CN103438151B - Compensation principle based multistage double-mass flywheel - Google Patents

Abstract

The invention discloses a compensation principle based multistage double-mass flywheel which comprises a primary flywheel, a driven disc and a secondary flywheel, wherein two compensation mechanisms are uniformly distributed on the secondary flywheel; and a coordinate system is established by taking the center of the primary flywheel as an origin of coordinates, a molded line of an inner edge in a quadrant I is determined by a polar equation, a molded line in a quadrant II is mirrored by the quadrant I about a Y axis, and molded lines in a quadrant III and a quadrant IV are mirrored by the quadrant I and the quadrant II about an X axis. The double-mass flywheel adopts three-stage torsional rigidity which both meets small rigidity requirements under the condition of small torsion angles and meets high counter torque requirements under the condition of large torsion angles, thereby realizing the purpose that a resonant speed is completely and effectively excluded from the normal working speed range of an engine, and avoiding the occurrence of system resonance; and in a process of rigidity switching, the torsional rigidity is continuous, so that the impact and noises caused by rigidity mutation are avoided, and the service life of each part of a transmission system is prolonged.

Description

Based on the multistage double mass flywheel of compensation principle

Technical field

The present invention relates to a kind of double mass flywheel that may be used for the fields such as automotive transmission damping, particularly relate to a kind of multistage double mass flywheel based on compensation principle.

Background technique

Clutch between from motor to gearbox adopts traditional driven disc type torshional vibration damper (ClutchTorsional vibration Damper, be called for short CTD), be difficult to reach the requirement of required high-comfort and torsion damping that vehicle driveline is proposed and Noise measarement.From the nineties, for solving the torsional vibration problems of vehicle driveline, with German LUK company for representative, propose the method with increasing quality and elastic element, with double mass flywheel, (Dual-mass flywheel torsion damper, is called for short DMF, replace former CTD, through 10 years update, drop into batch production, conclusive significant contribution has been made to car steering travelling comfort.The application of double mass flywheel; make the first whirling speed of vehicle driveline lower than engine idle rotational; second-order resonance rotating speed is higher than engine peak speed; thus make resonance be isolated in beyond engine work speed range completely, to reduce the torsional vibration of car load power train and noise, alleviation power train impact, realize the overload protection of motor and gearbox and start function to run under low-down rotating speed thus reduce in fuel consume etc. all to have played important effect.

Along with the breakthrough that turbosupercharging, in-cylinder direct injection are the key technology of representative, powerful motor obtains great development.For being suitable for high-power high torque (HT) motor, double mass flywheel is made to have flexibility when the little torsion angle of the slow-speed of revolution, the large torsion angle of high rotating speed has the object of the large rigidity of high counter torque lower than engine idle rotational to realize transmission system first whirling speed, in recent years, LUK company of Germany, Sachs company works out segmentation step variation rigidity double mass flywheel, although segmentation variation rigidity double mass flywheel has more flexibility when little torsion angle, when large torsion angle, there is larger counter torque, torque characteristics is continuous, but because each section of torque characteristics is still linear change, when switching, rigidity has sudden change, namely rigidity jump phenomenon is produced, cause gearbox gear to engage and produce impulsive load and noise.The torque of 2 grades of linear variation rigidity double mass flywheels and stiffness characteristics are as shown in Figure 1, 2.

For being lowered by system first whirling speed, need make, during little torsion angle, there is flexibility, namely needing to reduce K _{θ 1}, but result in (K _{θ 2}-K _{θ 1}) change increase, thus by K _{θ 1}be switched to K _{θ 2}time impact increase.Along with the appearance of more and more strong engine, double mass flywheel is just towards the future development maximized, though segmentation step variation rigidity double mass flywheel efficiently solves the flexibility of little torsion angle and the problem of large torsion angle high counter torque, rigidity jump phenomenon will become the bottleneck of restriction large development.

Summary of the invention

For the rigidity transition problem of the segmentation step variation rigidity double mass flywheel existed in prior art, the invention provides a kind of multistage double mass flywheel based on compensation principle, this flywheel effectively can not only reduce rigidity and to suddenly change the shortcoming of the impact brought, and the rigidity of little torsion angle condition lower spring can easily be reduced, thus further can reduce the first whirling speed of system.

In order to solve the problems of the technologies described above, present invention employs following technological scheme:

Based on the multistage double mass flywheel of compensation principle, this multistage double mass flywheel is three grades of double mass flywheels, comprise elementary flywheel, driven disc and secondary flywheel, described driven disc and secondary flywheel are installed in elementary flywheel, described driven disc is connected with secondary flywheel, on secondary flywheel and near cylindrical, be laid with two compensation mechanisms, described secondary flywheel is laid with two grooves radially arranged near cylindrical;

Described compensation mechanism comprises pivot pin, needle bearing, guide rod, guide groove and Returnning spring; Described pivot pin is through needle bearing, and needle bearing contacts with the inward flange of elementary flywheel; Described guide groove to insert in groove and with groove secure fit, one end of described guide rod is connected with pivot pin, and the other end puts in guide groove, and described Returnning spring is arranged in guide groove, and one end of Returnning spring is pressed on guide rod, and the other end is pressed on the bottom of groove;

With the center O of elementary flywheel for true origin sets up system of coordinates, the rule curved surface of the inward flange of the described elementary flywheel molded line in system of coordinates the Ith quadrant is determined by such as under type, wherein R ₁the initial parameters that elementary flywheel is given:

1) with radius R ₁circular arc is drawn at 0 ° ~ 7 °;

2) by polar equation obtain AB section, wherein, K _bfor Returnning spring Line stiffness; θ _a=7 °, 7 ° of < θ≤17 °; M _jABaB section compensating torque, and

Wherein: a ₀, a ₁, a ₂and a ₃all by the compensating torque function parameter that Function Fitting obtains, a ₀=14.7, a ₁=-0.2, a ₂=0.3, a ₃=0; M ₁=K _{θ 1}θ (0≤θ < 12 °), M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), θ ₁=12 °, K _{θ 1}be torsional stiffness during three two groups circumference spring series connection, K _{θ 2}it is torsional stiffness during two two groups circumference spring series connection;

3) take OB as radius R ₂circular arc BC section is drawn at 17 ° ~ 31 °;

4) by polar equation $\mathrm{\&rho;}\left(\mathrm{\&theta;}\right)=R_1-\sqrt{{(R_1-R_2)}^2+\frac{1}{k_b}{\&Integral;}_{{\mathrm{\&theta;}}_c}^{\mathrm{\&theta;}}{M}_{\mathrm{JCD}}\left(\mathrm{\&theta;}\right)\mathrm{d\&theta;}}$ Obtain CD section, wherein θ _c=31 °, 31 °≤θ < 40 °, M _jCDcD section compensating torque, and

Wherein: b ₀, b ₁, b ₂and b ₃all by the compensating torque function parameter that Function Fitting obtains, b ₀=1496.7, b ₁=-109.66, b ₂=2.8321, b ₃=-0.0192; M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), M ₃=K _{θ 1}θ ₁+ K _{θ 2}(θ ₂-θ ₁)+K _{θ 3}(θ-θ ₂) (35 °≤θ≤40 °), θ ₁=12 °, θ ₂=35 °; K _{θ 3}for only having a torsional stiffness during spring works;

5) take OD as radius R ₃one section of circular arc is drawn at 40 ° ~ 90 °;

Note: θ ₃=45 °, θ _b=17 °, θ _d=45 °

The rule curved surface of the inward flange of the described elementary flywheel molded line in system of coordinates the IIth quadrant is by the mirror image of the Ith quadrant about Y-axis, and the rule curved surface of the inward flange of the described elementary flywheel molded line in system of coordinates the IIIth quadrant and the IVth quadrant is by the Ith quadrant and the IIth quadrant mirror image about X-axis.

The invention has the beneficial effects as follows: have employed little rigidity requirement when three grades of transmissions had both met little torsion angle, reduce further the first whirling speed of system, make it the idling speed being significantly less than motor; Simultaneously, meeting under large torsion angle condition, there is the requirement of high counter-torque, and make the maximum speed of second-order resonance rotating speed higher than motor of system, achieve resonance speed to be effectively isolated in beyond the normal operating rotational speed range of motor completely, avoid the generation of system resonance; And one-level to secondary, secondary to three grade rigidity is when switching, because rigidity is continuous, not sudden change, avoids transmission system and to be suddenlyd change the impact of generation and noise by rigidity when rigidity switches, and extend the working life of each part of transmission system.

Accompanying drawing explanation

Fig. 1 is linear segmented variation rigidity double mass flywheel torque characteristic figure;

Fig. 2 is linear segmented variation rigidity double mass flywheel stiffness characteristics figure;

Fig. 3 is the plan view of multistage double mass flywheel;

Fig. 4 is the rear view of multistage double mass flywheel;

Fig. 5 is the torsional stiffness transmission diagram starting to realize the second level;

Fig. 6 is the torsional stiffness transmission diagram starting to realize the third level;

Fig. 7 is the torque molded line not introducing compensation mechanism;

Fig. 8 is the torque molded line introducing compensation mechanism;

Fig. 9 is the semi-section view of multistage double mass flywheel;

Figure 10 is torque type line chart;

Figure 11 is the molded lines of rule curved surface in system of coordinates I quadrant of the inward flange of elementary flywheel;

Figure 12 is the rule curved surface molded lines in a coordinate system of the inward flange of elementary flywheel;

Figure 13 is the structural profile view that balanced controls are arranged on secondary flywheel;

Figure 14 is balanced controls schematic diagram;

Figure 15 is balanced controls schematic diagram;

Figure 16 is balanced controls calculating chart.

In accompanying drawing: 1-elementary flywheel; 2-driven disc; 3-secondary flywheel; 4-chute; 5-pivot pin; 6-needle bearing; 7-guide rod; 8-guide groove; 9-Returnning spring; 10-strut; 11-balancing pole; 12-equilibrium block; 13-start gear ring; 14-spring seat; 15-spring; 16-spring seat; 17-spring; 18-spring seat; 19-spring; 20-spring seat; 21-bolt; 22-jump ring.

Embodiment

Below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.

As Fig. 3, shown in 4, based on the multistage double mass flywheel of compensation principle, this multistage double mass flywheel is three grades of double mass flywheels (three grades of segmentation variation rigidity double mass flywheels), comprise elementary flywheel 1, driven disc 2 and secondary flywheel 3, driven disc 2 and secondary flywheel 3 are installed in elementary flywheel 1, driven disc 2 is connected with secondary flywheel 3, on secondary flywheel 3, and be laid with four compensation mechanisms and four balanced controls near cylindrical, on secondary flywheel 3, and be laid with four grooves radially arranged and four chutes along the circumferential direction arranged 4 near cylindrical.

Motor drives elementary flywheel 1 to rotate by starting gear ring 13, thus band flexible spring seat 14 compresses the spring 15 that circumference is arranged, and the driven disc 2 then promoting to be connected with secondary flywheel 3 rotates, and secondary flywheel 3 is rotated.As the relative torsional angle θ < 12 ° of elementary flywheel 1 and secondary flywheel 3, the all spring seat 14 of spring 15, spring 17 and spring 19, spring seat 16, gap between spring seat 18 and spring seat 20 are not complete by compression, 3 circumferential springs 15, spring 17 and spring 19 series operation, as shown in Figure 3, realize the transmission of first order torsional stiffness, now total torsional stiffness is K _{θ 1}; When angle θ=12 ° turned over, spring seat 14 contacts with spring seat 16, and spring 15 is no longer compressed.After this, start to realize the torsional stiffness transmission of the second level as shown in Figure 5, the scope of corner is: 12 ° of < θ≤35 °, and spring 17 and the spring 19 of circumference form series operation, and now total torsional stiffness is K _{θ 2}; When angle θ=35 ° turned over, spring seat 16 contacts with spring seat 18, only still has gap between spring seat 18 and spring seat 19.After this in process, only spring 19 works, and starts the torsional stiffness transmission realizing the third level, and now total torsional stiffness is K _{θ 3}, as shown in Figure 6, its angle range is: 35 ° of < θ≤45 °.As shown in Figure 7, the torque molded line of Fig. 7 is the same with the Fig. 1 in technical background for above-mentioned torque molded line, same exist to be suddenlyd change produced impact by rigidity.

Therefore, innovation of the present invention is to introduce compensation mechanism, make as relative torsional angle 7 °≤θ < 17 ° and 31 °≤θ < 40 °, the compensating torque be made up of 3 functions is produced respectively in AB section and CD section, compensating torque molded line and former torque molded line are respectively at A, B, C, D point continuous and derivable, thus achieve continuous variable-stiffness, avoid and to be suddenlyd change produced impact by rigidity, as shown in Figure 8.

As shown in Figure 9, compensation mechanism comprises pivot pin 5, needle bearing 6, guide rod 7, guide groove 8 and Returnning spring 9.Driven disc 2 is connected with secondary flywheel 3 by bolt 21, and pivot pin 5 is through needle bearing 6, and needle bearing 6 contacts with the inward flange (inward flange refers to the circular wall of elementary flywheel 1 near the inner side relatively large radius of cylindrical) of elementary flywheel 1.Four grooves radially arranged are laid with on secondary flywheel 3 and near cylindrical, guide groove 8 to insert in groove and with groove secure fit, one end of guide rod 7 is arranged on pivot pin 5 by jump ring 22, the other end puts in guide groove 8, Returnning spring 9 is arranged in guide groove 8, one end of Returnning spring 9 is pressed on guide rod 7, and the other end is pressed on the bottom of groove.

With the center O of elementary flywheel 1 for true origin sets up system of coordinates, the rule curved surface profile molded line parameter of the inward flange of elementary flywheel 1, as shown in Figure 10,11: wherein, MJAB, MJCD are respectively the compensating torque of AB, CD, ρ refers to the polar equation at the rule molded line using x-axis as initial position, R ₁it is the initial parameters that elementary flywheel 1 is given.The rule curved surface of the inward flange of elementary flywheel 1 molded line in system of coordinates the Ith quadrant is determined by such as under type:

1) with radius R ₁circular arc is drawn at 0 ° ~ 7 °;

2) by polar equation obtain AB section, wherein, K _bfor Returnning spring Line stiffness; θ _a=7 °, 7 ° of < θ≤17 °; M _jABaB section compensating torque, and

Wherein: a ₀, a ₁, a ₂and a ₃all by the compensating torque function parameter that Function Fitting obtains, a ₀=14.7, a ₁=-0.2, a ₂=0.3, a ₃=0; M ₁=K _{θ 1}θ (0≤θ < 12 °), M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), θ ₁=12 °, K _{θ 1}be torsional stiffness during three two groups circumference spring series connection, K _{θ 2}it is torsional stiffness during two two groups circumference spring series connection;

3) take OB as radius R ₂circular arc BC section is drawn at 17 ° ~ 31 °;

4) by polar equation $\mathrm{\&rho;}\left(\mathrm{\&theta;}\right)=R_1-\sqrt{{(R_1-R_2)}^2+\frac{1}{k_b}{\&Integral;}_{{\mathrm{\&theta;}}_c}^{\mathrm{\&theta;}}{M}_{\mathrm{JCD}}\left(\mathrm{\&theta;}\right)\mathrm{d\&theta;}}$ Obtain CD section, wherein θ _c=31 °, 31 °≤θ < 40 °, M _jCDcD section compensating torque, and

Wherein: b ₀, b ₁, b ₂and b ₃all by the compensating torque function parameter that Function Fitting obtains, b ₀=1496.7, b ₁=-109.66, b ₂=2.8321, b ₃=-0.0192; M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), M ₃=K _{θ 1}θ ₁+ K _{θ 2}(θ ₂-θ ₁)+K _{θ 3}(θ-θ ₂) (35 °≤θ≤40 °), θ ₁=12 °, θ ₂=35 °; K _{θ 3}for only having a torsional stiffness during spring works;

5) take OD as radius R ₃one section of circular arc is drawn at 40 ° ~ 90 °;

Explanation for penality function:

With 3 functions as compensating torque function

M _jAB=a ₀+ a ₁θ+a ₂θ ²+ a ₃θ ³(1) its torsional stiffness is

$\frac{{\mathrm{dM}}_{\mathrm{JAB}}}{\mathrm{d\&theta;}}=a_1+2a_2\mathrm{\&theta;}+3a_3{\mathrm{\&theta;}}^2---\left(2\right)$

The condition that AB section in Fig. 8 should meet is

Put A, some B torque be continuous, by formula (1):

$a_0+a_1{\mathrm{\&theta;}}_a+a_2{\mathrm{\&theta;}}_a^2+a_3{\mathrm{\&theta;}}_a^3=K_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_a---\left(3\right)$

$a_0+a_1{\mathrm{\&theta;}}_b+a_2{\mathrm{\&theta;}}_b^2+a_3{\mathrm{\&theta;}}_b^3=K_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_1+K_{\mathrm{\&theta;}2}({\mathrm{\&theta;}}_b-{\mathrm{\&theta;}}_1)---\left(4\right)$

Point A, some B rigidity continuous (torque tangent slope is equal), by formula (2):

$a_1+2a_2{\mathrm{\&theta;}}_a+3a_3{\mathrm{\&theta;}}_a^3=K_{\mathrm{\&theta;}1}---\left(5\right)$

$a_1+2a_2{\mathrm{\&theta;}}_b+3a_3{\mathrm{\&theta;}}_b^2=K_{\mathrm{\&theta;}2}---\left(6\right)$

Be made up of formula (3)-(6) with a ₀, a ₁, a ₂and a ₃for the fourth order linear equation group of parameter to be asked

$\left(\begin{array}{cccc}1& {\mathrm{\&theta;}}_a& {\mathrm{\&theta;}}_a^2& {\mathrm{\&theta;}}_a^3\\ 1& {\mathrm{\&theta;}}_b& {\mathrm{\&theta;}}_b^2& {\mathrm{\&theta;}}_b^3\\ 0& 1& 2{\mathrm{\&theta;}}_a& 3{\mathrm{\&theta;}}_a^2\\ 0& 1& 2{\mathrm{\&theta;}}_b& 3{\mathrm{\&theta;}}_b^2\end{array}\right)\left[\begin{array}{c}{a}_0\\ a_1\\ a_2\\ a_3\end{array}\right]=\left[\begin{array}{c}{K}_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_a\\ K_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_1+K_{\mathrm{\&theta;}2}({\mathrm{\&theta;}}_b-{\mathrm{\&theta;}}_1)\\ K_{\mathrm{\&theta;}1}\\ K_{\mathrm{\&theta;}2}\end{array}\right]---\left(7\right)$

Identical process is done to CD section, forms with b ₀, b ₁, b ₂and b ₃for the fourth order linear equation group of parameter to be asked

$\left(\begin{array}{cccc}1& {\mathrm{\&theta;}}_c& {\mathrm{\&theta;}}_c^2& {\mathrm{\&theta;}}_c^3\\ 1& {\mathrm{\&theta;}}_d& {\mathrm{\&theta;}}_d^2& {\mathrm{\&theta;}}_d^3\\ 0& 1& 2{\mathrm{\&theta;}}_c& 3{\mathrm{\&theta;}}_c^2\\ 0& 1& 2{\mathrm{\&theta;}}_d& 3{\mathrm{\&theta;}}_d^2\end{array}\right)\left[\begin{array}{c}{b}_0\\ b_1\\ b_2\\ b_3\end{array}\right]=\left[\begin{array}{c}{K}_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_1+K_{\mathrm{\&theta;}2}({\mathrm{\&theta;}}_c-{\mathrm{\&theta;}}_1)\\ K_{\mathrm{\&theta;}1}{\mathrm{\&theta;}}_1+K_{\mathrm{\&theta;}2}({\mathrm{\&theta;}}_2-{\mathrm{\&theta;}}_1)+K_{\mathrm{\&theta;}3}({\mathrm{\&theta;}}_d-{\mathrm{\&theta;}}_2)\\ K_{\mathrm{\&theta;}2}\\ K_{\mathrm{\&theta;}3}\end{array}\right]---\left(8\right)$

With Gaussian elimination solving equations (7) and (8) respectively, try to achieve a ₀, a ₁, a ₂and a ₃and b ₀, b ₁,

DE section: M=M ₃=K _{θ 1}θ ₁+ K _{θ 2}(θ ₂-θ ₁)+K _{θ 3}(θ-θ ₂) (40 °≤θ≤45 °)

The compensating torque function of double mass flywheel is (the compensating torque function parameter obtained by Function Fitting)

AB section:

CD section:

The rule curved surface of the inward flange of elementary flywheel 1 molded line in system of coordinates the IIth quadrant is by the mirror image of the Ith quadrant about Y-axis, the rule curved surface of the inward flange of elementary flywheel 1 molded line in system of coordinates the IIIth quadrant and the IVth quadrant by the Ith quadrant and the IIth quadrant mirror image about X-axis, as shown in figure 12.

The basic principle introducing compensating torque is as follows: the needle bearing 6 on secondary minute wheel 3 and the rule curved face contact on elementary flywheel 1, and needle bearing 6 forms sliding pair by guide rod 7 and guide groove 8, and guide groove 8 and secondary flywheel 3 are connected with interference fit form, owing to there being the existence of Returnning spring 9 bottom guide rod 7, needle bearing 6 and the rule Surface forming geometric constraint on elementary flywheel 1, because elementary flywheel 1 and secondary flywheel 3 relatively rotate, thus add extra moment of torsion, form compensated torque.Now the torsion molded line of flywheel and rigidity molded line all there occurs change, and the rigidity namely between two-stage is not undergone mutation, and torque molded line also becomes smooth.

When in the process of flywheel in high speed rotating, although the quality m1 of guide groove 8, Returnning spring 9 and needle bearing 6 is less, will produce large inertial force P1, this inertial force greatly exceed the directed force F K of spring.For this reason, the present invention works out balanced controls (inertia pendulum balanced controls), as shown in figure 13, balanced controls comprise strut 10, balancing pole 11 and equilibrium block 12, one end of strut 10 to be arranged in chute 4 and to be slidably matched with chute 4, and balancing pole 11 is fixed on the other end of strut 10, and one end and the guide rod 7 of balancing pole 11 are hinged, equilibrium block 12 is fixed on the other end of balancing pole 11, and balancing pole 11 is parallel with the surface of secondary flywheel 3 along the circle distribution of secondary flywheel 3.

As shown in Figure 14 and Figure 15, A is elementary flywheel, B is secondary flywheel, its center of rotation is at O point, and set flywheel turns angular velocity as ω, the quality of guide groove 8, Returnning spring 9 and needle bearing 6 is m1, and its barycenter is at O1 point, the track of the center O3 point of chute 4 is take O as the center of circle, and RO3 is the circular arc of radius.D1=LO1O3 is determined according to structure, O1O3 opposite direction, apart from O3 be d2 be equilibrium block, its quality is m2, d2=LO2O3, and meeting d1 × m1=m2 × d2, the sketch of this mechanism is actual is a slide-block mechanism, as shown in figure 16, ω is the angular velocity of flywheel turns, and L1, L2 are respectively inertial force P1, P2 perpendicular distance to line of force.

What finally illustrate is, above embodiment is only in order to illustrate technological scheme of the present invention and unrestricted, although with reference to preferred embodiment to invention has been detailed description, those of ordinary skill in the art is to be understood that, can modify to technological scheme of the present invention or equivalent replacement, and not departing from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of right of the present invention.

Claims (1)

1. based on the multistage double mass flywheel of compensation principle, this multistage double mass flywheel is three grades of segmentation variation rigidity double mass flywheels, comprise elementary flywheel (1), driven disc (2) and secondary flywheel (3), driven disc (2) is connected with secondary flywheel (3) and is arranged in elementary flywheel (1), upper and be laid with two compensation mechanisms near cylindrical at secondary flywheel (3), secondary flywheel (3) is upper and be laid with two grooves radially arranged near cylindrical;

Described compensation mechanism comprises pivot pin (5), needle bearing (6), guide rod (7), guide groove (8) and Returnning spring (9); Described pivot pin (5) is through needle bearing (6), and needle bearing (6) contacts with the inward flange of elementary flywheel (1); Described guide groove (8) to insert in groove and with groove secure fit, one end of described guide rod (7) is connected with pivot pin (5), the other end puts in guide groove (8), described Returnning spring (9) is arranged in guide groove (8), one end of Returnning spring (9) is pressed on guide rod (7), and the other end is pressed on the bottom of groove;

Be that true origin sets up system of coordinates with the center O of elementary flywheel (1), the rule curved surface of the inward flange of described elementary flywheel (1) molded line in system of coordinates I quadrant is determined by such as under type, wherein R ₁the initial parameters that elementary flywheel (1) is given:

1) with radius R ₁circular arc is drawn at 0 ° ~ 7 °;

2) by polar equation obtain AB section, wherein, K _bfor Returnning spring Line stiffness; θ _a=7 °, 7 ° of < θ≤17 °; M _jABaB section compensating torque, and

Wherein: a ₀, a ₁, a ₂and a ₃all by the compensating torque function parameter that Function Fitting obtains, a ₀=14.7, a ₁=-0.2, a ₂=0.3, a ₃=0; M ₁=K _{θ 1}θ (0≤θ < 12 °), M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), θ ₁=12 °, K _{θ 1}be torsional stiffness during three two groups circumference spring series connection, K _{θ 2}it is torsional stiffness during two two groups circumference spring series connection;

3) take OB as radius R ₂circular arc BC section is drawn at 17 ° ~ 31 °;

4) by polar equation $\mathrm{\&rho;}\left(\mathrm{\&theta;}\right)=R_1-\sqrt{{(R_1-R_2)}^2+\frac{1}{k_b}{\&Integral;}_{{\mathrm{\&theta;}}_c}^{\mathrm{\&theta;}}{M}_{\mathrm{JCD}}\left(\mathrm{\&theta;}\right)}\mathrm{d\&theta;}$ Obtain CD section, wherein θ _c=31 °, 31 °≤θ < 40 °, M _jCDcD section compensating torque, and

Wherein: b ₀, b ₁, b ₂and b ₃all by the compensating torque function parameter that Function Fitting obtains, b ₀=1496.7, b ₁=-109.66, b ₂=2.8321, b ₃=-0.0192; M ₂=K _{θ 1}θ ₁+ K _{θ 2}(θ-θ ₁) (12 °≤θ < 35 °), M ₃=K _{θ 1}θ ₁+ K _{θ 2}(θ ₂-θ ₁)+K _{θ 3}(θ-θ ₂) (35 °≤θ≤40 °), θ ₁=12 °, θ ₂=35 °; K _{θ 3}for only having a torsional stiffness during spring works;

5) take OD as radius R ₃one section of circular arc is drawn at 40 ° ~ 90 °;

The rule curved surface of the inward flange of described elementary flywheel (1) molded line in system of coordinates the IIth quadrant is by the molded line of the Ith quadrant about the mirror image of Y-axis, and the molded line in the IIIth quadrant and the IVth quadrant is by the Ith quadrant and the IIth quadrant molded line mirror image about X-axis.