阅读说明：本技术 一种耗能弹簧复合颗粒阻尼器 (Energy-consuming spring composite particle damper ) 是由 邵建红 黄浩 王驰明 于 2021-07-21 设计创作，主要内容包括：本发明公开了一种耗能弹簧复合颗粒阻尼器,包括阻尼筒体和置于所述阻尼筒体内的弹簧挡板,所述弹簧挡板将所述阻尼筒体内部分隔成容动腔体和阻尼腔体,且弹簧挡板能够沿着所述阻尼筒体内部运动以改变所述容动腔体和所述阻尼腔体的大小；容动腔体中设置有阻尼弹簧,阻尼腔体内放置阻尼颗粒；还包括阻尼杆,阻尼杆的一端部从阻尼筒体靠近容动腔体的端面穿入到容动腔体,然后穿设在弹簧挡板中,且该端能够穿过弹簧挡板后进入到所述阻尼腔体中；位于阻尼筒体外部的所述阻尼杆套设有回杆弹簧。当外界振动或冲击力通过阻尼杆传递到阻尼器时,由弹簧k1和弹簧k2共同承担振动或冲击力,快速消耗其振动或冲击力,有效控制振动,工程应用价值较高。(The invention discloses an energy-consuming spring composite particle damper, which comprises a damping cylinder and a spring baffle arranged in the damping cylinder, wherein the spring baffle divides the inside of the damping cylinder into a capacity cavity and a damping cavity, and the spring baffle can move along the inside of the damping cylinder to change the sizes of the capacity cavity and the damping cavity; a damping spring is arranged in the containing cavity, and damping particles are placed in the damping cavity; the damping cylinder is characterized by also comprising a damping rod, wherein one end part of the damping rod penetrates into the movable accommodating cavity from the end surface, close to the movable accommodating cavity, of the damping cylinder and then penetrates into the spring baffle plate, and the end part of the damping rod can penetrate through the spring baffle plate and then enters into the damping cavity; and a rod return spring is sleeved on the damping rod positioned outside the damping cylinder. When external vibration or impact force is transmitted to the damper through the damping rod, the spring k1 and the spring k2 bear the vibration or impact force together, the vibration or impact force is consumed rapidly, vibration is controlled effectively, and the engineering application value is high.)

1. The composite particle damper of the energy dissipation spring is characterized in that: the damping cylinder is characterized by comprising a damping cylinder body (4) and a spring baffle (5) arranged in the damping cylinder body (4), wherein the spring baffle (5) divides the inside of the damping cylinder body (4) into a containing and moving cavity (41) and a damping cavity (42), and the spring baffle (5) can move along the inside of the damping cylinder body (4) to change the sizes of the containing and moving cavity (41) and the damping cavity (42);

a damping spring (3) is arranged in the containing cavity (41), and damping particles (6) are placed in the damping cavity (42);

the damping device is characterized by further comprising a damping rod (1), wherein one end of the damping rod (1) penetrates into the movable accommodating cavity (41) from the end face, close to the movable accommodating cavity (41), of the damping cylinder (4), then penetrates into the spring baffle (5), and can penetrate through the spring baffle (5) and then enter into the damping cavity (42);

the damping rod (1) located outside the damping cylinder (4) is sleeved with a rod returning spring (2).

2. The dissipative spring composite particle damper according to claim 1, wherein: a gap A exists between the spring baffle (5) and the inner wall of the damping cylinder (4), a gap B exists between the damping rod (1) and the spring baffle (5), and the diameter of the damping particles (6) is far larger than the gap A and the gap B.

3. The dissipative spring composite particle damper according to claim 2, wherein: one end of the damping spring (3) is abutted against the spring baffle (5), and the other end of the damping spring is abutted against the upper wall of the movable cavity (41).

4. The dissipative spring composite particle damper according to claim 3, wherein: the damping rod (1) stretches into the end part in the damping cavity (42) is provided with a hammer head (11), and the hammer head (11) is always positioned in the damping cavity (42) in the motion process.

5. The dissipative spring composite particle damper according to claim 4, wherein: a stop block (12) is fixed at the outer end part of the damping rod (1), one end part of the rod returning spring (2) is abutted against the stop block (12), and the other end of the rod returning spring is abutted against the outer wall of the damping cylinder body (4).

6. The dissipative spring composite particle damper according to claim 5, wherein: the integral rigidity coefficient k of the damper satisfies a formula I:

wherein K1 is the stiffness coefficient of the return spring (2), and K2 is the stiffness coefficient of the damper spring (3).

7. The dissipative spring composite particle damper according to claim 6, wherein: the damping force F of the damper is calculated by the formula II:

wherein the content of the first and second substances,is the motion speed of the damping rod (1), c is the damping coefficient, and the negative sign is the damping force and the motion speedIn the opposite direction, alpha is the correction factor, f_PP is the pressure exerted by the spring on the dampening particles (6), which is the coefficient of friction of the dampening particles (6) under spring pressure.

8. The dissipative spring composite particle damper according to claim 7, wherein: the motion displacement x of the damping rod (1) is calculated by a formula III:

wherein m is the weight of the damping rod (1), c is the damping coefficient, and k is the overall stiffness coefficient of the damper，Is the acceleration of the damping lever (1),refers to the movement speed of the damping rod (1);

in addition, m, c, and k satisfy the following formulas four and five:

wherein the content of the first and second substances,for a dimensionless damping ratio of the system, ω_nIs the natural frequency of the damping rod (1);

solving the formula three to obtain a formula six:

wherein x is the solved displacement of the damping rod (1), A₁And A₂Is the initial condition.

9. The dissipative spring composite particle damper according to claim 8, wherein: the damping particles (6) adopt particles or powder with 2 or more different diameters.

Technical Field

The invention relates to a damper, in particular to an energy-consuming spring composite particle damper.

Background

The hydraulic damper has excellent vibration damping and shock resistance, and the resistance provided by the hydraulic oil consumes the motion energy brought by vibration and shock, so that the safety of the equipment under severe environment conditions is protected. However, the problems of leakage of hydraulic oil, blockage of a hydraulic damping hole, deterioration of the deterioration performance of the hydraulic oil and the like caused by aging of a sealing rubber part are easily caused under the influence of a working environment, and the vibration of low amplitude high frequency or high amplitude low frequency cannot be effectively controlled.

Disclosure of Invention

In order to solve the defects of the prior art, the invention provides the energy-consuming spring composite particle damper, when external vibration or impact force is transmitted to the damper through the damping rod, the spring k1 and the spring k2 bear the vibration or impact force together, the vibration or impact force is consumed rapidly, the vibration is controlled effectively, the cost is low, and the engineering application value is high.

In order to achieve the technical purpose, the invention adopts the following technical scheme: an energy-consuming spring composite particle damper comprises a damping cylinder and a spring baffle arranged in the damping cylinder, wherein the spring baffle divides the inside of the damping cylinder into a containing cavity and a damping cavity, and the spring baffle can move along the inside of the damping cylinder to change the sizes of the containing cavity and the damping cavity;

a damping spring is arranged in the containing cavity, and damping particles are placed in the damping cavity;

the damping cylinder is characterized by further comprising a damping rod, one end of the damping rod penetrates into the containing and moving cavity from the end face, close to the containing and moving cavity, of the damping cylinder and then penetrates into the spring baffle, and the end of the damping rod can penetrate through the spring baffle and then enters into the damping cavity;

and a rod return spring is sleeved on the damping rod positioned outside the damping cylinder.

Further, a gap A exists between the spring baffle and the inner wall of the damping cylinder, a gap B exists between the damping rod and the spring baffle, and the diameter of the damping particles is far larger than the gap A and the gap B.

Furthermore, one end of the damping spring is abutted against the spring baffle, and the other end of the damping spring is abutted against the upper wall of the containing cavity.

Furthermore, the end part of the damping rod extending into the damping cavity is provided with a hammer head, and the hammer head is always positioned in the damping cavity in the motion process.

Furthermore, a stop block is fixed at the outer end part of the damping rod, one end part of the rod returning spring is abutted against the stop block, and the other end of the rod returning spring is abutted against the outer wall of the damping cylinder.

Further, the overall stiffness coefficient k of the damper satisfies the formula one:

and, k₁＜k₂，；

Wherein K1 is the rate of stiffness of the return spring and K2 is the rate of stiffness of the damping spring.

Further, the damping force F of the damper is calculated by formula two:

and c is α · f_P·P，；

Wherein the content of the first and second substances,is the motion speed of the damping rod, c is the damping coefficient, and the negative sign is the damping force and the motion speedIn the opposite direction, alpha is the correction factor, f_PP is the pressure exerted by the spring on the dampening particles, which is the coefficient of friction of the dampening particles under the spring pressure.

Further, the motion displacement x of the damping rod is calculated by the formula three:

wherein m is the weight of the damping rod, c is the damping coefficient, k is the overall stiffness coefficient of the damper,is the acceleration of the damping rod or rods,refers to the motion speed of the damping rod;

in addition, m, c, and k satisfy the following formulas four and five:

wherein the content of the first and second substances,for a dimensionless damping ratio of the system, ω_nIs the natural frequency of the dampening bar;

solving the formula three to obtain a formula six:

wherein x is the solved displacement of the damping rod, A₁And A₂Is the initial condition.

Further, the damping particles are particles or powder with 2 or more different diameters.

In conclusion, the invention achieves the following technical effects:

1. the composite blocking type damper is adopted, the damping rod is directly connected with the equipment, the damping cylinder is connected with the base, when external vibration or impact force is transmitted to the damper through the damping connecting rod, the spring k1 and the spring k2 bear the vibration or impact force together, and in addition, the vibration or impact force is quickly consumed under the damping influence generated by damping particle materials;

2. the damping material is influenced by the action of the spring k2 and the spring baffle, when the damping rod extrudes the damping cavity under the action of vibration or impact, stronger damping force can be generated due to the change of the shape, and the vibration or impact energy is converted into heat energy, collision energy and the like to be dissipated;

3. compared with the scheme that the hydraulic shock absorber adopts hydraulic oil filled inside, the hydraulic shock absorber is filled with particles or powder materials inside, the structural sealing requirement and the manufacturing cost are reduced, and the problems of aging, leakage, blockage, deterioration and the like of a sealing element are effectively reduced;

4. the internal damping rod and the damping particle are made of stainless steel materials, and are replaced after being worn, so that the whole structure is simple and easy to maintain;

5. the invention reduces the manufacturing cost of the hydraulic damper and reduces the maintenance workload.

Drawings

FIG. 1 is a schematic view of a damper provided by an embodiment of the present invention;

FIG. 2 is a damping curve corresponding to a single particle size;

fig. 3 is a damping curve corresponding to graded particles.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings.

The present embodiment is only for explaining the present invention, and it is not limited to the present invention, and those skilled in the art can make modifications of the present embodiment without inventive contribution as needed after reading the present specification, but all of them are protected by patent law within the scope of the claims of the present invention.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

Example (b):

as shown in fig. 1, the damper comprises a damping cylinder 4 and a spring baffle 5 disposed in the damping cylinder 4, wherein the spring baffle 5 divides the inside of the damping cylinder 4 into a movable cavity 41 and a damping cavity 42, and the spring baffle 5 can move along the inside of the damping cylinder 4 to change the size of the movable cavity 41 and the damping cavity 42.

The damping cylinder 4 may be cylindrical, square, or irregular, and since the spring baffle 5 is moved in the inner space of the damping cylinder 4 in this embodiment, the shape of the spring baffle 5 is matched with the inner shape of the cylinder. However, for the convenience of installation and the aesthetic property of the damper, a cylindrical structure is generally adopted, the upper end of the damper, that is, the stop 12 of the damping rod 1 in fig. 1, is fixed at the lower end of the object to be damped, and the lower end of the damping cylinder 4 is fixed, so that the damper can be used.

Still include damping rod 1, damping rod 1's an end from damping barrel 4 is close to the terminal surface of holding movable cavity 41 and penetrates holding movable cavity 41, then wears to establish in spring damper 5, and this end can pass spring damper 5 and enter into in the damping cavity 42 behind. The end part of the damping rod 1 extending into the damping cavity 42 is provided with a hammer head 11, and the hammer head 11 is always positioned in the damping cavity 42 in the movement process.

Initially, a through hole is formed at the upper end of the cylinder body for the damping rod 1 to pass through, and a through hole is formed in the spring baffle 5 for the damping rod 1 to pass through. The clearance between damping rod 1 and these two through-holes is minimum, is being close to under the prerequisite of guaranteeing the motion and forms sealed state, and this clearance as long as guarantee the granule not pass through can, compare with liquid damping, this device is low to sealed requirement, need not use the rubber spare, does not leak the jam scheduling problem.

The spring baffle 5 and the cylinder body are not fixedly connected, so that the spring baffle 5 can move to increase the capacity movement cavity 41 and reduce the damping cavity 42, or reduce the capacity movement cavity 41 and increase the damping cavity 42.

A gap A exists between the spring baffle 5 and the inner wall of the damping cylinder 4, a gap B exists between the damping rod 1 and the spring baffle 5, and the diameter of the damping particles 6 is far larger than the gap A and the gap B, so that the particles are prevented from flowing into the movable cavity 41 from the two gaps, and the particles are ensured to move only in the damping cavity 42.

Move and be provided with damping spring 3 in the cavity 41, damping spring 3's one end butt spring damper 5, the upper wall that cavity 41 was moved to the other end butt, when spring damper 5 (the extrusion of damped granule 6) went upward, compression damping spring 3, when damping granule 6 loses power and does not extrude spring damper 5, damping spring 3 tension extrusion spring damper makes its down recovery to initial condition with spring damper 5 extrusion. Because after the granule loses power (lose power and be referred to and lose damping rod 1 application of force), the granule can not reply initial condition by oneself, and also can not all fall by oneself, and make the surface unevenness of granule, damping spring 3 loses the extrusion back of granule, utilizes the tension of self to extrude the spring baffle downwards for the whole grain surface that flattens that descends of spring baffle, reaches initial condition.

In addition, the stiffness of the damping spring 3 is different, the tension applied to the spring baffle 5 is different, the descending speed and the descending force of the spring baffle 5 are influenced, the speed and the descending force of the particles are also influenced, and the friction force of the particles is also influenced in combination with the mutual extrusion of the particles during the recovery.

The damping spring 3 may be: the first type is a form structure sleeved outside the damping rod 1, and the second type is a form structure arranged on the side edge of the damping rod 1. Fig. 1 shows a first form of the damping rod 1, which is sleeved on the outside, but a second form of the damping rod 1 can be selected, in which the damping spring 3 is divided into a plurality of sub-springs around the damping rod 1 for the balance of the spring baffle force. The first type of damping spring 3 has a stiffness coefficient that is the spring's own stiffness coefficient, and the second type of damping spring has a combined stiffness coefficient in which a plurality of sub-springs are combined. In either form, there is a rate K2 of the damping spring 3.

Damping particles 6 are placed in the damping cavity 42, the particles are limited in the damping cavity 42 by the aid of the spring baffle 5 and the hammer 11, when the damping rod 1 is stressed, the hammer 11 moves along with the damping rod to extrude into the particles, and the particles are compact in an initial state, so that the hammer 11 enters the damping cavity to enable potential energy of the hammer 11 to be converted into frictional energy among the particles through collision, extrusion and friction among the particles, namely the potential energy is converted into internal energy, the kinetic energy of the hammer 11 is consumed, and a damping effect is achieved.

In this process, tup 11 gets into damping cavity 42, collide between the granule, the extrusion, the friction, when tup 11 continues to get in, the collision between the granule increases, thereby upwards (the direction shown in the figure) extrusion spring baffle 5, the bottom side of spring baffle 5 receives the extrusion of granule, the upside receives damping spring 3's tension, the extrusion power of granule is greater than damping spring 3's tension, make spring baffle 5 go upward under the extrusion of granule, make damping cavity 42 increase, it reduces to hold movable cavity 41, at this moment, relative motion takes place between spring baffle 5 and the damping rod 1, spring baffle 5 goes upward extrusion damping spring 3, make damping spring 3 compress, in this process, the granule converts the kinetic energy into internal energy, realize the conversion of energy. When the vibration disappears, namely the hammer head 11 moves upwards, the particles are loosened and fall down, the tension of the damping spring 3 is greater than the friction force of the particles, and the spring baffle 5 starts to move downwards to flatten the particles to restore to the initial state.

The stiffness of the damping spring 3 is adjustable. In the process, it can also be seen that the stiffness of the damping spring 3 also affects the upward speed, the upward force and the upward displacement of the spring baffle 5, when the stiffness coefficient of the damping spring 3 increases, the downward force applied to the spring baffle 5 by the damping spring also increases, the upward extrusion force of the particles on the spring baffle 5 needs to consume a part of the force to offset the force of the damping spring 3, and the upward extrusion operation on the spring baffle 5 is performed after the upward extrusion force is offset, so that the stiffness coefficient of the damping spring 3 increases, the force for offsetting increases, and the remaining force for making the spring baffle 5 rise decreases, and thus, the spring baffle 5 presses the particles more tightly, the stress increases, and the damping force also increases. Therefore, the rigidity of the damping spring 3 is adjusted, the damping force among particles can be changed, and the damping force of the whole device can be changed.

The design of the hammer head 11 directly influences the magnitude of the damping force, in the invention, the design of different damping rods can be adopted, including but not limited to a symmetrical smooth structure, a bullet structure, a piston disc structure and other structures, different structures provide different damping effects, the damping magnitude and the rod structure have a direct relation, and the damping magnitude can be selected according to actual conditions.

In the present embodiment, the hammer head 11 takes the form of a cone.

The damping rod 1 positioned outside the damping cylinder 4 is sleeved with a rod returning spring 2. The outer tip of damping rod 1 is fixed with dog 12, and one end butt dog 12 of returning the pole spring 2, the other end butt damping barrel 4 outer walls, when damping rod 1 went down to accomplish the shock attenuation and need go upward to reset, returns pole spring 2 tension and acts on the top with dog 12 for damping rod 1 resets.

On one hand, in the embodiment, the two springs are used for providing damping force for friction between the particles and the damping rod to form a double-spring structure of the damper, the two springs are used for decoupling the stiffness coefficient and the damping coefficient, and a moving system is converted into a mathematical system, so that the dynamic characteristics are more clear, and various dynamic working condition requirements can be met during actual use design.

In the present embodiment, the overall stiffness coefficient k of the entire damper satisfies the formula one:

where K1 is the rate of stiffness of the return spring 2, and K2 is the rate of stiffness of the damper spring 3.

The rigidity of the K1 is less than that of the K2, and the type, the rigidity and the like of the spring are selected according to the vibration reduction or the impact force.

The structure of the double springs can give consideration to damping and load at the same time, the double springs provide damping force for particles, and the requirement of large load can be met according to selection of different stiffness. The existing damping is generally a single-spring structure, and cannot give consideration to damping and load. The springs provide rigidity for the structure, the upper springs provide rebound rigidity required by the buffer, and the lower springs provide pre-pressure required by damping, so that the damping effect of the structure is improved. The two springs are matched, and the damping and the load can be simultaneously considered.

On the other hand, the damping particles 6 are particles or powders of 2 or more different diameters. In order to make the damping characteristic of particle damping smoother, the invention adopts particle grading selection and selects one or more particles with different particle diameters, so that the damping characteristic curve of the damper is smoother and the optimal damping effect is exerted.

The diameter of the damping particles 6 is between 0.01mm and 2mm, and stainless steel is selected.

Several different collocation options are given below:

single particle: as shown in table 1 below:

particle size	0.1	0.2	0.3	0.5	0.8	1	1.2	1.5	1.6	1.8	2
												Damping ratio	0.01	0.02	0.04	0.03	0.025	0.02	0.015	0.013	0.012	0.008	0.006

The damping ratios corresponding to different particle diameters are different, the damping ratios corresponding to particles with different particle diameters are shown in the figure, as shown in figure 2, the curve corresponding to table 1 is shown, the horizontal axis is the unit of the particle diameter of the particles is mm, the vertical axis is the damping ratio, as can be seen from the figure, the damping ratio reaches the peak when the particle diameter is about 0.3mm, and the damping ratio is larger between 0.2 and 1 mm.

Grading particles:

as shown in table 2 below:

grading	30％2mm+70％0.5mm	30％2mm+70％0.8mm	30％2mm+70％1.0mm	30％1mm+70％0.5mm	30％1mm+70％0.8mm
						Damping ratio	0.035	0.031	0.025	0.037	0.042

The invention provides a grading mode, wherein grading is the matching selection of 2 or more different diameter particles, the first mode is a 30% matching mode of 2mm + 70% and 0.5mm, the matched damping ratio is 0.035, the second mode is 30% 2mm + 70% 0.8mm, the matched damping ratio is 0.031, the third mode is 30% 2mm + 70% 1.0mm, the matched damping ratio is 0.025, the fourth mode is 30% 1mm + 70% 0.5mm, the matched damping ratio is 0.037, the fifth mode is 30% 1mm + 70% 0.8mm, and the matched damping ratio is 0.042.

In the embodiment, 2 different diameters are selected for grading matching, wherein the proportion of the larger diameter is 30%, the proportion of the smaller diameter is 70%, the gap with the large diameter can be filled with the small diameter, and the damping ratio is improved during friction collision.

FIG. 3 is a graph corresponding to the above Table 2, and it can be seen from FIGS. 2 and 3 that the damping ratio in FIG. 2 is between 0.02 and 0.04 for a damping ratio between 0.2 and 1mm of a single particle, the damping ratio in any one of the grading modes in FIG. 3 is above 0.025 or even reaches 0.042, and the damping ratio in the grading mode is substantially above the damping ratio in the single particle, and the diameter of the grading mode can be selected in a wide range, while the single particle with a large damping ratio can be selected only between 0.2 and 1mm of a particle.

After determining the particle selection, the damping force F of the damper is calculated by equation two:

wherein the content of the first and second substances,is the motion speed of the damping rod 1, c is the damping coefficient, and the negative sign is the damping force and the motion speedIn the opposite direction, alpha is the correction factor, f_PTo be the coefficient of friction of the dampening particles 6 under spring pressure, P is the pressure exerted by the spring on the dampening particles 6.

In the above formula, according to the known alpha and f_PAnd P, calculating the damping coefficient c, and calculating the damping coefficient according to the known c,The damping force F can be found.

The motion displacement x of the damping rod 1 is calculated by the formula three:

the above is the differential equation of motion of the system, where m is the weight of the damping rod 1, c is the damping coefficient, k is the overall stiffness coefficient of the damper,in order to damp the acceleration of the rod 1,refers to the motion speed of the damping rod 1, and x refers to the motion displacement of the damping rod 1;

in addition, m, c, and k satisfy the following formulas four and five:

wherein the content of the first and second substances,for a dimensionless damping ratio of the system, ω_nIs the natural frequency of the damping rod 1;

solving the formula three to obtain a formula six:

wherein x is the solved displacement of the damping rod 1, A₁And A₂The value of (c) is determined by the initial conditions.

For the displacement x after solving, the first-order derivation yields the velocitySecond order derivation to obtain accelerationThe motion trajectory can be seen, summarizing the characteristics of the damper.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not intended to limit the present invention in any way, and all simple modifications, equivalent variations and modifications made to the above embodiments according to the technical spirit of the present invention are within the scope of the technical solution of the present invention.