Automotive suspension adaptive damper

FIELD: transport.

SUBSTANCE: damper comprises working cylinder, control unit and accumulation tank. Piston with hollow rod is arranged inside working cylinder to displace therein. Said rod is closed by cover with elements for attachment to vehicle. Indirect-action controlled solenoid valve comprises distribution chamber and serial inlet chamber, outlet annular chamber, gate chamber and that of control valve. Working cylinder top cylindrical part accommodates limiting bush surrounding said rod. Rod bottom section has through upper working openings. Tube with spring-loaded valve with through lower working openings arranged at its lower end, inside said rod in piston, and rigidly secured therein. Closed cavity between rod and tube at rod top is communicated with inlet chamber of said controlled solenoid valve while tube top is communicated with distribution chamber of said solenoid valve.

EFFECT: higher reliability, simplified design.

8 dwg

 

The invention relates to mechanical engineering, in particular to hydraulic shock absorbers of vehicles, and can be used in the suspensions of vehicles.

Known hydraulic shock absorber of the suspension of the vehicle (Aigosthena, Gamerelated. The hydraulic shock absorber of the suspension of the vehicle. SU 1157292, IPC F16F 5/00; VS 17/04, Appl. 27.04.1983, publ. 23.05.85), comprising a housing with working cameras direct and reverse connected via a valve system, the compensation chamber and the rod attached to the shock absorber element associated with unsprung part of the vehicle, provided with axial channel and the radial Windows, blocked by a valve in the form of a spring-loaded mass, and the inlet channel connecting the camera forward stroke with Bolotnikova device, placed on the internal working surfaces of the housing and exits the spool device is connected by a channel with a reverse camera.

The presence of the compression valve on the piston determines the possibility of a breakout of the shock absorber at the end of the forward stroke. And the presence of a spool device with inertial mass makes it possible breakout of the shock absorber at the end of the reverse when driving on the "frequency profile", because in this mode, the inertial mass is constantly moving, the period of the Cesky opening the channel between cameras direct and reverse. The breakout of the shock absorber, as a rule, leads to rapid failure of the shock absorber, sharply reducing its reliability and durability.

Known adjustable shock absorber (Adjustable shock absorber. Program self-study 406. Adaptive control chassis DCC. Design and principle of operation. http://volkswagen.msk.ru the prototype), containing the guide of the piston rod, which concentrically sequentially fixed (outer) tube-reservoir, an intermediate cylinder and work (inner) cylinder. Inside the working cylinder moves the piston, which is located a piston valves, and at the base of the working cylinder is placed a valve compression. A piston fixed to the rod is moved along the guide. A closed annular cylindrical channel formed by the working and intermediate cylinders, the base and the guide rod, on the one hand is connected with the overflow drain with the working chamber 1 formed by a working cylinder and with the other input channel of an adjustable valve. Output channel controlled valve is connected with the working chamber 2 of the shock absorber formed by the tube - reservoir, an intermediate cylinder and the guide rod. Adjustable valve made according to the scheme of the hydraulic valve indirect action with electromagnetic control. The governing body of the valve is, consequently, the shock absorber as a whole, is an electromagnet, which fixes the position of the anchor associated with the cylinder and plunger. Depending on the amount of current supplied to the coil of an electromagnet, set a certain position of the head of the follower, and hence the area of the bore between the head of the plunger and the control plate in the control circuit of the valve, and along with it, and the degree of damping of the shock absorber.

The disadvantages of the prototype is that due to the nature of its design and organization of the working process when the shock absorber possible breakdowns as at the stage of compression, and phase damping, which inevitably leads to damage to the shock absorber with subsequent failure. This fact dramatically reduces the reliability of the shock absorber as a whole. The disadvantages of the prototype should also include some of the complexity of the design caused by the introduction into the circuit of an adjustable valve special valve Fail Safe for the implementation of the "Fail Safe"mode, and the impossibility of implementing this design shock absorber "locking mode", where the whole shock turns into a single rigid link. This mode is required for stabilization of the vehicle.

The basis of the invention is the technical problem consisting in increasing the reliability and service life of the shock absorber due to the exclusion of the possibility of a breakout of the shock absorber when it is working, as well as in the implementation of "locking mode", and the simplification of the structure when it is cheaper.

This task is solved in that the absorber containing fixed in the guide rod slave cylinder with fasteners to the vehicle, within which is movably placed a piston with a hollow stem that is moved in the guide and close the top cover with fasteners to the vehicle and containing a control unit, tank and adjustable solenoid valve indirect actions, including the distribution cavity, and consistently placed in the input cavity, the output ring cavity, the cavity of the valve and the cavity of the control valve in the cavity of the valve placed the main valve is a valve with a Central throttle opening, clamped to the spring case that may overlap with the input cavity and the output ring cavity, and the cavity of the control valve is placed control valve direct acting, clamped to the spring case and is rigidly connected with the armature of the controlling electromagnet, functionally connected with the control unit, according to the invention, the upper cylindrical surface of the working cylinder mounted guide sleeve covering the stock, in the lower part of the stem is made through ve is hnie working Windows, inside rod, piston rigidly and concentrically attached tube, the lower end of which is movable in the axial direction is set valve through lower operating Windows, squeezed from a tube spring, a closed cavity between the rod and the tube in the upper part of the rod is connected by pipeline to the input cavity is controlled solenoid valve, the tube is in its upper parts are connected by pipeline to a distribution cavity controlled solenoid valve, input and distribution of oral controlled solenoid valve are connected by the bypass valve, distribution and output ring cavity controlled solenoid valve are connected by the bypass valve, the output ring cavity adjustable electromagnetic the valve is connected by pipeline to a storage tank.

The invention is illustrated by drawings, where: figure 1 shows a diagram of the shock absorber at phase end; figure 2 - diagram of the shock absorber in the compression phase; figure 3 - diagram of the shock absorber at the last moment the compression phase; figure 4 - diagram of the controlled electromagnetic valve; figure 5 (a, b, C, d, e, f, g, h) is a view of a possible implementation form of the working window (view. A); figure 6 - a qualitative picture of the dependence of square F-section working the th window of the height h of the lumen of the working window in moments of overlap of the piston of the working window at the approach of the piston to the border of the working area; 7 is a graph of dependence of ring gap Z in the pipe bore control valve of the value I of the control current in the regulated solenoid valve; Fig - operating characteristic of the shock absorber on the various adjustment modes.

The absorber consists of the working cylinder 1, within which is movably mounted a piston 2 mounted on the hollow rod 3 is moved along the guide 4, and restrictive bushing 5. The top of the stem is closed by a cover 6. In stock, in its lower part, is made from the upper working end-to-end Windows 7. Inside the stock posted by tube 8 rigidly connected with the piston 2 and the cover 6. Inside the tube 8, in the bottom, placed the valve 9, which can move along it in the axial direction under the action of the spring 10 is constantly striving to take the extreme lower position, as shown in figure 1. In the valve, in its lower part, the lower working end-to-end window 11.

The rod 3 forms with the tube 8 is closed annular cavity 12, in which the lower part can be reported due to the presence of the upper working Windows 7 with newportnews cavity 13, and at the top through pipe 14 to the input cavity 15 of the controlled electromagnetic valve 16. Internal closed cavity 17 of the tube 8 in the lower part may be reported due to the presence of the bottom of the working window 11 with podpornoy on the spine 18, and at the top through pipe 19 distribution cavity 20 of the controlled electromagnetic valve 16.

Working Windows (as the upper 7 and lower 11) can be made as a through hole defined profile in the plan may have, for example, a triangular profile - figa, figb, square profile - FIGU, rectangular profile - Figg etc. Profile working Windows 11 and 7 are identical to each other and is selected based on the need of implementation in each case the desired law of motion of the rod when approaching it to the extreme and boundary conditions.

The shock absorber using the nodes 21 and 22 (e.g., eyes) attached to the corresponding elements of the suspension of vehicles.

The width H of the bounding sleeve 5 must be greater than the height H1working Windows 7

Adjustable solenoid valve 16 according to the functional performance is a hydraulic valve indirect action with electromagnetic control. It includes the main valve (shut-off and control element) - the valve 23, which is tightened under the action of the spring 24 and the annular surface 25 to the annular surface 26 of the adjustable solenoid valve 16. In the center of the valve 23 has a throttle orifice 27 of small diameter. Moving the main valve to protect and 23 controls the control valve 28 - small valve direct acting, which is released from the control plate 29 of the valve 16 by the spring 30. Head (right end) of the control valve 28 is made in the form of a cone 31 connected by a smaller diameter of the bounding disk 32.

Control valve 28 is rigidly connected with the armature 33 of the electromagnet, the contacts 34 and which, further, the coil 35 is supplied control current I.

On the outer surface of the armature 33 is made of an axial groove 37 through which the cavity of the control valve 38 is communicated with the cavity 39. Cavity 13, 18, 12 and 17 are filled with oil.

In the input cavity 15 and the distribution cavity 20 of the controlled electromagnetic valve 16 is provided by the bypass valve 40 and 41 made of, for example, in the form of an elastic plate of low rigidity.

The shock absorber works as follows.

At phase end, when moving rod 3 and piston 2 upward, as shown in figure 1, the oil from the cavity 13 is displaced by the piston 2 through the upper working Windows 7 in a closed cavity 12 and then flows through the pipe 14 into the input cavity 15 of the controlled electromagnetic valve 16, and then, bypassing the annular gap width X between the annular surface 25 of the valve 23 and the annular surface 26 of the adjustable solenoid valve 16 in the output ring cavity 42 of the controlled electromagnetic valve 16, Kotor is connected through window 43 to the junction cavity 20 of the controlled electromagnetic valve 16. From the distribution cavity 20 oil through the pipe 19 enters the cavity 17 and then through the lower working window 11 in podporchennuyu cavity 18, to complement its increasing volume.

Note that throughout phase release a certain quantity of oil, by volume, is equal to the volume displaced from the cavity 13 of the rod 3 passes through the pipe 44 from the cavity 45 of the storage tank 46 to the output ring cavity 42 and, further, in the above-mentioned path in podporchennuyu cavity 18 of the shock absorber.

Communicating sections throttle openings 27 and ring gap Z between the cone 31 and the control plate 29 are selected comparable among themselves. Therefore, the flow of oil through the orifice 27 and the annular gap Z between the cone 31 of the control valve 28 and the control plate 29 is also commensurable with each other. As a result, the oil pressure in the cavity of the valve 47 is smaller than in the input cavity 15 of the electromagnetic valve 16, and the spring 24 is chosen such, that the power of N15oil pressure at the valve 23 from the input cavity 15 was balanced by a set of forces N47oil pressure-side cavity of the valve 47 and forces N24the elasticity of the spring 24

In the flap 23 occupies a position between the annular surfaces 25 of the valve and valve 26 is 16 is formed an annular gap X. Main volume of oil, overcoming the flow resistance in the annular gap X, comes from the output of the ring cavity 42 through the window 43, opening the bypass valve 41, into the distribution cavity 20 of the controlled electromagnetic valve 16 and then through the pipe 19, a closed cavity 17 and the lower working window 11 in podporchennuyu cavity 18 of the shock absorber, compensating caused the depression associated with the increase of its volume.

A slight amount of oil corresponding to very small (compared to the pipeline 14) to flow through the orifice 27 is supplied into the cavity 47 and then through the annular gap Z between the control plate 29 and cone 31 of the control valve 28 in the cavity 38 and via the control channel 48 in the annular cavity 42.

This process continues up until the upper boundary of the upper working Windows 7, corresponding to the cross section I-I, will not reach the plane of the annular surface 49 of the bounding sleeve 5. At this moment working Windows 7 yet fully open to the entire height H1. Upon further movement of the piston working Windows 7 gradually begin to overlap the bounding sleeve 5, i.e. the height h of the lumen of the working window begins to decrease from a value of H1to 0, and the area F of the cross section of the working window from the values of Fmaxto 0 (Fig.6).

<> We emphasize that when the piston 2 reaches the position at which the cross section II-II working Windows reached to the plane of the annular surface 49 of the bounding sleeve 5, working Windows 7 will be in effect (1), fully overlapped, i.e. at this moment

Thus, further movement of the piston due to nsimemory oil, it is impossible. Thus ruling out the possibility of a breakout of the shock absorber at the end of phase end, i.e. the possibility of collision plane 50 of the piston 2 with restrictive sleeve 5 with the dramatic tension of the shock absorber, which may be, for example, when driving the vehicle at high speed on rough roads, in particular when getting wheels in the road ditch.

Thus, section II-II upper working Windows 7, corresponding to the lower face working Windows 7, and the position of the plane of the annular surface 49 of the bounding sleeve 5 define the upper boundary position of the piston 2.

It should be borne in mind that, as the oil pressure in the cavity 13 (and hence in the input cavity 15 of the controlled electromagnetic valve 16 is much higher than in the cavity 20 (which is connected with the output ring cavity 42 of the controlled electromagnetic valve 16), the bypass valve 40 during all phases of the closed end.

We emphasize that the level of damping amortizationbased it is noted above the value of the hydraulic resistance in the annular gap X.

At the stage of compression, when the moving rod 3 and piston 2 downward, as shown in figure 2, the oil under pressure piston is displaced from podpornoy cavity 18 and is fed through the bottom of the working window 11 into the cavity 17 and then through the pipe 19 in the distribution cavity 20 of the controlled electromagnetic valve 16. The oil pressure relief valve 40 opens and the oil gets in the input cavity 15 of the controlled electromagnetic valve 16, filling, due to the presence of the pipeline 14, the cavity 12 and working Windows 7, increasing the volume of the cavity 13.

While part of the oil corresponding to the volume digaudio into the cavity 13 of the shaft 3, is derived without the annular gap width X between the annular surface 25 of the valve 23 and the annular surface 26 of the adjustable solenoid valve 16 in the output ring cavity 42 of the controlled electromagnetic valve 16 and then through the pipe 44 in the cavity 45 of the storage tank 46.

The subsequent path of the oil is the same as in the previous phase of the call.

The above process is repeated until such time as the valve 9 will not affect the stop 51. Thus, further movement of the piston 2 down will cause the lower valve 9 into the tube 8 until the moment when the upper boundary of the lower working Windows 11 corresponding to the cross section III-III, will not reach the plane of the annular surface 52 of the bottom is th end of the tube 8. At this point, the working window 11 is fully open to the entire height H1. Upon further movement of the piston 2 down working Windows 11 start (just as it was at phase end) gradually overlap tube 8, i.e. the height h of the lumen of the working window begins to decrease from a value of H1to 0, and the area F of the cross section of the working window from the values of Fmaxto 0 (Fig.6).

We emphasize that when the piston 2 reaches the position at which the lower edge of the lower working Windows 11 corresponding to the cross section IV-IV, reaches the plane of the annular surface 52 of the lower end of the tube 8, working Windows 7 will be fully covered, i.e. at this moment will be performing ratio (3). This position of the piston shown in figure 3. Thus, further movement of the piston down in the power of nsimemory oil, it is impossible. Thus ruling out the possibility of a breakout of the shock absorber at the end of the compression phase, i.e. the possibility of collision plane 53 of the piston 2 or other parts with the base of the working cylinder 1 with a sharp compression of the shock absorber, which may be, for example, when driving the vehicle at high speed on rough roads, in particular the impact of the wheel on the knoll.

Thus, section IV-IV of the bottom of the working window 11 corresponding to the bottom face of the working window 11, and the position to which Lavoy surface 52 of the lower end of the tube 8 define the lower boundary position of the piston 2.

It must be borne in mind that to exclude the ingress of air into the cavity 13 of the oil level in the absorber, namely in the cavity 54, must not be lower than the position indicated by the section V-V

Note that choosing a particular form of working Windows 7 and 11 can be formed one or another law of motion of the piston approaching its extreme positions II-II and IV-IV. In particular, choosing in the working window a shape corresponding to figa, you can implement a more gradual reduction of the area F of the cross section of the working window (curve 6.1 figure 6), and consequently a more gradual increase in the resistance of the shock absorber, i.e. more effective damping of the dynamic loads in the suspension of the vehicle.

It should also be borne in mind that when describing the design of the absorber tacitly assumed that working Windows 7 and 11 are of the same height equal to H1. In actual structures, based on the requirements of implementing the necessary performance, the window can have a different height.

It should be noted that in both of the two above phases, in phase and compression phase damping of the shock absorber at a constant control pressure in the control unit 55 on the adjustable solenoid valve 16, which is in the form of the control current I supplied to the contacts 34 (in this, the control valve 28 OST the fast fixed) coil 35, i.e. if the condition

I=Const

works like a conventional known construction non-adjustable shock absorbers. When this throttle mode is implemented through special recruitment and profiling forms working Windows 7 and 11, and valve mode through the appropriate selection of the stiffness of the spring 24 valves 23: by increasing the speed of the piston, i.e. by increasing the oil pressure in the input cavity 15 of the controlled electromagnetic valve 16 valve 23 automatically moves to the left, increasing the annular gap X between the annular surfaces 25 and 26. The latter circumstance leads to an increase in oil consumption through the annular gap X of the main valve and, as consequence, to decrease the resistance of the shock absorber, to decrease its degree of damping.

Thus, the adjustable solenoid valve 16 at a constant control pressure in the control unit 55 operates as a conventional unloading valve in a conventional unregulated absorber. One of these operation modes of the electromagnetic valve 16, the appropriate occasion

depicted in figure 4: if the control current I on the contacts 34 is equal to zero, the armature 33 under the action of the spring 30 leftmost limited, for example, the stop 56. In this case, the oil consumption witecka the future via the control channel 48 is defined by the annular gap Y between the bounding disk 32 and the control plate 29, since in this position (as will be shown below)

Here Z is the ring gap in the pipe bore control valve 28 to the gap between the conical surfaces 57 and 58 of the cone 31 and the control plate 29, respectively.

Note that the mode (4), known as the Fail Safe mode (program emergency motion) is one of the standard modes of operation of the shock absorber. It occurs, for example, when the failure of the control unit 55.

It should be noted that the proposed absorber, in contrast to the above case (4), allows a wide area, depending on road conditions, to adjust its operating characteristics - dependence of the force P on the rod from the value of the speed V of the rod (Fig)

I.e. in terms of functionality it is adaptive absorber.

This is achieved by external influences from the control unit 55, by changing the magnitude of the control current I at the contacts 34 of the coil 35. Consider these more General modes of operation of the shock absorber when the control unit 55 on the contacts 34 of the coil 35 is supplied control current I, i.e. we consider the cases when

In these cases, the anchor 33, and therefore the control valve 28, begins to act more electromagnetic the sludge N Ithat should be equal to the resultant of all forces acting on it

Here: N47- force oil pressure-side cavity of the valve 47 to the valve 28; N38- force oil pressure-side cavity of the control valve 38 to the control valve 28; N30the force of elasticity of the spring 30.

When the magnitude of the control current I to the electromagnetic force NI(left side of the equality (8)) is also increased by the corresponding amount. This leads to a slight shift control valve 28 to the right along the axis. The latter, in turn, causes the compression of the spring 30 and, consequently, leads to an increase in the magnitude of the force N30up until the right part of equality (8) does not increase by the same amount. Thus the equality (8) is again restored.

Thus, when the magnitude of the control current I at the contacts 34 of the coil 35, the control valve 28 is moved to the right along its axis, and the annular gap Z in the pipe bore control valve is reduced (7). Reduction ring gap Z automatically causes the reduction of the flow of oil through it and, as a consequence - increase in oil pressure in the cavity of the valve 47 and the appropriate power of N47(the right part of equality (2) is increased). But this circumstance causes a shift salonki right along its axis (unloading the spring 24), at the same time (proportionally) to reduce the amount of force N24the elasticity of the spring 24 to the extent that the equality (2) is recovered. However, moving to the right of the valve 23 causes the reduction of the annular gap X, i.e. an increase in the hydraulic resistance of the electromagnetic valve 16, and hence increase the degree of damping of the shock absorber.

Thus, when the magnitude of the control current I at the contacts 34 of the coil 35, the degree of damping of the shock absorber is also increasing.

It should be noted that the performance of the main working surface of the control valve 28 in the form of a tapered cylindrical surface 57 connected by a smaller diameter of the bounding disk 32, on the one hand, helps to reduce the axial size of the valve, and on the other, extends the capability of varying the operating characteristics of the valve due to the possibility of varying the additional parameter - the angle of the tapered cylindrical surface 57. The presence of the restraining disc 32 allows to exclude from the scheme additional special valve Fail Safe, necessary in the prototype to implement a "Fail Safe"mode, which contributes to simplification of the structure.

We emphasize that the "technological" range

in real who's designs are impractical to use because of the inevitable errors.

The value of the control current

I=I1

corresponds to the operation of the shock absorber in the "low degree of damping" (mode "Comfort") - curve 1 in Fig. This mode is in demand when driving on bad roads.

The value of the control current

I=I2

corresponds to the operation of the shock absorber in the normal degree of damping" (the "Normal"mode) - curve 2 on Fig. This mode is in demand when driving in normal traffic conditions.

The value of the control current

I=I3

corresponds to the operation of the shock absorber with high degree of damping ' ('Sport') curve 3 Fig. This mode is in demand when riding at high speeds on good roads.

Note that (7)

0<I1<I2<I3<Imax,

and

0<Z3<Z2<Z1<Zmax.

It should be emphasized that the proposed absorber, in contrast to the known, also allows you to implement "locking mode"

I=Imax→Z=0,

wherein a ring gap Z is equal to zero. In this case, the oil pressure in the cavities 15 and 47 aligned and the valve 23 under the action of the spring 24 occupies the extreme right position. This annular surface 25 of the valve 23 is pressed against the annular surface 26 of the electromagnetic valve 16 and the annular gap X becomes zero.

I=I max→Z=0→X=0.

Cavity 15 and 42 of the electromagnetic valve 16 closed and the movement of the piston and rod is locked. The shock absorber becomes one hard link. The locking mode is required, for example, to stabilize the vehicle during cornering, when the rolls, as well as when braking and acceleration - i.e. when "pitching" of the vehicle.

In conclusion, we note that for mode (4), as already mentioned, the following relation holds : (5). Will check it. In practice, the value of Y is advisable to choose from the condition (7)

Then taking into account (10) in the interval (9) function (6) graphically would be 7.1 (Fig.7).

Thus, the use of the proposed design solution absorber will increase its reliability, durability, due to avoid the possibility of electrical breakdown of the shock absorber in its work to simplify and, therefore, reduce the cost of construction by eliminating special valve Fail Safe for the implementation of the "Fail Safe"mode, to extend the functionality of the shock absorber due to the emergence of the possibility of implementing the locking mode.

Adaptive shock absorber of the suspension of the vehicle containing fixed in the guide rod slave cylinder with fasteners to the vehicle, within which is movably placed the piston with alum shaft, roaming in the guide and close the top cover with fasteners to the vehicle and containing a control unit, tank and adjustable solenoid valve indirect actions, including the distribution cavity, and consistently placed in the input cavity, the output ring cavity, the cavity of the valve and the cavity of the control valve in the cavity of the valve placed the main valve is a valve with a Central throttle opening, clamped to the spring case, which may overlap with the input cavity and the output ring cavity, and the cavity of the control valve is placed control valve direct acting, clamped to the spring case and is rigidly connected with the armature of the control electromagnet, functionally connected with the control unit, characterized in that the upper cylindrical surface of the working cylinder mounted guide sleeve covering the stock, in the lower part of the stem is made through the upper working Windows, inside rod, piston rigidly and concentrically attached tube, the lower end of which is movable in the axial direction is set valve through lower operating Windows, squeezed from a tube spring, a closed cavity between the rod and the tube in the upper part of the rod is connected by means of the Tr is aprovada with the input cavity is controlled solenoid valve, the tube is in its upper parts are connected by pipeline to a distribution cavity controlled solenoid valve, input and distribution of oral controlled solenoid valve are connected by the bypass valve, distribution and output ring cavity controlled solenoid valve are connected by the bypass valve, the output ring cavity controlled solenoid valve is connected by pipeline to a storage tank.



 

Same patents:

FIELD: transport.

SUBSTANCE: damper comprises external tube secured on rod guide, idle cylinder and working cylinder with piston secured on rod. Indirect-action controlled solenoid valve is arranged inside said tube. Valve inlet communicates with chamber composed by said working and idle cylinders. Valve outlet communicates with chamber made by idle cylinder and tube. Working cylinder piston and rod end chambers are communicated with chamber made by external tube and idle cylinder by means of bypass valves arranged in rod guide and base. Working cylinder walls have through working walls to communicate piston and rod end chambers with chamber made by working and idle cylinder. Bypass valve is arranged at lower working opening.

EFFECT: higher reliability, simplified design.

9 dwg

FIELD: machine building.

SUBSTANCE: damper comprises reservoir to accommodate viscous fluid. Web divides reservoir inner into two chambers. Opening made in web allows communication between said chambers via variable-cross-section adjustable duct. Said opening is provided with viscous fluid restrictor. The latter comprises adjustable duct shaping element with through hole arranged to displace linearly. Annular elastic element is arranged between shaping element face and web side surface. Seat comprises backrest, headrest, actuator and retainer. Unlocking appliance incorporates mechanism for converting load in rotation and mechanism incorporating said damper.

EFFECT: damper stiffness adjusted in response to impact force, adjustable headrest.

25 cl, 23 dwg

FIELD: machine building.

SUBSTANCE: pneumatic damper consists of case and hollow piston forming closed working volume for working medium and of fasteners of device or system. A free of fastening edge of the case is equipped with a device consisting of brake shoes and a drive pressing them at a proper moment to external surface of the hollow rod with required force. The first and the second additional closed volumes are communicated with working volume by means of valve units and are made as separate tanks of high and low pressure with devices of automatic inlet and outlet of working medium from closed working volume. A processor controls operation of devices for inlet and outlet and also operation of a drive of the brake shoes. By means of sensors the processor continuously tracks specified working parametres of the damper according to one or a rank of programmed damping characteristics. The tanks can be replaceable, while the processor is common for several dampers.

EFFECT: simplified design, upgraded quality of damping and reliable contact of vehicle wheel with road bed.

4 cl, 1 dwg

FIELD: transport.

SUBSTANCE: spring comprises air spring 1, unloader vessel 2, compressor 3, pickup of pressure difference between unloader vessel 2 and air spring 1, unloader valve 7, pickup of position C of spring connection with receiver of oscillations relative to point A of spring connection with oscillation source, air pump 9 with outlet 10 and inlet 11 valves. Tube 5 communicates compressor 3 and unloader vessel 2. Tube 6 communicates air spring 1 and unloader vessel 1. Tube 12 communicates inlet valve 11 with intake tank 14. Tube 13 communicates unloader valve 7 with intake tank 14. Air spring 1 is additionally communicated via tubes 5 and 6 with unloader vessel 2 and compressor 3. Pressure difference pickup is communicated with sir spring 1, unloader vessel 2 and unloader valve 7. Position pickup 8 is communicated with compressor 3 and unloader valve 7.

EFFECT: ruling out transport facility body vibrations.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building and can be used to control vibrations of damped mass and to stabilise its static position. Said system comprises suspension that incorporates hydraulic engine with double-acting electro hydraulic booster. Hydraulic engine plunger is articulated via flexible element with stabilised mass. Hydraulic engine power cylinder casing is coupled via flexible element with wheel axle or vehicle frame. Said system incorporates controller to generate control law on the basis of preset reference properties of motion and current state of stabilised mass and hydraulic engine plunger. One of controller inputs is connected via acceleration transducer with stabilised mass, while another input is connected via power cylinder casing current collector and double-way rod bars with feedback potentiometre. The latter controls power cylinder plunger positions at every time interval. Controller output is connected with electro hydraulic booster input.

EFFECT: reduced accelerations, higher accuracy of stabilisation.

1 dwg

FIELD: transport.

SUBSTANCE: system includes vertical hydraulic dampers installed under the body, car body vibration frequency sensors installed on the body in location area of each damper, car speed sensor, control unit, electric power supply. Each damper is made in the form of piston pump with pressure and free flow cavities for working liquid, which are interconnected with each other through a throttle. Damper is equipped with throttle stock with possibility of regulating resistance coefficient owing to covered throttle hole. Stock of throttle of each damper is equipped with the drive made in the form of electromagnet the core of which is connected to throttle stock. Outputs of car body vibration frequency sensors, car speed sensor, electric power supply are connected to control unit inputs. Coil of electromagnet of each damper is attached to the appropriate control unit output. Control unit provides automatic supply of the required value of the necessary electric signal to electromagnets of each damper.

EFFECT: increase of quality of vibration protection.

2 cl, 1 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

Dynamic damper // 2374520

FIELD: machine building.

SUBSTANCE: invention relates to devices of vibroprotective technology and is provided for reduction of oscillation intensity of object connected by bearing resilient member with basis. Damper contains oscillator, control assembly, the first and the second speed transducer, executive setting, electrically connected to outlet of control assembly. Oscillator is implemented in the form of mass connected to object by resilient member. The first speed transducer is installed on object and is connected to the first outlet of control assembly. The second speed transducer is installed on the basis and is connected to the second inlet of control assembly. Executive device is implemented in the form of hydraulic cylinder with pin and rod. Over-piston and under-piston cavities of hydraulic cylinder are connected to the first channel with built-in electric valve and the second channel with built-in throttle. Electric valve is electrically connected to outlet of control assembly. Hydraulic cylinder is pivotally fixed on object. Rod is pivotally fixed on the basis.

EFFECT: increasing the efficiency of object vibroprotection.

2 dwg

FIELD: machine building.

SUBSTANCE: invention relates to automotive machine building, particularly, to automotive cushioning systems. The proposed shock absorber comprises hydraulic cylinder filled with working fluid and accommodating piston and rod, and hydraulic accumulator. The rod lower part is furnished with radial throttling orifices and spring-loaded control plunger with edge covering aforesaid orifices. The said radial throttling orifices are spaced along the rod length so that the said control plunger jumps the orifices in turn, thus gradually varying the total flow section. The control plunger is fitted in the piston, outside the working fluid flows, and can deviate from its normal position only under gravity.

EFFECT: higher comfort and controllability of vehicle in running over irregular road coat.

3 dwg

Dynamic dampener // 2354867

FIELD: mechanical engineering.

SUBSTANCE: invention refers to mechanical engineering, particularly to dampeners of vibrations of mechanical engineering equipment. The dynamic dampener of vibrations consists of a case, divided into three chambers by means of elastic elements in form of membranes and an insertion. The upper and lower chambers are filled with magnetic liquid, while the middle one is filled with air. Systems of channels arranged in the insertion connect the upper and lower chambers. The case of the dampener is enveloped with a coil connected to a control block. From the sensor of vibration acceleration installed on the projecting rod of the insertion signals are transmitted to the control block.

EFFECT: expanding working range of frequency damping and its regulating.

1 dwg

FIELD: transport.

SUBSTANCE: damper comprises external tube secured on rod guide, idle cylinder and working cylinder with piston secured on rod. Indirect-action controlled solenoid valve is arranged inside said tube. Valve inlet communicates with chamber composed by said working and idle cylinders. Valve outlet communicates with chamber made by idle cylinder and tube. Working cylinder piston and rod end chambers are communicated with chamber made by external tube and idle cylinder by means of bypass valves arranged in rod guide and base. Working cylinder walls have through working walls to communicate piston and rod end chambers with chamber made by working and idle cylinder. Bypass valve is arranged at lower working opening.

EFFECT: higher reliability, simplified design.

9 dwg

FIELD: machine building.

SUBSTANCE: damper comprises reservoir to accommodate viscous fluid. Web divides reservoir inner into two chambers. Opening made in web allows communication between said chambers via variable-cross-section adjustable duct. Said opening is provided with viscous fluid restrictor. The latter comprises adjustable duct shaping element with through hole arranged to displace linearly. Annular elastic element is arranged between shaping element face and web side surface. Seat comprises backrest, headrest, actuator and retainer. Unlocking appliance incorporates mechanism for converting load in rotation and mechanism incorporating said damper.

EFFECT: damper stiffness adjusted in response to impact force, adjustable headrest.

25 cl, 23 dwg

FIELD: transport.

SUBSTANCE: hydraulic damper comprises high-pressure tube 10. Piston 14 divides tube 10 into compression chamber CC and draft chamber CT communicated via piston 14. Hydraulic fluid tank 14 communicates with compression chamber CC. Control valve VC communicates draft chamber CT with tank 20 and comprises tubular case 40 with radial channel open toward tubular case inner chamber and tank 20. Locking rod 60 displaces axially in tubular case 40 between control valve open and closed position to communicate draft chamber CT with tank 20. Actuator A displaces locking rod 60 in tubular case 40.

EFFECT: higher tightness, fine adjustment.

23 cl, 12 dwg

Hydraulic damper // 2457375

FIELD: machine building.

SUBSTANCE: proposed device comprises hollow case accommodating hydraulic cylinder to make working fluid chamber. Hydraulic cylinder piston and rod are arranged to produce piston and rod ends. Damping device is arranged between case and cylinder and furnished with cover coupled with structural element accommodating restrictor and safety valve to communicate said piston and rod ends with said chamber. Cover has annular groove with seal fitted therein and is arranged to make drain chamber communicated with aforesaid chamber. Annular groove with support and sealing elements fitted therein is arranged at structural element on rod side. Safety valve is made up of plunger with flanges and cylindrical guide housing locking element to move relative plunger flange for contact with seat arranged on structural element for communication of rod en with drain chamber and, further, with aforesaid chamber. Cover seal is made up of sealing scraper. Annular grooves in cover and structural elements are open toward drain chamber wherein adjusting washer with annular ledge is arranged to lock sealing scraper. Said locking element has toroidal grooves on working fluid flow path at safety valve open.

EFFECT: simplified design, expanded operating performances.

4 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: pneumatic suspension contains rubber-cord casing (1) with cover (2) forming main working cavity (3), additional cavity (4) and partition (5) positioned between them. On partition (5) there is secured a cylinder with the central axial orifice inside of which there is installed valve device (6). A shaped partition with an opening on a side facet is made inside the cylinder. At the side of the cylinder there is arranged winding of an electro-magnet covered with a cover and connected to control system (7) of the valve device. The valve device consists of a hollow shut-off element in form of a cube controlled with the electro-magnet and shutting-off the opening.

EFFECT: increased reliability of suspension operation at impact actions.

3 dwg

Hydraulic damper // 2409777

FIELD: machine building.

SUBSTANCE: damper consists of case, of enclosed in it cylinder, of rod installed in cylinder, of stop and piston with relief orifices arranged successively on rod, and of valve unit made as packages of disks of various diametre, upper of which interacts with stop. The stop has circular grooves on external surface, whereon there are loosely fit compressed disks of the valve unit; notably, the package of disks of smaller diametre interacts with the end of the grooving, while the package of the disks of bigger diametre interacts with the end of the piston. On the circular working face at the upper end of the piston there is installed the working package of flexible disks centred along external diametre in the central cavity of the fixed cover, positioned in side slots of the rod. The spring-loaded valve is loosely fit with its internal diametre on external surface of the rod, while with its lower end it overlaps internal diametre of the package of the flexible disks, thus facilitating a calculated gap between the lower end of the valve and the central stop of the piston.

EFFECT: increased stability of rebound valve operation.

4 dwg

Damper // 2408804

FIELD: machine building.

SUBSTANCE: damper consists of cylinder chamber filled with fluid, of piston installed inside cylinder chamber, of rod connected to piston and of accumulator. The accumulator facilitates generation of damping force produced by the piston rod due to fluid flow from the side of compression in the cylinder chamber. One coil of spiral damping groove is formed on internal periphery of the cylinder chamber within the ranges of piston stroke. Width of the damping groove is constant along its whole length. Depth of the damping groove is gradually diminishes along the spiral in the direction whereto the piston rod is pushed out. The length of the piston along axial line is less, than pitch of the damping groove.

EFFECT: simplified design and more efficient control of damping force of damper.

6 cl, 7 dwg

FIELD: automotive industry.

SUBSTANCE: invention relates to automotive industry, particularly to automotive shock absorbers. Proposed shock absorber comprises casing, cylinder, compensating chamber communicating, via throttling orifices, with the cylinder chamber, rotary controlled-from-outside ring to vary throttling orifice cross section, push rod, piston with bypass valve and blow-back valve, compression spring and guide bushing. Aforesaid rotary ring is fitted in the rod end and fixed to the compression spring end. The spring other end faces the piston and is fastened to the push rod. Ring surface in contact with the throttling orifice surface have various-cross section calibrated orifices. Turning the push rod in the guide bushing allow the channels to form, together with throttling orifices, through orifices with different cross section area.

EFFECT: increased shock absorber damping ability, possibility to adjust aforesaid ability.

3 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: invention relates to automotive machine building, particularly, to automotive cushioning systems. The proposed shock absorber comprises hydraulic cylinder filled with working fluid and accommodating piston and rod, and hydraulic accumulator. The rod lower part is furnished with radial throttling orifices and spring-loaded control plunger with edge covering aforesaid orifices. The said radial throttling orifices are spaced along the rod length so that the said control plunger jumps the orifices in turn, thus gradually varying the total flow section. The control plunger is fitted in the piston, outside the working fluid flows, and can deviate from its normal position only under gravity.

EFFECT: higher comfort and controllability of vehicle in running over irregular road coat.

3 dwg

FIELD: automotive industry.

SUBSTANCE: controlled hydraulic shock absorber comprises telescopic hydraulic two-tube shock absorber. The rod of the shock absorber is made of a hollow rod provided with the flange having a groove for roller thrust bearing and vertical slots from the other side. The hollow of the rod receives the hollow rod of by-pass valve for permitting vertical movement. The top section of the rod is provided with trapezium right thread, and the bottom section is provided with the stop for the spring of the valve. The driven pinion is screwed on the threaded part of the rod of the by-pass valve. The bottom of the driven pinion abuts against the roller thrust bearing that is mounted in the groove in the flange of the hollow rod. The second driven pinion is screwed on the threaded part of the valve rod. The top side of the pinion abuts against the roller thrust bearing. The third roller thrust bearing is interposed between the driven pinions. The driven pinions engage the driving gears mounted on the shaft of the electric motor. The control unit is connected with the electric motor and receives the signal from the pickups of suspension vibration and velocity pickup.

EFFECT: improved shock absorbing.

FIELD: transport.

SUBSTANCE: damper comprises external tube secured on rod guide, idle cylinder and working cylinder with piston secured on rod. Indirect-action controlled solenoid valve is arranged inside said tube. Valve inlet communicates with chamber composed by said working and idle cylinders. Valve outlet communicates with chamber made by idle cylinder and tube. Working cylinder piston and rod end chambers are communicated with chamber made by external tube and idle cylinder by means of bypass valves arranged in rod guide and base. Working cylinder walls have through working walls to communicate piston and rod end chambers with chamber made by working and idle cylinder. Bypass valve is arranged at lower working opening.

EFFECT: higher reliability, simplified design.

9 dwg

Up!