Automotive suspension adaptive damper

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

 

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, 27.04.1983), 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, periodically opening the anal 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 with 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 therefore and 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 of amortizat the RA by eliminating the possibility of a breakout of the shock absorber when it is working, as well as in the implementation of the "blocking mode" and simplify the design of the shock absorber.

This task is solved in that the adaptive shock absorber of the suspension of the vehicle containing fixed on the guide rod outer tube tank with annular cavities formed is also enshrined in the guide rod and the intermediate cylinder and the working cylinder within which the piston rod is fixed, the piston is moved in the working cylinder, and containing installed in the receiver-tank adjustable solenoid valve indirect actions, including sequentially placed in it the main valve-a valve with a Central throttle opening, biasing the inner surface of the electromagnetic valve spring, and a control valve direct acting, rigidly associated with the anchor control electromagnet, the inlet of the adjustable solenoid valve indirect actions connected with the cavity formed by the workers and the intermediate cylinder, and the outlet from the cavity formed intermediate the cylinder and the tube - reservoir, nadporshnevaya and podpornega cavity of the working cylinder is connected with a cavity formed by an outer tube-reservoir and the intermediate cylinder through the bypass valve, install the Lenno accordingly, in the guide stem and base, according to the invention, in the walls of the working cylinder, the upper and lower parts are through working Windows, connecting, respectively, nadporshnevaya and podporchennuyu cavity of the working cylinder with a cavity formed by the work and intermediate rolls, the lower the operating window is a bypass valve, and the piston is made of a monolithic, in addition, the cylinder control valve direct action is executed in the form of a cone, mud from the side of the smaller diameter of the bounding disk.

The invention is illustrated by drawings, where figure 1 shows a diagram of the shock absorber in the compression phase; figure 2 - diagram of the shock absorber at phase end; figure 3 - diagram of the shock absorber at the initial compression phase; figure 4 - diagram of the controlled electromagnetic valve; figure 5 (a, b, C, d, e, f, g, h) - some options for possible implementation form of the working window (view. A); figure 6 - a qualitative picture of the dependence of the square of the F section of the working 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 option possible run-shaped cross-section of the working window; Fig is a graph of dependence of ring gap Z in the pipe bore control valve of the value I operated the total current in the regulated solenoid valve; figure 9 - the operating characteristic of the shock absorber on the various adjustment modes.

The absorber consists of a concentrically arranged outer tube of the tank 1, the intermediate cylinder 2 and the working cylinder 3, the top of which is fixed on the guide 4 stem 5 connected to the monolithic (not containing valves or chokes) the piston 6. The piston 6 is placed movably in the working cylinder 3, which together with the intermediate cylinder 2 is fixed on the base 7. Tube-tank 1 bottom is closed by the cover 8. In the lower part of the guide 4 posted by-pass valve 9 is made, for example, in the form of an elastic plate of low rigidity. Similar to the bypass valve 10 is placed on the lower frame 11, which limits the extreme lower position of the piston 6. In the base 7 also has a similar bypass valve 12, overlying the inlet window 13. The working cylinder 3 forms with the intermediate cylinder 2 ring cavity 14, which, on the one hand, through the top of the working window 15 is communicated with newportnews cavity 16, and on the other, through the channel 17, with the inlet 18 of the controlled electromagnetic valve 19. Working window (as the upper 15 and lower 11) can be made as a through hole defined profile (figure 5), or as a hole of variable cross-section (7), the inner surface is knosti 20 which has the same profile, and the outer surface 21 may have a shape of a circle. The profile of the working window 11 and 15 are symmetrical relative to each other. The thickness H of the piston 6 must be greater than the height H1working Windows:.

Outer tube-tank 1 together with the intermediate cylinder 2 forms a ring cavity 22, through which the channel 23 is connected with the outlet 24 of the controlled electromagnetic valve 19. The shock absorber using nodes 25 and 26 (e.g., eyes) attached to the corresponding elements of the suspension of vehicles.

Adjustable solenoid valve 19 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 27, which is tightened under the action of the spring 28 and the annular surface 29 to the annular surface 30 of the controlled electromagnetic valve 19. In the center of the valve 27 has a throttle orifice 31 of small diameter. The movement of the main valve - valve 27 controls the control valve 32 is small valve direct acting, which is released from the control plate 33 of the valve 19 by the spring 34. The head (left end) of the control valve 32 is made in the form of a cone 35 connected by a smaller diameter of the bounding disk 36.

p> The control valve 32 is rigidly connected with the armature 37 of the electromagnet, the contacts 38 and which, further, the coil 39 is supplied control current I.

On the outer surface of the armature 37 is made of the axial groove 40 through which the cavity 41 and 42 are communicated with each other. The annular cavity 14 when you open the valve 10 may be communicated through the window 11 with podpornoy cavity 43. Cavity 22, 14, 16 and 43 are filled with oil.

The shock absorber works as follows.

At the stage of compression, when moving rod 5 and piston 6 downward, as shown in figure 1, the oil under pressure of the piston opens the valve 10 and through the working window 11 is displaced in the annular cavity 14, filling due to the presence of the working window 15 increasing the volume of the cavity 16. While part of the oil corresponding to the volume digaudio into the cavity 16 of the rod 5 passes through the channel 17 into the inlet 18 and then into the input cavity is controlled solenoid valve 19, and then, bypassing the annular gap width X between the annular surface 29 of the valve 27 and the annular surface 30 of the controlled electromagnetic valve 19 in the output cavity 44 of the controlled electromagnetic valve 19.

Due to the presence of the working window 15, the oil pressure in the cavities 43 and 16 is almost the same and much more than in the cavity 22, through which the channel 23 is connected with the outlet 24 reguliruemoj the electromagnetic valve 19. For this reason, at the stage of compression bypass valve 12 is closed.

Through cross section of the throttle orifice 31 and the annular channel between the cone 35 and the control plate 33 select comparable among themselves. Therefore, the flow of oil through the orifice 31 and the annular channel between the cone 35 of the control valve 32 and the control plate 33 is also commensurable with each other. As a result, the oil pressure in the cavity 45 is smaller than in the input cavity (inlet 18) solenoid valve 19, and the spring 28 is chosen such, that the power of N18oil pressure from the inlet 18 was balanced by a set of forces N45oil pressure from the cavity 45 and forces N28the elasticity of the springs 28:

In the flap 27 is a situation in which between the annular surfaces of the valve 29 and 30 of the valve 19 is formed an annular gap X. the main volume of oil, overcoming the flow resistance in the annular gap X, arrives from the cavity 44 through the outlet 24 of the valve 19 and the channel 23 in the annular cavity 22 of the shock absorber.

It is established that the level of damping of the shock absorber is determined by the above mentioned value of the hydraulic resistance in the annular gap X.

Minor same amount by weight of the a, the corresponding very small (compared with the input hole 18) to flow through the orifice 31 is supplied into the cavity 45 and then through the annular gap Z between the control plate 33 and the cone 35 of the control valve 32 in the cavity 41, and via the control channel 46 and the cavity 44 in the outlet 24 of the valve 19.

This process continues until the lower end plane 47 of the piston 6 reaches the position I-I (corresponding to the level of the upper border of the working window 11), wherein the working window 11 is fully opened to a height of H1. Upon further movement of the piston down the working window 11 is gradually closed by the piston 6, 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 in the plane 47 of the piston 6 position II-II working window 11, in view of (1), completely blocked, ie,

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 47 of the piston 6 with the base 7 with a sharp compression of the shock absorber, which may be, for example, when driving the vehicle at high speed on what erovnu the road, in particular, the impact of the wheel on the knoll.

Thus, the position II-II plane 47 of the piston 6, corresponding to the bottom face of the working window 11, defines the lower boundary position of the piston 6.

It should be noted that during the compression phase, in addition to the initial point, the bypass valve 9 is closed, since the oil pressure in the cavities 16, 43 and 14, i.e. in the input hole 18 of the controlled electromagnetic valve 19, more than in the cavity 22, which is connected with the outlet 24 of the controlled electromagnetic valve 19. For this reason, during the compression phase the bypass valve 12 is always closed.

At phase end, when moving rod 5 and the piston 6 up, as shown in figure 2, the oil from the cavity 16 is displaced by the piston 6 through the working window 15 into the cavity 14 and then flows through the channel 17 into the inlet 18 of the controlled electromagnetic valve 19. The subsequent path of the oil is the same as in the previous stage of compression. The only difference here is that due to some dilution in podpornoy cavity 43 of the bypass valve 12 is opened and the increase in the volume of oil in podpornoy cavity 43 is compensated by its flow through the inlet window 13 of the cavity 22, which is connected with the outlet 24 of the controlled electromagnetic valve 19. Since the oil pressure in the cavity 16 (i.e. in the input resp is rtii 18 adjustable electromagnetic valve 19 is much higher than in the cavity 22 (which is connected with the outlet 24 of the controlled electromagnetic valve 19), then the bypass valve 9 during all phases of the closed end.

The above process is repeated up until the upper surface 48 of the piston 6 reaches the position III-III (corresponding to the level of the lower border of the working window 15), wherein the working window 15 is still completely open to a height of H1. Upon further movement of the piston of the working window 15 (the same as it was at the stage of compression) is gradually closed by the piston 6, 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 in the plane 48 of the piston 6 provisions IV-IV working window 15, due to (1), fully overlapped, i.e. the execution of the relation (3). 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 48 of the piston 6 with the guide 4 of the stem with a sharp extension of the shock absorber, which may be, for example, when driving the vehicle at high speed on rough roads, in particular, when the wheels hit a hole in the road.

Therefore clicks the zoom, article IV-IV plane 48 of the piston 6 which corresponds to the top face of the working window 15, defines the upper boundary position of the piston 6.

Consider the initial movement of the piston 6 at the stage of compression of the extreme upper position, when his plane 48 still occupies the position of IV-IV (Fig 3). At this point in the cavity 16 creates a vacuum, under which the spill valve 9 is opened and the increase in the volume of the cavity 16 is compensated by the inflow of oil through the window 49 of the cavity 22. But this occurs only at a specified point, allowing you to avoid a gap in the continuity of the volume of oil in the cavity 16. In subsequent moments of time the oil in the cavity 16 will flow through the opening window 15 as described in the analysis of shock absorber in the compression phase.

It must be borne in mind that to exclude the ingress of air into the cavity 16, the oil level in the damper must not be lower than the position indicated by the section V-V

Note that choosing a particular form of working holes 11 and 15, it is possible to form a particular law of motion of the piston approaching its extreme positions II-II and IV-IV. In particular, choosing window 15 a shape corresponding to figure 5, and figure 5, it is possible to implement a more gradual reduction of the area F of the cross section of the working window (curve 6.1. figure 6), and therefore smoother took the giving of the resistance of the shock absorber, i.e. more effective damping of the dynamic loads in the suspension of the vehicle.

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 50 on the adjustable solenoid valve 19, which is in the form of the control current I supplied to the contacts 38 (in this, the control valve 32 remains stationary) coil 39, i.e. when 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 form of working holes 15 and 11, and valve mode through the appropriate selection of the stiffness of the spring 28 of the valve 27: by increasing the speed of the piston, i.e. by increasing the oil pressure in the input hole 18 of the electromagnetic valve 19, the valve 27 is automatically moved to the right, increasing the annular gap X between the annular surfaces 29 and 30. 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 electromagnetic valve 19 at a constant control in which deistvii from the control unit 50 functions as a conventional unloading valve in a conventional unregulated absorber. One of these operation modes of the electromagnetic valve 19, the appropriate occasion

depicted in figure 4: if the control current I on the contacts 38 are equal to zero, the armature 37 under the action of the spring 34 occupies the extreme right position, limited, for example, the stop 51. In this case, the flow rate of the oil flowing through the control channel 46, is defined by the annular gap Y between the bounding disk 36 and the control plate 33, as in this position (as will be shown below)

Here Z is the ring gap in the pipe bore of the control valve 32 is a gap between the conical surfaces 52 and 53 of the cone 35 and the control plate 33, 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 50.

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 stem (figure 9):

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

This is achieved by externally the impact from the control unit 50 by changing the magnitude of the control current I at the contacts 38 of the coil 39. Consider these more General modes of operation of the shock absorber when the control unit 50 on the contacts 38 of the coil 39 is supplied, the control current I, i.e. we consider the cases when

In these cases, the anchor 37, and, therefore, the control valve 32 begins to operate additional electromagnetic force N1that should be equal to the resultant of all forces acting on it:

Here: N45- force oil pressure from cavity 45 on the valve 32; N41- force oil pressure from cavity 41 on the valve 32; N34the force of elasticity of the spring 34.

When the magnitude of the control current I to the electromagnetic force N1(left side of the equality (8) is also increased by the corresponding amount. This causes a slight displacement control valve 32 to the left along the axis. The latter in turn causes compression of the spring 34 and, consequently, leads to an increase in the magnitude of the force N34up 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 38 of the coil 39 of the control valve 32 moves to the left along its axis, and the annular gap Z in the pipe bore control valve, reduces energy is SJ (Fig). 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 45 and the corresponding forces N45(the right part of equality (2) is increased). But this circumstance causes a shift valve 27 to the left along its axis (unloading the spring 28), at the same time (proportionally) to reduce the amount of force N28the elasticity of the spring 28 to the extent that the equality (2) is recovered. However, the leftward displacement of the valve 27 causes the reduction of the annular gap X, i.e. an increase in the hydraulic resistance of the electromagnetic valve 19, and hence increase the degree of damping of the shock absorber.

Thus, when the magnitude of the control current I at the contacts 38 of the coil 39, 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 32 in the form of a tapered cylindrical surface 52 connected by a smaller diameter of the bounding disk 36, 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 inclination of the conical Qili the shape of the surface 52. The presence of the restraining disc 36 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 designs to use is not advisable due to inevitable errors.

The value of the control current I=I1corresponds to the operation of the shock absorber in the "low degree of damping" (mode "Comfort") - curve 1 in figure 9. This mode is in demand when driving on bad roads.

The value of the control current I=I2corresponds to the operation of the shock absorber in the normal degree of damping" (the "Normal"mode) - curve 2 in figure 9. This mode is in demand when driving in normal traffic conditions.

The value of the control current I=I3corresponds to the operation of the shock absorber with high degree of damping" (mode "Sport") - curve 3 in figure 9. This mode is in demand when riding at high speeds on good roads.

Note that (pig)

0<I1<I2<I3<Imaxand 0<Z3<Z2<Z1<Zmax.

It is interesting to note that the proposed absorber, in contrast to the known, also allows you to implement "locking mode"

I=Imax→Z=0,

when the cat the rum ring gap Z is equal to zero. In this case, the oil pressure in the cavities of the inlet 18 and 45 are aligned and the valve 27 under the action of the spring 28 occupies the leftmost position. This annular surface 29 of the valve 27 is pressed against the annular surface 30 of the electromagnetic valve 19 and the annular gap X is equal to zero:

I=Imax→Z=0→X=0.

The inlet 18 of the electromagnetic valve 19 is closed and the movement of the piston and rod is locked. 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 (Fig)

Then taking into account (10) in the interval (9) function (6) graphically would be 8.1 (Fig).

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 amortizatio is and due to the emergence of the possibility of implementing the locking mode.

Adaptive shock absorber of the suspension of the vehicle containing fixed on the guide rod outer tube tank with annular cavities formed is also enshrined in the guide rod and the intermediate cylinder and the working cylinder within which the piston rod is fixed, the piston is moved in the working cylinder, and containing installed in the receiver-tank adjustable solenoid valve indirect actions, including sequentially placed in it the main valve-a valve with a Central throttle opening, biasing the inner surface of the electromagnetic valve spring, and a control valve direct acting, rigidly connected with the armature of the controlling electromagnet, the inlet of the adjustable solenoid valve connected to the cavity formed by the workers and the intermediate cylinder, and the outlet from the cavity formed intermediate the cylinder and the tube-reservoir, nadporshnevaya and podpornega cavity of the working cylinder is connected with a cavity formed by an outer tube-reservoir and the intermediate cylinder through the bypass valves installed respectively in the guide rod and the base, characterized in that the walls of the working cylinder, the upper and lower parts, the imp is tive end-to-end working Windows, connecting respectively nadporshnevaya and podporchennuyu cavity of the working cylinder with a cavity formed by the work and intermediate rolls, the lower the operating window is a bypass valve, and the piston is made of a monolithic, in addition, the cylinder control valve direct action is executed in the form of a cone, mud from the side of the smaller diameter of the bounding disk.



 

Same patents:

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: automotive industry.

SUBSTANCE: hydraulic shock absorber comprises hydraulic cylinder (1) and rod with piston (2). The piston is provided with throttle openings (3) and receives the relief compression valve (4) and relief delivery valve (5). The shock absorber receives outer pipeline (6) for communication the top and bottom spaces of hydraulic cylinder (1), step motor (11) provided with mechanical drive (12) for control of compression (8) and delivery (10) cock-throttles, and control unit (13) connected with step motor (11). The pipeline receives, connected in parallel, the unit composed of by-pass valve (7) and compression cock-throttle (8) connected in series and unit composed of by-pass valve (9) and delivery cock-throttle (10) connected in series.

EFFECT: improved shock absorbing.

1 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 engineering.

SUBSTANCE: invention can be used in suspensions of vehicles. proposed hydraulic damper consists of reservoir with eye plate, cylinder with intake valve, piston with relief valve of extension/rebound - compression stroke, rod provided with throttling hole and return valve, guide with adjustable throttling hole and set of guides and sealing cups and rings, and upper eye plate. Ball bearings are installed in eye plates. Guide and cover are assembled into one base part - guide, in which sealing cups and rings, guide polymeric rings and needle are installed. Said needle is designed to adjust resistance at throttling mode of extension/rebound stroke directly on test stand without disassembling of said damper. Damper contains additional polymeric ring installed in scraper. Said ring prevents contact of chromium coating of rod with metal of scraper and getting of hard foreign finely divided particles into sealing unit.

EFFECT: improved serviceability of hydraulic telescopic damper under unfavorable conditions, provision of convenience in its adjustment.

8 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building, particularly, to vehicle suspensions. The suspension includes operating cylinder damper body with two springs. One spring is installed between damper body and piston connected with dismountable rod. The rod consists of upper half inside which channel is drilled for liquid input for damping control, and lower half. Piston with choke valves is fixed between halves of rod. The second spring is installed between the piston connected with rod and the piston forming cavity for liquid in the lower part of cylinder to change force.

EFFECT: possibility of stepless force and damping regulation.

3 dwg

Up!