CN110704961A

CN110704961A - Variable-force spring support and hanger series parameters and selection method thereof

Info

Publication number: CN110704961A
Application number: CN201910793720.0A
Authority: CN
Inventors: 林其略; 李仲雄; 金晓磊; 王煜; 任大成; 常松; 孙凯; 刘佳
Original assignee: China Sinogy Electric Engineering Co Ltd
Current assignee: China Sinogy Electric Engineering Co Ltd
Priority date: 2019-08-27
Filing date: 2019-08-27
Publication date: 2020-01-17

Abstract

The invention discloses a variable spring support and hanger series parameter and a selection method thereof, comprising the steps of determining the common ratio and the range of the priority number series of the main parameter of the variable spring support and hanger; according to the determined main parameter series of the variable spring support and hanger, compiling a complete characteristic table of the variable spring support and hanger series, and according to the working load, the thermal displacement and the direction of the required variable spring support and hanger, searching the complete specification of the required variable spring support and hanger from the selection table of the variable spring support and hanger series; the invention provides a visual, simple and clear specification selection table for a variable spring support and hanger, which can directly and rapidly search the required complete specification of the economical and reasonable variable spring support and hanger from the specification selection table only by knowing the working load, the thermal displacement and the direction of the variable spring support and hanger, so that the specification selected by the variable spring support and hanger is more economical and reasonable, and the selection of computer software is very simple.

Description

Variable-force spring support and hanger series parameters and selection method thereof

Technical Field

The invention relates to the field of pipelines, in particular to a variable force spring support and hanger series parameter and a selection method thereof.

Background

It is known that in determining a parameter or series of parameters of a product, a priority number and a priority number series should be selected. However, for the series of parameters, in order to select the specification of the variable spring hanger by direct table lookup, it is more desirable to select the theoretical values or the calculated values of the geometric series. However, due to the limitation of the standard size series of springs, the maximum load series of the traditional cylindrical helical spring variable support and hanger at home and abroad is almost close to the derivative series R8 of the priority coefficient, but the actual grade ratio deviation is still large, so that the selected specification is not economical and reasonable, and the difficulty is brought to direct table look-up selection.

Because the pipeline is in the alternation of hot and cold states in the whole using process, the acting force of the variable-force spring support and hanger on the pipeline is changed along with the pipeline, when the acting force of the variable-force spring support and hanger on the pipeline is equal to the load distributed to the support and hanger by the pipeline, the additional force of the variable-force spring support and hanger on the pipeline is zero, and therefore the zero load distribution of the variable-force spring support and hanger can be realized in the cold state and the hot state. The distribution of the suspended load to zero in a cold state is called as cold suspended zero; the distribution of the suspended load to zero in the thermal state is called thermal state suspended zero.

Disclosure of Invention

The invention aims to provide a variable force spring support and hanger series parameter and a selection method thereof, so as to solve the problems in the background technology.

In order to achieve the purpose, the invention provides the following technical scheme: a variable force spring support and hanger series parameter and its selection method, including the following concrete steps:

s1: determining the common ratio and the range of the priority number series of the main parameters of the variable-force spring support and hanger, selecting a proper spring specification according to the determined main parameter series of the variable-force spring support and hanger, and carrying out micro-adjustment on the relative minor dimension, namely the common ratio of the selected spring support and hanger parameter series is consistent, the common ratio comprises decimal multiple and decimal fraction of any value, and the priority number sequence of the load value under the maximum deformation comprises integral multiple of 40;

s2: compiling a complete characteristic table of the variable-force spring support and hanger series, and establishing allowable upward and downward heat displacement meters which are in one-to-one correspondence with the total deformation and displacement of the spring support and hanger and meet the requirement of load change coefficients; the specific programming mode is as follows:

s21: the load series of the variable-force spring support hanger under the maximum deformation is as follows:

P_i，max＝10^{(Np/40+(i-1)/R)}N

in the formula: p_i，maxThe maximum working load of the variable force spring with the specification number i is achieved;

r is the priority number series adopted by the variable force spring set;

N_p-priority order of maximum workload values with specification number 1;

i is the specification number;

the rigidity corresponding to the series j variable force spring with specification number i is as follows:

P_i，j＝P_i，max/F_j，max

＝10^{(Np/40+(i-1)/R)}/F_j，maxmm/N

in the formula: j is a series number (number of springs in series) of the variable force spring set, wherein j is 1 commonly called as a short spring;

P_i，j' -series j variable force spring rate with specification number i;

F_j，maxwhen the deformation amount (maximum deformation amount) of the variable force spring set series j under the maximum working load is 1, F_1，max75mm or 76mm (3') of the current traditional variable force spring support and hanger series at home and abroad can be selected, and 80mm can also be selected;

s22: according to the formula Δ_j，max＝F_j，max-F_j，min≥F_j，max(2/(1+[f_v]) Obtaining the minimum deformation and the variable spring travel required by the variable spring group series under different allowable load change coefficients and different maximum deformation, and compiling into a table; in the formula:

Δ_j，maxthe spring deformation is the spring deformation when the thermal displacement is allowed to be maximum under the conditions of zero suspension in a thermal state and upward thermal displacement or zero suspension in a cold state and downward thermal displacement;

[f_v]the allowable load variation coefficient of the variable-force spring support and hanger of different pipeline systems;

s23: compiling a variable force spring support and hanger series selection table according to the obtained table and the relational expression, wherein the table is divided into five groups and columns and five groups and rows, and the variable force spring support and hanger series selection table comprises the following steps:

five groups of columns sequentially comprise from left to right:

a first set of columns: to allow a coefficient of variation of load f_v]The relative displacement of the variable force spring support and hanger is less than or equal to 0.25;

a second set of columns: the deformation of the variable force spring support hanger is adopted;

third group of columns: the number of the rows of the load corresponding to different absolute deformation of the spring of the variable force spring support hanger depends on the specification number of the variable force spring support hanger;

fourth group of columns: to allow a coefficient of variation of load f_v]When the absolute deformation is less than or equal to 0.25, the allowable thermal displacement under different absolute deformation is divided into two grouping columns, namely a thermal state zero-hanging thermal displacement downward column (a cold state zero-hanging thermal displacement upward column) and a thermal state zero-hanging thermal displacement upward column (a cold state zero-hanging thermal displacement downward column);

fifth column group: to allow a coefficient of variation of load f_v]When the absolute deformation is less than or equal to 0.35, the allowable thermal displacement under different absolute deformation is divided into two grouping columns, namely a thermal state zero-hanging thermal displacement downward column (a cold state zero-hanging thermal displacement upward column) and a thermal state zero-hanging thermal displacement upward column (a cold state zero-hanging thermal displacement downward column);

the five group rows include:

a first group of row header rows including a group column, a group column name and a series number, a spring specification number;

the second group of behavior is a group of numerical values such as displacement, deformation, load, allowable thermal displacement and the like;

the third group of rows is a spring stiffness group row, which is respectively the spring stiffness of each spring specification corresponding to the series 1, the series 2, the series 3 and the series 4 from top to bottom;

the fourth group is a suspender diameter row, and the suspender diameter (mm) is configured corresponding to each spring specification;

the fifth group of behavior priority number sequence rows are the priority number sequence of the spring load value under the maximum deformation of each specification;

s3: and (4) selecting the spring support and hanger, and searching the complete specification of the required variable spring support and hanger from the series selection table of the variable spring support and hanger according to the working load and the thermal displacement and direction of the required variable spring support and hanger.

In a preferred embodiment of the present invention, the variable force spring is a cylindrical coil spring or a disc spring.

As a preferable scheme of the invention, the priority number series is R8, R10 or R20, the priority number series of the maximum working load value with the specification number of 1 is selected within the range of 90-105, and N for the R8 series_pThe value being an integer multiple of 5, for N of the R10 series_pThe value being an integer multiple of 4, for N of the R20 series_pThe value takes an integer multiple of 2.

In a preferred embodiment of the present invention, when j is 1, F is_1，max75mm, 76mm or 80mm is selected.

In a preferred embodiment of the present invention, the first set of rows in step S23 includes 4 rows, i.e., series 4, series 3, series 2, and series 1 from left to right, and is the relative spring displacement (stroke of the sign of the variable spring hanger assembly) of the variable spring hanger.

In a preferred embodiment of the present invention, in step S23, the second group of rows includes 4 rows, and the rows from left to right are series 4, series 3, series 2, and series 1, which are the absolute spring deformation amounts of the variable force spring hanger.

As a preferable embodiment of the present invention, the fourth step in step S23Is grouped as allowable load variation coefficient f_v]And (5) when the absolute deformation is less than or equal to 0.25, the allowable thermal displacement is allowed under different absolute deformation. The method is divided into two grouped columns of 'hot state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'hot state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement downward). Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

In a preferred embodiment of the present invention, the fifth group is the allowable load variation coefficient [ f ] in step S23_v]And (5) when the absolute deformation is less than or equal to 0.35, allowing the thermal displacement amount under different absolute deformation amounts. The method is divided into two grouped columns of 'hot state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'hot state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement downward). Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

As a preferred scheme of the invention, the variable force spring support and hanger type is composed of three digits, the first digit is a variable force spring set serial number (spring serial number) j, and the second and third digits are spring specification numbers.

As a preferred scheme of the invention, the variable force spring support and hanger selection program enters different selection modules according to the required zero hanging mode Z and the thermal displacement direction O, so that the time consumption of selecting springs requiring zero hanging in a thermal state and downward thermal displacement (or zero hanging in a cold state and upward thermal displacement) is greatly shortened, and meanwhile, the multi-specification springs requiring zero hanging in a thermal state and upward thermal displacement (or zero hanging in a cold state and downward thermal displacement) are optimized.

Compared with the prior art, the invention has the beneficial effects that:

1. the variable spring support and hanger series provided by the invention completely conforms to the geometric series, has strong regularity, makes the specification of the variable spring support and hanger more economical and reasonable, and also makes the selection of computer software extremely simple.

2. The invention provides a visual, simple and clear specification selection table of a variable force spring support and hanger, which can directly and rapidly search the complete specification of the required economical and reasonable variable force spring support and hanger and the diameter of a matched connecting suspender from the specification selection table only by knowing the working load, the thermal displacement and the direction of the variable force spring support and hanger; the invention also can use the selection software of the variable spring support and hanger to quickly, economically and reasonably give the complete specification of the variable spring support and hanger, so that the specification selected by the variable spring support and hanger is more economic and reasonable.

3. The mathematical model of the variable-force spring support and hanger series provided by the invention reduces the pipeline stress analysis and operation time by more than 10%; the provided small program for selecting the variable force spring support and hanger can enable a technician to easily select the specification, the installation load, the installation compression value (or deformation value) and the actual load variation coefficient of the variable force spring support and hanger by using Excel according to the requirements of the working load, the thermal displacement size and direction and the load variation coefficient of the hanger.

4. The variable force spring support and hanger provided by the invention adopts a small program, and creatively enters the hanging zero mode Z and the thermal displacement direction O according to requirements into different selection modules, so that the time consumption for selecting springs when the hot state hanging zero and the thermal displacement are required to be downward (or the cold state hanging zero and the thermal displacement are required to be upward) is greatly shortened; and simultaneously optimizing the multi-specification spring which is required to be selected from the springs with zero suspension in a hot state and upward thermal displacement (or with zero suspension in a cold state and downward thermal displacement).

Drawings

FIG. 1 is a block diagram of a variable force spring selection routine;

FIG. 2R 8(90-215)36-75 series spring picklists (No.01-No. 14);

FIG. 3R 8(90-215) table (Nos. 15-26) for series 36-75 spring selection;

FIG. 4R 10(92-224)38-80 series spring picklists (No.01-No. 17);

FIG. 5R 10(92-224)38-80 series spring picklists (No.18-No. 34);

FIG. 6R 20(90-224)38-80 series spring picklists (No.01-No. 17);

FIG. 7R 20(90-224)38-80 series spring picklists (No.18-No. 34);

FIG. 8R 20(90-224)38-80 series spring picklists (No.35-No. 51);

FIG. 9R 20(90-224)38-80 series spring picklists (Nos. 52-68).

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Example 1: the invention provides a technical scheme that: a variable force spring support and hanger series parameter and its selection method, including the following concrete steps:

P_i，max＝10^{(Np/40+(i-1)/R)}N

r is the priority number series adopted by the variable force spring set;

N_p-priority order of maximum workload values with specification number 1;

i is the specification number;

P_i，j＝P_i，max/F_j，max

＝10^{(Np/40+(i-1)/R)}/F_j，maxmm/N

P_i，j' -series j variable force spring rate with specification number i;

five groups of columns sequentially comprise from left to right:

fourth group of columns: to allow variation of loadCoefficient [ f ]_v]When the absolute deformation is less than or equal to 0.25, the allowable thermal displacement under different absolute deformation is divided into two grouping columns, namely a thermal state zero-hanging thermal displacement downward column (a cold state zero-hanging thermal displacement upward column) and a thermal state zero-hanging thermal displacement upward column (a cold state zero-hanging thermal displacement downward column);

the five group rows include:

Further, the variable force spring is a cylindrical spiral spring or a disc spring.

Further, the priority number series is R8, R10 or R20, the priority number series of the maximum working load value with the specification number of 1 is selected from the range of 90-105, and the N is selected for the R8 series_pThe value being an integer multiple of 5, for N of the R10 series_pThe value being an integer multiple of 4, for N of the R20 series_pThe value takes an integer multiple of 2.

Further, when j is 1, F_1，max75mm, 76mm or 80mm is selected.

Further, in step S23, the first set of rows includes 4 rows, which are series 4, series 3, series 2, and series 1 from left to right, and are the relative spring displacement amounts of the variable force spring support hangers (stroke of the variable force spring support hanger assembly tags).

Further, in step S23, the second group of rows includes 4 rows, which are series 4, series 3, series 2, and series 1 from left to right, and are the absolute spring deformation amounts of the variable force spring hangers.

Further, the fourth array is the allowable load variation coefficient [ f ] in step S23_v]And (5) when the absolute deformation is less than or equal to 0.25, the allowable thermal displacement is allowed under different absolute deformation. The method is divided into two grouped columns of 'hot state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'hot state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement downward). Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

Further, the fifth group is the allowable load variation coefficient [ f ] in step S23_v]And (5) when the absolute deformation is less than or equal to 0.35, allowing the thermal displacement amount under different absolute deformation amounts. The method is divided into two grouped columns of 'hot state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'hot state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement downward). Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

Furthermore, the variable force spring support and hanger model is composed of three digits, the first digit is the variable force spring set serial number (spring serial number) j, and the second and third digits are the spring specification numbers.

Furthermore, the variable-force spring support and hanger selection program enables a hanging zero mode Z and a thermal displacement direction O to enter different selection modules according to requirements, time consumption of selecting springs requiring hot hanging zero and thermal displacement downward (or cold hanging zero and thermal displacement upward) is greatly shortened, and meanwhile, optimization is conducted on multi-specification springs requiring hot hanging zero and thermal displacement upward (or cold hanging zero and thermal displacement downward) selection.

The invention provides a visual, simple and clear specification selection table of a variable force spring support and hanger, and the required complete specification of the variable force spring support and hanger, which is economic and reasonable, can be directly and quickly checked from the specification selection table of the invention as long as the working load, the thermal displacement and the direction of the variable force spring support and hanger are known; the variable spring support and hanger of the invention can also be used for selecting software, and the complete specification of the variable spring support and hanger can be rapidly, economically and reasonably given. Specifically, the method comprises the following steps:

the load system of the variable force spring support hanger under the maximum deformation is as follows:

P_i，max＝10^{(Np/40+(i-1)/R)}N (1)

r is the priority number series adopted by the variable force spring set;

N_p-priority order of maximum workload values with specification number 1;

i is the specification number;

P_i，j′＝P_i，max/F_j，max

＝10^{(Np/40+(i-1)/R)}/F_j，maxmm/N (2)

P_i，j' -series j variable force spring rate with specification number i;

for the maximum working load of the variable force spring with the specification number of i + 1:

P_i+1，max＝10^(Np/40+i/R)N

＝P_i，max·10^(1/R)N

＝Pi，max·q_RN (3)

in the formula: q. q.s_R-the maximum working load series step ratio of the variable force spring is as follows:

q_R＝10(1/R) (4)

from this formula, one can obtain:

series R8, q_R＝1.333521432；

Series R10, q_R＝1.258925412；

Series R20, q_R＝1.122018454。

For the maximum working load of the variable force spring with the specification number of i + n:

P_i+n，max＝10^{(Np/40+(i+n-1)/R)}N

＝P_i，max·10^((n-1)/R)N

＝P_i，max·q_R ^(n-1)N(5)

the rigidity corresponding to a series j variable force spring with specification number i + n is as follows:

P_i+n，j′＝P_i+n，max/F_j，maxN/mm

＝P_i，j′/q_R ^(n-1)N/mm (6)

the same load may occur in different spring gauges, but the amount of spring deflection at the load decreases as the spring gauge increases. The amount of deformation of the variable force spring at the maximum working load in the increased specification is shown in table 1.

TABLE 1 deformation of the same working load in different specification numbers under different series grade ratios and different spring deformation

Assuming that four displacement (stroke) series of the variable force spring support and hanger (i.e. j is 1, 2, 3, 4), the maximum deformation and displacement of the spring (the displacement limited by the spring support and hanger) are:

series 1: maximum deformation F_1，maxmm，

Minimum amount of deformation F_1，minmm

Maximum displacement amount delta_1，max＝F_1，max-F_1，minmm；

Series 2: maximum deformation F_2，max＝2F_1，maxmm，

Minimum amount of deformation F_2，min＝2F_1，mmmm，

Maximum displacement amount delta_2，max＝2Δ_1，maxmm；

Series 3: maximum deformation F_3，max＝3F_1，maxmm，

Minimum amount of deformation F_3，min＝3F_1，minmm，

Maximum displacement amount delta_3，max＝3Δ_1，maxmm；

Series 4: maximum deformation F_4，max＝4F_1，maxmm，

Minimum amount of deformation F_4，min＝4F_1，minmm，

Maximum displacement amount delta_4，max＝4Δ_1，maxmm。

The corresponding spring rate series for each series is:

series 1: p_i，1’＝10^{(Np/40+(i-1)/R)}/F_1，maxN/mm； (7)

Series 2: p_i，2’＝10^{(Np/40+(i-1)/R)}/(2F_1，max)＝P_i，1’/2N/mm； (8)

Series 3: p_i，3’＝10^{(Np/40+(i-1)/R)}/(3F_1，max)＝P_i，1’/3N/mm； (9)

Series 4: p_i，4’＝10^{(Np/40+(i-1)/R)}/(F_1，max)＝P_i，1’/4N/mm。 (10)

The minimum deflection Fjmin in the formula depends on the allowable load change coefficient [ f ] of the variable force spring support hanger assembly_v]The size of (2).

Coefficient of variation of load f_vNamely:

f_v＝|Δ_t|·P’/P_J(11)

in the formula, | Delta_t| is the absolute value of the thermal displacement;

p' is the spring stiffness of the variable force spring support and hanger;

P_Jthe working load of the variable force spring support and hanger is provided.

Different standards, variable force spring support and hanger for different pipeline systems allowed load variation coefficient [ f_v]There may be different requirements. For most pipelines, [ f ] is usually specified_v]Less than or equal to 0.25; for unimportant pipelines, there is a standard regulation [ f ]_v]≤0.35。

The corresponding allowable thermal displacement value under the allowable load change coefficient of the variable force spring support and hanger is related to the zero hanging mode and the thermal displacement direction. If the load distribution method adopts 'hot state hanging zero' (the additional force of the spring of the pipe system is zero in the hot state) and the thermal displacement is downward (adopts 'cold state hanging zero' (the additional force of the spring of the pipe system is zero in the cold state) and the thermal displacement is upward), the calculation formula of the relation between the allowable thermal displacement and the deformation of the series j is as follows:

[Δ_j]＝MIN([f_v]·F_j，F_j-F_j，min) (12)

from the above formula, it can be seen that: [ Delta ] of_j]Increasing as the F value increases. Under the same working load, the larger the spring deformation F is, the larger the allowable thermal displacement is. So the minimum spring is only needed to be found to meet the working load.

Therefore, the larger spring than the larger spring in Table 1 is at P_j，maxDeformation magnitude to maximum deformation F_j，maxThe range of the spring gauge number is selected according to the load.

If the load distribution method adopts 'hot state zero suspension' and the thermal displacement is upward (adopts 'cold state zero suspension' and the thermal displacement is downward), the relation between the allowable thermal displacement and the deformation of the series j is as follows:

[Δ_j]＝MIN([f_v]·F_j，F_jmax-F_j) (13)

from the above formula can be seen：[f_v]·F_jWith F_jThe value increases and increases, and F_jmax-F_jThen with F_jThe value decreases and decreases, therefore, [ Delta ]_j]Maximum value appearing at f_v]·F_j＝F_jmax-F_jWhen is at time

F_j，[Δ]max＝F_jmax/(1+[f_v]) (14)

Usually, the load distribution method adopts a spring deformation F when the thermal displacement is allowed to be maximum upwards (adopting a thermal displacement downwards and a thermal state zero suspension) by adopting a thermal state zero suspension method_j，[Δ]maxAs the stroke middle point of the variable force spring support hanger, namely:

F_j，min≤F_jmax-2(F_jmax-F_j，[Δ]max)

≤F_jmax-2(F_jmax-F_jmax/(1+[f_v]))

≤F_jmax(2/(1+[f_v])-1)

Δ_j，max＝F_jmax-F_j，min

≥F_jmax(2/(1+[f_v]) (15)

the minimum deformation and the travel of the variable force spring set 1 under different allowable load variation coefficients and different maximum deformation can be obtained according to the formula shown in the table 2.

TABLE 2 allowable load variation coefficient and maximum deflection effect on minimum deflection requirement of variable force spring

According to the above relation, we can compile a visual, simple and clear selection table of variable spring hangers and support series for easily selecting the specification of the economical and reasonable variable spring hangers and support.

Compared with the conventional variable spring support and hanger system list, the variable spring support and hanger system selection list increases the corresponding allowable thermal displacement value of the deformation (displacement) of the variable spring support and hanger under a certain allowable load change coefficient; the hanger rod diameter and the priority sequence of the maximum load of the hanger rod are selected and matched by the variable force spring support hangers with different spring numbers.

The variable spring hanger series selection table is divided into five groups:

the first group from left to right is an allowable load variation coefficient_fv]The relative displacement (the stroke range of the variable spring support and hanger) of the variable spring support and hanger is less than or equal to 0.25, which is the same as the conventional variable spring support and hanger series list, wherein the first group of rows comprises 4 rows, and the relative displacement of the variable spring support and hanger of the series 4, the series 3, the series 2 and the series 1 is from left to right;

the second group is the deformation of the variable spring support and hanger, and the absolute deformation of the variable spring support and hanger of series 4, series 3, series 2 and series 1 is from left to right;

the third group is load (P) of variable force spring support hanger corresponding to different absolute deformation of spring_i，Fj＝P_i，j’·F_j) The number of the lines depends on the specification number of the variable force spring support and hanger;

the fourth group is allowable load variation coefficient f_v]The allowable thermal displacement under different absolute deformation amounts is less than or equal to 0.25, and the fourth column is thermal displacement downward (delta) of' thermal state suspension zero_j]＝MIN(0.25F_j，F_j-F_j，min) And "thermal null" thermal displacement up ([ Delta ]_j]＝MIN(0.25F_j，F_jmax-F_j) Two grouped columns, each grouped column contains 4 columns, and the left and right are series 1, series 2, series 3 and series 4 which are allowable heat displacement amounts under different absolute deformation amounts;

the fifth group is the allowable load variation coefficient f_v]Allowable thermal displacement amount under different absolute deformation amounts of not more than 0.35, and a fifth column of 'thermal state suspension zero' thermal displacement downward ([ delta ] j)]＝MIN(0.35F_j，F_j-F_j，min) And "thermal phase hang zero" thermal displacement up ([ f)_v]＝MIN(0.35F_j，F_j _max-F_j) Two grouped columns, each grouped column comprising 4 columns, from left to right, series 1, series 2,

seriesColumns

3 and 4 are the allowable thermal displacement amounts for different absolute deformation amounts. .

The variable spring hanger series selection table is divided into five groups:

the third group of rows is a spring stiffness group row, and the spring stiffness corresponding to each spring specification of the series 1, the series 2, the series 3 and the series 4 from top to bottom is as follows:

P_i，j′＝＝10^{(Np/40+(i-1)/R)}/F_j，max＝10^(i_R/40)/F_j，max(16)

wherein the priority number i_R＝N_p+40(i-1)/R；

The fourth group is a suspender diameter row, the suspender diameter configured corresponding to each spring specification is clear at a glance when the spring specification is selected;

fifth group of action priority number sequence numbers (i)_R) The row, i.e., the priority sequence of spring load values at maximum deflection for each specification.

The variable force spring support and hanger model is composed of three digits: the first is the number j (number of springs connected in series) of the maximum spring deformation amount series; the second, three positions are spring gauge numbers.

The following can be seen from the attached drawings 2-9 of the selection table of the variable spring support and hanger series: under the same working load, the same thermal displacement size and direction and the same allowable load change coefficient, more than one spring number and the number of serial connection can be selected. Starting from economically and reasonably selecting the specification of the variable-force spring support and hanger, firstly, the smaller the serial number is, the better the serial number is, and the height of the spring of the same specification number is close to the multiple of the serial number, so that the total height, the weight, the manufacturing cost and the occupied space position of the variable-force spring support and hanger can be increased by times, and the variable-force spring support and hanger is obviously neither economical nor unreasonable; secondly, under the same serial number, the smaller the specification number is, the smaller the total height, weight, cost and occupied space of the variable force spring support and hanger are, and the smaller the additional force generated by the variable force spring support and hanger on the pipeline in the thermal displacement process of the pipeline is due to the small spring stiffness.

For the case of "hot zero suspension" with downward thermal displacement (with "cold zero suspension" with upward thermal displacement), the cold load of "hot zero suspension" (the hot load of "cold zero suspension") is smaller than the working load (the distributed load of the supporting and suspending points), so that the minimum spring number meeting the working load is found from the attached fig. 2 to 9, and then the serial number meeting the thermal displacement value is searched.

For the case of "hot lifting zero" with upward hot displacement (with "cold lifting zero" with downward hot displacement), the cold load of "hot lifting zero" (the hot load of "cold lifting zero") is greater than the working load (the distributed load of the supporting and lifting point), so that the smallest spring number that satisfies the working load, which does not necessarily satisfy the hot displacement value, is found from fig. 2 to fig. 9, and the spring number of the hinge with large size needs to be found. Large 1 to 2 springs can be found for the R8 series, large 2 to 3 springs can be found for the R10 series, and large 5 to 6 springs can be found for the R20 series. However, as the spring number increases, the amount of deformation corresponding to the working load becomes smaller. For the case of "hot suspension zero" and upward thermal displacement (for "cold suspension zero" and downward thermal displacement), the maximum allowable thermal displacement of the spring is a certain value between the maximum deformation and the minimum deformation of the spring, and the magnitude and the maximum deformation of the spring are related to the allowable load change coefficient, that is:

F_Δmax＝F_max/(1+[f_v]) (17)

when the deformation of the spring under the working load is larger than F_ΔmaxWhen the amount of allowable thermal displacement is smaller, the amount of allowable thermal displacement is increased; when the deformation of the spring under the working load is less than F_ΔmaxAfter that, the allowable thermal displacement amount is rather decreased as the spring deformation amount becomes smaller.

Therefore, although 2 to 3 or even 5 to 6 gauge springs can be found for the R10 or R20 series, which correspond to a work load, there are only 2-3 gauge springs that correspond to a deflection that is close to or less than the maximum allowable thermal displacement of the spring.

Therefore, according to the selection concept, the proper spring number and the proper number of the series (namely the number of the series of the springs) can be easily selected from the selection table of the series of the variable force spring supports and hangers (figures 2-9) according to the working load, the magnitude and the direction of the thermal displacement and the allowable load change coefficient. The cold load of the 'hot suspension zero' and the corresponding spring deformation (the hot load of the 'cold suspension zero' and the corresponding spring deformation) can be approximated by interpolation according to the upper and lower adjacent values.

Example 2: in order to select the variable force spring support and hanger more conveniently and obtain more accurate data, the invention compiles a variable force spring support and hanger selection program, and a flow chart of the variable force spring support and hanger selection program is shown in an attached figure 1.

Specifically, the database of the variable spring support and hanger selection program stores various main parameters of the common variable spring support and hanger series for selection.

Firstly, after inputting engineering code, pipeline code and number of supporting and hanging point, inputting selected variable force spring series scheme code T_yAllowable load variation coefficient [ f ]_v]Z-hoisting mode and Z-supporting hoisting point working load P_JVertical thermal displacement value | delta of supporting and hanging point_ytL and the thermal displacement direction O.

Then, carrying out pretreatment of selection of the variable-force spring support hanger: and according to the input condition, whether the variable force spring is suitable for selection is initially judged. If it is not appropriate to select a variable force spring, the process is terminated, otherwise the next step is entered.

And then, entering different selection modules according to the required hoisting zero mode Z and the thermal displacement direction O:

1. for a requirement that the hot state is suspended at zero and the thermal displacement is downward (or the cold state is suspended at zero and the thermal displacement is upward), i.e. ZO ═ 1, then:

a. according to the working load P of the supporting and hanging point_JDirectly determining a selected variable force spring specification number i from a database of variable force spring series schemes;

b. the series 1 springs according to the determined variable force spring specification number i meet the allowable load change coefficient f_v]The allowable thermal displacement value | delta satisfying the supporting and hanging point vertical thermal displacement value is calculated_ytNumber of springs connected in series required for lj；

c. If the number of series j of springs required exceeds the maximum number of series for a variable force spring series solution (e.g., j_max4), the program displays that "no suitable variable force spring can be selected", and the operation is terminated, otherwise, the selected variable force spring model number is given, and the thermal state load P is given_hCold load P_cThermal deformation F_hCold deformation F_cAnd the actual load variation coefficient f_v。

2. For a requirement of zero hot lift with hot displacement up (or zero cold lift with hot displacement down), ZO ═ 1, then:

a. according to the working load P of the supporting and hanging point_JAnd supporting point vertical thermal displacement value | delta_ytI, initially selecting the specification number i of the variable force spring₀And calculating the working load P of the spring with the specification at the supporting and hanging point_JAnd allowable load variation coefficient [ f_v]The allowable amount of thermal displacement of;

b. calculating ratio initial selection variable force spring specification number i₀Big I₁Spring working load P at supporting and hanging point_JAnd allowable load variation coefficient [ f_v]The allowable amount of thermal displacement of;

c. comparing the allowable thermal displacement of two specification springs, determining the specification number of the optimized variable force spring, and calculating the vertical thermal displacement value | delta & lt/EN & gt satisfying the requirement of the supporting and hanging point_ytThe number j of springs required for | is connected in series;

d. if the number of series j of springs required exceeds the maximum number of series for a variable force spring series solution (e.g., j_max4), the program displays that "no suitable variable force spring can be selected", and the operation is terminated, otherwise, the selected variable force spring model number is given, and the thermal state load P is given_hCold load P_cThermal deformation F_hCold deformation F_cAnd the actual load variation coefficient f_v。

Example 3: the improved R8 priority number derivative series aims at the existing cylindrical spiral spring variable support and hanger series at home and abroad.

As shown in FIGS. 2 and 3 (for space reasons, the table for selecting springs in the series R8(90-215)36-75 has to be divided into two tables of FIGS. 2 and 3, i.e. selecting springsThe third column of the table is spring numbers 01-14 and 15-26 in the tables of FIGS. 2 and 3, respectively); specifically, a load series of the cylindrical spiral spring variable-force support hanger under the maximum deformation adopts an R8 priority number derivative series, and the corresponding maximum load level ratio q is_R1.333521432; the maximum work load value of 177.8N with specification number of 01 and corresponding priority number sequence N_pIs 90; the maximum number of the specification numbers is 26, the maximum working load value is 237137N, and the corresponding priority number sequence is 215; the minimum deformation and the maximum deformation of the short spring (the serial number of the springs is 1) are respectively 36mm and 75 mm; the maximum serial number of the variable force support and hanger series is 4.

P_imax＝10^(90/40+i/8)N

The method comprises the following steps: i is the number of specifications, and the embodiment adopts 26 specification series, namely 01-26;

assume that four displacement (stroke) series are used, the corresponding maximum deformation and displacement amounts of which are:

series 1: minimum amount of deformation F_1minMaximum deformation F of 36mm_1max＝75mm；

Series 2: minimum amount of deformation F_2minMaximum deformation F of 72mm_2max＝150mm；

Series 3: minimum amount of deformation F_3minMaximum deflection F of 108mm_3max＝225mm；

Series 4: minimum amount of deformation F_4min144mm, maximum deflection F_4max＝300mm。

The corresponding stiffness series is:

series 1: p_i1’＝10^(90/40+i/8)/75N/mm；

Series 2: p_i2’＝10^(90/40+i/8)/150N/mm；

Series 3: p_i3’＝10^(90/40+i/8)/225N/mm；

Series 4: p_i4’＝10^(90/40+i/8)/300N/mm。

Assuming that the working load of the variable-force spring support and hanger is 10000N, the thermal displacement of the pipeline at the support and hanger point is 19mm downwards.

If a load distribution method of 'hot-state hoisting zero' is adopted, the set load (namely cold-state load) of the variable-force spring support and hanger is smaller than the working load due to downward thermal displacement. It will be seen from figure 3 that the

spring numbers

15, 16, 17 may be selected, although the 15 spring is most suitable. Along 10000N, the series 1 is found to the right at the allowable load variation coefficient [ f [ ]_v]The allowable downward thermal displacement is 26.25mm when the allowable downward thermal displacement is 0.35, the requirement of downward thermal displacement of 19mm can be met, the type of the variable force spring support and hanger can be 115, the deformation of the variable force spring support and hanger under a working load (setting load) is 75mm, the deformation of the variable force spring support and hanger under a cold load (setting load) is 75mm-19 mm-56 mm, and the corresponding cold load can be checked from the attached figure 2 to obtain 7467N; at the allowable load variation coefficient f_v]The allowable downward thermal displacement is 18.75mm when the allowable downward thermal displacement is 0.25, the requirement of downward thermal displacement of 19mm cannot be met, and the number of the springs in series can only be increased, namely the model of the variable force spring support and hanger is 215, the deformation of the variable force spring support and hanger under the working load (setting load) is 150mm, the deformation of the variable force spring support and hanger under the cold load (setting load) is 150mm-19mm 131mm, the corresponding cold load is 8667N when 130mm is obtained from the drawing 2, the corresponding cold load is 8800N when 132mm is obtained, and the obtained value is 8733.5N by an interpolation method.

If the load distribution method of 'cold state hoisting zero' is adopted, the set load of the variable force spring support and hanger is larger than the working load due to the downward thermal displacement. Therefore, spring number 15 cannot meet the requirements, and only spring

numbers

16 and 17 may be selected. 10000N found in the column of spring number 16 of FIG. 3 is between 9957N and 10135N, where the springs of series 1 are deformed by 56mm and 57mm, and then the allowable load change coefficient [ f ] of series 1 is found to the right_v]0.35 allows a downward thermal displacement of between 19mm and 18 mm; at the allowable load variation coefficient f_v]When the allowable downward thermal displacement is 0.25 mm, the allowable downward thermal displacement is between 14mm and 14.25mm, the requirement of downward thermal displacement of 19mm cannot be met, and only the number of the springs in series can be increased, namely the model number of the variable force spring support hanger is 216. At this time, the deformation of the series 2 spring is between 112mm and 114mm, the spring deformation under the working load (setting load) is 112.04mm, the deformation of the spring under the thermal state is 131.04mm, and the corresponding thermal state load is 11649N. From FIG. 3, it can be seen that: the allowable thermal displacement of the spring number 17 when the load is 10000N is smaller than that of the spring number 16, and therefore, the allowable thermal displacement is not considered.

Example 4: in order to make the specification of the spiral spring variable-force support hanger more economical, the load under the maximum deformation and the maximum displacement can be series-encrypted.

As shown in FIGS. 4 and 5 (for reasons of space, the R10(92-224)38-80 series spring selection table has to be divided into two tables of FIGS. 4 and 5, i.e. the third group of the spring selection table is spring numbers 01-17 and 18-34 respectively shown in the two tables of FIGS. 4 and 5), specifically, the load series of the cylindrical helical spring variable force support hanger under the maximum deformation adopts the R10 priority series, and the corresponding maximum load level ratio q is higher than that of the cylindrical helical spring variable force support hanger_R1.258925; the maximum work load value with the specification number of 01 is 199.5N, and the corresponding priority number sequence N_pIs 92; the maximum number of the specification numbers is 34, the maximum working load value is 398107N, and the corresponding priority number sequence is 224; the minimum deformation and the maximum deformation of the short spring (the serial number of the springs is 1) are respectively 38mm and 80 mm; the maximum serial number of the variable force support and hanger series is 4

P_imax＝10^(92/40+i/10)N

In the formula: i-number of specifications, the present embodiment employs 34 specification series, i.e., 01-34.

series 1: minimum amount of deformation F_1min38mm, maximum deflection F_1max＝80mm；

Series 2: minimum amount of deformation F_2min76mm, maximum deflection F_2max＝160mm；

Series 3: minimum amount of deformation F_3min114mm, maximum deflection F_3max＝240mm；

Series 4: minimum amount of deformation F_4min152mm, maximum deflection F_4max＝320mm。

The corresponding stiffness series is:

series 1: p_i1’＝10^(92/40+i/10)/80N/mm；

Series 2: p_i2’＝10^(92/40+i/10)/160N/mm；

Series 3: p_i3’＝10^(92/40+i/10)/240N/mm；

Series 4: p_i4’＝10^(92/40+i/10)/320N/mm。

If the load distribution method adopts 'hot state zero suspension' and the thermal displacement is upward (adopts 'cold state zero suspension' and the thermal displacement is downward), the calculation formula of the relationship between the thermal displacement and the deformation is as follows:

Δ＝MIN([f_v]·F，80-F)；

if the load distribution method adopts 'hot state zero suspension' and the thermal displacement is downward (adopts 'cold state zero suspension' and the thermal displacement is upward), the calculation formula of the relationship between the thermal displacement and the deformation is as follows:

Δ＝MIN([f_v]·F，F-38)

If a load distribution method of 'hot-state hoisting zero' is adopted, the variable force spring support and hanger sets the load as a cold-state load, and the cold-state load is smaller than the working load due to downward hot displacement. It will be seen from figure 5 that the spring numbers 18-21 may be selected, although the 18-number spring is most suitable. Along 10000N, the series 1 is found to the right at the allowable load variation coefficient [ f [ ]_v]The allowable downward thermal displacement amount is 20mm when the allowable downward thermal displacement amount is 0.25; at the allowable load variation coefficient f_v]The allowable downward thermal displacement is 28mm when the allowable downward thermal displacement is 0.35, the requirement of downward thermal displacement of 19mm can be met, the type of the variable force spring support and hanger can be 118, the deformation of the variable force spring support and hanger under a working load (setting load) is 80mm, the deformation of the variable force spring support and hanger under a cold load (setting load) is 80mm-19 mm-61 mm, and the corresponding setting load is 7625N.

If the load distribution method of 'cold state hoisting zero' is adopted, the set load of the variable force spring support and hanger is larger than the working load due to the downward thermal displacement. So spring number 18 does not meet the requirements and only spring numbers 19-21 may be selected. Find from the column of spring number 19 of FIG. 510000N is between 9914N and 10071N, the deformation of 10000N is 63.02mm by interpolation, the series 1 is found by right-hand check and interpolation_v]The allowable downward thermal displacement amount is 16.98mm when the allowable downward thermal displacement amount is 0.35; at the allowable load variation coefficient f_v]The allowable downward thermal displacement amount is 15.76mm when the allowable downward thermal displacement amount is 0.25, the requirement of downward thermal displacement of 19mm cannot be met, and only the serial number of springs can be increased, namely the model of the variable force spring support and hanger is 219; similarly, looking at FIG. 5 and using interpolation, the thermal deformation and load of the variable spring hanger can be 145.04mm and 11412N, respectively.

Example 5: the load series of example 4 was changed to the R20 priority series.

As shown in FIGS. 6-9 (for reasons of space, the R20(90-224)38-80 series spring selection table has to be divided into four tables of FIGS. 6, 7, 8 and 9, i.e. the third group of the spring selection table is divided into spring numbers 01-17, 18-34, 35-51 and 52-68 which are respectively listed in the four tables of FIGS. 6, 7, 8 and 9), specifically, the load series of the cylindrical coil spring variable force support hanger under the maximum deformation adopts the R20 priority number series, and the corresponding maximum load level ratio q is compared with the maximum load level ratio q_R1.122018; the maximum work load value of 177.8N with specification number of 01 and corresponding priority number sequence N_pIs 90; the maximum number of the specification numbers is 68, the maximum working load value is 398107N, and the corresponding priority number sequence is 224; the minimum deformation and the maximum deformation of the short spring (the serial number of the springs is 1) are respectively 38mm and 80 mm; the maximum serial number of the variable force support and hanger series is 4.

Specifically, the load system of the spring variable-force support and hanger under the maximum deformation and the maximum displacement is as follows:

P_imax＝10^(90/40+i/20)N

in the formula: i-number of specifications, the present embodiment employs 68 specification series, i.e. 01-68;

assuming that four displacement (stroke) series are used, the corresponding maximum deformation and displacement may be:

The corresponding stiffness series is:

series 1: p_i1’＝10^(92/40+i/20)/80N/mm；

Series 2: p_i2’＝10^(92/40+i/20)/160N/mm；

Series 3: p_i3’＝10^(92/40+i/20)/240N/mm；

Series 4: p_i4’＝10^(92/40+i/20)/320N/mm。

Δ＝MIN([f_v]·F，80-F)；

Δ＝MIN([f_v]·F，F-38)

in fact, the maximum load level ratio 1.122018 for example 5 compared to example 4 is q for example 4_RAbout half of 1.258925, the specification number 68 is one time the specification number 34 of example 4. That is, the division of the entire even spring number of example 5 by 2 is the entire spring number of example 4.

If the load distribution method of 'hot-state zero hanging' is adopted, the variable force spring support and hanger sets the load as a cold-state load, and the cold-state load is downward due to the thermal displacementThe load is less than the working load. It can be seen from fig. 8 that spring numbers 36-42 are optional. Of course, a 36 gauge spring is most suitable. Along 10000N, the series 1 is found to the right at the allowable load variation coefficient [ f [ ]_v]The allowable downward thermal displacement amount is 20mm when the allowable downward thermal displacement amount is 0.25; at the allowable load variation coefficient f_v]0.35 allows a downward thermal displacement of 28 mm. The model of the variable force spring support and hanger is 136. Similarly, looking at FIG. 8 and using interpolation, the cold deformation and load of the variable spring hanger can be 61mm and 7625N respectively.

If the load distribution method of 'cold state hoisting zero' is adopted, the set load of the variable force spring support and hanger is larger than the working load due to the downward thermal displacement. Therefore, the spring number 36 cannot meet the requirement, and only the spring numbers 37-42 can be selected. From the column of spring number 37 of fig. 8, 10000N is between 9958N and 10098N, looking to the right to find that series 1 is at the allowable load change factor f_v]When the allowable downward thermal displacement is between 9mm and 8mm when the allowable downward thermal displacement is 0.35 and 0.25, the requirement of downward thermal displacement of 19mm cannot be met, and only the serial number of springs can be increased, namely the model of the variable force spring support and hanger is 337; 10000N found in a column of spring number 38 is between 9914N and 10071N, the 10000N strain is 63.02mm by interpolation, the series 1 is found to the right by interpolation_v]The allowable downward thermal displacement amount is 16.98mm 1 at 0.35; at the allowable load variation coefficient f_v]The allowable downward thermal displacement amount is 15.76mm when the allowable downward thermal displacement amount is 0.25, the requirement of downward thermal displacement of 19mm cannot be met, and only the serial number of springs can be increased, namely the model of the variable force spring support and hanger is 238; 10000N found in a column of spring number 39 is between 9888N and 10064N, the 10000N deformation is 56.02mm by interpolation, the series 1 is found to the right by interpolation_v]The allowable downward thermal displacement amount is 19.62mm at 0.35; the requirement of downward thermal displacement of 19mm is met, and the model of the variable force spring support and hanger is 139; while allowing the coefficient of variation of the load to be in f_v]When the displacement is 0.25, the allowable downward thermal displacement is 14.02mm, the requirement of downward thermal displacement of 19mm cannot be met, and only the number of the springs in series can be increased, namely the model number of the variable force spring support hanger is 239. Spring10000N found in column No. 40 is between 9906N and 10104N, and the deformation of 10000N is 50.02mm by interpolation, but the allowable downward thermal displacement is smaller than spring No. 39, so it is not selected.

Summarizing, the working load of the variable-force spring support and hanger is 10000N, the thermal displacement of the pipeline at the support and hanger point is 19mm downwards, and a load distribution method of 'cold state suspension zero' is adopted to realize the allowable load change coefficient [ f_v]At 0.25, the model of the variable force spring support and hanger can be 337, 238, 239, wherein with the model 238 being the most economical and reasonable, looking at fig. 8 and using interpolation, the thermal deformation and load of the variable force spring support and hanger can be 145.04mm and 11412N, respectively; at the allowable load variation coefficient f_v]At 0.35, the type of the variable spring support and hanger can be 337, 238, 139, wherein the type 139 is the most economical and reasonable, and the thermal deformation and the load of the variable spring support and hanger are 75.02mm and 13335N respectively by looking at FIG. 8 and interpolating.

It can be found that: in example 5, compared with example 4, the load series was changed from R10 to R20 priority series. The total even spring number of example 5 divided by 2 is the total spring number of example 4. Therefore, in most cases, the actual specification and the size of the variable force spring support and hanger selected under the same parameters are the same, the working load and the thermal displacement in the embodiment are the same, if the spring number selected by the load distribution method of 'thermal state hanging zero' in the embodiment 5 and the embodiment 4 is 136 and 118 respectively, and the division of 36 by 2 is 18; if the load distribution method of 'thermal state zero hanging' is adopted for selection, and the load variation coefficient is allowed to be [ f_v]0.25, examples 5 and 4 selected spring numbers 238 and 219, respectively, 38 divided by 2 was 19, the number in series was also 2; if the load distribution method of 'thermal state zero hanging' is adopted for selection, and the load variation coefficient is allowed to be [ f_v]The spring numbers of 0.35, 139 and 219 for the spring numbers selected in the embodiment 3 and the embodiment 2, 1 for the serial number of the embodiment 3 and 2 for the serial number of the embodiment 2, although the spring number of the embodiment 3 is one larger, the weight and the height of the variable force spring support hanger are smaller than those of the embodiment 4, which is more economical.

Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.

Claims

1. A variable force spring support and hanger series parameter and its selection method, characterized by that, including the following concrete steps:

P_i，max＝10^{(Np/40+(i-1)/R)}N

r is the priority number series adopted by the variable force spring set;

N_p-priority order of maximum workload values with specification number 1;

i is the specification number;

P_i，j′＝P_i，max/F_j，max

＝10^{(Np/40+(i-1)/R)}/F_j，maxmm/N

P_ij' -series j variable force spring rate with specification number i;

five groups of columns sequentially comprise from left to right:

fourth group of columns: to allow a coefficient of variation of load f_v]Allowable thermal displacement amounts under different absolute deformation amounts of less than or equal to 0.25 are divided into 'thermal state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'thermal state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement upward)Zero thermal displacement down) two grouped columns;

the five group rows include:

2. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the variable force spring is a cylindrical spiral spring or a disc spring.

3. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the priority number series is R8, R10 or R20, the priority number series of the maximum working load value with the specification number of 1 is selected within the range of 90-105, and for the N of the R8 series_pThe value being an integer multiple of 5, for N of the R10 series_pThe value being an integer multiple of 4, for N of the R20 series_pThe value takes an integer multiple of 2.

4. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: when j is 1, F_1，max75mm, 76mm or 80mm is selected.

5. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: in step S23, the first group of rows includes 4 rows, which are series 4, series 3, series 2, and series 1 from left to right, and allow load variation coefficient [ f ] for the variable force spring support hanger_v]The relative displacement of the spring is less than or equal to 0.25.

6. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: in step S23, the second group of rows includes 4 rows, which are series 4, series 3, series 2, and series 1 from left to right, and are the absolute deformation amounts of the springs of the variable force spring support and hanger.

7. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the fourth array is the allowable load variation coefficient f in step S23_v]And (5) when the absolute deformation is less than or equal to 0.25, the allowable thermal displacement is allowed under different absolute deformation. The method is divided into two grouped columns of 'hot state zero suspension' thermal displacement downward ('cold state zero suspension' thermal displacement upward) and 'hot state zero suspension' thermal displacement upward ('cold state zero suspension' thermal displacement downward). Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

8. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the fifth group is the allowable load variation coefficient [ f ] in step S23_v]And (5) when the absolute deformation is less than or equal to 0.35, allowing the thermal displacement amount under different absolute deformation amounts. The method is divided into a thermal displacement downward direction of 'thermal state zero suspension' (thermal displacement upward of 'cold state zero suspension') and a thermal displacement upward direction of 'thermal state zero suspension' (thermal displacement upward of 'cold state zero suspension') (cold state zero suspension)Phase hang zero "hot shift down") two grouped columns. Each grouping column contains 4 columns, series 1, series 2, series 3, series 4 from left to right.

9. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the variable force spring support and hanger model is composed of three digits, the first digit is the variable force spring set serial number (spring serial number) j, and the second and third digits are the spring specification number.

10. The variable force spring hanger series parameters and the selection method thereof according to claim 1, wherein: the variable force spring support and hanger selection program enables a zero hanging mode Z and a thermal displacement direction O to enter different selection modules according to requirements, time consumption of selecting springs requiring zero hanging in a hot state and downward thermal displacement (or zero hanging in a cold state and upward thermal displacement) is greatly shortened, and meanwhile, optimization is conducted on multi-specification springs requiring zero hanging in a hot state and upward thermal displacement (or zero hanging in a cold state and downward thermal displacement) selection.