Oscillation damping method and device for its implementation (versions)

FIELD: machine building.

SUBSTANCE: inclination angle of relationship between resistance force modulus and deflection speed modulus of an elastic member is changed if current resistance force modulus differs from the specified value. The specified value of resistance force is changed depending on current deflection of the elastic member. The specified current value of resistance force is set so that it is directly proportional to modulus of current deflection of elasticity force, which is corrected to resistance force vector, of the elastic member of its static value. The device for implementing the method represents a hydraulic telescopic damper, in which the resistance force, the modulus of which depends on the modulus of deflection variation speed, is created during the suspension deflection variation. As per the first version, the damper includes a bar fixed at the compression chamber bottom. The bar has a four-sided variable cross-section in the working section of its length. At the damper compression, the bar is retracted into inner cavity of the stock. As per the second version, the damper includes two bars, as well as a compensating chamber that is separated from the compression chamber with a partition wall and partially filled with liquid. The bars are made in the form of a rotation body and installed inside the first and the second guide elements respectively with possibility of longitudinal movement.

EFFECT: preventing resonance, and minimising the resultant force acting on the under-spring mass of the transport vehicle.

17 cl, 10 dwg

 

The technical FIELD TO WHICH the INVENTION RELATES.

The present invention relates to galenian oscillations of different oscillatory systems. The most successful present invention can be used in the suspension of vehicles. Also it can be used for damping any mechanical and electromagnetic vibrating systems.

PRIOR art

Oscillatory system, regardless of the physical nature, contains at least one first element, which has an inertial property of the at least one second element, which, changing its state under the action of external, in relation to this element of force, stores potential energy and thus creates a potential force acting on the associated element of the other elements of the oscillating system, and at least one third element, which is in the process of circulation of energy between the said first and second elements to create a force of resistance, impeding the circulation, and outputs energy from the vibrating system by its expenditure for the performance of work outside the oscillatory system.

In many cases, the use of vibrating systems there is a need to minimize the force acting on said first element when exposed to N. the oscillatory system external disturbances of different frequencies, the amplitude and shape. One of the most relevant cases, the necessity of solving this problem is the suspension of the vehicle.

Suspension of a vehicle is a mechanical oscillatory system, which contains:

- mentioned first element, which is the sprung mass of the vehicle;

- unsprung mass of the vehicle, through which the vehicle rests on the supporting surface (the road) and through which external perturbations (changes in the profile of the support surface) is transmitted to the suspension;

- mentioned the second element, which is the elastic suspension elements and which under the action of external, in relation to him, the force changes its deflection and force creates tension, which acts on the associated element of the sprung and unsprung masses of the vehicle;

- said third element, which is the damper and which during the change of the deflection mentioned second element generates circulating in the suspension of mechanical energy and generates a force of resistance, the module which has a direct dependency on the module, the rate of change of the deflection mentioned second element and which slows down the change of the deflection.

Suspension of the vehicle is designed to reduce de is relevant to the sprung mass forces, as well as to reduce fluctuations of the force which presses the unsprung mass to the supporting surface when changing the profile of the support surface.

The highest value of force acting on the sprung mass, and vibration forces, clamping unsprung mass to the supporting surface, occur when the resonant oscillations of the suspension.

To reduce the force acting on the sprung mass, and vibration forces, clamping unsprung mass to the supporting surface, carry out the damping of the suspension by the dissipation of mechanical energy circulating in a sling.

To prevent resonance effects, it is necessary to set the angle of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, which corresponds to the aperiodic perturbations are damped suspension. However, when this angle dependence of the power module resistance between the module and the rate of change of deflection experience the following negative effects:

on the unsprung and sprung mass effect from the suspension excessively large, the resulting force during compression of the suspension under the influence of changes in the profile of the support surface speed which exceeds the speed characteristic of the resonance of the suspension;

- excessively decreases the resultant force, prij the host unsprung mass to the supporting surface (up to and including loss of contact unsprung mass reference surface), during the stretching of the suspension under the influence of changes in the profile of the support surface speed which exceeds the speed characteristic of the resonance of the suspension.

To reduce these negative effects, it is necessary to set the angle of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, which corresponds to oscillatory perturbations are damped suspension. The less (more) the angle of the mentioned dependence of the power module resistance between the module and the rate of change of the deflection, the greater (lesser) extent, decrease the negative effects characteristic of aperiodic damping, but increase the resonance phenomena.

Well-known and widely used method of damping oscillations of a suspension of a vehicle, in which

set the angle of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, which corresponds to oscillatory perturbations are damped suspension,

reduce (increase) the angle of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, if the current module mentioned resistance greater than (less than) the specified values.

The rate of change of deflection of the suspension depends on the frequency, amplitude and phase fluctuations. Consequently, the aforementioned preset value corresponds to an infinitely large number of possible combinations of different phases, amplitudes and frequencies. For this reason, the known method does not allow you to minimize the force acting on the sprung mass, and vibration forces, clamping unsprung mass to the supporting surface when exposed to the vehicle changes the profile of the reference surface with different frequency, amplitude and shape.

A well-known method of damping of the suspension mentioned in the book "the Suspension of the car. Oscillation and smoothness" (Chapter 3, "the Oscillatory parameters of the vehicle and its suspension, paragraph 14 "Friction in the suspension. Shock absorbers), the author Reverting, third edition, publishing house "engineering", Moscow, 1972, patent RU 2286491 C2 and EN 2120389 C1 and the application DE 4139746 A1.

The closest analogue of the present invention is a method for damping oscillations of a suspension of a vehicle, is known from the patent RU 2127675 C1 (item 8 claims) and international patent application WO 02/101262 A1, published on 19 December 2002 in the WIPO Gazette, in which, as in the well-known way,

set the angle of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, which corresponds to oscillatory perturbations are damped suspension,

reduce (increase) the angle of the mentioned dependence of the power module resistance from the fashion of the I rate of change of deflection, if the current module mentioned resistance greater than (less than) the specified values.

Unlike well-known method in the method known from the patent RU 2127675 C1 and international patent application WO 02/101262 A1

change mentioned preset value depending on the current trough mentioned elastic element, at least part of the course mentioned suspension.

The method, known from the patent RU 2127675 C1 and international patent application WO 02/101262 A1, does not establish any pattern of change in the mentioned set value depending on the current trough mentioned elastic element. For this reason, this method does not provide absolute minimization of the resulting force acting on the sprung mass, and vibration forces, clamping unsprung mass to the supporting surface, when exposed to the vehicle changes the profile of the reference surface with different frequency, amplitude and shape.

Another case of minimization of the force acting on said first element oscillating system is to minimize fluctuations of the voltage drop across the inductance of the electromagnetic oscillating circuit when exposed to the contour of external electromotive forces of different frequencies, amplitudes and shapes.

Mechanical and electromagnetic the oscillatory system have the same patterns of development of an oscillatory process, which is identical, from a mathematical point of view, equations. Therefore, a method is known from the patent RU 2127675 C1 and international patent application WO 02/101262 A1, can be used for damping oscillations of the electromagnetic oscillating system, which is an electromagnetic oscillating circuit, which contains:

- mentioned first element, which is the inductance;

- mentioned second element, which is the electrical capacity, which under the action attached to the electrical potential difference changes its electric charge creates an electric potential difference, which affects associated with other circuit elements;

- said third element, which is the electrical resistance that during a change of electric charge mentioned second element generates circulating in the circuit of electromagnetic energy and creates an electric potential difference, which is the force of resistance, the module which has a direct dependency on the module, the rate of change of electric charge referred to the second element and which slows down the change of this charge.

If the damping of the electromagnetic circuit method, known from the patent RU 2127675 C1 and international bid, medium, small the invention WO 02/101262 A1, is that

set the angle of the mentioned dependence of the power module resistance between the module and the rate of change of electric charge, which corresponds to oscillatory perturbations are damped circuit,

reduce (increase) the angle of the mentioned dependence of the power module resistance between the module and the rate of change of electric charge, if the current module mentioned resistance is greater (less) than the specified value

change mentioned preset value depending on the current electric charge mentioned electric capacity, at least part of the maximum interval changes in the magnitude of its electric charge.

While retaining the same drawbacks which are inherent in the use of this method for damping oscillations of a mechanical oscillatory system.

Due to the identity development of mechanical vibrations and electromagnetic vibrating systems method, known from the patent RU 2127675 C1 and international patent application WO 02/101262 A1, can be expressed in a generalized form as a way of damping the oscillations of the oscillatory system containing at least one first element, which has an inertial property of the at least one second element, which, changing its state under the action of external, with respect to the volume element, power, stores potential energy and thus creates a potential force acting on the associated element of the other elements of the oscillating system, and at least one third element, which is in the process of circulation of energy between the said first and second elements removes energy from the vibrating system by its expenditure for the performance of work outside the oscillatory system and generates a force of resistance, the module which is the direct dependence of the module of the speed change state referred to the second element and which slows down the change, in which

set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, which corresponds to oscillatory perturbations are damped vibrating system,

reduce (increase) the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, if the current module mentioned resistance is greater (less) than the specified value

change mentioned preset value depending on the current state of this second element, at least part of the maximum interval value changes of its state.

For the case of mechanical damping the oscillations of the way, known from the patent RU 2127675 C1 and international patent application WO 02/101262 A1, can be carried out by using as mentioned third element of the mechanical oscillatory system which outputs circulating in her mechanical energy, the device known from international patent application WO 02/101262 A1. This device is a hydraulic telescopic damper, which contains:

the working cylinder, the inner cavity of which is filled with liquid,

the stock, which is intended for the perception of external load and is mounted coaxially with the said work cylinder with the possibility of progressive (return) movement in said working cylinder under compression (tension) damper

the inner cavity of the mentioned shaft, which communicates with the internal cavity referred to the working cylinder,

the piston, which is attached to the end of the said rod and divides the inner cavity referred to the working cylinder on the compression chamber, the volume of which decreases with compression of the damper, and the camera stretching, the amount of which decreases with tension damper,

valve compression, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said compression chamber, and the output from ersta of the said chambers stretch,

valve strain, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said chambers stretch, and the outlet of the said compression chamber,

the first shut-off element, which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said compression chamber,

the second closing element which is part of the mentioned valve extension overlaps the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said chambers stretch,

the first elastic element, the force of elasticity which prevents moving the first mentioned locking element under the action of said liquid flowing from the said compression chamber, and which is part of the mentioned valve compression

the second elastic element, the force of elasticity which prevents the movement of this second locking element under the action of said liquid flowing from the said chamber stretching, and which is part of the mentioned valve stretching,/p>

the first pillar, which interacts with the first-mentioned elastic element is a part of the said valve compression and is part of the internal surface, which is made conical,

the first guide element, along which the first mentioned bearing has the ability reciprocating movement in the direction of the first mentioned elastic element,

the second pillar, which communicates with the said second elastic element is a part of the said valve extension and is part of the internal surface, which is made conical,

the second guide element along which the above-mentioned second bearing has the ability reciprocating movement in the direction mentioned second elastic element,

the rod, which is attached to the bottom of the said compression chamber, a slide in said internal cavity mentioned rod under compression damper has a tetrahedral variable cross-section in the working portion of its length, which is equal to the maximum during the above-mentioned stock,

the first slot in the first mentioned guide element from the first side surface of the above-mentioned rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the second slot in the first mentioned healthy lifestyles the next element from the second side surface of the above-mentioned rod, which is the opposite referred to the first side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the third hole is made in the above-mentioned second guide element from the third side surface of the above-mentioned rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the fourth hole is made in the above-mentioned second guide element from the fourth side surface of the above-mentioned rod, which is the opposite referred to the third side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the first stop of cylindrical shape, which is mounted in said first hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said first lateral surface of the rod and its opposite end communicates with the tapered inner surface of the first mentioned support,

the second focus, which is identical to the aforementioned first stop mounted in said second hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said second lateral surface of the rod and its opposite end interaction is there with the tapered inner surface of the first mentioned support,

the third emphasis of cylindrical shape, which is referred to in the third hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said third side surface of the rod and its opposite end communicates with the tapered inner surface of the aforementioned second support,

fourth stop, which is identical to the aforementioned third stop, is set in the above-mentioned fourth hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said fourth lateral surface of the rod and its opposite end communicates with the tapered inner surface of the aforementioned second support,

the first reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface of the first mentioned stop and the surface of the first mentioned holes,

the second reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface of the aforementioned second stop and the surface of the aforementioned second hole.

DISCLOSURE of INVENTIONS

The present invention solves the problem of preventing the resolution of the ANSA in oscillatory system and minimize the resulting force, acting on said first element oscillating system, which has inertial properties, when exposed to an oscillating system external disturbances of different frequencies, amplitudes and shapes.

The result of this task for the mechanical oscillatory system, which is the suspension of the vehicle, are:

- minimization of fluctuations in the force which presses the unsprung mass of the vehicle to the supporting surface;

- improve the comfort of the vehicle;

- improved handling and stability of the vehicle;

- improved braking and acceleration dynamics of the vehicle;

- reduction of the average operational fuel consumption and harmful emissions;

- reduction of dynamic loads on the roadway and increase its service life;

- reduce the dynamic load on the sprung and unsprung masses of the vehicle and increase their lifespan.

The proposed method, as the closest analogue is the way of the damping of the oscillating system containing at least one first element, which has an inertial property of the at least one second element, which, changing its state under the action of external, in relation to that e is the COP, power, stores potential energy and thus creates a potential force acting on the associated element of the other elements of the oscillating system, and at least one third element, which is in the process of circulation of energy between the said first and second elements removes energy from the vibrating system by its expenditure for the performance of work outside the oscillatory system and generates a force of resistance, the module which is the direct dependence of the module of the speed change state referred to the second element and which slows down the change, in which

reduce (increase) the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, if the current module mentioned resistance is greater (less) than the specified value

change mentioned preset value depending on the current state of this second element, at least part of the maximum interval value changes of its state.

The proposed method differs from the closest analogue to the fact that:

during reduction module deviations of the current state of this second element from the static state current set-mentioned set value is directly proportional to p. epigenome to the vector mentioned resistance module of the current deviations mentioned potential forces mentioned second element from its static value,

to achieve the greatest technical effect of using the proposed method

during reduction module deviations of the current state of this second element from the static state current set-mentioned specified value refer to the vector mentioned resistance module of the current deviations mentioned potential forces mentioned second element from its static value,

set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned oscillatory system, if the current module mentioned power resistance equal to or less than the current mentioned given value,

set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned oscillatory system, if the current module mentioned resistance more current mentioned C is a given value,

set the angle of the mentioned dependence of the power module resistance from the module of the speed change state mentioned second element corresponding to the aperiodic damping of the perturbations mentioned oscillatory system, the maximum possible for the constructive and technological limitations of the device that implements the method, if the current module mentioned power resistance equal to or less than the current mentioned given value,

set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, the corresponding oscillatory perturbations are damped mentioned oscillatory system, the minimum possible for the constructive and technological limitations of the device that implements the method, if the current module mentioned resistance more current mentioned given value,

during the increase of the modulus of the deviation of the current state of this second element from the static condition set mentioned specified value is less than 10% from those listed to the vector referred to the force of resistance of the static module of the potential magnitude of the said force mentioned second element,

to increase the amplitude of the external perturbation, which are able in order to take oscillatory system,

change the current referred to the specified value in direct relation to the module current deviations mentioned potential forces mentioned second element from its static value, at most, on the part of maximum interval values of the deviations of a condition mentioned second element from the static state during the increase of the modulus of the deviation.

A special case of the proposed method is a method for damping oscillations of a mechanical oscillatory system, which is the suspension of the vehicle, which is characterized by the fact that

perform damping of the oscillations of a mechanical oscillatory system, which is a suspension of a vehicle, in which:

- referred to the first element of the oscillating system is the sprung mass of the vehicle;

- mentioned the second element of the oscillating system is the elastic suspension element that associates mentioned the sprung mass of the vehicle with its unsprung mass, through which the suspension takes external disturbance.

- mentioned condition mentioned second element of the oscillating system is mentioned deflection of the elastic element, and the potential power of this element is the force of elasticity of the elastic ale the NTA;

- mentioned third element of the vibrating system is the damper that associates mentioned the sprung and unsprung masses of the vehicle and which in time changes mentioned deflection of the elastic element generates a force of resistance, slowing down the change of the deflection and the module which has a direct dependency on the module, the rate of change of the deflection,

set and change the angle of the mentioned dependence of the power module resistance mentioned damper unit rate of change of the above mentioned deflection of the elastic element,

set and change the mentioned preset value depending on the current deviations mentioned by the elastic force of the mentioned elastic element from its static value.

A special case of the proposed method is a method for damping oscillations of the electromagnetic oscillating system, which is the electromagnetic resonant circuit, which is characterized by the fact that

carry out the oscillation of the electromagnetic oscillating system, which is an electromagnetic circuit, in which:

- referred to the first element of the oscillating system is the inductance of the loop;

- mentioned the second element of the oscillating system is the electrical capacity is antura;

- mentioned condition mentioned second element of the oscillating system is the electrical charge of the mentioned electric capacity, and the potential power of this element is the difference of electric potentials in this capacity;

- mentioned third element of the oscillatory system is active electrical resistance of the circuit, which during a change of electric charge mentioned electrical capacitance creates an electric potential difference, which represents the power of resistance, slowing down the change of the electric charge mentioned electric capacity and a module which has a direct dependency on the module, the rate of change of charge,

set and change the angle of the mentioned dependence of the power module resistance mentioned active electrical resistance between the module and the rate of change of electric charge mentioned electrical capacitance,

set and change the mentioned preset value depending on the current deviation of the electrical potential difference at the above-mentioned electric capacity from its static value.

The proposed method for damping oscillations of a mechanical oscillatory system, which is the suspension of the vehicle, may be the implementation of the flax through the use as mentioned third element of the oscillating system of any of the two variants of the device, described below.

The first variant of the device for implementing the method, and device are known from international patent application WO 02/101262 A1 is a device for damping oscillations of a suspension of a vehicle, which includes at least one elastic element, which generates a force of elasticity, acting on associated with these the elastic element of the sprung mass and unsprung mass of the vehicle, and represents a hydraulic telescopic damper, which at the time of the change of the deflection mentioned suspension creates a force of resistance, the module depends on module speed changes mentioned trough, and which contains

the working cylinder, the inner cavity of which is filled with liquid,

the stock, which is intended for the perception of external load and is mounted coaxially with the said work cylinder with the possibility of progressive (return) movement in said working cylinder under compression (tension) damper

the inner cavity of the mentioned shaft, which communicates with the internal cavity referred to the working cylinder,

the piston, which is attached to the end of the said rod and divides the inner cavity referred to the working cylinder on the compression chamber, the volume of which decreases with compression of the damper, and h is the camera stretching, the amount of which decreases with tension damper,

valve compression, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said compression chamber, and the outlet of the said chamber stretching,

valve strain, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said chambers stretch, and the outlet of the said compression chamber,

the first shut-off element, which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said compression chamber,

the second closing element which is part of the mentioned valve extension overlaps the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said chambers stretch,

the first elastic element, the force of elasticity which prevents moving the first mentioned locking element under the action of said liquid flowing from the said compression chamber, and which is the hour of the people mentioned valve compression

the second elastic element, the force of elasticity which prevents the movement of this second locking element under the action of said liquid flowing from the said chamber stretching, and which is part of the mentioned valve strain,

the first pillar, which interacts with the first-mentioned elastic element is a part of the said valve compression and is part of the internal surface, which is made conical,

the first guide element, along which the first mentioned bearing has the ability reciprocating movement in the direction of the first mentioned elastic element,

the second pillar, which communicates with the said second elastic element is a part of the said valve extension and is part of the internal surface, which is made conical,

the second guide element along which the above-mentioned second bearing has the ability reciprocating movement in the direction mentioned second elastic element,

the rod, which is attached to the bottom of the said compression chamber, a slide in said internal cavity mentioned rod under compression damper has a tetrahedral variable cross-section in the working portion of its length, which is equal to the maximum during the above-mentioned stock,

the second hole made in the above-mentioned first guide element from the second side surface of the above-mentioned shaft, which is opposite to the first mentioned side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the third hole is made in the above-mentioned second guide element from the third side surface of the above-mentioned rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the fourth hole is made in the above-mentioned second guide element from the fourth side surface of the above-mentioned rod, which is the opposite referred to the third side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,

the first stop of cylindrical shape, which is mounted in said first hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said first lateral surface of the rod and its opposite end communicates with the tapered inner surface of the first mentioned support,

the second focus, which is identical to the aforementioned first stop mounted in said second hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said second lateral surface of the rod and its opposite end communicates with the tapered inner surface of the first mentioned support,

the third emphasis of cylindrical shape, which is referred to in the third hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said third side surface of the rod and its opposite end communicates with the tapered inner surface of the aforementioned second support,

fourth stop, which is identical to the aforementioned third stop, is set in the above-mentioned fourth hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said fourth lateral surface of the rod and its opposite end communicates with the tapered inner surface of the aforementioned second support,

the first reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface referred to is th first stop and the surface of the first mentioned holes,

the second reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface of the aforementioned second stop and the surface of the aforementioned second hole.

The proposed device differs from the device known from international patent application WO 02/101262 A1, that:

each value of the above-mentioned deflection of the suspension corresponds to the cross section of the above-mentioned rod in the working portion of its length,

at the working length of the above-mentioned rod, the distance between the said first and the said second lateral surfaces of the rod in each cross section of the rod corresponds to the equation (e1):

where

L1- the distance between the said first and the said second side surfaces of the above-mentioned rod in each cross section of the rod;

Ln1- the maximum distance between the said first and the said second side surfaces of the above-mentioned rod corresponding to the undeformed condition mentioned first elastic element;

α1- the angle between the longitudinal axis of the above-mentioned rod and cone inner surface of the first mentioned support;

X1corresponding to each cross-section by mentioning is that rod setpoint module mentioned resistance, which opens the said valve compression;

S1- the cross-sectional area referred to the working cylinder;

Sk1- the area referred to the outlet of the inlet channel mentioned compression valve;

C1- the rigidity of the first mentioned elastic element,

at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the above-mentioned rod, the distance between the said third and said fourth side surfaces of the rod in each cross section of the rod corresponds to the equation (E2):

where

L2- the distance between the said third and said fourth side surfaces of the above-mentioned rod in each cross section of the rod;

Ln2- the maximum distance between the said third and said fourth side surfaces of the above-mentioned rod corresponding to the undeformed state referred to the WTO the CSOs of the elastic element;

α2- the angle between the longitudinal axis of the above-mentioned rod and cone inner surface mentioned second support;

X2corresponding to each cross section of the above-mentioned rod setpoint module mentioned resistance, which opens the said valve stretching;

S2- the difference between the cross-sectional area referred to the working cylinder and the cross-sectional area of the mentioned stock;

Sk2- the area referred to the outlet of the inlet channel mentioned valve stretching;

With2- rigidity mentioned second elastic element,

at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and the corresponding this cross is the cross section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is less than 10% from those listed to the longitudinal axis of the damper module static values mentioned by the elastic force,

at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is less than 10% from those listed to the longitudinal axis of the damper module static values mentioned by the elastic force,

at most, on the part of the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that the priest is ecnomy section of the rod module deviations mentioned by the elastic force from its static value,

at most, on the part of the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

the flow area mentioned valve compression corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the flow area mentioned valve stretching corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the total flow section of the mentioned first and said second inductors corresponds to the angle of inclination of the mentioned dependence of the power module resistance from module speed changes the trough, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned suspension.

The second variant of the device for implementing the method, and device are known from international patent application WO 02/101262 A1 is a device for damping oscillations of a suspension of a vehicle, which includes at least one elastic element, which generates a force of elasticity, acting on associated with these the elastic element of the sprung mass and unsprung mass of the vehicle, and represents a hydraulic telescopic damper, which at the time of the change of the deflection mentioned suspension creates a force of resistance, the module depends on module speed changes mentioned trough, and which contains

the working cylinder, the inner cavity of which is filled with liquid,

the stock, which is intended for the perception of external load and is mounted coaxially with the said work cylinder with the possibility of progressive (return) movement in said working cylinder under compression (tension) damper

the piston, which is attached to the end of the said rod and divides the inner cavity referred to the working cylinder on the compression chamber, the volume of which decreases p and the compression of the damper, and the camera stretching, the amount of which decreases with tension damper,

valve compression, which has at least one inlet channel, which has an input hole of the said compression chamber, and the outlet from the other cameras mentioned damper

valve strain, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said chambers stretch, and the outlet of the said compression chamber,

the first shut-off element, which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said compression chamber,

the second closing element which is part of the mentioned valve extension overlaps the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said chambers stretch,

the first elastic element, the force of elasticity which prevents moving the first mentioned locking element under the action of said liquid flowing from the said compression chamber, and which is frequently the Yu mentioned valve compression

the second elastic element, the force of elasticity which prevents the movement of this second locking element under the action of said liquid flowing from the said chamber stretching, and which is part of the mentioned valve strain,

the first pillar, which interacts with the first-mentioned elastic element is a part of the said valve compression and is part of the internal surface, which is made conical,

the first guide element, along which the first mentioned bearing has the ability reciprocating movement in the direction of the first mentioned elastic element,

the second pillar, which communicates with the said second elastic element is a part of the said valve extension and is part of the internal surface, which is made conical,

the second guide element along which the above-mentioned second bearing has the ability reciprocating movement in the direction mentioned second elastic element.

The proposed device differs from the device known from international patent application WO 02/101262 A1, that:

contains the compensation chamber, which is separated from the compression chamber wall and partially filled with the said liquid,

contains bypass the first valve, which connects the compression chamber with the said camera strain during compression of the damper and has a negligible resistance to the expiration of the said liquid from the said compression chamber,

mentioned headrace canal mentioned valve compression is performed in the above-mentioned partition and has an output hole of the said compensation chamber,

contains the first rod, which is mounted coaxially with the said work cylinder inside the first mentioned guide element with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the above-mentioned rod-shaped body of rotation with a concave or convex lateral surface,

one end of the first mentioned rod is located in said compression chamber, and the working length of the rod is located in said compensation chamber,

contains the second rod, which is mounted coaxially with the said work cylinder inside the mentioned second guide element with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the above-mentioned rod-shaped body of rotation with a concave or convex lateral surface,

contains at least first and second holes drilled in amanuta the first guide element and the axis of which is perpendicular to the longitudinal axis of the first mentioned rod,

contains at least third and fourth openings made in the above-mentioned second guide element and the axis of which is perpendicular to the longitudinal axis referred to the second rod,

contains at least first and second identical balls are installed respectively in said first and second holes with the possibility of reciprocating rolling along the axis of these holes and each of which one side interacts with the side surfaces of the first mentioned rod, and the opposite side communicates with the tapered inner surface of the first mentioned support,

contains at least third and fourth identical balls are installed respectively in said third and fourth holes with the possibility of reciprocating rolling along the axis of these holes and each of which on one side communicates with the side surface of the aforementioned second rod, and the opposite side communicates with the tapered inner surface of the aforementioned second support,

contains the third leg, which is connected with located in the compression chamber by the end of the first mentioned rod,

contains the fourth pillar, which is connected with reversed in the direction of the said compression chamber by the end of this second rod,

the content is it the first spring, which is installed between the said third support and said fourth support

contains a second spring which is installed between the said third support and said wall and rigidity which relates to the rigidity of the first mentioned spring, as the maximum speed mentioned rod to the length of the work area first mentioned rod,

contains a third spring which is installed between the above fourth pillar and the said piston and stiffness which relates to the rigidity of the first mentioned spring, as the maximum speed mentioned rod to the length of the work area mentioned second rod,

each value of the above-mentioned deflection of the suspension corresponds to the cross-section of the first mentioned rod in the working portion of its length,

each value of the above-mentioned deflection of the suspension corresponds to the cross-section referred to the second rod in the working portion of its length,

at the working length of the first mentioned rod diameter in each cross section of the rod corresponds to the equation (E3):

where

D1- the diameter of the first mentioned rod in each cross section of the rod;

Dn1- maximum diameter of the first mentioned rod, corresponding nereformiruem the th state mentioned first elastic element;

α1- the angle between the longitudinal axis of the first mentioned rod and cone inner surface of the first mentioned support;

X1corresponding to each cross-section mentioned first rod setpoint module mentioned resistance, which opens the said valve compression;

S1- the cross-sectional area of the mentioned stock;

Sk1- the area referred to the outlet of the inlet channel mentioned compression valve;

C1- the rigidity of the first mentioned elastic element,

at the working length of the first mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length referred to the second rod, the diameter of each cross section of the rod corresponds to the equation (E4):

where

D2the diameter of this second rod in each cross section of the rod;

Dn2- maximum diameter of this second rod, which is adequate undeformed condition mentioned second elastic element;

α2- the angle between the longitudinal axis of this second rod and cone inner surface mentioned second support;

X2corresponding to each cross-section mentioned second rod setpoint module mentioned resistance, which opens the said valve stretching;

S2- the difference between the cross-sectional area referred to the working cylinder and the cross-sectional area of the mentioned stock;

Sk2- the area referred to the outlet of the inlet channel mentioned valve stretching;

With2- rigidity mentioned second elastic element,

at the working length referred to the second rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the first mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and testvolume this cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length referred to the second rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the first mentioned rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X1for each cross-section of the rod is less than 10% from those listed to the longitudinal axis of the damper module static values mentioned by the elastic force,

at the working length referred to the second rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is less than 10% from those listed to the longitudinal axis of the damper module static values mentioned by the elastic force,

at most, on the part of the working length of the first mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional brought to the longitudinal axis of dempf the RA and corresponding to this cross-section of the rod module deviations mentioned by the elastic force from its static value,

at most, on the part of the working length referred to the second rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

the flow area mentioned valve compression corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the flow area mentioned valve stretching corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

contains at least one orifice that connects the mentioned internal cavity referred to the working cylinder with the compensatory camera

the flow area is mentioned throttle corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned suspension.

DESCRIPTION of DRAWINGS

1 shows a first variant of the device for implementing the method.

Figure 2 shows a second variant of the device for implementing the method.

Figure 3 shows time diagrams of changes the dynamic tension in the element body of the car VAZ-2110 in the bracket front right front suspension "MacPherson" while driving at a speed of 40 km/h on a smooth boulder when serial reception suspension and experimental rack suspension.

Figure 4 shows the timing diagram changes the dynamic tension in the element body of the car VAZ-2110 in the bracket front right front suspension "MacPherson" while driving at a speed of 30 km/h on the broken cobblestone when serial reception suspension and experimental rack suspension.

Figure 5 shows the timing diagram changes the dynamic tension in the element body of the car VAZ-2110 in the bracket front right front suspension "MacPherson" while driving at 50 km/h on worn (broken) asphalt when serial reception suspension and experimental rack suspension.

the and Fig.6 shows the timing diagram changes the dynamic tension in the element body of the car VAZ-2110 in the bracket front right front suspension "MacPherson" while driving with a speed of 90 km/h on a smooth asphalt when serial reception suspension and experimental rack suspension.

The IMPLEMENTATION of the INVENTION

The possibility of achieving the stated technical result using the proposed method is confirmed by the following analysis of the reactions of mechanical oscillatory system, representing a simplified model of the suspension of the vehicle, various changes to the profile of the support surface.

Consider a mechanical oscillatory system contains the sprung and unsprung masses, which are connected by the elastic element, which generates a force of elasticity, acting on the sprung and unsprung masses, and the item that during a change of deflection of the elastic element generates mechanical energy from the suspension and creates a force of resistance, which slows down the change of the deflection and the module which has a direct dependency on the module, the rate of change of deflection.

In this oscillatory system adopted the following assumptions:

- on the sprung and unsprung mass of the force of gravity;

all forces act along the same straight line;

- the direction of gravity is taken as a negative direction;

- the resultant force pressing the unsprung mass to the supporting surface, is balanced by the reaction of the support on which ernesti.

The resultant force acting on the sprung mass, described by equation (E5).

where

F is the resultant force acting on the sprung mass;

Fest - static value of the elastic force;

ΔFe - deviation of the elastic force from a static value (positive values when you deflection, greater than the static deflection, and negative values when you deflection, less than the static deflection);

Fr - resistance force;

M is the sprung mass;

G - module acceleration of free fall.

As in the static state power of elasticity balances the weight of the sprung mass, equation (E5) can be written in the form (e).

(e5.1) F=ΔFe+Fr

The resultant force pressing the unsprung mass to the supporting surface, is described by equation (E6).

where

Fa - resultant force pressing the unsprung mass to the supporting surface;

Fest - static value of the elastic force;

ΔFe - deviation of the elastic force from a static value (positive values when you deflection, greater than the static deflection, and negative values when you deflection, less than the static deflection);

Fr - resistance force;

MA - unsprung mass;

G - module acceleration of free fall.

Predlagaemom the way drag force is described by equations (e) and (e).

where

Fr - resistance force;

K1tangent of the angle dependence of the power module resistance between the module and the rate of change of deflection corresponding to the condition:

K1>2×(M×C)0,5, where M is referred to the sprung mass, stiffness mentioned elastic suspension elements (maximum rigidity, if this element has a variable stiffness);

V - the current rate of change of deflection of the suspension (positive values during suspension compression, negative for tension);

X - mentioned current set value;

K2tangent of the angle dependence of the power module resistance between the module and the rate of change of deflection corresponding to the condition:

0,0001×2×(M×C)0,5<K2<0,3×2×(M×C)0,5, where M is referred to the sprung mass, stiffness mentioned elastic element suspension (minimum rigidity, if this element has a variable stiffness).

In turn, the current referred to the specified value X set in accordance with equations (I) and (e).

ifΔFe>0 and V<0, or ifΔFe<0 and V>0

ifΔFe≥0 and V>0, or ifΔFe≤0 and V<0

Since the proposed method provides ustanovleny.vozmozhno small mentioned the given value X for the case described by equation (e), approximately can be considered fair equation (e).

ifΔFe≥0 and V>0, or ifΔFe≤0 and V<0

Since in the proposed method, K1set as large as possible, and K2set as low as possible, we can approximately assume that during a change of the deflection of the suspension module resistance force Fr in each moment of time committed to the current mentioned the given value of X and corresponds to the equations (e) and (e).

ifΔFe>0 and V<0, or ifΔFe<0 and V>0

ifΔFe≥0 and V>0, or ifΔFe≤0 and V<0

The analysis of the response of the suspension to change the profile of the support surface

1. The changing profile of the support surface in the form of a ledge →

1.1. The entrance to roughness:

- deviation of the elastic force from the static valueΔFe is zero;

- the rate of change of deflection of the suspension V is equal to zero;

- resistance force Fr is equal to zero;

- equation (e) has the form F=0, that is, the resultant force acting on the sprung mass equal to zero;

- equation (E6) has the form Fa=-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is equal to the sum of the sprung weight and podressorennoj masses.

1.2. The entrance to the roughness:

module deflection deflection from static value increases, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static valueΔFe is greater than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (I) approximately can be considered that the resistance force Fr approaches zero from positive values, as mentioned current set value X set probably small;

- equation (e) has the form F→ΔFe, i.e. the resultant force acting on the sprung mass, is committed to the value of the current deviation of the elastic force from the static value;

- equation (E6) has the form Fa→-Fest-ΔFe-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the sum of the value of the current deviation of the elastic force from the static value and the weight of the sprung and unsprung masses;

- pendant stores energy equal to the work completed by the excess of the elastic force on the weight of the sprung mass.

1.3. Movement after entry into roughness:

module deflection deflection from static values is reduced, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static valueΔFe is greater than zero;

- the rate of change of deflection of the suspension V is less than zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess of the elastic force on the weight of the sprung mass, and the work performed by the force of resistance.

2. The changing profile of the support surface in the form of a downturn →

2.1. The entrance to the irregularities discussed in paragraph 1.1.

2.2. Exit roughness:

module deflection deflection from static value increases, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V Myung is above zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr tends to zero from negative values, as mentioned current set value X set probably small;

- equation (e) has the form F→ΔFe, i.e. the resultant force acting on the sprung mass, is committed to the value of the current deviation of the elastic force from the static value;

- equation (E6) has the form Fa→-Fest-ΔFe-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the sum of the value of the current deviation of the elastic force from the static value and the weight of the sprung and unsprung masses;

- pendant stores energy equal to the work completed by the excess weight of the sprung mass above the restoring force.

2.3. Movement after exit roughness:

module deflection deflection from static values is reduced, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as decodeimage point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess weight of the sprung mass above by elastic force, and the work performed by the force of resistance.

3. The changing profile of the support surface in the form of a ledge →

If time travel irregularities more time aperiodic return of the suspension in the position of static equilibrium, it turns out the serial combination of travel irregularities discussed in paragraph 1, and the irregularities discussed in paragraph 2. Therefore, in this paragraph considers the case when the passage roughness less time aperiodic return of the suspension in the position of static equilibrium.

3.1. The entrance to the ledge discussed in paragraph 1.1.

3.2. The entrance to the ledge discussed in paragraph 1.2.

3.3. Movement after entry to the ledge discussed in paragraph 1.3. Thus there is only a partial aperiodic return to a static condition and partial dissipation stored in the Veske energy.

3.4. The exit ledge

Considered two phases of the exit ledge. The first phase is when the current deviation of the deflection of the elastic element from the static value is positive. The second phase is when the current deviation of the deflection of the elastic element from the static value is negative. The real exit ledge, depending on the geometry of the protrusion, may consist of either only the first phase, or from the sequence of the first and second phases.

3.4.1. The first phase of the exit ledge:

module deflection deflection from static values is reduced, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static valueΔFe is greater than zero;

- the rate of change of deflection of the suspension V is less than zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface tends to su is IU the weight of the sprung and unsprung masses;

because of the equality of the work performed by the excess of the elastic force on the weight of the sprung mass, and the work performed by the power of resistance, is the dissipation of stored energy suspension, which corresponds to the difference between the initial and final values of the deviation of deflection from static values in the course of this phase.

3.4.2. The second phase of the exit ledge:

module deflection deflection from static value increases, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V is less than zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr tends to zero from negative values, as mentioned current set value X set probably small;

- equation (e) has the form F→ΔFe, i.e. the resultant force acting on the sprung mass, is committed to the value of the current deviation of the elastic force from the static value;

- equation (E6) has the form Fa→-Fest-ΔFe-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the sum of the value of the current deviation of the elastic force from the static value and the weight of the sprung and unsprung mA is s;

- pendant stores energy equal to the work completed by the excess weight of the sprung mass above the restoring force.

3.5. Movement after the exit ledge

We consider two variants of movement after the exit ledge. The first option is when the return to a static condition begins from the first phase of the exit ledge. The second option is when the return to a static condition begins from the second phase of the exit ledge.

3.5.1. The first version of the movement after the exit ledge:

module deflection deflection from static values is reduced, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static valueΔFe is greater than zero;

- the rate of change of deflection of the suspension V is less than zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, strem is raised to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess of the elastic force on the weight of the sprung mass, and the work performed by the force of resistance.

3.5.2. The second variant of the movement after the exit ledge:

module deflection deflection from static values is reduced, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess weight of the sprung mass above the power pack is treat, and work performed by the force of resistance.

4. The changing profile of the support surface in the form of depression →

If time travel irregularities more time aperiodic return of the suspension in the position of static equilibrium, it turns out the serial combination of travel irregularities discussed in paragraph 2, and the irregularities discussed in paragraph 1. Therefore, in this paragraph considers the case when the passage roughness less time aperiodic return of the suspension in the position of static equilibrium.

4.1. The entrance to the basin is discussed in paragraph 1.1.

4.2. Exit into the hollow discussed in paragraph 2.2.

4.3. Movement after the Congress into the hollow discussed in paragraph 2.3. Thus there is only a partial aperiodic return to a static condition and partial dissipation of stored energy suspension.

4.4. Leaving depression

Considered two phases out of the depression. The first phase is when the current deviation of the deflection of the elastic element from the static value is negative. The second phase is when the current deviation of the deflection of the elastic element from the static value is positive. A real departure from depression, depending on the geometry of the basin, may consist of either only the first phase, or from the sequence of the first and second phases.

4.4.1. The first phase is yezda of depression:

module deflection deflection from static values is reduced, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

because of the equality of the work performed by the excess weight of the sprung mass above by elastic force, and the work performed by the power of resistance, is the dissipation of stored energy suspension, which corresponds to the difference between the initial and final values of the deviation of deflection from static values in the course of this phase.

4.4.2. The second phase of the exit trough;

module deflection deflection from adicheskogo value increases, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static valueΔFe is greater than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (s) approximately can be considered that the resistance force Fr approaches zero from positive values, as mentioned current set value X set probably small;

- equation (e) has the form F→ΔFe, i.e. the resultant force acting on the sprung mass, is committed to the value of the current deviation of the elastic force from the static value;

- equation (E6) has the form Fa→-Fest-ΔFe-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the sum of the value of the current deviation of the elastic force from the static value and the weight of the sprung and unsprung masses;

- pendant stores energy equal to the work completed by the excess of the elastic force on the weight of the sprung mass.

4.5. Movement after leaving depression

We consider two variants of movement after leaving the basin. The first option is when the return to a static condition begins from the first phase of exit from the basin. The second option is when the return to a static condition begins from the second phase of exit from the valley.

4.5.1. The first version magic cube MOV what I'm after departure from depression:

module deflection deflection from static values is reduced, and the deviation of deflection is less than zero;

- deviation of the elastic force from the static valueΔFe is less than zero;

- the rate of change of deflection of the suspension V greater than zero.

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (a.) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess weight of the sprung mass above by elastic force, and the work performed by the force of resistance.

4.5.2. The second option movements after leaving depression:

module deflection deflection from static values is reduced, and the deviation of deflection greater than zero.

- deviation of the elastic force from the static is wow ΔFe is greater than zero;

- the rate of change of deflection of the suspension V is less than zero;

in accordance with equation (I) approximately can be considered that the resistance force Fr is committed to the value of the current deviation of the elastic force from a static value and opposite in sign, as mentioned current point value X is set equal to the current deflection of the elastic force from the static value;

- equation (e) has the form F→0, i.e. the resultant force acting on the sprung mass, tends to zero;

- equation (E6) has the form Fa→-Fest-Ma×G, that is, the resultant force pressing the unsprung mass to the supporting surface, is committed to the total weight of the sprung and unsprung masses;

- return to the static state is aperiodic in nature because of the equality of the work performed by the excess of the elastic force on the weight of the sprung mass, and the work performed by the force of resistance.

As follows from the above analysis, a significant deviation of the resultant force acting on the sprung mass from zero, and the resulting force which presses the unsprung mass to the supporting surface, a static value is only:

- when the current deflection of the suspension is greater than the static values during compression of the suspension when hitting on p is patsta;

- when the current deflection is less than the static values in the process of stretching the suspension when exit barriers.

In all other situations, the resultant force acting on the sprung mass, is not very different from zero, and the resulting force pressing the unsprung mass to the supporting surface, differs little from the static value.

The occurrence of resonance of the sprung mass and the unsprung resonance mass is impossible, since for a single reduction process module deflection of the deflection of the elastic element from the static value is the dissipation of all energy stored in the suspension during the previous single scaling module deflection of the deflection of the elastic element from the static value.

This technical result is valid for changes of the profile of the support surface of any amplitude (within the limits of suspension travel), repetition rate (within the performance of the device for implementing the method and form as:

- equations (E5) and (e) describe the instantaneous value of the resulting force acting on the sprung mass;

- equation (E6) describes the instantaneous value of the resulting force which presses the unsprung mass to the supporting surface;

- equation (e) and (e) describe the instantaneous value of the force by the resistance;

- equation (e) and (e) describe the instantaneous mentioned preset value;

- any changes to the profile of the support surface can be represented by the combination considered in the analysis of irregularities.

The proposed method of damping oscillations of a mechanical oscillatory system, which is the suspension of the vehicle, can be implemented by connecting the sprung mass of the vehicle with its unsprung mass damper, which represents any of the two proposed variants of the device for implementing the method.

The first variant of the device for implementing the method depicted in figure 1.

Design description of the device

The device is a Monotube hydraulic telescopic damper. The stem seal and the compensation gas chamber in figure 1 are not shown and are not described because they are similar to those traditionally used in Monotube hydraulic telescopic dampers and to the essence of the invention do not have a relationship.

The device has the following construction:

contains the working cylinder (1), an internal cavity which is filled with liquid,

contains the stem (2), which is intended for the perception of external load and is mounted coaxially with the work Qili the drôme (1) with the possibility of progressive (return) movement in the working cylinder (1) compression (tension) damper

the rod (2) has an internal cavity which communicates with the internal cavity of the working cylinder (1),

contains a piston (3)which is mounted at the end of the rod (2) and divides the inner space of the working cylinder (1) on the compression chamber (4), the amount of which decreases with compression of the damper, and the camera stretching (5), the amount of which decreases with tension damper,

contains valve compression, which has at least one inlet channel (6), which is made in the piston (3) and has an inlet side of the compression chamber (4)and the outlet-side chamber of the expansion (5),

contains valve strain, which has at least one inlet channel (7), which is made in the piston (3) and has an inlet-side chamber of the expansion (5)and the outlet from the compression chamber (4),

contains the first closing element (8), which is part of the mentioned compression valve, closes off the outlet of the inlet channel (6) of the valve and is mounted for movement under the action of said fluid flowing out of the compression chamber (4),

contains the second closing element (9), which is part of the mentioned valve extension overlaps the outlet of the inlet channel (7) of the valve and is mounted for movement under the action of said fluid is flowing from the cell strain (5),

contains the first elastic element (10), the force of elasticity which prevents the displacement of the first locking element (8) under the action of said fluid flowing out of the compression chamber (4), and which is part of the mentioned valve compression

contains a second elastic element (11), the force of elasticity which prevents the displacement of the second locking element (9) under the action of said liquid flowing from the chamber of expansion (5), and which is part of the mentioned valve strain,

contains the first support (12), which interacts with the first elastic element (10)is part of the mentioned compression valve and is part of the internal surface, which is made conical,

contains the first guide element (13)along which the first support (12) has the ability reciprocating movement in the direction of the first elastic element (10),

contains the second support (14), which interacts with the second elastic element (11)is a part of the said valve extension and is part of the internal surface, which is made conical,

contains the second guide element (15)along which the second bearing (14) has the ability reciprocating movement in the direction of the second elastic element (11),

contains a rod (16), which is attached to the bottom of the camera SG is ment (4), slide in said internal cavity of the stem (2) compression damper has a tetrahedral variable cross-section in the working portion of its length, which is equal to the maximum fly rod (2),

contains the first slot in the first guide element (13) from the first side surface of the rod (16) and whose axis is perpendicular to the longitudinal axis of the rod (16),

includes a second slot in the first guide element (13) from the second side surface of the rod (16), which is opposite to the first mentioned side surface of the rod (16), and the axis perpendicular to the longitudinal axis of the rod (16),

contains the third hole (similar to the aforementioned first hole, figure 1 is shown, as are perpendicular to the plane of the drawing)made in the second guide element (15) from the third side surface of the rod (16) and whose axis is perpendicular to the longitudinal axis of the rod (16),

has a fourth hole (similar to the aforementioned second hole, figure 1 is shown, as are perpendicular to the plane of the drawing)made in the second guide element (15) from the fourth side surface of the rod (16), which is the opposite referred to the third side surface of the rod (16), and the axis of which is perpendicularly the longitudinal axis of the rod (16),

contains the first stop (17) of cylindrical shape, which is mounted in said first hole with the possibility of reciprocating movement along the axis of this hole and one of its end having the form of a convex cylindrical surface, interacts with said first lateral surface of the rod (16), and its opposite end having the shape of an inclined convex cylindrical surface, interacts with the tapered inner surface of the first support (12),

contains the second stop (18)which is identical to the first stop (17)is installed in said second hole with the possibility of reciprocating movement along the axis of this hole and one of its end having the form of a convex cylindrical surface, interacts with said second lateral surface of the rod (16), and its opposite end having the shape of an inclined convex cylindrical surface, interacts with the tapered inner surface of the first support (12),

includes a third stop (identical to the stop (17), in figure 1 are not depicted, as it is located perpendicular to the plane of the drawing), which is mentioned in the third hole with the possibility of reciprocating movement along the axis of this hole and one of its end having the form of a convex cylindrical surface is STI, communicates with said third side surface of the rod (16), and its opposite end having the shape of an inclined convex cylindrical surface, interacts with the tapered inner surface of the aforementioned second support (14),

contains the fourth stop (identical to the stop (18), in figure 1 are not depicted, as it is located perpendicular to the plane of the drawing), which is set in the above-mentioned fourth hole with the possibility of reciprocating movement along the axis of this hole and one of its end having the form of a convex cylindrical surface, interacts with the said fourth lateral surface of the rod (16), and its opposite end having the shape of an inclined convex cylindrical surface, interacts with the tapered inner surface of the aforementioned second support (14),

contains the first reactor, which connects the compression chamber (4) with the camera stretching (5) and which is formed by a gap between the side surface of the first thrust bearing (17) and the surface of the first mentioned holes,

contains the second reactor, which connects the compression chamber (4) with the camera stretching (5) and which is formed by a gap between the side surface of the second stop (18) and the surface of the aforementioned second hole,

at the working length of the rod (16) the distance between the UE is first mentioned and said second side surfaces of the rod in each cross section of the rod corresponds to the equation (e1),

at the working length of the rod (16) the distance between the said third and said fourth side surfaces of the rod in each cross section of the rod corresponds to the equation (E2),

at the working length of the rod (16), which corresponds to the extended condition mentioned suspension referred to in equation (e1) specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the rod (16), which corresponds to the compressed condition mentioned suspension referred to in equation (E2) specified value of X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the rod (16), which corresponds to the compressed condition mentioned suspension referred to in equation (e1) specified value of X1for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

on-site long the s rod (16), which corresponds to the extended condition mentioned suspension referred to in equation (E2) specified X2for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

the flow area mentioned valve compression in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the flow area mentioned valve tension in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the total flow section of the mentioned first and said second inductors corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle e is Oh dependencies which corresponds to the aperiodic damping of the perturbations mentioned suspension.

Description of the device

When the reciprocating moving rod (2) in the working cylinder (1) first stop (17) slides along the first mentioned side surface of the rod (16)and the second stop (18) mentioned slides along the second side surface of the rod (16).

If during the movement of the rod (2) is an increase in the distance between the first and second side surfaces of the rod (16), the stops (17) and (18) are drawn from the axis of the damper and press the first support (12) along the first guide element (13) in the direction of the first elastic element (10). When this occurs, the compression of the first elastic element (10) and increase the elastic force, which presses the first locking element (8) to the piston (3). This leads to an increase of the excess mentioned pressure fluid in the compression chamber (4), in which the first closing element (8) opens the outlet of the inlet channel (6) compression valve during compression of the damper.

If during the movement of the rod (2) there is a reduction of the distance between the first and second side surfaces of the rod (16), the stops (17) and (18) are shifted to the axis of the damper under the action of the first support (12)which moves along the first guide element (13) in the direction from the first elastic element (10) modestiam his power of elasticity. When this occurs, the tension of the first elastic element (10) and decrease it by the elastic force, which presses the first locking element (8) to the piston (3). This leads to the reduction of excess pressure mentioned fluid in the compression chamber (4), in which the first closing element (8) opens the outlet of the inlet channel (6) compression valve during compression of the damper.

During the stretching of the damper outlet of the inlet channel (6) is permanently closed due to excessive pressure of said fluid in the chamber extension (5) and the elastic force of the first elastic element (10), which press the first closing element (8) to the piston (3).

When the reciprocating moving rod (2) in the working cylinder (1) said third fence glides along the mentioned third side surface of the rod (16), and the fourth fence glides along the mentioned fourth side surface of the rod (16).

If during the movement of the rod (2) is an increase in the distance between the third and fourth side surfaces of the rod (16), the third and fourth stops nominated from the axis of the damper and press the second bearing (14) along the second guide element (15) in the direction of the second elastic element (11). When this occurs, the compression of the second elastic element (11) and increase the elastic force, which presses the Torah closing element (9) to the piston (3). This leads to an increase of the excess mentioned pressure fluid in the chamber extension (5), wherein the second closing element (9) opens the outlet of the inlet channel (7) of the valve tension during stretching of the damper.

If during the movement of the rod (2) there is a reduction of the distance between the third and fourth side surfaces of the rod (16), the third and fourth lugs are shifted to the axis of the damper under the action of the second support (14), which moves along the second guide element (15) in the direction from the second elastic element (11) under the action of the elastic force. When this occurs, the tension of the second elastic element (11) and reduced by the elastic force, which presses the second closing element (9) to the piston (3). This leads to the reduction of excess pressure mentioned fluid in the chamber extension (5), wherein the second closing element (9) opens the outlet of the inlet channel (7) of the valve tension during stretching of the damper.

During compression of the damper outlet of the inlet channel (7) permanently closed due to excessive pressure of said fluid in the compression chamber (4) and the elastic force of the second elastic element (11), which press the second closing element (9) to the piston (3).

The module resistance forces generated by the damper during compression of the damper, anywayse equation (E10).

where

Fr - resistance force;

S1- the cross-sectional area of the working cylinder (1);

P45- excessive pressure of said fluid in the compression chamber (4) in relation to the pressure of the fluid in the cell strain (5).

The excess pressure of said fluid in the compression chamber (4) in relation to the pressure of the fluid in the chamber extension (5) at the time of opening the said valve compression is described by equation (e11).

where

P45- excessive pressure of said fluid in the compression chamber (4) in relation to the pressure of the fluid in the chamber extension (5);

With1the rigidity of the first elastic element (10);

Le1the deflection of the first resilient element (10);

Sk1- the area of the outlet of the inlet channel (6) compression valve.

The deflection of the first resilient element (10) is described by equation (E12).

where

Le1the deflection of the first resilient element (10);

L1- the distance between the said first and the said second lateral surfaces of the rod (16) in this cross-section of the rod;

Ln1- the maximum distance between the said first and the said second lateral surfaces of the rod (16), corresponding to the undeformed state first is th elastic element (10);

α1- the angle between the longitudinal axis of the rod (16) and the inner conical surface of the first support (12).

Successive substitution of equation (e12) in equation (e11) and equation (e11) in equation (E10) yields equation (E10) to (e).

Substitution of equations (E1), which determines the value of L1in equation (e) leads to the equality.

Thus, during compression mentioned suspension opening the said valve compression occurs when the equality of the power module resistance |Fr| and the above-mentioned specified value X1corresponding to the current cross-section of the rod (16).

As

- at the working length of the rod (16), which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

- at the working length of the rod (16), which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values KJV is anotai the elastic force,

- the total flow section of the mentioned first and said second inductors corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned pendants

- flow section mentioned valve compression in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the module mentioned resistance is changed in accordance with equations (I) and (e) for the case of V>0, i.e. the considered device provides an implementation of the proposed method during compression mentioned suspension.

The module resistance forces generated by the damper during stretching damper is described by equation (E13).

where

Fr - resistance force;

S2- the difference between the cross-sectional area of the working cylinder (1) and the cross-sectional area of the rod (2);

P54redundant Yes the feeding of said liquid in the chamber of the expansion (5) in relation to the pressure of the fluid in the compression chamber (4).

The excess pressure of the said liquid in the chamber of the expansion (5) in relation to the pressure of the fluid in the compression chamber (4) at the time of opening the said valve stretching is described by equation (e14).

where

P54excess - mentioned pressure fluid in the chamber of the expansion (5) in relation to the pressure of the fluid in the compression chamber (4);

With2- stiffness of the second elastic element (11);

Le2the deflection of the second elastic element (11);

Sk2- the area of the outlet of the inlet channel (7) of the valve extension.

The deflection of the second elastic element (11) is described by equation (e15).

where

Le2the deflection of the second elastic element (11);

L2- the distance between the said third and said fourth side surfaces of the rod (16) in this cross-section of the rod;

Ln2- the maximum distance between the said third and said fourth side surfaces of the rod (16), corresponding to the undeformed state of the second elastic element (11);

α2- the angle between the longitudinal axis of the rod (16) and the inner conical surface of the second support (14).

Successive substitution of equation (e15) in equation (e14) and equation (e14) in equation (E13) yields equation (E13) to the go (e13.1).

Substitution of equation (E2), which determines the value of L2in equation (e13.1) leads to the equality |Fr|=X2.

Thus, during the stretching mentioned suspension opening the said valve stretching occurs when the equality of the power module resistance |Fr| and the above-mentioned specified value X2corresponding to the current cross-section of the rod (16).

As

- at the working length of the rod (16), which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

- at the working length of the rod (16), which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

- the total flow section of the mentioned first and said second inductors corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is about more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned pendants

- flow section mentioned valve tension in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the module mentioned resistance is changed in accordance with equations (I) and (e) for the case of V<0, that is, considering the device provides an implementation of the proposed method during the stretching mentioned suspension.

The second variant of the device for implementing the method shown in figure 2.

Design description of the device

The device is a twin-tube hydraulic telescopic damper. The stem seal and guide bushing stem figure 2 shows conventionally, as they are similar to those traditionally used in twin-tube hydraulic telescopic dampers and to the essence of the invention do not have a relationship.

The device has the following construction:

contains the working cylinder (1), an internal cavity which is filled with liquid,

contains the stem (2), to the which is intended for the perception of external load and is mounted coaxially with the working cylinder (1) with the possibility of progressive (return) movement in the working cylinder (1) compression (tension) damper

contains a piston (3)which is mounted at the end of the rod (2) and divides the inner space of the working cylinder (1) on the compression chamber (4), the amount of which decreases with compression of the damper, and the camera stretching (5), the amount of which decreases with tension damper,

contains valve compression, which has at least one inlet channel (6), which has the inlet side of the compression chamber (4)and the outlet from the other chamber of the damper,

contains valve strain, which has at least one inlet channel (7), which is made in the piston (3) and has an inlet-side chamber of the expansion (5)and the outlet from the compression chamber (4),

contains the first closing element (8), which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel (6) and is mounted for movement under the action of said fluid flowing out of the compression chamber (4),

contains the second closing element (9), which is part of the mentioned valve extension overlaps the outlet of the inlet channel (7) and is mounted for movement under the action of said liquid flowing from the chamber of expansion (5),

contains the first elastic element (10), the force of elasticity which prevents the displacement of the first for the priori element (8) under the action of said fluid, flowing from the compression chamber (4), and which is part of the mentioned valve compression

contains a second elastic element (11), the force of elasticity which prevents the displacement of the second locking element (9) under the action of said liquid flowing from the chamber of expansion (5), and which is part of the mentioned valve strain,

contains the first support (12), which interacts with the first elastic element (10)is part of the mentioned compression valve and is part of the internal surface, which is made conical,

contains the first guide element (13)along which the first support (12) has the ability reciprocating movement in the direction of the first elastic element (10),

contains the second support (14), which interacts with the second elastic element (11)is a part of the said valve extension and is part of the internal surface, which is made conical,

contains the second guide element (15)along which the second bearing (14) has the ability reciprocating movement in the direction of the second elastic element (11),

contains a compensation chamber (16), which is separated from the compression chamber (4) by a partition (17) and partially filled with the said liquid,

includes bypass valve, which connects the compression chamber (4) with gameroulette (5) during compression of the damper and has a negligible resistance to the expiration of the mentioned fluid from the compression chamber (4),

the inlet channel (6) mentioned valve compression is made in the partition wall (17) and has an outlet opening from the compensation chamber (16),

contains the first rod (18)which is mounted coaxially with the working cylinder (1) inside the first guide element (13) with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the rod (2), made in the form of rotation of a body with a concave side surface,

one end of the first rod (18) is located in the compression chamber (4), and the working length of the rod is located in the compensation chamber (16),

contains the second rod (19)which is mounted coaxially with the working cylinder (1) within the second guide element (15) with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the rod (2), made in the form of rotation of a body with a concave side surface,

contains at least first and second holes in the first guide element (13) and an axis which is perpendicular to the longitudinal axis of the first rod (18),

contains at least third and fourth openings made in the second guide element (15) and the axis of which is perpendicular to the longitudinal axis of the second rod (19),

contains at least the first (20) and second (21) is identical balls, the plant respectively in said first and second holes with the possibility of reciprocating rolling along the axis of these holes and each of which on one side communicates with the side surface first rod (18), and the opposite side communicates with the tapered inner surface of the first support (12),

contains at least a third (22) and fourth (23) is identical balls are installed respectively in said third and fourth holes with the possibility of reciprocating rolling along the axis of these holes and each of which on one side communicates with the side surface of the second rod (19), and the opposite side communicates with the tapered inner surface of the second support (14),

contains the third leg (24), which is connected with located in the compression chamber (4) by the end of the first rod (18),

contains the fourth bearing (25), which is connected with facing the compression chamber (4) by the end of the second rod (19),

contains the first spring (26), which is installed between the third pillar (24) and the fourth pillar (25),

contains the second spring (27), which is installed between the third pillar (24) and (via intermediate parts) by a partition (17) and stiffness which refers to the stiffness of the first spring (26), as the maximum stroke (2) refers to the length of the working section of the first rod (18),

contains a third spring (28), which is installed between the fourth pillar (25) and the piston (3) and stiffness which refers to the stiffness of the first spring (26), as the maximum stroke (2)refers to the length of the work area of the second rod (19),

each value of the above-mentioned deflection of the suspension corresponds to the cross-section of the first rod (18) in the working portion of its length,

each value of the above-mentioned deflection of the suspension corresponds to the cross-section of the second rod (19) in the working portion of its length,

at the working length of the first rod (18) the diameter of each cross section of the rod corresponds to the equation (E3),

at the working length of the second rod (19) diameter of each cross section of the rod corresponds to the equation (E4),

at the working length of the first rod (18), which corresponds to the extended condition mentioned suspension referred to in equation (E3) given the value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

at the working length of the second rod (19), which corresponds to the compressed condition mentioned suspension referred to in equation (E4) to the specified value of X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

n the working length of the first rod (18), which corresponds to the compressed condition mentioned suspension referred to in equation (E3) given the value of X1for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

at the working length of the second rod (19), which corresponds to the extended condition mentioned suspension referred to in equation (E4) to the specified value of X2for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

the flow area mentioned valve compression in any phase of its opening corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the flow area mentioned valve tension in any phase of its opening corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to the oscillatory zatuchni the perturbations mentioned pendants

contains the guide sleeve shaft (29),

contains a throttle that connects the camera stretching (5) with the compensation chamber (16) and is formed by a gap between the rod (2) the inner surface of the guide sleeve (29),

the flow area mentioned throttle corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned pendants

contains the inlet channel (30) of the said by-pass valve, which is made in the piston (3) and has an inlet side of the compression chamber (4)and the outlet-side chamber of the expansion (5),

mentioned bypass valve mounted on the piston (3) from the camera stretching (5) and closes its locking element exit opening of the inlet channel (30),

contains the inlet channel (31), which is made in the partition wall (17) and has an inlet from the compensation chamber (16)and the outlet from the compression chamber (4),

contains the inlet valve, which is mounted on the partition wall (17), closes its locking element exit opening of the inlet channel (31) and has a negligible resistance to the flow of the UE is mentioned fluid from the expansion chamber (16) into the compression chamber (4).

Description of the device

During the progressive (return) movement of the rod (2) in the working cylinder (1) compression (tension) springs (26), (27)and (28). The third bearing (24) is (removed) with respect to the partition wall (17)and the fourth bearing (25) is (deleted) against the piston (3).

The amount of movement of the third support (24) and the associated first rod (18) relative to the balls (20) and (21) is equal to the product of the moving rod (2) on the ratio of the stiffness of the first spring (26) to the stiffness of the second spring (27). Because the length of the working section of the first rod (18) is equal to the product of the maximum stroke of the rod (2) on the ratio of the stiffness of the first spring (26) to the stiffness of the second spring (27), each position of the rod (2) in the working cylinder (1) corresponds to one cross-section of the first rod (18), which interact balls (20) and (21).

The amount of movement of the fourth bearing (25) and the associated second rod (19) relative to the balls (22) and (23) is equal to the product of the moving rod (2) on the ratio of the stiffness of the first spring (26) to the rigidity of the third spring (28). Since the length of the work area of the second rod (19) is equal to the product of the maximum stroke of the rod (2) on the ratio of the stiffness of the first spring (26) to the rigidity of the third spring (28), each position of the rod (2) in the working cylinder (1) corresponding to the one cross-section of the second rod (19), interacts with the balls (22) and (23).

When increasing the diameter of the cross-section of the first rod (18) in the process of moving rod (2) balls (20) and (21) slides out from the axis of the damper and press the first support (12) along the first guide element (13) in the direction of the first elastic element (10). When this occurs, the compression of the first elastic element (10) and increase the elastic force, which presses the first locking element (8) to the partition (17). This leads to an increase of the excess mentioned pressure fluid in the compression chamber (4), in which the first closing element (8) opens the outlet of the inlet channel (6) compression valve during compression of the damper.

When reducing the diameter of the cross-section of the first rod (18) in the process of moving rod (2) balls (20) and (21) are rolled back to the axis of the damper under the action of the first support (12)which moves along the first guide element (13) in the direction from the first elastic element (10) under the effect of the elastic force. When this occurs, the tension of the first elastic element (10) and decrease it by the elastic force, which presses the first locking element (8) to the partition (17). This leads to the reduction of excess pressure mentioned fluid in the compression chamber (4), in which the first closing element (8) opens the outlet of the inlet channel (6) cleanstate during compression of the damper.

During the stretching of the damper outlet of the inlet channel (6) is permanently closed due to excessive pressure of said fluid in the compensation chamber (16) and the elastic force of the first elastic element (10), which press the first closing element (8) to the partition (17).

When increasing the diameter of the cross section of the second rod (19) in the process of moving rod (2) balls (22) and (23) slides out from the axis of the damper and press the second bearing (14) along the second guide element (15) in the direction of the second elastic element (11). When this occurs, the compression of the second elastic element (11) and increase the elastic force, which presses the second closing element (9) to the piston (3). This leads to an increase of the excess mentioned pressure fluid in the chamber extension (5), wherein the second closing element (9) opens the outlet of the inlet channel (7) of the valve tension during stretching of the damper.

When reducing the diameter of the cross section of the second rod (19) in the process of moving rod (2) balls (22) and (23) are rolled back to the axis of the damper under the action of the second support (14), which moves along the second guide element (15) in the direction from the second elastic element (11) under the action of the elastic force. When this occurs, the tension of the second elastic element (11) and decrease the elastic force to ora presses the second closing element (9) to the piston (3). This leads to the reduction of excess pressure mentioned fluid in the chamber extension (5), wherein the second closing element (9) opens the outlet of the inlet channel (7) of the valve tension during stretching of the damper.

During compression of the damper outlet of the inlet channel (7) permanently closed due to excessive pressure of said fluid in the compression chamber (4) and the elastic force of the second elastic element (11), which press the second closing element (9) to the piston (3).

During compression of the damper mentioned fluid is flowing from the compression chamber (4) into the compression chamber (5) through the mentioned bypass valve, which has a negligible resistance to the expiration. The volume of said liquid, equal digimemo in the working cylinder (1) volume of the stock (2)shall expire in the compensation chamber (16) from the camera stretching (5) through the said orifice and out of the compression chamber (4) through the said valve compression (if this valve is open).

During the stretching of the damper mentioned liquid flowing from the chamber of expansion (5) into the compression chamber (4) through the said valve extension (if this valve is open) and through the said orifice in the compensation chamber (16). The volume of said liquid, equal nominated from the working cylinder (1) volume of the stock (2)comes from the compensation chamber (16) mentioned through the second inlet valve, which renders this flow is negligibly small resistance in the compression chamber (4),

The module resistance forces generated by the damper during compression of the damper, is described by equation (e16).

where

Fr - resistance force;

S1- the cross-sectional area of the rod (2);

P1excess - mentioned pressure fluid in the working cylinder (1).

The excess pressure of said fluid in the working cylinder (1) at the time of opening the said valve compression is described by equation (e17).

where

P1excess - mentioned pressure fluid in the working cylinder (1);

With1the rigidity of the first elastic element (10);

Le1the deflection of the first resilient element (10);

Sk1- the area of the outlet of the inlet channel (6) compression valve.

The deflection of the first resilient element (10) is described by equation (e18).

where

Le1the deflection of the first resilient element (10);

D1the diameter of the first rod (18) in this cross-section of the rod;

Dn1- maximum diameter of the first rod (18)corresponding to the undeformed state of the first elastic element (10);

α1- the angle between the longitudinal axis of the first rod (18) and the inner conical surface is of the first support (12).

Successive substitution of equation (e18) in equation (E17) and equation (e17) in equation (a) yields equation (a) to (e16.1).

Substitution of equation (E3), which determines the value of D1in equation (e16.1) leads to the equality |Fr|=X1.

Thus, during compression mentioned suspension opening the said valve compression occurs when the equality of the power module resistance |Fr| and the above-mentioned specified value X1corresponding to the current cross-section of the first rod (18).

As

- at the working length of the first rod (18), which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

- at the working length of the first rod (18), which corresponds to the compressed condition mentioned suspension referred to the specified value X1for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

- flow section referred to throttle corresponds to the angle of inclination of the aforementioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned pendants

- flow section mentioned valve compression in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the module mentioned resistance is changed in accordance with equations (I) and (e) for the case of V>0, i.e. the considered device provides an implementation of the proposed method during compression mentioned suspension.

The module resistance forces generated by the damper during stretching damper is described by equation (e19).

where

Fr - resistance force;

S2- the difference between the cross-sectional area of the working cylinder (1) and the cross-sectional area of the rod (2);

P54excess - mentioned pressure fluid in the chamber of the expansion (5) in relation to the pressure of the fluid in the compression chamber (4).

The excess pressure of the said liquid in the chamber of the expansion (5) with respect to pressure this is hidcote in the compression chamber (4) at the time of opening the said valve stretching is described by equation (E20).

where

P54excess - mentioned pressure fluid in the chamber of the expansion (5) in relation to the pressure of the fluid in the compression chamber (4);

With2- stiffness of the second elastic element (11);

Le2the deflection of the second elastic element (11);

Sk2- the area of the outlet of the inlet channel (7) of the valve extension.

The deflection of the second elastic element (11) is described by equation (e21).

where

Le2the deflection of the second elastic element (11);

D2the diameter of the second rod (19) in this cross-section of the rod;

Dn2- maximum diameter of the second rod (19)corresponding to the undeformed state of the second elastic element (11);

α2- the angle between the longitudinal axis of the second rod (19) and the internal conical surface of the second support (14).

Successive substitution of equation (E21) in equation (E20) and equation (E20) in equation (e19) yields equation (e19) to (e).

Substitution of equation (e4), which determines the value of D2in equation (e19.1) leads to the equality |Fr|=X2.

Thus, during the stretching mentioned suspension opening the said valve stretching occurs when the equality of the power module resistance |Fr| and upomyanutoj the given values of X 2corresponding to the current cross-section of the second rod (19).

As

- at the working length of the second rod (19), which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,

- at the working length of the second rod (19), which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is equal to 1% of the cast to the longitudinal axis of the damper module static values mentioned by the elastic force,

- flow section referred to throttle corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned pendants

- flow section mentioned valve tension in any phase of the opening of this valve corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, Tangen is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned pendants

the module mentioned resistance is changed in accordance with equations (I) and (e) for the case of V<0, that is, considering the device provides an implementation of the proposed method during the stretching mentioned suspension.

The possibility of achieving the stated technical result using the proposed method for the case of damping oscillations of the electromagnetic oscillating system is also confirmed by the above analysis of the reactions of mechanical oscillatory system. This assertion is based on the fact that the processes of development of vibrations in mechanical and electromagnetic oscillating systems are subject to the General laws. It is obvious from the comparison of equations (E5), (e) and (e)describing the mechanical oscillatory system with equations (E20), (e) and (e)describing the electromagnetic oscillating system.

Equation (E20) is equivalent to equation (E5).

where

ULthe electric potential difference acting on the electromagnetic inductance of the circuit (equivalent resultant force acting on the sprung mass);

Ucst- static value of the difference of electric potentials on the first floor is some capacity electromagnetic circuit (equivalent static force values of elasticity);

Ucd- deviation of the electrical potential difference in electric capacitance magnetic circuit from static values, positive values when the charge is greater than the static charge, and negative values at a charge less than the static charge (equivalent to the deviation of the elastic force from the static value);

Ur- the difference of electric potentials on the active resistance of the magnetic circuit (equivalent resistance);

U0- external constant electric potential difference applied to the electromagnetic circuit (equivalent to the weight of the sprung mass).

Equation (e) and (e) is equivalent to equations (e) and (e).

where

Ur- the difference of electric potentials on the active resistance of the magnetic circuit (equivalent resistance);

R1tangent of the angle dependence of the power module resistance between the module and the rate of change of electric charge capacity (the amount of active electric resistance of the electromagnetic circuit)corresponding to the condition:

R1>2×(L/C)0,5, where L is the inductance of the electromagnetic circuit, the value of electric capacitance magnetic circuit;

I - the current SC is the rate of change of electric charge capacity (strength of the electric current in the electromagnetic circuit), positive values with increasing charge, negative - decreasing;

X - mentioned current set value;

R2tangent of the angle dependence of the power module resistance between the module and the rate of change of electric charge capacity (the amount of active electric resistance of the electromagnetic circuit)corresponding to the condition:

0,0001×2×(L/C)0,5<R2<0,3×2×(L/C)0,5, where L is the inductance of the electromagnetic circuit, the magnitude of the electric capacitance of the electromagnetic circuit.

The proposed method of damping oscillations of the electromagnetic oscillating system, which is the electromagnetic resonant circuit, may be implemented using a device that regulates the amount of current active resistance circuit depending on the value of the current deviation of electric charge capacity of the circuit from static values according to the algorithm specified in the proposed method. An example of such a device can be a device, consisting of:

the first digital voltage meter (electric potential difference);

- second digital voltage meter (electric potential difference);

- digital control unit;

- resistive matrix type "R-2R", which changes its active fight is s depending on filed on the digital control code.

Resistive matrix included in the electromagnetic resonant circuit as its active electrical resistance. Measuring input of the first digital voltage meter connected to the electrical capacitance of the circuit and measures the potential difference on it. The measuring input of the second digital voltage meter connected to the resistive matrix and measures the potential difference on it. Outputs both digital meters are connected to the inputs of the control unit. The output control unit connected to the control input of the resistive matrix.

The device operates as follows. The first and second voltage meters measure current, potential difference in electrical capacitance of the circuit and the resistive matrix. The control unit performs the following operations:

- defines the static value of the potential difference in electric capacitance by calculating a permanent member of the decomposition in Fourier series according to the potential difference in electrical capacitance of the circuit from time to time;

- specifies the value of the module of the current deviation of the potential difference in electrical capacitance circuit from static values;

- determines the current direction of change module deflection potential difference in electrical capacitance circuit against static value (increase or Eisenia) by comparing two consecutive time values for this module;

- compares the current unit of potential difference on the active resistance circuit module of the current deviation of the potential difference on the electric capacity from static values and, given the current direction of change in modulus of the deviation of the potential difference on the container with static values and stored values of inductance and capacitance of the circuit, calculates the required current value of the active resistance of a path laid in his memory the algorithm of the proposed method;

- emits a corresponding control code to the control input of a resistive matrix.

Resistive matrix changes its current active electrical resistance in accordance with the received from the control unit code.

Experimental confirmation of the possibility of achieving the stated technical effect

The possibility of achieving the claimed technical effect is confirmed by the results of a comparative test of the car VAZ-2110 equipped with standard dampers (shock-absorbing struts), and the same car equipped with experimental dampers. Experimental dampers represented the first variant of the device for implementing the method.

The tests were carried out on roads R the importance of quality. Comparative runs were conducted professional driver test on the same roads with a maximum repetition mode and motion.

Figure 3-6 shows time diagrams of changes the dynamic tension in the element body, to which is fixed the front right side front suspension type "MacPherson". Dynamic tension in the element of a body is directly proportional to the resultant force acting on the vehicle, and the fluctuations of the force of clamping the wheel to the road (because the front suspension is rigidly connected with the wheel). A value of zero dynamic voltage corresponds to the condition of static equilibrium, positive values correspond to the excess force acting on the body, and the efforts of clamping the wheel to the road, compared with the static condition, while negative values correspond to the negative of the force acting on the body, and the efforts of clamping the wheel to the road, compared with the static condition.

As seen from the time chart, when using serial samples there were significant fluctuations in dynamic tension, which varied greatly depending on the quality of the road surface, and on the 16th second timing diagram of serial sample presented in figure 4, fixed pronounced prabhupadas. When using the present invention, the dynamic voltage insignificantly different from zero and had a small maximum deviation almost regardless of the quality of the road surface and driving style. Accordingly, the resultant force acting on the vehicle, tends to zero, and the force holding the wheel to the road, looked after its static value.

Were also made comparative tests for controllability. Maximum speed maneuver "pristavka" (abrupt change lanes for serial dampers amounted to 82 km/h, and in experimental dampers was 88 km/h Maximum speed turning radius of 25 meters and mass dampers 62 km/h, and in experimental dampers was 65 km/h

In addition, the operation of the car VAZ-2110, equipped with experimental dampers, on the run of about 20 thousand kilometers (approximately 60% of the mileage in urban areas and 40% of mileage in terms of country tracks) recorded a decline in average operational fuel consumption by 15 percent.

1. Method of damping oscillations of the oscillatory system containing at least one first element, which has an inertial property of the at least one second element, which, changing from the second state under the action of external in relation to this element of force, stores potential energy and thus creates a potential force acting on the associated element of the other elements of the oscillating system, and at least one third element, which is in the process of circulation of energy between the said first and second elements removes energy from the vibrating system by its expenditure for the performance of work outside the oscillatory system and generates a force of resistance, the module which is the direct dependence of the module of the speed change state referred to the second element, and which slows down the change, at which
reduce (increase) the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, if the current module mentioned resistance is greater (less) than the specified value
change mentioned preset value depending on the current state of this second element, at least part of the maximum interval value changes its state,
characterized in that
during reduction module deviations of the current state of this second element from the static state current set-mentioned set value is directly proportional to refer to the vector UE is mentioned resistance module of the current deviations mentioned potential forces mentioned second element from its static value.

2. The method according to claim 1, characterized in that
during reduction module deviations of the current state of this second element from the static state current set-mentioned specified value refer to the vector mentioned resistance module of the current deviations mentioned potential forces mentioned second element from its static value.

3. The method according to claim 1 or 2, characterized in that
set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned oscillatory system, if the current module mentioned power resistance equal to or less than the current mentioned given value,
set the angle of the mentioned dependence of the power module resistance from the module of the speed change state referred to the second element, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned oscillatory system, if the current module mentioned resistance more current referred to the given knowledge is to be placed.

4. The method according to claim 3, characterized in that
during the increase of the modulus of the deviation of the current state of this second element from the static condition set mentioned specified value not more than 10% from those listed to the vector referred to the force of resistance of the static module of the potential magnitude of the said force referred to the second element.

5. The method according to claim 4, characterized in that
change the current referred to the specified value in direct relation to the module current deviations mentioned potential forces mentioned second element from its static value, at most, on the part of maximum interval values of the deviations of a condition mentioned second element from the static state during the increase of the modulus of the deviation.

6. The method according to claim 5, characterized in that
perform damping of the oscillations of a mechanical oscillatory system, which is a suspension of a vehicle, in which the first-mentioned element oscillating system is the sprung mass of the vehicle, referred to as the second element of the vibrating system is elastic element mentioned suspension that associates mentioned the sprung mass of the vehicle with its unsprung mass, through which the aforementioned suspension is sprinked external perturbations, the said condition mentioned second element of the oscillating system is mentioned deflection of the elastic element, and the potential power of this element is the force of elasticity of the elastic element, said third element oscillating system is a damper that associates mentioned the sprung and unsprung masses of the vehicle, and which during the changes mentioned deflection of the elastic element generates a force of resistance, slowing down the change of the deflection, and a module which has a direct dependency on the module, the rate of change of the deflection,
set and change the angle of the mentioned dependence of the power module resistance mentioned damper unit rate of change of the above mentioned deflection of the elastic element,
set and change the mentioned preset value depending on the current deviations mentioned by the elastic force of the mentioned elastic element from its static value.

7. Device for damping oscillations of a suspension of a vehicle, which includes at least one elastic element, which generates a force of elasticity, acting on associated with these the elastic element of the sprung mass and unsprung mass of the vehicle, and represents a hydraulic telesc the microscopic damper, during the change of the deflection mentioned suspension creates a force of resistance, the module depends on module speed changes mentioned trough, and which contains
the working cylinder, the inner cavity of which is filled with liquid,
the stock, which is intended for the perception of external load and is mounted coaxially with the said work cylinder with the possibility of progressive (return) movement in said working cylinder under compression (tension) damper,
the inner cavity of the mentioned shaft, which communicates with the internal cavity referred to the working cylinder,
the piston, which is attached to the end of the said rod and divides the inner cavity referred to the working cylinder on the compression chamber, the volume of which decreases with compression of the damper, and the camera stretching, the amount of which decreases with tension damper,
valve compression, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said compression chamber, and the outlet of the said chamber stretching,
valve strain, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said chambers stretch, and the outlet side mentioned the second compression chamber,
the first shut-off element, which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said compression chamber,
the second closing element which is part of the mentioned valve extension overlaps the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said chambers stretch,
the first elastic element, the force of elasticity which prevents moving the first mentioned locking element under the action of said liquid flowing from the said compression chamber, and which is part of the mentioned valve compression
the second elastic element, the force of elasticity which prevents the movement of this second locking element under the action of said liquid flowing from the said chamber stretching, and which is part of the mentioned valve stretching,
the first pillar, which interacts with the first-mentioned elastic element is a part of the said valve compression and is part of the internal surface, which is made conical,
the first guide element along which mentioned what I first bearing has an opportunity reciprocating movement in the direction of the first mentioned elastic element,
the second pillar, which communicates with the said second elastic element is a part of the said valve extension and is part of the internal surface, which is made conical,
the second guide element along which the above-mentioned second bearing has the ability reciprocating movement in the direction mentioned second elastic element,
the rod, which is attached to the bottom of the said compression chamber, a slide in said internal cavity mentioned rod under compression damper has a tetrahedral variable cross-section in the working portion of its length, which is equal to the maximum during the mentioned rod,
the first slot in the first mentioned guide element from the first side surface of the above-mentioned rod, and the axis perpendicular to the longitudinal axis of the rod,
the second hole made in the above-mentioned first guide element from the second side surface of the above-mentioned shaft, which is opposite to the first mentioned side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,
the third hole is made in the above-mentioned second guide element from the third side surface of the above-mentioned rod and the axis of which is perpendicular about Olney axis of the rod,
the fourth hole is made in the above-mentioned second guide element from the fourth side surface of the above-mentioned rod, which is the opposite referred to the third side surface of the rod and the axis of which is perpendicular to the longitudinal axis of the rod,
the first stop of cylindrical shape, which is mounted in said first hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said first lateral surface of the rod and its opposite end communicates with the tapered inner surface of the first mentioned support,
the second focus, which is identical to the aforementioned first stop mounted in said second hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said second lateral surface of the rod and its opposite end communicates with the tapered inner surface of the first mentioned support,
the third emphasis of cylindrical shape, which is referred to in the third hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said third side surface of the rod, and the opposite with the AMI end communicates with the tapered inner surface of the aforementioned second support,
fourth stop, which is identical to the aforementioned third stop, is set in the above-mentioned fourth hole with the possibility of reciprocating movement along the axis of this hole and one end communicates with said fourth lateral surface of the rod and its opposite end communicates with the tapered inner surface of the aforementioned second support,
the first reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface of the first mentioned stop and the surface of the first mentioned openings,
the second reactor, which connects the compression chamber with the said camera stretching and which is formed by a gap between the side surface of the aforementioned second stop and the surface of the aforementioned second hole,
characterized in that
each value of the above-mentioned deflection of the suspension corresponds to the cross section of the above-mentioned rod in the working portion of its length,
at the working length of the above-mentioned rod, the distance between the said first and the said second lateral surfaces of the rod in each cross section of the rod corresponds to the equation
L1=Ln1+2·tgα1·(X1/S1)·Sk1/C1,
where L1- the distance is their between the said first and the said second side surfaces of the above-mentioned rod in each cross section of the rod;
Ln1- the maximum distance between the said first and the said second side surfaces of the above-mentioned rod corresponding to the undeformed condition mentioned first elastic element;
α1- the angle between the longitudinal axis of the above-mentioned rod and cone inner surface of the first mentioned support;
X1corresponding to each cross section of the above-mentioned rod setpoint module mentioned resistance, which opens the said valve compression;
S1- the cross-sectional area referred to the working cylinder;
Sk1- the area referred to the outlet of the inlet channel mentioned valve compression;
C1- the rigidity of the first mentioned elastic element,
at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at the working length of the above-mentioned rod, the distance between the said third and said fourth side surfaces of the rod in each of the MD cross-section of the rod corresponds to the equation
L2=Ln2+2·tgα2·(X2/S2)·Sk2/C2,
where L2- the distance between the said third and said fourth side surfaces of the above-mentioned rod in each cross section of the rod;
Ln2- the maximum distance between the said third and said fourth side surfaces of the above-mentioned rod corresponding to the undeformed condition mentioned second elastic element;
α2- the angle between the longitudinal axis of the above-mentioned rod and cone inner surface mentioned second support;
X2corresponding to each cross section of the above-mentioned rod setpoint module mentioned resistance, which opens the said valve stretching;
S2- the difference between the cross-sectional area referred to the working cylinder and the cross-sectional area of the mentioned stock;
Sk2- the area referred to the outlet of the inlet channel mentioned valve stretching;
With2- rigidity mentioned second elastic element,
at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to the above is to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value.

8. The device according to claim 7, characterized in that
at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value.

9. The device according to claim 7 or 8, characterized in that
the flow area mentioned valve compression corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned suspension
the flow area mentioned valve stretching corresponds to the angle of inclination of the mentioned dependence of the power module t is tyuleniy unit rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned suspension
the total flow section of the mentioned first and said second inductors corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned suspension.

10. The device according to claim 9, characterized in that
at the working length of the above-mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is not more than 10% from those listed to the longitudinal axis of the damper static values mentioned by the elastic force,
at the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is not more than 10% from those listed to the longitudinal axis of the damper static values mentioned by the elastic force.

11. The device according to claim 10, characterized in that
at most, on the part of the working length of the mentioned article is Rina, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at most, on the part of the working length of the above-mentioned rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value.

12. Device for damping oscillations of a suspension of a vehicle, which includes at least one elastic element, which generates a force of elasticity, acting on associated with these the elastic element of the sprung mass and unsprung mass of the vehicle, and represents a hydraulic telescopic damper, which at the time of the change of the deflection mentioned suspension creates a force of resistance, the module depends on module speed changes mentioned trough, and which contains
the slave cylinder, I heard the Yaya cavity which is filled with liquid,
the stock, which is intended for the perception of external load and is mounted coaxially with the said work cylinder with the possibility of progressive (return) movement in said working cylinder under compression (tension) damper,
the piston, which is attached to the end of the said rod and divides the inner cavity referred to the working cylinder on the compression chamber, the volume of which decreases with compression of the damper, and the camera stretching, the amount of which decreases with tension damper,
valve compression, which has at least one inlet channel, which has an input hole of the said compression chamber, and the outlet from the other cameras mentioned damper
valve strain, which has at least one inlet channel, which is made in the above-mentioned piston and has an input hole of the said chambers stretch, and the outlet of the said compression chamber,
the first shut-off element, which is part of the mentioned compression valve, closes the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said liquid flowing from the said compression chamber,
the second closing element which is part of the mentioned valve extension overlaps the mentioned outlet of the inlet channel of the valve and is mounted for movement under the action of said fluid, flowing from the above-mentioned camera stretching,
the first elastic element, the force of elasticity which prevents moving the first mentioned locking element under the action of said liquid flowing from the said compression chamber, and which is part of the mentioned valve compression
the second elastic element, the force of elasticity which prevents the movement of this second locking element under the action of said liquid flowing from the said chamber stretching, and which is part of the mentioned valve stretching,
the first pillar, which interacts with the first-mentioned elastic element is a part of the said valve compression and is part of the internal surface, which is made conical,
the first guide element, along which the first mentioned bearing has the ability reciprocating movement in the direction of the first mentioned elastic element,
the second pillar, which communicates with the said second elastic element is a part of the said valve extension and is part of the internal surface, which is made conical,
the second guide element along which the above-mentioned second bearing has the ability reciprocating movement in the direction mentioned second elastic element,
trichomania fact, what
contains the compensation chamber, which is separated from the compression chamber wall and partially filled mentioned liquid
includes bypass valve, which connects the compression chamber with the said camera strain during compression of the damper and has a negligible resistance to the expiration of the said liquid from the said compression chamber,
mentioned headrace canal mentioned valve compression is performed in the above-mentioned partition and has an output hole of the said compensation chamber,
contains the first rod, which is mounted coaxially with the said work cylinder inside the first mentioned guide element with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the above-mentioned rod-shaped body of rotation with a concave or convex lateral surface,
one end of the first mentioned rod is located in said compression chamber, and the working length of the rod is located in said compensation chamber,
contains the second rod, which is mounted coaxially with the said work cylinder inside the mentioned second guide element with the possibility of longitudinal movement and the working portion of its length which is less than the maximum stroke of the aforementioned rod, made in the form of rotation of a body with a concave or convex lateral surface,
contains at least first and second holes made in the above-mentioned first guide element, and an axis which is perpendicular to the longitudinal axis of the first mentioned rod,
contains at least third and fourth openings made in the above-mentioned second guide element, and an axis which is perpendicular to the longitudinal axis referred to the second rod,
contains at least first and second identical balls are installed respectively in said first and second holes with the possibility of reciprocating rolling along the axis of these holes, and each of which one side interacts with the side surfaces of the first mentioned rod, and the opposite side communicates with the tapered inner surface of the first mentioned support,
contains at least third and fourth identical balls are installed respectively in said third and fourth holes with the possibility of reciprocating rolling along the axis of these holes, and each of which on one side communicates with the side surface of the aforementioned second rod, and the opposite side communicates with the tapered inner surface of the aforementioned second support,
soda is separated by the third leg, which is connected with located in the compression chamber by the end of the first mentioned rod,
contains the fourth pillar, which is connected with reversed in the direction of the said compression chamber by the end of this second rod,
contains the first spring which is installed between the said third support and said fourth support
contains a second spring which is installed between the said third support and said partition, and stiffness which relates to the rigidity of the first mentioned spring, as the maximum speed mentioned rod to the length of the work area first mentioned rod,
contains a third spring which is installed between the above fourth pillar and the said piston, and stiffness which relates to the rigidity of the first mentioned spring, as the maximum speed mentioned rod to the length of the work area referred to the second rod.

13. The device according to item 12, characterized in that
each value of the above-mentioned deflection of the suspension corresponds to the cross-section of the first mentioned rod in the working portion of its length,
each value of the above-mentioned deflection of the suspension corresponds to the cross-section referred to the second rod in the working portion of its length,
at the working length of the first mentioned rod, the diameter of each of the om cross-section of the rod corresponds to the equation
D1=Dn1+2·tgα1·(X1/S1)·Sk1/C1,
where D1- the diameter of the first mentioned rod in each cross section of the rod;
Dn1- maximum diameter of the first mentioned rod, corresponding to the undeformed condition mentioned first elastic element;
α1- the angle between the longitudinal axis of the first mentioned rod and cone inner surface of the first mentioned support;
X1corresponding to each cross-section mentioned first rod setpoint module mentioned resistance, which opens the said valve compression;
S1- the cross-sectional area of the mentioned stock;
Sk1- the area referred to the outlet of the inlet channel mentioned valve compression;
C1- the rigidity of the first mentioned elastic element,
at the working length of the first mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at the working length upomyanutoj the second rod, the diameter of each cross section of the rod corresponds to the equation
D2=Dn2+2·tgα2·(X2/S2)·Sk2/C2,
where D2the diameter of this second rod in each cross section of the rod;
Dn2- maximum diameter of this second rod corresponding to the undeformed condition mentioned second elastic element;
α2- the angle between the longitudinal axis of this second rod and cone inner surface mentioned second support;
X2corresponding to each cross-section mentioned second rod setpoint module mentioned resistance, which opens the said valve stretching;
S2- the difference between the cross-sectional area referred to the working cylinder and the cross-sectional area of the mentioned stock;
Sk2- the area referred to the outlet of the inlet channel mentioned valve stretching;
With2- rigidity mentioned second elastic element,
at the working length referred to the second rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations upomyanutyi elasticity from its static value.

14. The device according to item 13, wherein
at the working length of the first mentioned rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at the working length referred to the second rod, which corresponds to the compressed condition mentioned suspension referred to the specified value X2for each cross-section of the rod is reduced to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value.

15. The device according to item 13 or 14, characterized in that
the flow area mentioned valve compression corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned suspension
the flow area mentioned valve stretching corresponds to the angle mentioned zavisimost and power module resistance between the module and the rate of change of deflection, the tangent of which is less than 30% and more than 0.01% of the maximum tangent angle of this dependence, which corresponds to oscillatory perturbations are damped mentioned suspension
contains at least one orifice that connects the mentioned internal cavity referred to the working cylinder with the compensatory camera,
the flow area mentioned throttle corresponds to the angle of inclination of the mentioned dependence of the power module resistance between the module and the rate of change of deflection, the tangent of which is more than the minimum tangent of the angle of inclination of this dependence, which corresponds to the aperiodic damping of the perturbations mentioned suspension.

16. The device according to item 15, wherein
at the working length of the first mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is not more than 10% from those listed to the longitudinal axis of the damper static values mentioned by the elastic force,
at the working length referred to the second rod, which corresponds to the extended condition mentioned suspension referred to the specified value X2for each cross-section of the rod is not more than 10% from those listed to the longitudinal axis of the damper static values in Omanthai the elastic force.

17. The device according to item 16, characterized in that
at most, on the part of the working length of the first mentioned rod, which corresponds to the compressed condition mentioned suspension referred to a specified value of X1for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value,
at most, on the part of the working length referred to the second rod, which corresponds to the extended condition mentioned suspension referred to a specified value of X2for each cross-section of the rod is directly proportional to refer to the longitudinal axis of the damper and associated with that cross-section of the rod module deviations mentioned by the elastic force from its static value.



 

Same patents:

FIELD: transport.

SUBSTANCE: invention relates to railway transport. The system contains vertical hydraulic dampers installed under body. Each damper is made as piston pump with discharge and free-flow intercommunicating via throttle chambers for working fluid. The throttle is equipped with rod of variable cross-section with thrusts for end positions. Throttle rod movement drive is made as return spring and solenoid. Solenoid core is connected with throttle rod. Solenoid coils are attached to output terminals of control unit. Input terminals of control unit are connected with electric power source and oscillation frequency sensors installed on body in the area of each damper location. Control unit provides automatic change of end positions of throttle rod by solenoid electric power switching on or off according to indications of corresponding sensors of body vibration frequency.

EFFECT: design simplification and improvement of car movement smoothness.

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FIELD: machine building.

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Vibration isolator // 2480643

FIELD: machine building.

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5 dwg

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FIELD: mechanics.

SUBSTANCE: invention relates to devices designed to reduce vibration and shock effects, and may be used in designing anti-vibration and anti-shock protection of whatever engineering systems and structures. The damper incorporates a rod, damping elements and plates. The rod is a multi-layer design, the layers featuring different acoustic susceptibility. Every layer is fabricated as a thin-wall cylinder supported by a leg and having a thread made on the cylinder inner surface and the leg outer surface. The damper is provided with tight casing filled with a liquid and fitted on the rod. The damping elements are made in the form of split plates forming the petals, every petal featuring a different intrinsic frequency of elastic oscillations. Higher rigidity of coupling is provided.

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FIELD: machine building.

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6 dwg

FIELD: machine building.

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EFFECT: decreased dimensions, higher capacity, reduced dynamic load transmitted to damped entity.

2 cl, 3 dwg

Vibration isolator // 2480643

FIELD: machine building.

SUBSTANCE: vibration isolator contains the first and the second base, bearing flexible element and hydraulic damper attached between bases and two retainers. Hydraulic damper is made in a form of cylinder with piston and rod. At the bottom front part of the cylinder there is a subsidiary cavity and installed valve and throttling element. The valve is designed for fluid passing from subsidiary cavity to under-piston cavity of the cylinder. Subsidiary cavity is connected to above-piston cavity of the cylinder by hydraulic channel. Throttling element is designed for fluid passing from under-piston cavity into subsidiary cavity with obtaining stepped characteristic of dissipative force. The first retainer is attached to the first base and pin-connected to the rod. The second retainer is fixed on the second base and pin-connected to the cylinder. These two connections provide horizontal location of hydraulic damper.

EFFECT: increase of vibration isolation efficiency of objects via obtaining optimal stepped-falling characteristic of compensating influence.

5 dwg

FIELD: machine building.

SUBSTANCE: vibration damper includes a post, in which two hydraulic cylinders are located, one of which is located in horizontal plane, and the other one is located at an angle of 20° to vertical plane, which are connected to hydraulic system. Hydraulic cylinder includes a hollow plunger with a roller having the possibility of back-and-forth movement along a guide bushing. Plunger is connected to a flexible membrane fixed on the housing of hydraulic cylinder. Hydraulic cylinders are connected through connection pipes to a hydropneumatic accumulator through a check valve and a throttle controlled from the control system.

EFFECT: improving the efficiency and quick action of vibration damper.

3 dwg

FIELD: machine building.

SUBSTANCE: damper includes at least two chambers partially filled with liquid, which are interconnected with each other on their lower ends. At least one chamber is tightly closed on its upper end so that a closed air space is formed above liquid. At least one other chamber on its upper end is opened at least partially. Closed air space (V0) is divided at least into two air sections (V01-V0n). One air section (V01) is located immediately above liquid (3), and one or more air sections (V02-V0n) are connected to air section(V01) located immediately above liquid (3), and/or with the corresponding neighbouring air section (V02-V0n) through holes (7). Holes (7) are made so that they can be closed with a seal irrespective of each other by means of valves. Sensor (10) determines the load variation, and thus natural vibration frequency of facility or mechanism structure. Measurement values of sensor (10) are used with control unit (8) so that value of closed air space (V0) can be controlled by valve opening and closing.

EFFECT: achieving the possibility of adjusting the damping value with low energy consumption considering dynamically varying load.

6 cl, 10 dwg

FIELD: machine building.

SUBSTANCE: invention refers to damper devices, particularly those which use gas in the chambers with elastic walls. The device includes main flexible element (1), auxiliary flexible element (7) and dynamic oscillation absorber in the form of electric motor (22). Both flexible element are connected to each other with tough connection of upper end (16) of auxiliary tank (4) with base (18) of the auxiliary additional tank (10). Each flexible element is equipped with damping device consisting of electromagnetic valve, driven by the control system (21). Dampered object is connected to electropneumatic flexible element with supports (19) connected to the additional tank (4). Electric motor (22) is located at the bottom of auxiliary additional tank (10), connected to the control system (21) and has roll on the shaft with cable (25) reeled around it.

EFFECT: increase of damper properties.

3 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: device for damping mechanical oscillations consists of chamber, of flexible shell installed in chamber and forming pressure tight cavity. A cartridge with slots is installed inside this cavity by means of flanges. By means of pipelines and via an electric valve outside the chamber the pressure tight cavity of the shell is alternately connected to a source of compressed air and to atmosphere via an exhaust branch. A sensor of relative transfers is coupled with input of a control block of the electric valve, outputs of which are connected to winding of movable coils and electric valve. The chamber contains the flexible element and a slotted spring secured on rods and positioned with a little gap between the flexible element and the flexible shell. The procedure for damping mechanical oscillations consists in power and weight transfer between a deformed and an accumulating element by means of discrete commutation of flexible elements.

EFFECT: raised efficiency of oscillation damping in resonance zone.

2 cl, 2 dwg

Vibration isolator // 2382254

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

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