Damping system of vertical vibrations of railway passenger car body

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

 

The technical field

The invention relates to mechanical engineering, to devices for damping vibrations, in particular rail transport, mainly in the means of damping passenger cars.

The level of technology

The known device damping (USSR Author's certificate No. 495467, CL F16F 9/06, 1973 - [1] and RF application No. 2006124009 - [2]), which uses a conductive liquid with a ferromagnetic powder. The disadvantage of these devices is the low efficiency of vibration protection.

The known device damping (USSR Author's certificate No. 1753091, CL F16F 6/00, 1992 - [3], RF patents №2150621- [4] and # 2249734, CL F16F 5/00, 2004 - [5]), where the damping is carried out with the aid of the elastic elements of the bellows. In these devices, the efficiency of vibroprotection increased due to a change in resonance frequency of the device.

Known hydraulic vibration dampers (A.S. 1084508, 1983 - [6], the patents of the Russian Federation 2324088 - [7], 2324089 - [8], 2268419 - [9], 2215232 - [10], U.S. patent 3731709 - [11]), where the damping using the torquing moment, perceived elastic piston rod.

Also known device with magnetically operated valves (patent RF №2313716, CL F16 31/08, 2007 - [12], No. 2307279, CL F16 31/08, 2007 [13], patent DE No. 10009835, CL F16 31/08, F16 01, 2007 - [14]). The disadvantage of these devices is the inability to apply in a complex condition which the conditions of operation, in particular the inability to apply for railway wagons.

System damping passenger cars, in particular with hydraulic dampers are designed for damping of power oscillations cars, especially in the resonant modes, when from the effects of roughness on the moving path of the carriage tends to increase the amplitudes of the car, which increases the load on the wagon and railroad, worsens the conditions of passenger comfort. To ensure sustainable processes oscillations of the car with any combination of disturbing forces acting on it when driving at various speeds, it is advisable to ensure that the main parameter of hydraulic dampers, namely the coefficient of resistance varied in accordance with the moving speed and the frequency of oscillations of a body.

Known hydraulic vibration dampers, where the use of safety and check valves with spring-loaded locking bodies and the throttle channel, which connects nadporshnevaya the cylinder chamber with the reservoir with the working fluid formed between the housing and the cylinder (see avts of the USSR №362958, CL 61F 5/10, 1972 - [15]; avsw of the USSR №1006819, CL F16F 5/00, 1983 - [16]; avsw 1044859 - [17]; avsw of the USSR №1325225, CL F16F 5/00, 1987 - [18]; the vibration damper passenger cars KVZ-Institute - [19]; the vibration damper pass the passenger cars 4065.33.000 ER, TVZ, 2003 - [20] the patent of the Russian Federation 2020310 CL F16F 5/00, 1994 - [21], 2145010 CL F16F 5/00, 2000 - [22], 2230241, 2006 - [23], 2145010 CL F16F 5/00, 2000 - [24]).

These devices can be used in difficult conditions, but they create resistance forces are not widely adjustment and are not always able to provide smoothness, and hence the creation of comfortable conditions for people in vehicles such absorbers.

A known system for damping vibrations of a car body of a railway passenger car [25] M.M. Sokolov, Varava V.N., Leviticus G.M. vibration Dampers rolling stock. M. "Transport", 1985, p.17, 2.1, containing installed under the body hydraulic dampers, each of which is made in the form of a piston pump with pressure and non-pressure cavities for the working fluid, communicating with each other through a throttle with a certain section of the bore hole. When fluctuations in the body during the movement of the carriage over rough railroad tracks in each hydraulic damper is pushing fluid through a narrow flow cross section of the throttle. Meanwhile, the mechanical vibration energy of the car is converted into heat, reducing the intensity of these fluctuations. With constant coefficient of hydraulic dampers (constant cross-section bore hole of the throttle) about the same cross section of the throttle, consequently, the resistance coefficient is chosen to reduce the amplitude of oscillations of the body, to provide good damping of the body in the zone of the main resonance, i.e. at low speeds of movement of the carriage and low frequencies of oscillations of a body. In such hydraulic dampers at high frequency oscillations of the body that occur at high speeds of movement of the carriage, the working fluid does not have time to flow through the choke. Dampers at this like hard solids and increase the dynamic coefficient of transmission of the impact of the roughness of the road on the body. This is a significant disadvantage of the system damping [25] and proves the feasibility of using the system, the dampers which have an adjustable coefficient of resistance.

Closest to the proposed technical solution to the technical essence and purpose is the system damping vertical oscillations of the body of the passenger car containing hydraulic dampers with capability of adjustment of their resistance (Damper suspension of the vehicle. RF patent №2235233, F16F 5/00, 9/18, 9/34, 9/36, 2004 - [26]). This system contains installed under the body vertically hydraulic dampers, each of which is made in the form of a piston pump with pressure and non-pressure Palast the mi for the working fluid, communicating with each other through the throttle with stock overlap throttle openings associated with the travel drive rod and the ability to adjust the resistance coefficient of the damper. The stock throttle known in the damping system [26] performed with the circular groove that moves when the axial movement of the rod in the area of the bore of the throttle, which results in a change in the degree of overlap bore throttle and the drag coefficient of the damper. The other end of the rod is threaded and secured in the threaded bore of the housing of the hydraulic dampers with the release of the screw head of the stem to the outside of the damper casing. Drive axial movements of the rod is provided by rotation of the head stock. The advantage of this system damping [26] is the adjustable drag coefficients, for example, after their manufacture and in operation by implementing a preset in accordance with the terms of the proposed mode of operation and quality of the railroad tracks. The disadvantage of this system is the inability to control drag coefficients of the dampers during the movement of the wagons.

Disclosure of inventions

The basis of the invention the task is to provide system damping body met the aqueous passenger car, which improves the quality of protection against vibration and improving comfort conditions for passengers by improving the dynamic characteristics of vibration of the car body in a vertical plane during all modes of operation.

The solution of this problem is achieved by the fact that in the known system damping vibrations of a car body of a railway passenger car, containing installed under the body vertically hydraulic dampers, each of which is made in the form of a piston pump with pressure and non-pressure cavities for the working fluid, communicating with each other through a throttle, and is equipped with a stock throttle with capability of adjustment coefficient of resistance due to the overlap of the throttle openings, according to the invention introduced the sensors frequency oscillations of the car body mounted on the body in the area of location of each damper speed sensor carriage, control unit, power supply, stock throttle each damper is equipped with a drive, made in the form of an electromagnet, the core of which is connected with the stem of the throttle, the outputs of the sensors, the frequency of oscillations of the car body, a speed sensor of the car, the power source is connected to the inputs of the control unit, the coil of an electromagnet of each of the dampers is connected to its corresponding output block of the control, moreover, the control unit is made with automatic filing the required size of the desired electrical signal to the electromagnets of each damper for the implementation of the coefficient in accordance with a programmed dependence of the instantaneous values of the coefficient of each of the damper from the frequencies of the body and the speed of the car, minimizing the vertical accelerations of the body.

Provided also that in the control unit implements the algorithm of its operation in accordance with the programmed dependence of the instantaneous values of the coefficient of each of the n buffers having the form:

when fto<2,

when fto=[2-4],

when fto>4,

where p=45 if V=[0-140];

if V=[140-220];

p=25 if V>220;

to - serial number of the hydraulic damper of the carriage;

βto- the instantaneous value of the coefficient of K-th damper depending on the frequency and speed of the car (KNS/m);

R - coefficient taking into account the speed of the carriage;

fto- frequency oscillations of the car body in the area of installation of K-th damper (Hz);

V - speed of movement of the carriage along the path (km/h).

The introduction of these p is Isakov allows you to create a damping system with automatic change hydraulic dampers passenger car, providing a decrease in the intensity of fluctuations in the body not only in the primary resonance zone (at low speeds of movement of the carriage and low frequencies of oscillations of a body), but in the above-resonance zones that occur at high speeds of movement of the carriage and high frequency oscillations of the body. Due to this improved dynamic characteristics of the car in General, improves the smoothness of the car, i.e. improved quality of protection against vibration and improving comfort conditions for passengers.

In the analysis of technical solutions to meet the criterion of "novelty" revealed that some of the features of the declared total is new, therefore, the invention conforms to the criterion "novelty". In the analysis of the invention in accordance with the criterion of "inventive step" revealed that the introduction of a new distinctive characteristics leads to new technical properties: the dependence of the drag coefficient depending on the frequency and speed, the control unit produces signals to control the solenoids of the hydraulic dampers in accordance with this dependence, the outcome is a variable coefficient of damping and minimizing the vertical accelerations of the body in a given time.

The technical solution of the analyzed volume of the KTA has novelty and meets the criterion of "inventive step", because it represents a new set of features and new technical features, but also represents a new location, number and connection elements. The proposed device is not obvious from the prior art. In addition, through the proposed technical solution achieved a result that meets existing needs in the creation of a hydraulic shock absorbers with high efficiency vibration protection for comfortable transportation of passengers. Marketing research has shown the urgent need for such a product on the market.

Brief description of drawings

The essence of the proposed invention is illustrated by the drawing, which schematically presents an embodiment of the system damping vertical oscillations of the car body of a railway passenger car (considered damping system with four dampers).

Positions on the drawing:

1 - hydraulic damper,

1.1 - the body of the damper,

1.2 - rod-piston damper

1.3 - pressure cavity damper

1.4 - pressure cavity damper

1.5, 1.6 - return valves damper

1.7 - throttle opening (throttle) damper

1.8 - stock throttle.

1.9 - electromagnet (EM) actuator stem of the throttle.

1.10 - induction coil e is Amanita,

1.11 - recoil electromagnet,

2 - sensor frequency (DF) of the oscillations of the car body,

3 - speed sensor (DS) movement of the car,

4 - power source (PIS),

5 - the control unit (cu).

The implementation of the invention

Implementation of the proposed system damping vertical oscillations of the car body is considered on the example of its implementation with four hydraulic dampers (see drawing). The proposed damping system contains installed under the body vertically hydraulic dampers 1, each of which is accommodated in the housing 1.1 damper rod-piston 1.2. Case 1.1 is made with two cavities for the working fluid: pressure cavity 1.3 and gravity cavity 1.4. The damper is equipped with two check valves, one of which 1.5 is installed in the piston, the other 1.6 - in the body of the damper. Pressure cavity 1.3 communicates with the pressure cavity 1.4 through the orifice (throttle) 1.7, which is covered by the stock throttle 1.8. The stock throttle 1.8 in the area of the throttle hole 1.7 performed with the annular groove and axial movements of the rod changes the flow area of the throttle, and hence the coefficient of the damper. Drive axial movements of the rod 1.8 is an electromagnet 1.9 reel 1.10 and core associated with the stock 1.8 throttle. In this arrangement, the heart is nick electromagnet and the stock throttle 1.8 made in one piece (rod - the core of the overlap of the throttle openings of the damper). The specified rod - core 1.8 is spring-loaded relative to the housing of the solenoid return spring 1.11.

The proposed system damping sensor 2 frequency of oscillation of the carriage, mounted in the car body in the area of location of each of the hydraulic dampers, speed sensor 3, the movement of the carriage along the path, the power source 4 and the control unit 5. Each of the sensors 2, 3 and the power source 4 connected to the respective input terminals of the control unit 5, the output terminals of which are electrically connected with the coils of the electromagnets 1.9 each damper.

The control unit 5 is designed to generate electrical control signals electromagnet of each damper and automatic transfer them to the electromagnets 1.9 respective dampers. In the control unit 5, the algorithm for generating signals in accordance with programmed (and incorporated initially in the control unit) the dependence of the drag coefficient of the damper on the speed of the car (speed sensor) and the oscillation frequency of the body (frequency sensors)which minimizes the vertical accelerations of the body in a given time.

Programmed dependence of the instantaneous values of the coefficient weather resistance is of each damper, in the General case when the damping system n hydraulic dampers, is:

when fto<2;

when fto=[2-4];

when fto>4,

where p=45 if V=[0-140];

if V=[140-220];

p=25 if V>220;

to - serial number of the hydraulic damper of the carriage;

βto- the instantaneous value of the coefficient of K-th damper depending on the frequency and speed of the car (KNS/m);

R - coefficient taking into account the speed of the carriage;

fto- frequency oscillations of the car body in the area of installation of K-th damper (Hz);

V - speed of movement of the carriage along the path (km/h).

This dependence is obtained in the generalized multivariate analysis of fluctuations in the body of the car with a computer simulation of the dynamics of passenger cars with a wide frequency spectrum real disturbing influences railroad tracks on the wagon, as well as in the sea trials of passenger cars.

For the considered example, this dependence takes the form:

βto=p if fto<2;

when fto=[2-4];

βto=10 when fto>4,

where p=45 if V=[0-140];

if V=[140-220];

p=25 if V>220.

PR is degema system damping vertical oscillations of the body of the passenger car is as follows.

Arising from the movement of the car over bumps railway track vibrations of the car body is called in each hydraulic damper 1, the moving rod-piston 1.2 relative to the housing 1.1. Circular movement of the rod-piston 1.2 up-down and proper operation of check valves 1.5 and 1.6 hydraulic dampers work as piston pumps, pumping the working fluid from the pressure cavity 1.4 in the pressure cavity 1.3, and through the orifice 1.7 squeeze out the fluid in the pressure cavity 1.4. When installed above each damper in the area of location of each damper sensors 2 frequency oscillations of the car body (DF-1, DF-2, DF-3, DF-4) the signals to the corresponding inputs of the control unit 5. To the input unit 5 is the voltage from the power source 4 and the signals from the sensor 3 speed car. At low speeds (from 0 to 140 km/h) and low frequencies of oscillations of a body in the areas of sensors 2 (up to 2 Hz) in accordance with the system of equations (1), the control unit 5 via output contact signals (for example, in the form of voltages or currents) to the electromagnetic coil 1.10 corresponding to this position of the core-rod 1.8 under the influence of the retracting force of the magnetic field of this coil springs 1.11, in which it overlaps the pass CE is giving throttle openings 1.7, providing the resistance coefficient of the damper is equal to its maximum value of β=45 KNS/m, the optimal damping oscillation in the zone of the main resonance.

With increasing speed of the car (more than 140 km/h) or with increasing frequency oscillations (>2 Hz) the control unit is in other functional dependencies of the system of equations (1), namely:

when fto=[2-4],

where

In this mode (by increasing the speed of up to 220 km/h and the oscillation frequency to 4 Hz) coefficients of resistance of the dampers gradually reduced, and at frequencies greater than 4 Hz constant minimal value equal to 10 KNS/m this eliminates the major drawback of the system damping of cars with dampers having constant values of drag coefficients configured for damping of the primary resonance vibrations at low speed car and the low frequencies of oscillations of a body). In the known system, as noted previously, at high speeds of cars and high frequencies of oscillations of a body working fluid dampers do not have time to flow through a narrow orifice, and dampers like hard solids, increasing the dynamic gain exposure unevenness way Namazov. In the proposed system damping, this disadvantage is eliminated due to the fact that the drag coefficients are automatically adjusted to the speed and frequency of fluctuations in the body, reducing the vertical acceleration of the body, the dynamic impact of the way to the car that provides increased smoothness and durability of the car. Thanks considerably distinctive features of the invention in the proposed system dampers are independent from each other of the control circuit. They react in the common speed of the car and different for each damper oscillation frequency of the body. Therefore, the system responds not only to increase the speed of the car and frequencies of oscillations of a body or of reducing them, but on different combinations of these parameters, for example to increase the oscillation frequency in the area of low velocity motion of the car or on the lower frequencies in the zone of high velocities. Thus, the overall system dampens resonance phenomena not only in the area of the main resonance (low frequency), but in the above-resonance zones that occur at high speeds of movement of the carriage and high frequency oscillations of the body that may occur throughout the operational range of the speed of the cars, as well as on the railroad tracks with different quality adapter is Rozhen canvas.

The effectiveness of the proposed system damping is confirmed by the results of computer simulation of the dynamics of cars with different modes of motion and trial of passenger cars.

As you can see from the example implementation, the proposed solution can be implemented using the available tools and techniques and allows you to get a new technical result. The invention can be replicated and, therefore, meets the criterion of "industrial applicability".

Industrial applicability

The proposed damping system manufactured and tested. The test results have shown that it improves the smoothness of passenger cars by 7-10%. Currently we are preparing the production for making party test cars.

Sources of information

1. USSR author's certificate No. 495467, CL F16F 9/06, 1973.

2. RF application No. 2006124009, CL F16F 9/06, 2006.

3. USSR author's certificate No. 1753091, CL F16F 6/00, 1992.

4. RF patent №2150621.

5. RF patent №2249734, CL F16F 5/00, 2004

6. USSR author's certificate No. 1084508, 1983.

7. RF patent №2324088.

8. RF patent №2324089.

9. RF patent №2268419.

10. RF patent №2215232.

11. U.S. patent No. 3731709.

12. RF patent №2313716, CL F16 31/08, 2007

13. RF patent №2307279, CL F16 31/08, 2007

14. Patent DE No. 10009835, CL F16 31/08, F16 01, 2007

15. The author is a certificate of the USSR No. 362958, CL 61F 5/10, 1972

16. USSR author's certificate No. 1006819, CL F16F 5/00, 1983

17. USSR author's certificate No. 1044859 - [17].

18. USSR author's certificate No. 1325225, CL F16F 5/00, 1987

19. The vibration damper passenger cars KVZ-the Institute, 2004.

20. The vibration damper passenger cars 4065.33.000 ER, TVZ, 2003.

21. RF patent №2020310 CL F16F 5/00, 1994

22. RF patent №2145010 CL F16F 5/00, 2000

23. RF patent №2230241, 2006

24. RF patent №2145010, CL F16F 5/00, 2000

25. Sokolov M., Varava V.N., Leviticus G.M. vibration Dampers rolling stock. M: "Transport", 1985, p.17, 2.1.

26. The damper of the suspension of the vehicle. RF patent №2235233, F16F 5/00, 9/18, 9/34, 9/36, 2004 the Prototype.

1. System damping vertical oscillations of the car body of railway passenger car that contains installed under the body vertically hydraulic dampers, each of which is made in the form of a piston pump with pressure and non-pressure cavities for the working fluid, communicating with each other through a throttle, and is equipped with a stock throttle with capability of adjustment coefficient of resistance due to the overlap of the throttle openings, characterized in that the input sensors, the frequency of oscillations of the car body mounted on the body in the area of location of each damper speed sensor carriage, the control unit, a source of elec is ropicana, the stock throttle each damper is equipped with a drive made in the form of an electromagnet, the core of which is connected with the stem of the throttle, the outputs of the sensors, the frequency of oscillations of the car body, a speed sensor of the car, the power source is connected to the inputs of the control unit, the coil of an electromagnet of each of the dampers is connected to its corresponding output control unit, and the control unit are made with automatic filing the required size of the desired electrical signal to the electromagnets of each damper for the implementation of the coefficient in accordance with a programmed dependence of the instantaneous values of the coefficient of each of the damper from the frequencies of the body and the speed of the car, minimizing the vertical accelerations of the body.

2. System damping vibrations of a car body of a railway passenger car according to claim 1, characterized in that the control unit implements the algorithm of its operation in accordance with the programmed dependence of the instantaneous values of the coefficient of each of the dampers, which is:
,

,
where p=45 if V=[0-140],
,
p=25 if V>220;
to - serial NR the R hydraulic damper of the car;
βto- the instantaneous value of the resistance coefficient to that of the damper depending on the frequency and speed of the car (KNS/m);
p - coefficient taking into account the speed of the carriage;
fto- frequency oscillations of the car body in the area of installation to the damper (Hz);
V - speed of movement of the carriage along the path (km/h).



 

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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: tuning to required damping frequency is performed. Dynamic rigidity or transfer factor dip is experimentally determined at first breadboard specimen. Then on increasing damper slit width, tuning frequency is increased along with increasing damping. Thereafter, tuning frequency is decreased by decreasing damper slit width. Aforesaid reduction is performed by increasing the number of slit pairs. Proposed device comprises interconnected pendulums pivoted to protected object. Each pendulum comprises weight suspended to aforesaid object. One object is located above the points of attachment of its suspension to the object, the others being located below aforesaid points. Tight cylindrical barrel is covered with cap and filled with hydraulic fluid. Movable modular hollow piston is arranged inside aforesaid cylindrical barrel fixed between two cylindrical springs. There is a system of channels inside aforesaid piston. It consists of top and bottom covers and uneven number of round plates. Aforesaid slits are formed by flat round rings arranged between aforesaid covers and plates. Former and latter comprise central bores, while even plates have peripheral orifices arranged nearby inner cylindrical surfaces of round rings.

EFFECT: higher efficiency.

2 cl, 3 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to mechanical engineering, particularly to items of structures' oscillation damping. Device is implemented in the form of variable cross-section body with decreasing by thickness section from outside boundary of mounting hardware to the object up to outside edge of body. Variable cross-section body is implemented in the form of disk or its fragment.

EFFECT: it is achieved effectiveness increase of absorbing of vibration.

8 cl, 4 dwg

FIELD: mechanics.

SUBSTANCE: support surface of rotor trunnion is made in the form of toroidal surface and installed on spherical support surface in cavity of support toe. The latter is installed on a damping element arranged in cavity of housing with lubricating liquid. Radius of toroidal surface of trunnion is 0.4÷0.95 of the radius value of spherical support surface of the toe, and distance between axial line of toroidal surface and trunnion axis is 0.05÷0.6 of the radius value of spherical support surface of the toe. Geometrical parametres of the support meet the ratio: , but not less than 1, where: r - radius of the toe sphere, m; ρ - radius of torodial surface, m; δ- distance between axial line of torodial surface and trunnion axis, m; P - axial load, H; F - radial load, H; β - slope angle of figure end from rotation axis under influence of radial load, rad.

EFFECT: increasing carrying capacity of support and decreasing costs for manufacturing and repairing thereof.

9 cl, 3 dwg

FIELD: mechanics.

SUBSTANCE: support surface of rotor trunnion is made in the form of toroidal surface and installed on spherical support surface in cavity of support toe. The latter is installed on a damping element arranged in cavity of housing with lubricating liquid. Radius of toroidal surface of trunnion is 0.4÷0.95 of the radius value of spherical support surface of the toe, and distance between axial line of toroidal surface and trunnion axis is 0.05÷0.6 of the radius value of spherical support surface of the toe.

EFFECT: increasing carrying capacity of support and decreasing costs for manufacturing and repairing thereof.

12 cl, 3 dwg

FIELD: mechanics.

SUBSTANCE: invention relates to machine building and is designed to absorb impact and vibration loads applied onto the base. The shock absorber incorporates an intermediate flexible-link weight arranged on the base and communicating with the damper representing a jet element with a cover and casing. The latter is furnished with tangential and axial channels, the latter communicating the aforesaid flexible link while the former communicates with the hydraulic-and-pneumatic accumulator.

EFFECT: higher damping efficiency.

4 dwg

FIELD: engines and pumps.

SUBSTANCE: device incorporates the casing with its position stabilised in space at external mechanical effects. It is arranged on the base to effect minor angular oscillations relative to the said base. The casing is made up of the upper and lower rings interconnected by struts. The upper ring is attached via the elastoviscous shock-absorbers arranged along the casing edges. The shock-absorbers consist of parallel flexible elements arranged in pairs and linear-type liquid dampers filled with viscous liquid. The brackets are attached to the car body floor.

EFFECT: simpler design and higher accuracy of lidar aiming in operating conditions in tracing objects.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: vibration insulator comprises base pillar, spring flexible members, and bearing units. The cross-section of the spring flexible member is variable in the plane parallel to the base. The area of the cross-section increases from the bearing unit that bears the object to be isolated to the pillar that rigidly receives the other end of the flexible member. The sides of the flexible member are bounded by straight lines inclined at an acute angle to the axis of the flexible unit. The bearing unit is made of a bushing The rod for securing the object to be isolated is rigidly connected with the bushing. The inner surface of the bushing is in a contact with the free end of the flexible member whose cross-section is round, square, or rectangular. The bushing movements are arrested by the stop made of a conical pin.

EFFECT: improved vibration insulation.

3 cl, 3 dwg

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