Hydraulic damper

FIELD: machine building.

SUBSTANCE: inside cylinder tube and hydraulic damper there are arranged inter-communicating piston cavity and controlled cavity. Both cavities are filled with oil in a pressurised state. Additionally, there is installed a piston travelling in axial direction in the piston cavity and a rod connected to the piston. A flexible element is installed in the control cavity in a position forming a reservoir in the control cavity by means of compression of oil with pressurising force; impact effect is damped so, that the flexible element is forced to elongate and contract when oil flows in/out of the reservoir due to travels of the rod.

EFFECT: simplicity and reduced dimension of design of hydraulic damper, retaining constant amount of oil in piston cavity.

10 cl, 3 dwg

 

The technical field of the invention

The present invention relates to a hydraulic damper, absorbing shock when stopping a moving object by using the resistance of the oil flow.

The prior art inventions

Hydraulic damper, for example as described in published Japanese patent application No. 2006-250309, has the configuration in which the piston cavity of the cylindrical tube filled with oil, such as mineral oil, and the braking piston located in the piston cavity in the position in which the gap for flow of oil remains on the outer periphery of the piston, and a rod connected with the piston, passes outwards from the cylindrical tube. Then the kinetic energy of the moving object is absorbed by the resistance to flow of the oil flowing through the gap for flow of oil when the piston is displaced by the collision with the moving object on the leading end of the rod.

The stock, which always returns the return spring to the initial position, repeats the process of moving to the initial position by encouraging the efforts of the recoil after a moving object collides and returned to the position of depreciation. At this time, as on the surface of the rod formed oil film due to adhesion of oil, and cover the existing piston cavity, the oil in the piston cavity gradually flows out through the rod through repetition of movements back and forth. In the result, the damping capacity of the damper is reduced, while the amount of oil in the piston cavity is gradually reduced, and, thus, the hydraulic damper wear.

In order to prevent the lowering of the dampening caused by such reduction in the amount of oil, the damper can be constructed, for example, as shown in figure 3. More precisely, separately from the piston cavity 23 which is placed in the piston 21 and the oil 22 in the inner cylindrical tube 20 is provided with a reservoir 24 which is connected with the piston cavity 23. The oil 22 in the tank 24 is always under pressure by means of a spring 26 via the pressure piston 25. Even though the oil in the piston cavity flows out through the rod 27, the amount of oil in the piston cavity 23 is always maintained constant so that the oil corresponding to the reduced quantity is replenished from the reservoir 24.

Thus, the damper having such a structure, designed to maintain the oil pressure in the tank 24 by means of a spring 26 via the pressure piston 25. Therefore, the design is complicated not only by the application of pressure, but also requires a large space DL the placement of the injection piston 25 and springs 26, what is the problem, because the axial length of the damper increases.

Patent document 1: Japanese unexamined patent application No. 2006-250309.

Disclosure of inventions

Technical task

The technical problem of the present invention is to provide a hydraulic damper is a simple and small structure capable of maintaining in the piston cavity constant amount of oil without the use of springs, the injection piston or the like.

In order to solve the above problem, the hydraulic damper of the present invention includes: a cylindrical tube having a first end and a second end at its both ends in the direction of the axial line and also having an intermediate wall between the two ends; a piston cavity and control cavity that is formed between the intermediate wall and the first end face and between the intermediate wall and the second end, respectively, to mutually communicate through a built-in portion formed in the intermediate wall; the oil enclosed in the piston cavity and regulatory cavity pumped in the state; the pressure adjustment element, which maintains the pressure by controlling the outside; a piston which moves in the axial direction to a position that maintains the gap for flow, che the ez which the oil flows between the inner periphery of the piston cavity and the outer periphery of the piston within the piston cavity; a rod mounted on the piston to pass through the intermediate wall, the regulating cavity and a second end, the leading end of which is displayed outside of the cylindrical tube; and an elastic element, which is located in the control cavity and compressed by displacing the efforts of the oil in the initial position, when the rod is in the off position so as to form a reservoir in the control cavity through the space created by the compression, and the elastic element is elastically elongates and shrinks due to leak/leakage of oil from the reservoir through the action of the rod.

In the present invention it is necessary that the size of the elastic element was the size that fills the entire regulatory cavity at the time when it is not compressed.

In addition, in the present invention in the first end of the cylindrical tube provided with an inlet opening for the inlet of the oil in the piston cavity and control cavity and also provided the pressure adjustment element that serves as a plug to seal the inlet opening to be movable forward and backward, so that the oil is blowing by moving the pressure adjustment element.

In this case, the inlet opening is formed of a fitting hole of a small diameter, open in the piston cavity, and side vents with internal re IBOY large diameter, open to the outside. the pressure adjustment element is formed from the connecting protruding part with a small diameter, tightly inserted into the fitting hole with the sealing element, and a part with an external thread of larger diameter screwed into a part with an internal thread. With this configuration, the oil is pumped in the state after rotation to move forward of the pressure adjustment element.

Also in the present invention, the second end may have a sleeve of cylindrical shape, passing along the rod to the position of the intermediate wall. Regulatory cavity may be formed between the outer periphery of the coupling and the inner periphery of the cylindrical tube, and the elastic element can be located between the outer periphery of the coupling and the inner periphery of the cylindrical tube.

In this case, the intermediate wall may be formed on the leading end of the coupling.

Advantages

According to the present invention is provided with a hydraulic damper with a simple and reduced design, ability to hold a constant amount of oil in the piston cavity, without using the spring discharge piston or similar.

Brief description of drawings

Figure 1 is a view in section of a hydraulic damper in accordance with the present invention.

Figure 2 is a view in brings and, depicting the situation where there is a lack of oil in the tank of the hydraulic damper of the present invention.

Figure 3 is a view in section of a hydraulic damper, which requires improvement.

Description of embodiments

1 and 2 depict one alternative implementation of a hydraulic damper according to the present invention. The damper has a cylinder tube 1. The cylindrical tube 1 has a first end face 2 located at the side of the near end in the direction of the axial line L, the second end 3 located at the side of the leading end, and an intermediate wall 12 located in the middle between them. In addition, the cylindrical tube 1 inside contains a piston cavity 4 and the regulating cavity 13, which is formed between the intermediate wall 12 and the first end face 2 and between the intermediate wall 12 and the second end face 3, respectively, to mutually communicate through a built-in part 12a of the intermediate wall 12; oil 18, the filling piston cavity 4 and the regulating cavity 13 in the pumped state; the piston 6 of the damper, which moves in the direction of the axial line L in the inner part of the piston cavity 4; rod 7 mounted on the piston 6, the leading end of which is displayed outside of the cylindrical tube 1, and expanding the elastic element 8, which always supports the oil 18 in ninetendo the state.

The cylindrical tube 1 and the first end face 2 is made as a single unit. The inlet opening 9 to the oil inlet 18 in the cylindrical tube 1 is formed in the middle section of the first end face 2. The inlet opening 9 is sealed by the cover element 10 serving as a pressure adjustment in order to maintain the received oil 18 in the pumped state.

The inlet opening has a connecting part 9a of the hole with a small diameter opening in the piston cavity 4, and the portion 9b of the hole with internal thread with a large diameter, open to the outer part, with a built-in with the environment. On the other hand the element 10 pressure adjustment is provided with the protruding portion 10A with a small diameter from the leading end, which is tightly inserted into the connecting part 9a of the hole through the sealing element 17, and the part 10b with the external thread of larger diameter, which is threaded into the portion 9b of the hole with internal thread. The oil 18 in the cylindrical tube 1 is under pressure by turning the adjustment element 10 pressure to move forward.

The second end face 3, which is formed separately from the cylindrical tube 1, is tightly inserted in the cylindrical tube 1 by means of ring seals 15. The second end 3 has as an integral part of the locking portion 3a, which is akrival leading end part of the cylindrical tube 1, and a cylindrical sleeve 3b, which passes to the inner side of the cylindrical tube 1 along the outer periphery of the rod 7 from the locking part 3a. The sealing element 16, which is tightly inserted between the locking part 3a and the outer periphery of the shaft 7, mounted in a carved recess 3c is formed with the outer edge of the inner periphery of the locking pieces 3a. The second end face 3 and the sealing element 16 is fixed in position with the annular locking element 11 mounted on the end portion of the cylindrical tube 1.

When this clutch 3b, as shown in figures 1 and 2, are made so as to be elongated in the axial direction of the cylindrical tube 1, and are made so as to also function as a support and guide rod 7. However, even if a bending load acts on the piston rod 7, the rod 7 can be moved forward and backward in the appropriate direction. Accordingly, it is possible to prevent the movement of the piston 6 from the position in which it can be destroyed, when the piston 6 is in contact with the surface of the wall of the piston cavity 4. This allows the elastic strip is stable to withstand shock loads.

The intermediate wall 12 is provided as a single unit at the leading end of the clutch 3b. Piston chamber 4 is formed between the intermediate wall 12 and the first that is CMA 2, and regulatory cavity 13 is formed between the intermediate wall 12 and the locking part 3A of the second end face 3. Accordingly, the piston chamber 4 is on the side of the near end of the cylindrical tube 1, which regulates the cavity 13 is on the side of the leading end of the cylindrical tube 1.

However, the intermediate wall 12 may be formed separately from the coupling 3b and is connected with the clutch 3b. Alternative intermediate wall 12 may be formed as one piece with the cylindrical tube 1. Additionally, the intermediate wall 12 may be formed as an independent element and tightly inserted into the cylindrical tube 1 so that the intermediate wall 12 was brought into contact with the leading end of the clutch 3b.

A piston 6 having a smaller external diameter than the internal diameter of the piston cavity 4, is placed in the piston cavity 4 to be moved in the direction of the axial line L of the cylindrical tube 1, with the gap S, supported in the place where the oil 18 flows between the outer periphery of the piston 6 and the inner periphery of the cylindrical tube 1. In addition, between the piston 6 and the first end 2 is the return spring 14, which always urges the piston 6 to move to the initial position (the position of the upper half of figure 1), where the piston 6 is provided in contact with the intermediate wall 12. Then, when Porsche is 6 moves to the position of the depreciation depicted in the lower half of figure 1, from the initial position, the oil 18 in part 4a of the cavity from the front side between the piston 6 and the first end 2 is moved to part 4b of the cavity from the side of the rod between the piston 6 and the intermediate wall 12 through the gap S at the same time when the piston 6 is returned to the initial position from the position of depreciation, the oil 18 in part 4b of the cavity from the side of the rod moves in part 4a of the cavity from the front side through the gap S. In this case, at the same time, the oil 18 in part 4b of the cavity from the side of the rod can move in the part 4a cavity from the front side through the gap P formed between the rod 7 and the piston 6.

In addition, the nearest end portion of the rod 7 is connected with the piston 6 and the piston 6 and the rod 7 as a whole is moved forward and backward in the direction of the axial line L of the cylindrical tube 1.

The rod 7 passes through the intermediate wall 12 and the second end face 3. The leading end part of the rod 7 is derived outside of the cylindrical tube 1, and a moving object that should be discouraged, faces the leading end part. When the shock effect caused by the moving object, attached to the rod 7, the piston 6 is shifted by the rod 7 and is discharged back to the first end of the piston 2 in the cavity 4, and when the effective force of a moving object is fixed, the piston 6 and the rod 7 are pushed by the lead is placed in the action of the return spring 14, to return to the initial position.

Governing the cavity 13 is a hollow cylindrical shape, surrounding the rod 7. Regulatory cavity 13 is formed between the outer periphery of the clutch 3b cylindrical shape formed on the second end face 3 and the inner periphery of the cylindrical tube 1. The outer diameter of the regulating cavity 13 is made larger than the inner diameter of the piston cavity 4.

The elastic element 8 has a cylindrical shape placed in the control cavity 13 to be tensile in the direction of the axial line L and in the diametrical direction of the cylindrical tube 1. The elastic element 8 can be made of microporous rubber, made of elastic foam (e.g., foam, made of nitrile rubber (NBR) or synthetic foam)having closed pores. The elastic element 8 is located in the control cavity 13 so as to surround the sleeve 3b. In initial position, where the rod 7 occupies the position of the leading end of the elastic element 8 is elastically compressed by the pressure of the pumped oil 18. The reservoir 5 is formed in the control cavity 13 through the space created by its compression.

It is necessary that the length in the direction of the axial line L, and the inner diameter and outer diameter of the elastic element 8 in an uncompressed condition b is approximately equal to the corresponding parameters governing the cavity 13, or a little less or a little more than they are. In other words, the preferred size of the elastic element 8 is to approximately fill the entire governing the cavity 13. In this case, the tank 5 in the control cavity 13 is not formed.

Under this condition, when the elastic element 8 is moved toward the second end face 3, depicted in the illustrated example. However, the elastic element 8 is not necessarily constantly occupies such position, and in some cases, the elastic element 8 occupies the Central part or another position in the control cavity 13.

The tank 5 is communicated with the piston cavity 4 through a built-in part 12a formed on the intermediate wall 12. Accordingly, the oil 18 received inside the piston cavity 4, and the tank 5 is located in a pumped state, which arose under the influence of elastic recovery efforts compressed elastic element 8.

The tank 5 absorbs the difference of volume between the two parts of the cavity 4a, 4b upon receipt of oil 18, the current to part 4b of the cavity from the side of the rod from the part 4a of the cavity from the front side, i.e. the oil corresponding to the volume of the rod 7, is in part 4b of the cavity from the side of the rod, when the piston 6 and the rod 7 are beginning to move away from its initial position, which is the position of the leading end to move to the position of depreciation. the AK as the number of the current oil 18 differs depending on the position of the piston 6, tank 5 is changed in accordance with the amount of oil 18. More specifically, when the piston 6 is pressed to move to the position of depreciation, the amount of oil flowing into the reservoir 5, gradually becomes larger, so that the volume of the tank 5 was increased, and the compression of the elastic element 8 is gradually becoming more. On the contrary, when the piston 6 is returned to the initial position from the position of depreciation, oil flows from the reservoir 5 so that the elastic element 8 has been extended and tank 5 is reduced.

Next will be described the operation of the hydraulic damper having the above configuration. When the damper is not operating, the piston 6 is advanced to the return spring 14 and occupies the initial position, when the piston 6 is in contact with the intermediate wall 12, as shown in the upper half of figure 1. At this time, the reservoir 5 is formed in the control cavity 13, the compressed elastic element 8, and the oil 18 in the cylindrical tube 1 is pumped condition under the force of recovery of the elastic element 8.

When a moving object collides with the rod 7 in this position, the piston 6 is advanced by the piston rod 7 and is moved to the position of depreciation, as shown in the lower half of figure 1. Then the oil 18 in part 4a of the cavity from the front side flows to part 4b of the cavity from the side of the rod through for the op's outer periphery of the piston 6 by moving the piston 6 and the rod 7, so that the kinetic energy of the moving object at this time was absorbed by the resistance to flow. Oil corresponding to the volume of the rod 7, is included in part 4b of the cavity from the side of the stem along with butter 18, the current in part 4b of the cavity from the side of the stock, flows into the reservoir 5, and optionally compresses the elastic element 8, in order to increase the reservoir 5.

When the force of impact of a moving object is not attached to the rod 7, the piston 6 and the rod 7 are returned to their initial position, which is the leading end, through the power of the trigger return spring 14. At this time, the oil displaced from the reservoir 5 through the elastic recoil of the efforts of the elastic element 8, and the oil flows in part 4a of the cavity from the front side through the part 4b of the cavity from the side of the stem, which allows the return of the piston 6. In addition, the compressed elastic element 8 is restored with the release of oil from the reservoir 5, which leads to the initial state shown in the top half of figure 1.

Repetition of the operation of the damper causes the shaft 7 to repeat the process of moving back and forth, the oil 18 is gradually flows to the outer side, Nalepa on the surface of the rod 7, and the amount of oil in the piston cavity 4 is gradually reduced. In this case, as shown in figure 2, the oil 18 in the tank 5 is replaced by elastic vozvratnoj effort of the elastic element 8 only the corresponding reduction, which has expanded piston cavity 4. As a result, the amount of oil in the piston cavity 4 is always maintained constant.

When the tank 5 is reduced, because the amount of oil in the piston cavity 4 is reduced, the compression ratio of the elastic element 8 is also reduced, so that the force of the oil pressure was decreased. When it is necessary to increase the pressure on the elastic element 8, increasing the volume of the tank 5 in comparison with this condition, the oil pressure may be increased by the delay element 10 pressure adjustment.

Thus, the reservoir 5 is formed by compression of the elastic element 8 using preemptive force of the oil, and the oil is displaced from the reservoir 5 in accordance with the number corresponding to the reduction of oil in the piston cavity 4, is based on the elastic return force of the elastic element 8. So, for example, compared with the case where it is used injection piston and spring, the configuration becomes simple, because it uses a small number of parts and it becomes possible to reduce the damper, reducing the length of the damper in the direction of the axial line L.

In the embodiment, the cylindrical elastic element 8 is made in the form of solid parts made of foam with closed pores, but can be used in any configuration, provided choppy element 8 can cause a volumetric change by hydraulic action. For example, the elastic element 8 may be made in the form of an inflatable chamber with a flexible and non-porous material, such as rubber. In addition, the elastic element 8 can be made by bending a plate of porous material in a cylindrical shape in accordance with the internal shape of the regulating cavity.

The reference list of items

1. cylindrical tube

2. the first end of the

3. the second end of the

3b. clutch

4. piston chamber

5. tank

6. piston

7. stock

8. elastic element

9. inlet

9a. the fitting holes

9b. part of the hole with internal thread

10. element pressure control

10a. the fitting protrusion

10b. the part with external thread

12. the intermediate wall

12a. soamsawali part

13. regulatory cavity

17. sealing element

18. oil

L axial line

's gap

1. Hydraulic damper, comprising:
a cylindrical tube having a first end and a second end at its both ends in the direction of the axial line and also having an intermediate wall between the two ends;
piston cavity and control cavity that is formed between the intermediate wall and the first end face and between the intermediate wall and the second end face, respectively, so as to mutually communicate across the built-in part, formed in the intermediate wall;
the oil enclosed in the piston cavity and regulatory cavity pumped in the state;
element pressure adjustment, which increases the pressure by controlling the outside, so as to increase the pumping force of the oil, which is reduced due to the reduction of the amount of oil by adjusting damper;
the piston, which moves in the axial direction to a position that supports the gap for flow, through which the oil flows between the inner periphery of the cylindrical tube and the outer periphery of the piston within the piston cavity;
a rod mounted on the piston so as to pass through the intermediate wall of the regulating cavity and a second end, the leading end of which is displayed outside of the cylindrical tube;
an elastic element, which changes its volume through the impact of hydraulic pressure and which is located in the control cavity and compressed by displacing force of the oil in the initial position, when the rod is in the off position so as to form a reservoir in the control cavity through the space created by the compression, and the elastic element is elastically elongates and shrinks due to leak/leakage of oil from the reservoir through the action of the rod.

2. The damper according to claim 1, in which the size of the elastic element is size, which fills the entire regulatory cavity at the time when it is not compressed.

3. The damper according to claim 1 or 2, in which the first end of the cylindrical tube provided with an inlet opening for the inlet of the oil in the piston cavity and control cavity, and also provided the pressure adjustment element that serves as a plug to seal the inlet opening, with the ability to move back and forth so that the oil was pumped through the forward movement of the pressure adjustment element.

4. The damper according to claim 3, in which the inlet opening is formed of a fitting hole of a small diameter, open in the piston cavity, and part of the hole with internal thread of larger diameter, open to the outside, and the pressure adjustment element is formed by connecting the protruding part and the small diameter, tightly inserted into the fitting hole with the sealing element, and a part with an external thread of larger diameter screwed into a part with an internal thread so that the oil was pumped state after turning the pressure adjustment element to move it forward.

5. The damper according to claim 1 or 2, wherein the second end has a coupling cylindrical shape, passing along the rod to the position of the intermediate wall, thus regulating chamber is formed between the outer lane is Feria clutch and the inner periphery of the cylindrical tube, an elastic element is located between the outer periphery of the coupling and the inner periphery of the cylindrical tube.

6. The damper according to claim 3, in which the second end has a coupling cylindrical shape, passing along the rod to the position of the intermediate wall, thus regulating chamber is formed between the outer periphery of the coupling and the inner periphery of the cylindrical tube, and the elastic element is located between the outer periphery of the coupling and the inner periphery of the cylindrical tube.

7. The damper according to claim 4, in which the second end has a coupling cylindrical shape, passing along the rod to the position of the intermediate wall, thus regulating chamber is formed between the outer periphery of the coupling and the inner periphery of the cylindrical tube, and the elastic element is located between the outer periphery of the coupling and the inner periphery of the cylindrical tube.

8. The damper according to claim 5, in which the intermediate wall is formed at the leading end of the coupling at the second end.

9. The damper according to claim 6, in which the intermediate wall is formed at the leading end of the coupling at the second end.

10. The damper according to claim 7, in which the intermediate wall is formed at the leading end of the coupling at the second end.



 

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1 dwg

FIELD: machine building.

SUBSTANCE: hydraulic shock absorber comprises a reservoir with an operating cylinder filled with a working fluid. Inside the cylinder there is a piston installed movably with valves. The piston is rigidly fixed on the stem interconnected with the protective jacket. The working cylinder and the protective jacket are made of diamagnetic material. The protective jacket contacts with its inner circular surface with the responsive surface of the working cylinder via a row of revolution solids. In the space between rows of solids of revolutions inside the specified protective jacket there is a ring rigidly fixed, made of a permanent magnet. The ring interacts with its magnetic field via an air gap and a wall of a working cylinder with a cylindrical circular generatrix surface of a magnetoconductive piston of a shock absorber.

EFFECT: increased reliability and simplified design of hydraulic shock absorbers.

3 dwg

FIELD: transport.

SUBSTANCE: proposed damper comprises body, cylinder, rod with piston and extra piston to divide said cylinder to three chambers. Different-stiffness spring is fitted in every said chamber. Said chambers are communicated by pipelines via controlled throttles and solenoid valves. Pipeline is connected with feed main and discharge line. Throttles and valves are controlled by control unit in response to signals fed by the driver.

EFFECT: wider adjustment band, simplified design.

3 cl, 2 dwg

Hydraulic damper // 2562666

FIELD: machine building.

SUBSTANCE: hydraulic damper consists of a working cylinder coupled with a housing via rolling bodies. A piston is made from magnetic material. A magnetic ring rigidly fixed on the housing is in contact with the piston through an air gap. A splined pin made from resilient material is mounted inside the working cylinder. The splined pin is interconnected with mating splines of the piston. The piston is equipped with vertical throttle channels. The channels pass into L-shaped channels on the end face surfaces. The outlet holes of the channels adjoin plates with a gap. The plates are rigidly fixed on the piston.

EFFECT: change of damping characteristics.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building. The shock-absorber includes cylinder, rod-piston, piston, three working cavities in each one of which there are internal and external springs with opposite direction of turns. The springs of each cavity are made with different tension. Cylinder has in each cavity one delivery and one drain hole. Delivery holes are connected by pipelines with electrically driven valves connected with delivery main line. The drain holes are connected by pipelines with adjustable throttles the outputs of which are connected into one main line attached to drain line via electrically driven valve. The electrically driven valves and adjustable throttles are assembled into valve and throttle units installed on the cylinder. Throttles and valves are controlled via data bus and signal amplifier unit by electronic control unit. The control unit receives signals from operating mode and various sensors selector.

EFFECT: wide range of shock-absorber characteristics adjustment, higher design reliability, manual and manual with automatic correction control of shock-absorber.

1 dwg

FIELD: machine building.

SUBSTANCE: invention relates to plain bearing for suspension strut of four-wheel vehicle. Proposed bearing comprises upper collar (3) made in synthetic rubber and furnished with circular lower surface (2), lower collar (5) made in reinforced-synthetic rubber and applied on the said upper collar to revolve about its axis. The said lower collar has also circular upper surface (4) arranged opposite surface (2), and circular thrust part (6) made in synthetic rubber and arranged between surfaces (2) and (4). Lower collar (5) has surface (36) making a seat of cylindrical spring (61) and arranged on lower surface (25). Lower collar (5) comprises circular thrust section (12), upper cylindrical section (24), formed entirely on upper surface (23) of section (12). Surface (4) and lower cylindrical section (26) are formed on lower collar (5). The lower cylindrical section (26) is formed entirely on surface (25) of circular thrust section (22). Note here that surface (25) of section (22) arranged on radially outer surface (26) makes surface (36) of the seat of spring (61). Note also that sections (12), (24) and (26) comprise multiple tapered chambers.

EFFECT: reduced vehicle suspension weight and running gear cost.

13 cl, 6 dwg

FIELD: machine building.

SUBSTANCE: invention relates to bearing structure of damper in hydraulic actuator. Structure for fixation of damper (72a, 72b) is located in hydraulic actuator. Coats (14, 16) are installed on of the cylinder (12) casing. Piston (18,) is installed inside the cylinder (12) casing. Damper groove (70a, 70b) contains the first and the second grooves. The first groove (74) is open from the side of end surface. The second groove (76) is located adjoining to the first groove (74) and expands relative to it. According to the first version damper groove (70a, 70b) is formed on the end surface of piston (18) perpendicularly to its axis and is directed to covers (14, 16). According to the second version damper groove is formed on the end surface of cover (14, 16) perpendicularly to its axis and is directed to piston (18). Damper (72a, 72b) contains basic element (80) and expanding relative to its guideline element (82).

EFFECT: creation of structure providing easy and reliably install damper on piston or covers.

7 cl, 17 dwg

Hydraulic damper // 2413887

FIELD: machine building.

SUBSTANCE: inside cylinder tube and hydraulic damper there are arranged inter-communicating piston cavity and controlled cavity. Both cavities are filled with oil in a pressurised state. Additionally, there is installed a piston travelling in axial direction in the piston cavity and a rod connected to the piston. A flexible element is installed in the control cavity in a position forming a reservoir in the control cavity by means of compression of oil with pressurising force; impact effect is damped so, that the flexible element is forced to elongate and contract when oil flows in/out of the reservoir due to travels of the rod.

EFFECT: simplicity and reduced dimension of design of hydraulic damper, retaining constant amount of oil in piston cavity.

10 cl, 3 dwg

FIELD: transport.

SUBSTANCE: proposed bearing 1 has top housing 3 made from synthetic resin with seat surface 10 for mount device 9 arranged on car body side and annular bottom surface 2, bottom housing 5 made from synthetic resin and annular thrust plain element 6 from synthetic resin. Annular top surface 4 is made integral with bottom housing 5 opposite surface 2, and seat surface 25 of suspended cylindrical spiral spring 7. Said housing is fitted on top housing 3 to rotate about axis O of housing 3 in direction Z. Thrust plain element 6 is arranged in annular clearance between surface 2 and surface 4 and features annular thrust surface sliding to thrust against surface 2 or surface 4. Mount surface 10, working surface and part of surface 25 where against thrusts spring 7 are fitted on bearing axle 1.

EFFECT: efficient bearing to reduce load from car body.

8 cl, 11 dwg

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