Vibration isolator

FIELD: machine building.

SUBSTANCE: invention relates to devices of vibroprotective engineering. Vibration isolator contains the first and the second basis, bearing resilient element and damper, fixed between basis, control assembly, stiffness corrector, displacement pickup and electromagnet. Damper is implemented in the form of goffered cylinder, in butt of which it is installed throttle and built-in the second electric valve. The second electric valve is connected to the second outlet of control assembly. Stiffness corrector consists of hydraulic cylinder with piston and rod and two springs, installed inside the "П"-shaped frame. Over- and under-piston cavities of hydraulic cylinder are connected by channel with built-in the first electric valve, connected to the first outlet of control assembly. Rod is pivotally fixed on the first basis, and ends of springs - on casing of hydraulic cylindera and on "П"-shaped frame. Displacement pickup is installed on the first basis and is connected to inlet of control assembly. Electromagnet is fixed on "П"-shaped frame and is connected to the third outlet of control assembly. Limb of magnet is connected by rod to casing of hydraulic cylinder.

EFFECT: there is achieved reliability growth of vibration isolator and effectiveness of objects protection against force impact by means of reduction of number of switching of stiffness corrector.

3 dwg

 

Vibration absorber relates to a device vibration protection technology and is designed to protect objects against the force of the impact, in particular, can be used in overhead cranes to reduce dynamic loads (reactions), the perceived load-bearing structures.

Known vibration absorber [1], containing the first Foundation intended for connection with a source of dynamic loads, the second basis intended for communication with the object of carrying the elastic element and the inertial damper mounted between the bases, and concealer rigidity, made in the form attached at the second base of the U-shaped frame, within which two springs associated with the inertial damper.

Minimum total bearing stiffness of the elastic element and springs corrector rigidity can be ensured only if a specific - custom - average (threshold) value of the applied force. If the threshold value of force differs from custom, the total rigidity of the insulator is increased and the efficiency of protection of the object from the periodic component of the force is reduced. In addition, the inertial damper permanently incorporated into the work, and through him, the periodic component of the force acts on the second substrate and respectively on the object.

Closest to the proposed insulator p the technical essence and the achieved result is vibration absorber [2], containing the first Foundation intended for connection with a source of dynamic loads, the second basis intended for communication with the object of carrying the elastic element and a damper mounted between the bases, the control unit, concealer rigidity, consisting of a hydraulic cylinder with a piston and rod and two springs mounted inside the U-shaped frame, and a displacement transducer mounted on the first substrate and connected to the input of the control unit, and over - and podpisniye cavity of the hydraulic cylinder are connected by a channel with a built-in first solenoid connected to the first output of the control unit.

The disadvantage of this insulator is that under the action of a periodic force reduction in the total stiffness of the load bearing elastic element and a spring is provided only when the three switches corrector rigidity for the period effect. When such an intense work of the insulator, when the spring corrector stiffness alternately form the compensatory effect of reducing the dynamic loads experienced by the object, increases the probability of failure of the control system. The damper, which turns on and off from time corrector stiffness, the periodic component of the force transmitted to the second base and the COO is responsible for the object. All this reduces the reliability of the insulator and the effectiveness of protection against forced entry.

The problem to which the invention is directed, is to increase the reliability of the insulator and the protection of objects against the force of the impact by reducing the number of switching corrector stiffness.

This vibration absorber containing the first Foundation intended for connection with a source of dynamic loads, the second basis intended for communication with the object of carrying the elastic element and a damper mounted between the bases, the control unit, concealer rigidity, consisting of a hydraulic cylinder with a piston and rod and two springs mounted inside the U-shaped frame, and a displacement transducer mounted on the first substrate and connected to the input of the control unit, and over - and podpisniye cavity of the hydraulic cylinder are connected by a channel with a built-in first solenoid connected to the first output of the control unit is further provided with an electromagnet mounted on the U-shaped frame, the damper is made in the form of a corrugated cylinder, the end of which has a throttle and built the second valve, and a rod pivotally mounted on the first base, and the ends of the springs on the housing of the hydraulic cylinder and the U-shaped frame, the CE shall Technik electromagnet is connected by a rod with the housing of the hydraulic cylinder, a second solenoid connected to the second output of the control unit, and an electromagnet connected to the third output of the control unit.

Figure 1 shows a General view of the insulator; figure 2 is a hydraulic cylinder with piston and piston rod, and a channel with a built-in first electrovalve (type a); figure 3 - graph of force (a) and schedule dynamic load (reaction), perceived second base (b).

Vibration absorber contains the first base 1, the second base 2 carrying the elastic element 3 and the damper 4 is fixed between the first and second bases 1, 2, concealer hardness 5, the electromagnet 6, the control unit 7 and the displacement sensor 8 mounted on the front of the base 1 and is connected to the input of the control unit 7.

The damper 4 is made in the form of a corrugated cylinder 9, the end of which has a throttle 10 and built a second solenoid 11.

Concealer hardness 5 consists of a hydraulic cylinder 12 with a piston 13 and rod 14, the two springs 15, 16 and a U-shaped frame 17, which is fixed on the second base 2.

Over - and podpisniye cavity of the hydraulic cylinder 12 is connected by a channel 18 with a built-in first solenoid 19. The rod 14 pivotally mounted on the first base 1. Springs 15, 16 pre-compressed, and their ends pivotally attached to the housing of the hydraulic cylinder 12 and the U-shaped frame is 17.

The first solenoid 19 is connected to the first output control unit 7. The second solenoid 11 is connected to the second output control unit 7.

The electromagnet 6 is fixed on the U-shaped frame 17 and is connected to the third output control unit 7. The core 20 of the electromagnet 6 is connected via a rod 21 with the housing of the hydraulic cylinder 12.

The first base 1 is intended for connection with a source of dynamic loads 22 and the second base 2 is intended for communication with the object 23.

Vibration absorber works as follows.

The source of dynamic loads 22 creates a force

where R0- threshold value force; R1the amplitude of the periodic component of the force; ω is the frequency; τ is the duration of the transition cycle.

This force causes movement of the first substrate 1. When the displacement sensor 8 generates an electrical signal U0that is input to the control unit 7. If a force is absent, the first base 1 is not moved, and the signal U0=0.

The control unit 7 generates control signals

The signals U1U2U3served respectively by the first solenoid 19, the second solenoid 22 and the electromagnet 6.

If power attack is ie is absent and the signal U 0=0, the signals U1=0, U2=0, U3=U30.

Implemented a standby mode of operation of the vibration damper.

The first solenoid 19 is de-energized (U1=0) and opens the channel 18, which connects the cavity of the hydraulic cylinder 12.

The second solenoid 11 is de-energized (U2=0) and eliminates the flow through it of air from the environment into the cavity corrugated cylinder 12 and Vice versa.

Under the influence of the signal U3=U30the electromagnet 6 is activated and locks the position of the hydraulic cylinder 12 relative to the second base 2 (the core 20 is connected by a rod 21 with the housing of the hydraulic cylinder 12, is pulled into the coil of an electromagnet 6). Thus the springs 15, 16 corrector hardness 5 are in a horizontal position (figure 1).

On the first cycle transition, when the force increases (P(t)≤P0), the conditions U0≠0 and 0<t<τ. The signals at the output of the control unit 7 does not change, i.e. U1=0, U2=0, U3=U30,and accordingly, the damper 4 is included in the work, and concealer hardness 5 - off from work.

The first base 1 and the rod 14 with the piston 13 is moved down.

The electromagnet 6 fixes the position of the hydraulic cylinder 12 relative to the U-shaped frame 17, and the springs 15, 16 remain in a horizontal position. The channel 18 is open, and when cm is the incarnation of the piston 13, the working fluid flows freely through the channel 18 from one cavity of the hydraulic cylinder 12 in another, not preventing, respectively, the displacement of the rod 14 and the first substrate 1 relative to the second base 2 (corrector hardness 5 off from work).

Corrugated cylinder 12 is compressed. The air pressure increases and the air flow passing through the throttle 10, creates a dissipative force, which reduces the acceleration of the first substrate 1 and the source of dynamic loads 22 (damper 4 is included in the work). This ensures the reduction of inertial force, which is transmitted to the second base 2 and, accordingly, on the 23rd through the base of the elastic element 3 and the damper 4. Accordingly, at the end of the first transition series of dynamic load (reaction R(t)), the perceived object 23, will be almost equal to the threshold value of the force R0≈R0.

In the main loop, when the force reaches a threshold (P(t)=P0) and has a periodic component of P1sin(ωt), the conditions U0≠0, t>τ, and the output control unit 7 generates signals U1=U10U2=

U20U3=0.

The periodic component of the force causes fluctuations of the first substrate 1 and the source of dynamic loads 22.

Under the influence of the signal U2=U20the second solenoid 11 is activated and ensures free flow through it of air surround the it environment in the cavity corrugated cylinder 9 and Vice versa. As a result, the damper 4 is turned off from work, and through him, the periodic component of the force is not transmitted to the second base 2 and, accordingly, the object 23.

Under the influence of the signal U1=U10the first solenoid 19 is activated and closes the channel 18. The working fluid does not flow through the channel 18 from one cavity of the hydraulic cylinder 12 in another, and, as a consequence, the position of the piston 13, the piston rod 14 and the hydraulic cylinder 12 is fixed relative to the first base 1.

At the same time under the influence of the signal U3=0, the electromagnet 6 is de-energized and the hydraulic cylinder 12 is released from connection with the second base 2 (has the ability to move with the core 20 of the electromagnet 6 and the rod 21 relative to the second base 2).

As a result of this hydraulic cylinder 12 varies together with the first base 1.

Springs 15, 16 corrector hardness 5, which is pre-compressed, respectively, deviate from the horizontal position and create a countervailing force at which the total rigidity of the insulator decreases sharply (corrector hardness 5 included in the work). As a consequence, decreases and the amplitude of the first substrate 1 and the source of dynamic loads 22. (Vibroprotection systems with quasi-zero stiffness. / Under. edit Knitaholic. - L.: Machine the structure, VIP, 1986. - 96 S.)

Since the amplitude of the periodic component of the reaction, which is perceived by the second base 2 and the object 23, proportional to the amplitude of the first base 1, its value becomes appreciably smaller than the amplitude of the periodic component of the force, i.e. R1<P1.

If the source of dynamic loads 22 ceases to generate a force signal U0=0, and the signals U1=0, U2=0, U3=U30.

As a result, implemented a standby mode of operation of the vibration damper.

On subsequent power effect describes the sequence of operation of the vibration damper is repeated.

Supply of insulator electromagnet 6, the core 20 which is connected by a rod 21 with the housing of the hydraulic cylinder 12, and the damper 4 in the form of a corrugated cylinder 9, the end of which has a throttle 10 and built a second solenoid 11, reduces the number of switching corrector hardness 5. This is possible because the threshold force is perceived elastic bearing element 3, and the periodic component of the force is compensated for by the springs 15, 16 corrector hardness 5, which turns on only when the power reaches a threshold. When this damper 4 and the offset hardness 5 work pooch the Reden - when the damper 4 is included in the work, concealer hardness 5 off from work and Vice versa, i.e. through the damper 4 of the periodic component of the force is not transmitted to the second base 2 and, accordingly, the object 23.

This significantly improves the reliability of the insulator and the effectiveness of protection of the object 23 from the power impact because it reduces the intensity of the work management system and ensures a minimum overall bearing stiffness of the elastic element 3 and the springs 15, 16 corrector stiffness 5.

Sources of information

1. USSR author's certificate SU 1462051 A1, F61F 15/04, bull. No. 8, 1989 (similar).

2. Patent RU 2234015 C1, F16F 9/56, 9/06, bull. No. 22, 2004 (the prototype).

Vibration absorber, containing the first Foundation intended for connection with a source of dynamic loads, the second basis intended for communication with the object of carrying the elastic element and a damper mounted between the bases, the control unit, concealer rigidity, consisting of a hydraulic cylinder with a piston and rod and two springs mounted inside the U-shaped frame, and a displacement transducer mounted on the first substrate and connected to the input of the control unit, and over - and podpisniye cavity of the hydraulic cylinder are connected by a channel with a built-in first solenoid connected to the first output control unit is s, characterized in that it further provided with an electromagnet mounted on U-shaped frame, the damper is made in the form of a corrugated cylinder, the end of which has a throttle and built the second valve, and a rod pivotally mounted on the first base, and the ends of the springs on the housing of the hydraulic cylinder and the U-shaped frame, the core of the electromagnet is connected by a rod with a housing of a hydraulic cylinder, a second solenoid connected to the second output of the control unit, and an electromagnet connected to the third output of the control unit.



 

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