Damping device of torsion excitation of hollow drive shaft

FIELD: machine building.

SUBSTANCE: device includes elongated element (7) that passes along inner space of drive shaft; at that, one end of element is fixed on one shaft end, and the other end of element is located at the other end of shaft and hydraulic damping device (11) fixed on the other shaft end for damping of vibrations of the other end of element (7). Damping device (11) includes cylinder-piston system (25) having the first and the second cylindrical hydraulic chambers (45a, 47a), tank (19) for hydraulic fluid and hydraulic circuit (29, 31, 33, 35), by means of which chambers (45a, 47a) are connected to hydraulic fluid tank (19). Damping device (11) is located so that any leak flow of hydraulic fluid from the first (45a) and the second (47a) chambers through the boundary line between piston and cylinder flows to hydraulic fluid tank (19).

EFFECT: creation of more compact design of hydraulic damping device of torsion excitation of hollow drive shaft with possibility of controlling the damping level and operating without cavitation.

12 cl, 5 dwg

 

This invention relates to a device for damping torsional perturbations of the hollow drive shaft.

You know the run of the drive shafts so that their critical speed (the speed at which they resonate) do not coincide with the working speeds of the driven equipment. This helps to eliminate torsional perturbation of the drive shaft. However, it is not always possible to perform the drive shaft. In addition, torsional perturbation of the drive shaft may occur due to the work of other equipment, not driven by the drive shaft, but near. Torsional perturbation of the drive shaft may occur due to operation of equipment connected to the driven equipment, such as United by means of an electrical circuit. This occurs, in particular, in connection with the distribution of high-power electronic equipment using thyristors.

When the drive shaft is not resilient enough to withstand arise in him torsional disturbances, counteract this by: increasing the strength of the drive shaft; reduce the magnitude of the torsional stresses applied to the drive shaft, and damping torsional perturbations of the drive shaft. This invention relates to the settlement is one of the three alternative solutions.

In WO-2005/121594-A2 disclosed a device for damping torsional perturbations of the drive shaft.

According to this invention a device for damping torsional perturbations of the hollow drive shaft, and the device comprises: an elongated element, which passes along the inner space of the drive shaft, with one end of the element is mounted on one end of the drive shaft and the other end of the element located at the other end of the drive shaft; and a hydraulic damping device mounted on the other end of the drive shaft for damping the other end member, a hydraulic damping device includes: a cylinder-piston system having first and second cylindrical chambers; a reservoir for hydraulic fluid; and a hydraulic circuit, using which the hydraulic chamber connected to a reservoir for hydraulic fluid, with hydraulic damping device is located so that any flux leakage of hydraulic fluid from the first and second hydraulic chambers through the interface between the piston and the cylinder is held in a reservoir for hydraulic fluid, the reservoir for hydraulic fluid surrounds the elongated element and passes along the inner space of the hollow drive the CSOs shaft from one end of the element to the other end.

In the device according to the preceding paragraph, it is preferable that the cylinder-piston system includes a piston located in the wall of the tank.

In the device according to the preceding paragraph, it is preferable that the actuating lever is held in the radial direction outward from the elongated member at the other end of the element, the lever acts on the piston.

In the device according to the preceding paragraph, it is preferable that a pair of actuating levers passes in a radial direction outward from the elongated member, the levers are located on opposite sides of the element and the hydraulic damping device includes: first and second cylinder-and-piston system, with one lever acts on the first cylinder-and-piston system, and the other arm acts on the second cylinder-piston system, with the first cylinder-piston system goes along the line of oscillation of a single lever, and the second cylinder-piston system goes along the line of oscillation of the other arm; and a hydraulic circuit through which the first and the second hydraulic chamber of a cylinder-piston systems are connected with the tank for hydraulic fluid.

In the device according to the preceding paragraph, it is preferable that each cylinder-piston system contains a single cylinder, containing the third single piston, each piston is located along its cylinder with the formation at each end of the first cylinder and the second hydraulic chambers of a cylinder-piston system.

In the device according to the preceding paragraph, it is preferable that the hydraulic circuit includes first and second sections, with each section includes first and second branches connected in parallel, with one branch contains a flow limiter, and the other branch contains a control valve that allows flow in only one direction from the reservoir, while the first section is connected between the tank and as the first hydraulic chamber of the first cylinder-and-piston system, and diagonally opposite the second hydraulic chamber of the second cylinder-and-piston system, and the second section is connected between the tank and as the second hydraulic chamber of the first cylinder-and-piston system, and diagonally opposite the first hydraulic chamber of the second cylinder-and-piston system.

In the device according to the paragraph before the previous paragraph, it is preferable that the first cylinder-piston system includes a first pair of cylinder-piston units, which are located opposite one another along the line of oscillation of one of the Executive arm, while the pistons of the first pair of piston nodes rely on against the opposite sides of one arm, and the second cylinder-piston system includes a second pair of cylinder-piston units, which are located opposite one another along the line of oscillation of the other Executive arm, while the pistons of the second pair of cylinder and piston nodes rely on the opposite side of the other arm.

In the device according to the preceding paragraph, it is preferable that each of the cylinder node contains a spring disposed in its hydraulic chamber, which pushes its piston to the Executive arm, and the piston each node contains a flow limiter and control valve connected in parallel, which are connected between the hydraulic chamber of the node and a reservoir for hydraulic fluid, the control valve allows fluid to flow only in one direction from the reservoir.

In the device according to the previous two paragraphs, it is preferable that the piston of each cylinder-piston unit consists of the Executive arm that extends from the piston in a generally radially outward, while the radially outer end of each of the Executive shoulder rests on one side of the actuating lever.

In the device according to the preceding six paragraphs, it is preferable that the reservoir for the hydraulic fluid passes around a pair of actuating levers.

In the device according to the preds the current paragraph, preferably, that spring-loaded piston located near the hydraulic damping device and the axis of rotation of the drive shaft, creates a pressure in the reservoir for hydraulic fluid.

Below is a description of examples of implementation of the invention with reference to the accompanying drawings, which depict:

figure 1 is a longitudinal section of the hollow drive shaft and devices according to this invention;

figure 2 is a section along the line II-II in figure 1;

figure 3 - alternative shown in figure 2;

figure 4 - cylinder node used in figure 3, on an enlarged scale;

5 is a modification of figure 3.

As shown in figure 1, a hollow drive shaft 1 is driven into rotation by the actuator 3 and causes the rotation of the block 5. The device according to this invention, contains hard to curl solid cylindrical gear element 7, concentric with the shaft 1, a pair of actuating levers 9a, 9b and hydraulic damping device 11. The damping device 11 is connected between the shaft 1 and driven in rotation by the unit 5. The actuator 3 is connected to the shaft 1 by means of fasteners 13, while the damping device 11 included between the shaft 1 and driven in rotation by the block 5 by means of fasteners 15 and the actuating levers 9a, 9b are connected to the transmission element 7 by means of fasteners 17. Attachment 13 also attach one horse the element 7 to the end of the shaft 1, connected to the actuator 3. Element 7 passes along the inner space of the hollow shaft 1. The levers 9a, 9b are located at one end of the element 7, remote from the fastening element 7 to the shaft 1, and are held in radial direction outward from the element 7 at an angular distance of 180 from each other. The levers 9a, 9b are communication with a hydraulic damping device 11. A description of the exact nature of this connection will be described below. Under pressure from the reservoir 19 to the hydraulic fluid remains around the element 7 and the levers 9a, 9b. Fluid is compressed spring-loaded piston 21 located in the driven unit 5. The piston 21 is connected to the tank 19 through the corrugated membrane 23.

Oscillatory twisting of the shaft 1 due to torsional disturbances leads to the corresponding relative rotational movement between the levers 9a, 9b and damping device 11. For example, if the curl facing the driven end of the shaft 1 clockwise facing the drive end of the shaft 1 is twisted counterclockwise. Twist clockwise to the end on the side of the driven unit causes a corresponding twisting clockwise damping device 11 connected to this end, and twisting counterclockwise end of the one hundred is an area of the actuator causes corresponding twisting counterclockwise transmission element 7, fastened to this end, and thus the corresponding twisting counterclockwise levers 9a, 9b. The relative angular position of the damping device 11 and levers 9a, 9b corresponds to twisting at the moment of time the shaft 1.

As shown in figure 2, the hydraulic damping device 11 includes first and second cylinder-and-piston system 25, 27, under pressure from the reservoir 19 to the hydraulic fluid, first and second restrictive orifice 29, 31, and first and second control valves 33, 35.

The first and second cylinder-and-piston system 25, 27 each contain a single cylinder 37, 39, containing a single piston 41, 43. Each piston 41, 43 is generally centrally along its cylinder 37, 39 with the formation at each end of the cylinder 37, 39 of the first and second hydraulic chambers 45a, 45b, 47a, 47b. Along each of the piston 41, 43 cut through the Central slit 49A, 49b for receiving one end 51A, 51b of the respective actuating lever 9a, 9b. Each cylinder-piston system 25, 27 passes through the oscillation of the end 51A, 51b of the respective actuating lever 9a, 9b.

The path of the fluid between diagonally opposite hydraulic chambers 45, 47b and under pressure reservoir 19 includes first and second branches connected in parallel, with one branch which contains restrictive opening 31, and the other branch contains a control valve 35. Similarly, the path of the fluid between diagonally opposite hydraulic chambers 47A, 45b and the tank 19 contains the first and second branches connected in parallel, with one branch contains a restrictive hole 29, and the other branch contains a control valve 33. Restrictive openings 29, 31 are made so that through them the flow is laminar. Check valves provide flow of fluid only in one direction from the reservoir 19. The control valves 33, 35 are made to provide a small pressure drop and fast response.

Hydraulic damping device 11 operates as follows.

As shown, particularly in figure 2, if due to torsional disturbances of the drive shaft 1 Executive levers 9a, 9b are rotated in the clockwise direction, it leads to forced displacement to the right of the piston 41 of a cylinder-piston system 25 and to the left of the piston 43 of a cylinder-piston system 27. This leads to a decrease in the hydraulic chambers 47a, 45b with the displacement of the fluid from the chambers 47a, 45b. The displaced fluid passes through the restrictive orifice 29 in the pressure tank 19 (it should be noted that the control valve 33 allows the passage is to Otok only in one direction from the reservoir 19). Due to the flow into the tank 19 and the pressure in the tank 19 fluid also flows from the reservoir 19. It passes through a control valve 35 and into the hydraulic chamber 45a, 47b. The pressure difference as in the first pair of chambers 45A, 47A, and the second pair of chambers 45b, 47b equal to the difference of pressure in a restrictive hole 29 and is proportional to the time, opposing angular twisting of the shaft 1. Since the flow through the restrictive orifice 29 depends on the speed of angular twisting of the shaft 1, a precise damping torque, which is proportional to the angular velocity of twisting. Provided that in a restrictive orifice 29 is kept laminar flow damping is purely linear and viscous in nature.

If torsional perturbation of the shaft 1 causes rotation of the levers 9a, 9b in the counterclockwise direction, the hydraulic damping device works as before, but in the opposite direction. Thus, the fluid exits the chambers 45A, 47b, passes through the restrictive opening 31, and out of the tank 19, passes through the check valve 33 and enters chamber 47A, 45b. In this case, the pressure difference as in the first pair of chambers 45A, 47A, and the second pair of chambers 45b, 47b equal to the difference of pressure in a restrictive orifice 31.

If the dynamic characteristics of the entire system the volumes are set correctly, the restrictive apertures 29, 31 can provide a fixed limit, i.e. to change the limits of the impossible. This leads to cost reduction. However, in the less well-specified system can be applied modified laminar holes to provide adjustable damping. In this case, the damping level can be adjusted to align with the actual current conditions.

The hydraulic system during their lifetime can lose compressibility due to the formation of gas bubbles/air. This results in a negligible impact in many hydraulic systems, however, in the above system can lead to failure, because it requires instantaneous damping torque in response to a very small angular displacement. The gas bubbles/air generated by cavitation in hydraulic fluid, i.e. a negative pressure in the hydraulic fluid, which leads to the separation of gas/air normally present in hydraulic fluid, from a solution with the formation of gas bubbles/air. Cavitation usually occurs when hydraulic fluid is drawn into the chamber due to the expansion chamber. In the above system, cavitation is prevented through the use of: (i) under pressure reservoir 19 and (ii) the control valves 33, 35, parallel to the s holes 29, 31 (check valves allow fluid to flow into the bypass restrictive apertures when the flow in the chamber 45A, 47A, 45b, 47b, which ensures a fast response to the expansion chambers 45A, 47A, 45b, 47b).

It should be noted that under the pressure tank 19 compensates for fluctuations in the volume within the hydraulic circuit. Such fluctuations may occur due to wear and tear (for example, on the contact surfaces, where the ends 51A, 51b of the Executive levers 9a, 9b abuts the piston 41, 43), changes in temperature and leakage of hydraulic fluid.

It should be noted that leakage of hydraulic fluid from the chambers 45A, 47A, 45b, 47b through the interface between the pistons 41, 43 and cylinders 37, 30 is in the tank 19, so that it remains in a closed hydraulic circuit and does not interfere.

Shown in figure 3 alternative hydraulic damping device 53 includes first and second cylinder-and-piston system 55, 57 and under pressure from the reservoir 19 to the hydraulic fluid as a reservoir 19 figure 2). The first system 55 comprises a pair of piston nodes 59A, 59b, which are located opposite each other on the line of oscillation of the end 51A of the Executive arm 9a, while the pistons of the nodes 59A, 59b against the opposite end face 51A. Similarly, the second cylinder-piston system 57 comprises a pair is eindrapportage nodes 61A, 61b located opposite each other on the line of oscillation of the end 51b of the Executive arm 9b, while the pistons of the nodes 61A, 61b against the opposite end face 51b. Each cylinder and piston node 59A, 59b, 61A, 61b contains a piston 63A, 63b, C, 63d, the hydraulic chamber 65A, 65b, 65s, 65d, spring 67a, 67b, s, 67d, restrictive orifice 69A, 69b, C, 69d and the control valve 71A, 71b, s, 71d. Each spring 67a, 67b, s, 67d is located in the corresponding chamber 65A, 65b, 65s, 65d and shifts the corresponding piston 63A, 63b, C, 63d to one side of the end 51A, 51b of the Executive arm 9a, 9b (it should be noted that this system is self-adjusting for any wear of the ends 51A, 51b). Each piston 67a, 67b, s, 67d contains a restrictive orifice 69A, 69b, C, 69d and the control valve 71A, 71b, s, 71d connected in parallel. Restrictive holes 69A, 69b, C, 69d and check valves 71A, 71b, s, 71d included between the chambers 65A, 65b, 65s, 65d and under pressure reservoir 19. Each control valve 71A, 71b, s, 71d allow passage of fluid only in one direction from the reservoir 19.

Hydraulic damping device 53 operates as follows.

If due to torsional disturbances of the drive shaft 1 Executive levers 9a, 9b are rotated in the clockwise direction, this force moves to the right the piston cylinder 63b knots is 59b and the left piston s cylinder node 59S. This reduces the size of the hydraulic chambers 65b, 65s, displacing the fluid chamber 65b, 65s. The displaced fluid passes through restrictive openings 69b, C in under pressure reservoir 19 (it should be noted that check valves 71b, s allow the passage of fluid only in one direction from the reservoir 19). Due to the flow into the tank 19 and the location of the tank 19 under the pressure of the fluid also exits the tank 19. It passes through check valves 71A, 71d and into the hydraulic chamber 65A, 65d. The pressure difference in the pair of chambers 65A, 65b, and a couple of cameras 65s, 65d is equal to the difference of pressure in a restrictive holes 69b, s and proportional to the time, opposing angular twisting of the shaft 1. Since the flow through restrictive openings 69b, C depends on the angular speed of the twisting shaft 1, a precise damping torque, which is proportional to the angular velocity of twisting. While ensuring laminar flow through restrictive openings 69b, C damping is purely linear and viscous in nature.

If torsional perturbation of the shaft 1 causes rotation of the levers 9a, 9b in the counterclockwise direction, the hydraulic damping circuit operates as before, but in the opposite direction. Thus, fluid comes out of the Cam, the R 65A, 65d, passes through the restrictive orifice 69A, 69d, and out of the tank 19, passes through the check valves 71A, 71b and enters the chamber 65b, 65s. In this case, the pressure difference as in the first pair of chambers 65A, 65b and the second pair of cameras 65s, 65d is equal to the difference of pressure in the restrictive apertures 69A, 69d.

Similarly, shown in figure 2, the hydraulic damping device is any leakage of hydraulic fluid from the chambers 65A, 65b, 65s, 65d through the interface between the piston 63A, 63b, C, 63d and their cylinders occurs in the tank 19, so that it remains in a closed hydraulic circuit and does not interfere.

In the shown figure 3 hydraulic damping device required restrictive orifices and check valves are located inside the first and second cylinder-piston systems 55, 57. This facilitates manufacture and different from that shown in Fig. 2 hydraulic damping device, in which the restrictive orifices and check valves are located outside the first and second cylinder-piston systems 25, 27.

Figure 4 shows in more detail the structure of the cylinder node 59A. The structure of the cylinder nodes 59b, 61a, 61b same. If the end 51A of the Executive arm 9a is moved to the right, it allows the piston 63A move to the right under the action of the spring 67a. It creates drop the pressure between the reservoir 19 and the chamber 65A, which moves to the left against the action of the spring 73, the control valve 71, a tapered end 75 of the control valve 71A. This removes the tapered end 73 of the relevant holes 77 of the piston 63A, opening the valve 71 and allowing fluid to pass into the chamber 65A. If the end 51A of the Executive arm 9a moves to the left, it compresses the springs 67a and 73, reducing the size of the chamber 65A and causing the passage of fluid from the chamber 65A through restrictive orifice 69A in the tank 19. It should be noted that when the end 51A is moved to the right or to the left, the cylinder and piston 63A is always pressed against the end 51 under the action of the spring 67a.

Hydraulic damping device of figure 5 is the same as figure 3, except for the addition of the Executive of the shoulders to the piston 63A, 63b, C, 63d, and change shape under pressure reservoir 19 is basically rectangular in shape. This allows you to move a cylinder-piston system 59A, 59b, 61A, 61b inside, providing a more compact, generally circular hydraulic damping device.

1. Device for damping torsional perturbations of the hollow drive shaft, comprising: an elongated element (7), which passes along the inner space of the drive shaft (1), with one end of the element (7) is fixed on one end of the drive shaft (1), and others is another end of the element (7) located at the other end of the drive shaft (1); and hydraulic damping device (11 or 53)mounted on the other end of the drive shaft (1) for damping the other end of the element (7), with hydraulic damping device (11 or 53) includes: a cylinder-piston system (25 or 55)having first and second cylindrical chambers (45A, 47A or 65A, 65b); tank (19) for hydraulic fluid; and a hydraulic circuit (29, 31, 33, 35 or 69A, 69b, 71a, 71b), through which hydraulic camera (45A, 47A or 65A, 65b) are communicated with the tank (19) for hydraulic fluid, with hydraulic damping device (11 or 53) is located so that any flux leakage of hydraulic fluid from the first and second hydraulic chambers (45A, 47A or 65A, 65b) through the interface between the piston and the cylinder is held in the tank (19) for hydraulic fluid, and a reservoir (19) for hydraulic fluid surrounds the elongated element (7) and passes along the inner space of the hollow shaft (1) from one end of the element (7) to the other end.

2. The device according to claim 1, in which a cylinder-piston system (25 or 55) includes a piston (41 or 63A, 63b), located in the vessel wall (19).

3. The device according to claim 2, in which the actuating lever (9a) is in the radial direction outward from the elongated element (7) at the other end of the element (7), the ri this lever (9a) acts on the piston (41 or 63 a, 63b).

4. The device according to claim 3, in which the pair of actuating arms (9a, 9b) is in the radial direction outward from the elongated element (7) at the other end of the elongated element (7), the arms (9a, 9b) are located on opposite sides of the element (7), and the hydraulic damping device (11 or 53) includes: first and second cylinder-and-piston system (25, 27 or 55, 57), one arm (9a) affects the first cylinder-piston system (25 or 55), and the other lever (9b) acts on the second the cylinder-piston system (27 or 57), the first cylinder-piston system (25 or 55) passes but the lines of one oscillation of the lever (9a)and the second cylinder-piston system (27 or 57) goes along the line of oscillation of the other lever (9b); and a hydraulic circuit (29, 31, 33, 35 or 69A, 69b, C, 69d, 71a, 71b, s, 71d), with which the first and second hydraulic chambers (45A, 47A, 45b, 47b or 65A, 65b, 65s, 65d) of the cylinder systems (25, 27 or 55, 57) connected to the tank (19) for hydraulic fluid.

5. Device but to claim 4, in which each cylinder-piston system (25, 27) contains a single cylinder (37, 39), containing a single piston (41, 43), each piston (41, 43) is located along its cylinder (37, 39) with the formation at each end of the cylinder (37, 39) of the first and second hydraulic chambers (45A, 47A, 45b, 47b) of a cylinder-piston system (25, 27).

6. The device according to claim 5, in which Hydra is symbolic circuit (29, 31, 33, 35) contains the first and second sections, each section includes first and second branches connected in parallel, one branch contains a limiter (29, 31) of the thread, and the other branch contains a check valve (33, 35), which provides flow only in one direction from the reservoir (19), the first section connected between the tank (19) and as the first hydraulic chamber (45) of the first cylinder-and-piston system (25)and diagonally opposite the second hydraulic chamber (47b) of the second cylinder-and-piston system (27), and the second section is connected between the tank (19) and as a second hydraulic chamber (47A) of the first cylinder-and-piston system (25)and diagonally opposite to the first hydraulic chamber (45b) of the second cylinder-and-piston system (27).

7. The device according to claim 4, in which the first cylinder-piston system (55) contains a first pair of cylinder-piston units (59A, 59b)located opposite one another along the line of oscillation of one of the Executive arm (9a), while the pistons (63A, 63b) the first pair of cylinder-piston units (59A, 59b) rely pas opposite sides of one arm (9a)and the second cylinder-piston system (57) contains a second pair of cylinder-piston units (61A, 61b)located opposite one another along the line of oscillation of the other actuating lever (9b)with pistons (S, 63d) of the WTO is th pair of cylinder-piston units (61A, 61b) rely on the opposite side of the other lever (9b).

8. The device according to claim 7, in which each cylinder-piston unit (59A, 59b, 61A, 61b) contains a spring (67a, 67b, s, 67d), located in its hydraulic chamber (65A, 65b, 65s, 65d), which presses its piston (63A, 63b, C, 63d) to the Executive arm (9a, 9b)and the piston (63A, 63b, C, 63d) of each node (59A, 59b 61A, 61b) contains limiter (69A, 69b, C, 69d) flow and check valve (71A, 71b, s, 71d), connected in parallel, are connected between the hydraulic chamber (65A, 65b, 65s, 65d) node (59A, 59b, 61A, 61b) and the tank (19) for hydraulic fluid, a control valve (71A, 71b, s, 71d) allows fluid to flow only in one direction from the reservoir (19).

9. Device but claim 8, in which the piston (63A, 63b, C, 63d) of each cylinder-piston unit (59A, 59b, 61, 61b) includes the Executive arm (79), which passes from the piston (63A, 63b, C, 63d) mainly radially outward, while the radially outer end of each of the Executive arm (79) rests on one side of the actuating lever (9a, 9b).

10. The device according to claim 7, in which the piston (63A, 63b, C, 63d) of each cylinder-piston unit (59A, 59b, 61A, 61b) includes the Executive arm (79), which passes from the piston (63A, 63b, 63c, 63d) mainly radially outward, while the radially outer end of each of the Executive arm (79) rests their is I on one side of the actuating lever (9a, 9b).

11. Device according to any one of claims 4 to 10, in which the tank (19) for hydraulic fluid passes around a pair of actuating arms (9a, 9b).

12. The device according to claim 11, in which the spring-loaded piston (21), located near the hydraulic damping device (11 or 53) and the axis of rotation of the drive shaft (1), creates pressure in the tank (19) for hydraulic fluid.



 

Same patents:

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: automotive industry.

SUBSTANCE: proposed seat comprise base, carcass with cushion and back coupled via scissors-type guide device and vibro isolation device pivoted to carcass with the help of bracket. Vibro isolation device comprises damping element and pendulum-type suspension. Upper and lower bases of vibro isolation device make an opening for support plate to come out. One end of support plate is jointed to pendulum suspension, another one is connected with objected to be vibration-isolated. Casing upper base has opening for pendulum suspension rod to pass through. Diametre of said hole matches that of damping element inner cylindrical surface. Flexible element represents helical coil spring enveloping pendulum suspension threaded rod. Spring lower base rests upon movable circular flange of hydraulic damping element, while upper base thrusts against cover with thrust ring that enveloped aforesaid spring. Cover has a opening for pendulum suspension rod to pass through with diametre that matches that of damping element inner cylindrical surface. Damping element is formed by two coaxial cylindrical sleeves to form tight circular chamber. Upper part of said chamber is closed by sealed circular flange, while washer fitted in thrust ring and rigidly coupled with damping device upper base tightly closes lower part. Said circular chamber accommodates circular piston with throttling orifices made therein. Piston is coupled with circular flange by three tie rods. Pendulum suspension represents a threaded rod arranged coaxially inside damping element. It is coupled with support plate and with cover.

EFFECT: higher comfort.

2 dwg

Damper // 2327067

FIELD: mechanics.

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

EFFECT: higher rigidity of couplings.

2 cl, 3 dwg

The invention relates to the building, namely the structural elements of the damper

The invention relates to a device cooling fluid shock absorber

The invention relates to transport machinery and can be used in suspension systems of vehicles, tracked vehicles, railway rolling stock

Vibration absorber // 2047020
The invention relates to the field of engineering, namely to means of protection from vibration of various objects

FIELD: mechanical engineering.

SUBSTANCE: device comprises flexible toroidal chamber that are fit on the body coaxially to the axis of its rotation and partially filled with fluid. The bearings are arranges in pair over the diameter of the chamber. Each pair is provided with flat spring and made of flexible rectangular outer projections that are in communication with the space of the chamber and made on the cylindrical side of the toroid parallel to its generatrix.

EFFECT: expanded functional capabilities.

2 dwg

FIELD: dampening vibrations in machines and mechanisms.

SUBSTANCE: proposed damper includes inertial masses connected with body through flexible members secured in U-shaped supports mounted on body. Flat bases of these supports are directed outside and are connected by side struts forming ring concentrically embracing the body. Flexible members are made in form of shaped compression coil springs which are mounted inside supports on flat bases and are oriented to body by radial direction. These springs have monotonically increasing stiffness due to smooth fit of turns on bearing plane. Inertial masses are secured on free tops of springs directed inside.

EFFECT: extended functional capabilities.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention is designed to eliminate parasitic vibrations of rotating bodies. Proposed torsional vibration damper contains housing installed on shaft for rotation and provided with working space partially filled with ferromagnetic fluid, hydraulic restrictor arranged in working space and permanent magnet installed stationarily outside the housing and enclosing the housing in zone of arrangement of ferromagnetic fluid. Housing is made in form of circular chamber enclosing the shaft and divided into compartments by inner solid radial partitions. Hydraulic restrictor is made in form of restrictors with ball valve installed in inner solid radial partitions of circular chamber with direction of passing of ferromagnetic fluid coinciding with direction of bypassing of circular chamber to one of sides.

EFFECT: improved efficiency of torsional vibration damping, enlarged operating capabilities.

2 dwg

FIELD: mechanical engineering, in particular, equipment for elimination of spurious vibrations of rotating bodies.

SUBSTANCE: torque vibration damper has casing mounted on rotating shaft and provided with annular cavity to be filled with working fluid, and permanent magnets made in the form of axially magnetized plates radially laid in pairs on cavity bases in opposed relation with respect to one another, with opposite poles facing one another with minimal distance from one another in circumferential direction, said distance exceeding height of cavity. Working fluid is combination of ferromagnetic liquid and high-viscosity liquid immiscible with ferromagnetic liquid.

EFFECT: increased damping effectiveness, simplified construction and reduced power losses in the process of rotation of bodies.

2 dwg

The invention relates to torsional vibration dampers installed in the driveline of the vehicle

The invention relates to autobalancing device with corrective move the mass of the liquid, namely, the balancing rings, household washing machines with a vertical axis of rotation

FIELD: machine building.

SUBSTANCE: shock absorber includes hydraulic cylinder, each of the cavities of which is connected to the main elastic elements by means of system of valves and throttles, and to hydropneumatic accumulators of high and low pressure through normally open non-return valves and throttles of constant section.

EFFECT: protection of equipment against impact loads.

2 cl, 1 dwg

FIELD: transport.

SUBSTANCE: invention relates to devices for transporter-launcher container (TLC) suspension. System of vertical cushioning includes pendulum gear containing surrounding TLC resting device which is kinematically connected using two first links with pneumatic shock absorbers which are installed on corresponding stationary platforms installed in the upper part of mine construction (MC). Plunger of each pneumatic shock absorber is contacting with rocker arm which is by its one end fixed on MC wall with possibility to rotate in vertical plane and by its other end is connected with the first link. Resting device is made as pivotally connected with the first links power ring on which bearing are mounted in which stud bolts are installed on which drum is fixed. Each stud bolt is made with axial bolt interacting with mating spherical pivot mounted on TLC. On the drum along circumference, radial retainers are installed which interact with mating TLC elements. System of horizontal cushioning includes upper and lower tiers of cushioning each one of which contains four damping devices which are fixed on MC wall and via lever mechanisms with the second links are kinematically connected with TLC using corresponding adapters.

EFFECT: higher reliability of device for TLC cushioning.

3 cl, 8 dwg

FIELD: machine building.

SUBSTANCE: unit of vibration absorption consists of two interconnected pneumatic elements made as closed elastic chambers filled with compressed air. The pneumatic elements are interconnected and connected with a source of compressed air by means of damping channels. The channels are flexible tubes made of elastic material with a calibrated internal cylindrical surface having throttling properties. The system of pneumatic elements or each of them are separately enclosed in a shell of three layers. The outer antifriction layer is made, for example, of woven-wire-cloth containing strong elastic fibres. The middles elastic woven layer is made, for example, of elastic synthetic fibres. The inner layer is made of solid protective material, such as industrial fabric. One of the pneumatic elements is connected to a valve for controlling pressure in the chambers of pneumatic elements, and the other one is to a source of compressed air.

EFFECT: increased efficiency of vibration isolation.

2 cl, 4 dwg

FIELD: construction.

SUBSTANCE: shock-absorbing device comprises a telescopic guide device (2), support boards (10), an elastic element (1). A telescopic guide device (2) is made in the form of opposite external (3) and internal (4) sleeves with a rubber-cord shell (5) and aligning elements (6, 7) installed between them. The elastic element (1) is made in the form of pneumatic shock absorbers arranged evenly around the external sleeve (3) of the telescopic guide device (2) They consist of a body (12), a plunger (13), a rubber-cord shell (14) between them and aligning elements (15, 16). Longitudinal axes of pneumatic shock-absorbers of the elastic element (1) are arranged at the angle 40-70 to the longitudinal axis of the guide device (2). Plungers (13) are connected in a hinged manner to boards (17), installed on the sites of the base ledges (18). At the end of the inner sleeve (4) of the telescopic guide device (2) there is a tight partition (20) installed with a valve electromagnet device (21). At the ends of plungers of all pneumatic shock-absorbers there are tight partitions installed with valve electromagnet devices.

EFFECT: improvement of device damping properties.

3 cl, 3 dwg

Rotor support // 2419000

FIELD: machine building.

SUBSTANCE: support consists of half-couple rotating and coupled with machine case directly or via damping unit. Contacting surfaces of the half-couple are spherical or of close to spherical shape. The rotating half-couple connected to the rotor, is made out of metal. Another half-couple is made completely out of ceramic material on base of aluminium and zirconium oxides, silicon carbide and nitride with dimension of particles up to 30 mcm.

EFFECT: durable wear resistant and strong support of higher bearing capacity.

6 cl, 1 tbl, 1 dwg

FIELD: machine building.

SUBSTANCE: method consists in periodic decreasing restoring force of pneumatic suspension at beginning of each stroke of release by means of supplying additional volume of gas to one additional flexible element (4) from autonomous source of power (7) and by means of its withdrawal from this additional flexible element (4) at beginning of each stroke of compression to atmosphere. Additionally, at the beginning of each stroke of compression there is performed periodic supply of additional volume of gas to the second additional flexible element (5) from autonomous source of power (7), while its withdrawal to atmosphere from second additional flexible element (5) is made at the beginning of each stroke of release.

EFFECT: control of flexible damping characteristics of pneumatic suspension in all amplitude-frequency range of external force.

2 dwg

FIELD: machine building.

SUBSTANCE: elastic force of pneumatic suspension is periodically increased in the beginning of each compression stroke by supplying of additional gas mass to additional elastic element from autonomous source of energy. Elastic force of pneumatic suspension is periodically decreased in the beginning of each rebound stroke by partial removal of additional gas mass from additional elastic element into atmosphere.

EFFECT: invention provides for adjustment of elastic-damping properties of pneumatic suspension in the whole amplitude-frequency range of external action.

2 dwg

FIELD: machine building.

SUBSTANCE: method is implemented owing to periodic decrease of restoring force of main pneumatic flexible element (3) of suspension. At the beginning of each rebound stroke additional mass of gas is supplied to additional flexible element (4) from an autonomous energy source (7). Also electromagnetic force effecting damped object (1) is additionally and briefly created by means of auxiliary damping electro-magnetic element (5). At the beginning of each compression stroke additional mass of gas is withdrawn from additional flexible element (4) into atmosphere.

EFFECT: raised damping properties of pneumatic suspension in all amplitude-frequency range of external effect.

1 dwg

Up!