the steady state was smaller than the maximum allowable service stress σth.
X. The crack would not propagate at 560° C. in the 100000 hour, and the bolts would be safe. The high-temperature steam value needed 24 bolts with the outer diameter Do=60 mm, the inner diameter Di=25 mm, and the material was Inconel 783 alloy.
The Examples mentioned above are only preferred examples in the invention, and they are not intended to limit the scope of the invention. Equivalent variations and modifications according to the invention in the scope of the present application for invention all fall in the technical scope of the invention.
All of the documents mentioned in the invention are incorporated herein by reference, as if each of them were incorporated herein individually by reference. It is to be further understood that various changes or modifications to the invention can be made by those skilled in the field after reading the above teachings of the invention, and these equivalent variations fall in the scope defined by the accompanying claims of the application as well.
| Number | Date | Country | Kind |
|---|---|---|---|
| 201610353421.1 | May 2016 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2016/084248 | 6/1/2016 | WO | 00 |
