CN110569560B - Method for superposing stresses of mirror topology tangential loaded circular ring - Google Patents

Method for superposing stresses of mirror topology tangential loaded circular ring Download PDF

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CN110569560B
CN110569560B CN201910760441.4A CN201910760441A CN110569560B CN 110569560 B CN110569560 B CN 110569560B CN 201910760441 A CN201910760441 A CN 201910760441A CN 110569560 B CN110569560 B CN 110569560B
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王世宇
柳金龙
王哲人
李海洋
王姚志豪
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Abstract

The invention discloses a method for superposing mirror image topological tangential loaded ring stress, which comprises the following steps: establishing a static model of the circular ring under the action of single tangential concentrated force on the micro-segment of the circular ring; calculating a distribution function of the tangential stress and the radial stress of the ring under the action of a single tangential concentrated force through a statics model; and obtaining the distribution function of the tangential stress and the radial stress of the mirror topology tangential loaded ring by using an superposition method. Compared with the prior art, the method has the characteristics of innovation, high efficiency, accuracy, universality and the like. According to the method, the relationship between the distribution of the tangential concentration force and the stress distribution can be researched.

Description

Method for superposing stresses of mirror topology tangential loaded circular ring
Technical Field
The invention relates to the field of stress distribution of material mechanics, in particular to a method for superposing stresses of a mirror topology tangential loaded ring.
Background
As early as ancient China, the ring structure is used by workers, and a waterwheel, also called a crown block, is an ancient water lifting irrigation tool and an operation machine developed by the workers in ancient China by fully utilizing hydraulic resources. A water bucket is arranged around the waterwheel, and the water bucket takes water to irrigate the land in the rotating process of the waterwheel. The waterwheel can be simplified into an annular structure, and the gravity generated by taking water from the bucket can be regarded as tangential force applied to the annular structure. It is necessary to study the stress distribution of the ring by the tangential force applied to the ring, because the stress distribution can be used to select the material meeting the allowable stress condition to manufacture the waterwheel, which determines the water intake amount. Ancient workers mainly select materials by experience. In modern engineering applications, the main research objects are engaged gears, racks and gear rings. During the meshing process of the gears, a force which points to the tooth surface along the meshing line is generated between the teeth, the component of the force along the tangential direction of the pitch circle is a driving force applied to the driven wheel, and the magnitude of the driving force determines the magnitude of the normal working load. Therefore, the stress distribution of the tangential load ring can be studied and can be guided in the design stage of the gear. The document (R.G. Parker.A. physical expansion for the efficiency of the planet in play to play with the planet in play vibration. J.Sound Vib,2000,236 (4): 561-573) investigated the effectiveness of the planet phase at a certain harmonic in suppressing planet vibration based on the forces acting on the sun and planet. Due to certain design objectives and assembly limitations, the space between the planet gears is sometimes uneven, the cycle symmetry is lost, and the document (j.lin and r.g. park.structurally characterized mechanics of planet gears with unequally spaced planet gears j.sound Vib,2000,233 (5): 921-928) analyzes the free vibration with an unequally spaced planet wheel system. At present, the stress distribution problem of a ring is not considered or simplified in the research of a plurality of gear dynamics, and due to the limitation of a ring stress distribution analysis technology, an analysis method of the ring stress distribution under the action of tangential concentrated force is particularly needed.
Disclosure of Invention
The invention provides a method for superposing stress of a mirror topology tangential loaded ring, which aims at the stress distribution problem of the tangential loaded ring, establishes a statics model on the micro-section of the ring by using a cross-section method, and calculates the stress distribution of the mirror topology tangential loaded ring by using an superposition method, so that the obtained result better meets the actual requirements of engineering, and the details are described as follows:
a method for stress superposition of a mirror topology tangential loaded ring, the method comprising the steps of:
establishing a static model of the circular ring under the action of single tangential concentrated force on the micro-segment of the circular ring;
calculating a distribution function of the tangential stress and the radial stress of the ring under the action of a single tangential concentrated force through a statics model;
and obtaining the distribution function of the tangential stress and the radial stress of the mirror topology tangential loaded ring by using an superposition method.
The static model specifically comprises the following components:
Figure BDA0002170093280000021
Figure BDA0002170093280000022
Figure BDA0002170093280000023
where θ is the angle of a certain mass point on the ring, F ef For tangential concentrated forces, F ff To make a virtual holding force, F sf For radially internal forces, F tf As tangential internal force, M bm Is a bending moment.
Further, the distribution function of the tangential stress and the radial stress of the ring under the action of the single tangential concentrated force is specifically as follows:
Figure BDA0002170093280000024
Figure BDA0002170093280000025
in the formula, F tfθ As tangential stress, F sfr For radial stress, a = bh is the cross-sectional area of the ring, h is the radial thickness, and b is the axial thickness.
Further, the distribution function of the tangential stress and the radial stress of the mirror topology tangential loaded ring is specifically as follows:
Figure BDA0002170093280000026
Figure BDA0002170093280000027
wherein N is the number of tangential concentrated forces, theta i1,j1 Is the ith 1 J in group 1 The position angle of the tangential concentrated force.
The technical scheme provided by the invention has the beneficial effects that:
1. the invention utilizes a section method to establish a statics model on the micro-segment of the ring, and solves the stress distribution of the ring under the action of single tangential concentrated force;
2. the invention adopts an superposition method to solve the stress distribution of the mirror image topology tangential loaded ring;
3. compared with the prior art, the method has the characteristics of innovation, high efficiency, accuracy, universality and the like. According to the method, the relationship between the distribution of the tangential concentration force and the stress distribution can be researched.
Drawings
FIG. 1 is a schematic view of the distribution of force on the whole ring and micro-segment under a single tangential concentrated force provided by the present invention;
wherein, (a) is a distribution schematic diagram of force on the ring under the action of single tangential force; (b) Is a schematic diagram of the distribution of force on the micro-segment of the circular ring under the action of single tangential force.
FIG. 2 shows the rotation θ provided by the present invention k The distribution diagram of the force on the whole ring and the micro-segment under the action of single tangential concentrated force of the angle;
FIG. 3 is a schematic diagram of the magnitude and distribution of tangential and radial stresses in a ring under a single tangential force provided by the present invention;
wherein, (a) is a schematic diagram of the distribution of tangential and radial stresses of the ring under the action of a single tangential concentrated force provided by the invention; (b) The invention provides a schematic diagram of the magnitude of tangential and radial stresses of a ring under the action of a single tangential concentrated force; (c) Rotation theta provided for the invention k The tangential and radial stress distribution of the ring under the action of the single tangential concentrated force of the angle is shown schematically.
FIG. 4 is a schematic diagram of the force distribution of the mirror topology tangential loaded ring provided by the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention are described in further detail below.
The embodiment of the invention provides a method which is strong in applicability and specially aims at stress superposition of a mirror topology tangential loaded ring. Firstly, establishing a static model of the ring under the action of a single tangential concentrated force on a micro-segment of the ring to obtain the distribution of each internal force of the loaded ring, solving the stress distribution of the ring under the action of the single tangential concentrated force according to the relation between the internal force and the stress in material mechanics, and then calculating the stress distribution of the mirror topology tangential loaded ring by adopting an overlay method. The method can also be used for solving the stress distribution of typical periodic structures such as a stator and a rotor of a rotating motor, an annular component in a micro device and the like.
The circular ring is acted by the tangential concentration force of the mirror topology; the superposition method of the stress distribution is basically characterized in that: the method adopts a superposition method to realize the stress distribution solution of the ring, and comprises the following specific steps:
(1) By utilizing a cross section method, a static model of the ring under the action of single tangential concentrated force is established on the micro-segment of the ring according to the force and moment balance principle:
Figure BDA0002170093280000041
Figure BDA0002170093280000042
Figure BDA0002170093280000043
where θ is the angle of a certain mass point on the ring, F ef For tangential concentrated forces, F ff To make a virtual holding force, F sf For radially internal forces, F tf As a tangential internal force, M bm Is a bending moment.
FIG. 1 is a graph showing the distribution of force on the rings and micro-segments when a single tangential concentrated force is applied. As shown in fig. 1 (a), the radius of the neutral circle of the circular ring is R, the radial thickness is h, the axial thickness is b, and the circular ring is subjected to a tangential force concentration F at θ =0 ef In the direction ofThe following steps. For research, a uniform virtual support is distributed around the circle, and the virtual support generates a virtual force F ff And the direction is upward, and the circular ring maintains balance under the action of a tangential concentrated force, a virtual torque and a uniformly distributed virtual force.
In order to research the stress distribution of the circular ring under a single tangential concentrated force, a micro-segment of d theta is cut at the position of the circular ring theta (theta epsilon (0,2 pi)), and the micro-segment is subjected to stress analysis by adopting a cross section method, as shown in figure 1 (b), O and O' are respectively the geometric center of the circular ring and the midpoint of the micro-segment, and F is sf 、F tf 、M bm And T tm Respectively radial internal force, tangential internal force, bending moment and torque.
(2) Since the study is of a circle in a micro-segment, d θ is a trace amount, and the concept of limit is utilized, a trigonometric function containing a trace amount can be simplified as follows:
Figure BDA0002170093280000044
/>
Figure BDA0002170093280000045
Figure BDA0002170093280000046
Figure BDA0002170093280000047
(3) Substituting the formulas (4) to (7) into the formulas (1) to (3) can be simplified:
Figure BDA0002170093280000048
Figure BDA0002170093280000051
dM bm =F sf Rdθ (10)
(4) Solving radial internal force
The radially inner force F is obtained from the formulae (8) and (9) sf With tangential concentrated force F ef The relationship of (1):
Figure BDA0002170093280000052
equation (11) is a second-order non-homogeneous differential equation of the radially inner force, and a characteristic equation can be obtained from equation (11):
λ sf 2 +1=0 (12)
in the formula, λ sf Is the eigenvalue of the eigen equation, the solution of which yields lambda sf1,2 And = ± i, i is an imaginary unit.
To solve a general solution of a differential equation, let a particular solution of the differential equation be:
F sf * =θ(a 1 cosθ+b 1 sinθ)+a 0 (13)
in the formula, a 0 、a 1 And b 1 Are all real numbers.
Substituting formula (13) into formula (11) can simplify:
Figure BDA0002170093280000053
a is obtained by undetermined coefficient method 0 、a 1 And b 1 Respectively as follows:
Figure BDA0002170093280000054
a 1 =0 (16)
Figure BDA0002170093280000055
thus, the solution of the differential equation is:
Figure BDA0002170093280000056
from the eigenvalues obtained from the eigen equation and a special solution of the differential equation, the general solution of the radial internal force can be obtained as:
Figure BDA0002170093280000057
in the formula, c 1 And c 2 Are real numbers.
(5) General solution for solving tangential internal force and bending moment
From formulae (8), (10) and (19):
Figure BDA0002170093280000061
Figure BDA0002170093280000062
(6) Solving radial deformation
For the small-curvature ring, the relation between the bending moment and the radial deformation can be known from the knowledge of material mechanics:
Figure BDA0002170093280000063
where v is the radial deformation of the ring and E and I are the elastic modulus and moment of inertia of the ring, respectively.
From equations (10), (11) and (22), the fifth-order heterogeneous differential equation of radial deformation can be obtained:
Figure BDA0002170093280000064
from equation (23), the characteristic equation can be derived as:
λ v 5 +2λ v 3v =0 (24)
solving to obtain λ v1 =0,λ v2,3 =±i,λ v4,5 And = ± i, i is an imaginary unit.
To solve a general solution of a differential equation, let a particular solution of the differential equation be:
v * =θ 2 (a 2 cosθ+b 2 sinθ)+a 0′ θ (25)
in the formula, a 0′ 、a 2 And b 2 Are all real numbers.
By substituting formula (25) for formula (23), the following can be obtained:
Figure BDA0002170093280000065
a is obtained by undetermined coefficient method 0′ 、a 2 And b 2 Respectively as follows:
Figure BDA0002170093280000066
a 2 =0 (28)
Figure BDA0002170093280000071
thus, the solution of the differential equation is:
Figure BDA0002170093280000072
from the eigenvalues obtained from the eigen equation and a particular solution of the differential equation, the general solution for radial deformation can be found as:
Figure BDA0002170093280000073
in the formula, a v1 ~a v5 Are all made ofReal numbers.
(7) Determining coefficients of general solutions using boundary conditions
The material mechanics knowledge shows that for the small-curvature ring, the corner on any section
Figure BDA0002170093280000074
Comprises the following steps:
Figure BDA0002170093280000075
taking the section analysis at the position of the circular ring theta =0, the tangential internal force is as follows:
Figure BDA0002170093280000076
from the formulae (20) and (33):
Figure BDA0002170093280000077
the rotation angles of the circular ring at the position of theta =0 are all zero, and can be known from formula (31):
Figure BDA0002170093280000078
from the formulae (21), (22) and (31):
Figure BDA0002170093280000079
the radial deformation of the circular ring is 0 at θ =0 and θ = pi, and it can be known from equation (31):
Figure BDA00021700932800000710
the small curvature circular ring is known from the assumption of no extension, and the tangential deformation u =0 of the circular ring at (0, pi), and is known from equation (31):
Figure BDA0002170093280000081
as can be seen from equations (34) and (36) - (38):
Figure BDA0002170093280000082
Figure BDA0002170093280000083
therefore, when a single tangential concentrated force acts, the radial internal force, the tangential internal force, the bending moment and the radial deformation of the ring are respectively as follows:
Figure BDA0002170093280000084
Figure BDA0002170093280000085
Figure BDA0002170093280000086
/>
Figure BDA0002170093280000087
from the relationship between internal force and stress in material mechanics and the equations (41) to (42), the tangential stress and the radial stress of the ring are respectively:
Figure BDA0002170093280000088
Figure BDA0002170093280000089
wherein A is the cross-sectional area of the ring.
(8) Superposition of stresses
As shown in fig. 2, the ring is at θ = θ k Is subjected to a tangential concentrated force F ef The action of (a) is that a virtual force balanced with the concentrated force is distributed around the circumference of the ring, and the tangential force and the virtual force are equal in magnitude and rotate in the direction of θ, respectively, as compared with fig. 1 (a) k And (4) an angle.
FIG. 3 (a) is a graph showing the distribution of the tangential and radial stresses in a ring under a single tangential concentrated force, the magnitude of which is shown in FIG. 3 (b). FIG. 3 (c) is a view showing a rotation of θ from FIG. 3 (a) k The resulting distribution of tangential and radial stresses after the corner.
Because the period of the tangential stress and the radial stress of the circular ring is 2 pi under the action of a single tangential concentrated force, the Fourier series expansion of the equations (45) and (46) is:
Figure BDA0002170093280000091
Figure BDA0002170093280000092
in the formula (I), the compound is shown in the specification,
Figure BDA0002170093280000093
and &>
Figure BDA0002170093280000094
Respectively as follows:
Figure BDA0002170093280000095
Figure BDA0002170093280000096
Figure BDA0002170093280000097
Figure BDA0002170093280000098
Figure BDA0002170093280000099
Figure BDA00021700932800000910
this is obtained by simplifying formulae (49) to (51) and substituting formula (47):
Figure BDA00021700932800000911
this is obtained by simplifying formulae (52) to (54) and substituting formula (48):
Figure BDA00021700932800000912
tangential concentrated force rotation theta k After the angle, the distribution of tangential and radial stresses of the ring should also be rotated by the same angle, i.e.:
Figure BDA00021700932800000913
Figure BDA00021700932800000914
in the formula, theta k The rotation angle when the first concentrated force is rotated to the kth concentrated force.
As shown in FIG. 4, a circle of a ring is subjected to N tangential concentration forces, whichThe N tangential concentrated forces are divided into 2 groups and arranged in a mirror image topology, such as a graph G i1 (i 1 =1,2), N/2 per group, as shown in fig. L i1,j1 (i 1 =1,2,j 1 =1,2.. N/2). Theta i1,j1 Described is the ith 1 J in the group 1 Angle of position of individual concentrated force, theta 2,j1 =θ 1,j1 + π. By using the superposition method, when the ring is subjected to N tangential concentrated forces, the first tangential concentrated force is acted at a position of theta =0, and the tangential stress and the radial stress of the ring are respectively as follows:
Figure BDA0002170093280000101
Figure BDA0002170093280000102
in summary, the embodiment of the present invention provides a method for superimposing stresses on a mirror topology tangential loaded ring. According to the method, a static model is established on the micro-section of the ring, the internal force of the loaded ring is obtained by adopting a cross-section method, the stress distribution of the loaded ring is obtained according to the relation between the internal force and the stress, the stress distribution of the mirror image topology loaded ring is obtained by utilizing an superposition method, the accuracy, the efficiency and the universality of the stress calculation of the ring are obviously improved, and the actual requirements of engineering are better met.
Those skilled in the art will appreciate that the drawings are only schematic illustrations of preferred embodiments, and the above-mentioned serial numbers of the embodiments of the present invention are only for description and do not represent the merits of the embodiments.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.

Claims (1)

1. A method for stress superposition of a mirror topology tangential loaded ring is characterized by comprising the following steps:
establishing a static model of the circular ring under the action of single tangential concentrated force on the micro-segment of the circular ring;
calculating a distribution function of the tangential stress and the radial stress of the ring under the action of single tangential concentrated force through a static model;
obtaining a distribution function of the tangential stress and the radial stress of the mirror topology tangential loaded ring by using an superposition method;
the statics model specifically comprises:
Figure FDA0004100629580000011
Figure FDA0004100629580000012
Figure FDA0004100629580000013
where θ is the angle of a certain point on the ring, F ef For tangential concentrated forces, F ff To make a virtual holding force, F sf For radially internal forces, F tf As a tangential internal force, M bm Is a bending moment;
the distribution function of the tangential stress and the radial stress of the ring under the action of the single tangential concentrated force is specifically as follows:
Figure FDA0004100629580000014
Figure FDA0004100629580000015
in the formula, F tfθ As tangential stress, F sfr For radial stress, a = bh is the cross-sectional area of the ring, h is the radial thickness, b is the axial thicknessDegree;
the distribution function of the tangential stress and the radial stress of the mirror topology tangential loaded ring is specifically as follows:
Figure FDA0004100629580000016
Figure FDA0004100629580000017
wherein N is the number of tangential concentrated forces, theta i1,j1 Is the ith 1 J in the group 1 The position angle of each tangential concentrated force; f tfθN Is tangential stress; f sfrN Is the radial stress.
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Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
房倩等.《圆形洞室围岩破坏模式模型试验研究》.《岩石力学与工程学报》.2011,第第30卷卷(第第3期期),全文. *

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