RU131106U1 - FIRST STAGE HYDRAULIC DAMPER OF SPRING SUSPENSION OF A VEHICLE - Google Patents

Abstract

1. The hydraulic damper of the first stage of the spring suspension of the vehicle, comprising a housing with a base and a cylinder coaxially placed in the housing, in which the piston with the rod is mounted to move, the piston is mounted to move relative to the rod and spring loaded from above and below by springs, an internal cavity the cylinder is divided by the piston into the supra-piston and sub-piston cavities, which are filled with a working fluid, the annular cavity between the cylinder and the body is filled with a working fluid partially bone, the bottom cylinder is closed by the bottom, and the top is closed by the guide sleeve, there is a compression throttle in the piston, there is a tension throttle in the guide sleeve, while the rod is passed through the central hole in the guide sleeve, and the entire cylinder-piston group of parts is fixed in the housing by a ring nut, case and the stem are provided with eyes, an inlet valve is mounted in the bottom, and a tensile throttle is connected through a radial channel in the guide sleeve to an overflow tube extending into the annular cavity, distinguishing The fact that the piston has a circular groove along the inner diameter, which is connected by vertical channels to the piston cavity of the cylinder, and the rod end has a through axial hole with a threaded outlet, equipped with rows of upper and lower radial holes at different levels. 2. The damper according to claim 1, characterized in that at least one row of radial upper holes of the rod at its level has an exit to the supra-piston cavity and at least one row of radial lower holes at its level has an exit to the sub-piston field

Description

The utility model relates to transport equipment, namely, to hydraulic dampers of the first stage of spring suspension, which perceives, when the vehicle is moving, besides harmonic, shock effects.

Known hydraulic shock absorber (RU 41345, F16F 5/00, publ. 20.10.2004) containing a housing in which a cylinder is installed with the formation of an annular tank with a working fluid, a piston with a rod placed in the cylinder with the formation of over - and subpiston cavities installed in the rod the bypass valve connecting the cavity with the working fluid with the over-piston cavity, the intake valves installed in the piston and piston cover, and the damping coefficient regulator, the damping coefficient regulator is made in the form of a spool dr a wiper with a variable hydraulic characteristic and a piston rod displacement transducer, while a slide valve throttle plunger with channels for supplying and discharging the working fluid from the piston cavity of the cylinder and into the annular container with the working fluid are placed in the rod cover, the piston rod displacement transducer is placed in the supra-piston cavity and made in the form of two conical spiral springs articulated over a large radius, interacting with a spaced between them and installed displacements relative to the piston rod with a carrier, one of the shoulders of which is connected by a hinge to the thrust of the piston of the spool throttle, the upper conical spring having greater rigidity than the lower one and attached to the rod cover with a smaller radius and the lower one on the piston rod.

A disadvantage of the known hydraulic shock absorber is the lack of performance in the first stage of spring suspension under shock from irregularities in the movement of the vehicle. In this hydraulic shock absorber, the spool throttle carrier has a very complex device and is driven by a spring in the over-piston cavity. Due to its complexity and high inertia, such a technical solution cannot normally respond to impact and therefore this hydraulic shock absorber cannot be used in the first stage of spring suspension of rolling stock.

Known hydraulic shock absorber (RU 69948, F16F 9/52, F16F 5/00, F16F 9/16, F16F 11/00, publ. 10.01.2008) containing a cylinder, a piston with a rod, an alternating throttle channel formed by two elements - a channel, connecting the piston and rod cavities of the cylinder and the element for changing the bore of the channel installed in the channel with the possibility of relative axial movement, the drive additional axial movement of the elements of the variable throttle channel in the direction of decreasing the bore with increasing temperature and increasing one section with decreasing temperature, resulting in additional axial movement variable throttle channel element is designed as a temperature-sensitive elements, and the damper is provided with a hydraulic oscillation damper variable throttle channel element. The sleeve is axially movable in the cylinder, the piston is installed in the sleeve, the channel connecting the piston and rod cavities of the cylinder is made in the side surface of the sleeve in the form of through grooves of variable width or through holes, while thermosensitive elements are installed between the sleeve and one end of the cylinder, and a spring is installed between the liner and the second end of the cylinder, and the hydraulic vibration damper of the variable throttle channel element is made in the form of an additional piston formed by lzoy with throttle channels communicating the cavity in the sleeve with the cavity of the cylinder. The channel connecting the piston and rod cavities of the cylinder is formed by grooves of variable depth on the inner side surface of the cylinder, and the piston is mounted with the possibility of axial movement relative to the rod, while on the one hand heat-sensitive elements are installed between the piston and the rod, and on the other hand, a spring installed in the cavity formed by the piston and the rod, and the hydraulic vibration damper of the variable throttle channel element is made in the form of an additional piston formed by a sleeve with a dross the channel connecting the cavity in the sleeve with the cylinder cavity. A cavity is made in the piston in which the control ring is mounted axially movable, the channel connecting the piston and rod cavities of the cylinder is made in the control ring, the element for changing the channel passage section is made in the form of a rod with a variable cross section located in the channel, while between thermosensitive elements are installed by the regulating ring and piston, and the hydraulic vibration damper of the variable throttle channel element is made in the form of an additional piston, formed a sleeve with a throttle channel communicating a cavity in the sleeve with a cylinder cavity.

A disadvantage of the known hydraulic shock absorber is the lack of performance in the first stage of spring suspension under shock from various irregularities of the path. In this hydraulic shock absorber, a spring is installed between the liner and the second end of the cylinder, but there is no exit of the working fluid from this cavity except the throttle channel, therefore, under shock impacts on the hydraulic shock, the working fluid will not be able to find a full exit from this cavity and the hydraulic shock will rigidly perceive this shock impact and rigidly transfer it to the sprung mass of the vehicle.

The closest set of features to the claimed object is adopted for the prototype hydraulic damper (RU 2435999, F16F 5/00, F16F 9/16, publ. 10.12.2011). The damper contains a base, guide and shock absorbing devices. The rod is rigidly fixed in the bottom of the cylindrical sleeve with the formation of a sealed annular cavity. The bottom of the cylindrical sleeve is fixed in the sleeve, rigidly connected with the base of the protected object. A spring is located in the annular cavity, which abuts against the bottom with the lower end, and with the upper end against the piston. The piston is made in the form of a disk and is located with a throttling clearance relative to the rod. In the upper part of the stem is a cover that is movable relative to the stem. The cover consists of an annular flange with a seal and a sleeve rigidly connected to the flange of the sleeve, covering the outer surface of the cylindrical sleeve through the seal. Coaxial to the rod is a spring, the upper end of which abuts against the cover, and the lower end into the piston. The support element of the vibration-insulated object is fixed on the lid. EFFECT: increased efficiency of vibration isolation.

A disadvantage of the known hydraulic damper is the lack of performance in the first stage of spring suspension during impacts from the rail at the joints, arrows and other irregularities. Since the throttle is located with a constant throttling clearance relative to the rod and there is no other passage of the working fluid, when impacted on the hydraulic damper, the working fluid will not be able to find an additional outlet from the under-piston or supra-piston cavities and the hydraulic damper will rigidly accept this impact and rigidly transfer it to the sprung mass.

The problem to which the claimed technical solution is directed is to increase the operability of the hydraulic damper of the first stage of spring suspension of the vehicle.

The technical task is achieved by the fact that the proposed hydraulic damper of the first stage of spring suspension of the vehicle, which contains a housing with a base and a coaxially placed cylinder in the housing, in which the piston with the rod is mounted to move, the piston is mounted to move relative to the rod and spring loaded top and bottom springs, the internal cavity of the cylinder is divided by the piston into the supra-piston and sub-piston cavities, which are filled with a working fluid , the annular cavity between the cylinder and the housing is partially filled with the working fluid, the cylinder is bottom-closed by the bottom and closed by the guide sleeve from the top, the piston has a compression throttle, and there is a tension throttle in the guide sleeve, while the rod is passed through the central hole in the guide sleeve, and the entire piston cylinder a group of parts is fixed in the housing by a ring nut, the housing and the stem are provided with eyes, an inlet valve is mounted in the bottom, a tensile throttle is connected through a radial channel in the guide sleeve overflow pipe exiting into the annular cavity, the piston has a circumferential groove on the inner diameter, which is connected with the subpiston vertical channels hollow cylinder and has a rod end with the blind axial bore with a threaded outlet provided with a series of upper and lower radial openings at different levels.

At least one row of radial upper holes at its level has an exit to the supra-piston cavity and at least one row of radial lower holes at its level has an exit to the sub-piston cavity.

The through hole at the end of the stem is closed with a bolt.

The technical result provided by the given set of features is to increase the operability of the hydraulic damper of the first stage of spring suspension of the vehicle by using a piston spring-loaded on both sides, movable relative to the rod and the presence of axial and radial holes in the rod. The set of distinctive features makes it possible to effectively limit at an acceptable level the inelastic resistance of the hydraulic damper of the first stage of spring suspension of a vehicle during impacts due to the displacement of the piston relative to the rod, which increases the volume of the cylinder cavity from the side of the impact and due to the overflow of the working fluid from the cylinder cavity from the side of the shock exposure. Limiting the permissible level of inelastic resistance of the hydraulic damper of the first stage of spring suspension of the vehicle reduces the impact from the path to the vehicle and, as a result, increases the smoothness of the rolling stock and reduces damage to the vehicle.

The essence of the proposed utility model is illustrated in the drawing, which shows a sectional view of the hydraulic damper of the first stage of spring suspension of the vehicle.

In the drawing are indicated:

1 - housing;

2 - case eye;

3 - cylinder;

4 - the piston;

5 - stock;

6 - piston ring;

7 - compression throttle;

8 - ball;

9 - spring;

10 - adjusting nut with a through hole in the center;

11 - a circular groove;

12 - vertical channel;

13 - hole axial through;

14 - upper radial holes;

15 - lower radial holes;

16 - a bolt;

17 - upper spring;

18 - lower spring;

19 - bottom;

20 - inlet valve;

21 - a directing sleeve;

22 - housing nut;

23 - rubber ring;

24 - tensile choke;

25 - radial channel;

26 - overflow pipe;

27 - working fluid;

28 - stem cuff;

29 - rod eye;

30 - a casing;

31 - a protective ring;

"A" is the piston cavity of the cylinder;

"B" - the piston cavity of the cylinder;

"B" is an annular cavity;

"G" - subcavity cavity;

"D" - the internal cavity of the through hole of the rod.

The claimed hydraulic damper of the first stage of spring suspension of the vehicle comprises a housing 1 with an eye 2. A cylinder 3 is coaxially placed in the housing, into which a piston 4 with a rod 5 and with a piston ring 6 is inserted for movement. The piston is movable with a minimum clearance relative to the rod, a compression throttle 7 is installed therein in the form of a calibrated hole, blocked by a ball 8, preloaded by a spring 9 with an adjusting nut 10 with a through hole in the center. From the side of the inner diameter in the piston 4, a circular groove 11 is made, which is connected by vertical channels 12 to the piston cavity "A" of the cylinder. The rod 5 from the end has a through hole 13 with a threaded outlet, equipped with rows of upper and lower radial holes at different levels. At least one row of upper radial holes 14 at its level has an exit to the piston cavity "B" and at least one row of lower radial holes 15 at its level can have an exit to the piston cavity when the piston 4 is displaced upward relative to the rod 5 The non-through hole from the end face of the rod 5 is closed by a bolt 16. The piston 4 from above is pressed by the spring of the upper 17, resting on the shoulder in the rod 5, and from the bottom is pressed by the spring of the lower 18, resting on the bolt of the through hole in the rod 5. The springs 17, 18 are installed with a calculated preload, which ensures the displacement of the piston 4 relative to the rod 5 only when a certain pressure of the working fluid on the piston 4 is reached. The bottom 3 is closed by the bottom 19 with the inlet valve 20, and the top is closed by the guide sleeve 21. The rod with a minimum clearance passed into the central hole of the guide sleeve. The entire piston and piston group is fixed in the housing by a nut of the housing 22 with a rubber ring 23. In the guide sleeve there is a tensile throttle 24 in the form of a calibrated hole and a through radial channel 25 connected to the overflow tube 26, which is attached to the guide sleeve and has an exit into the annular cavity "B " The over-piston “A” and under-piston “B” cavities of the cylinder and the rod cavity “D” are filled with working fluid 27, and the annular cavity “B” between the cylinder and the housing is partially filled with working fluid. The rod is sealed by a cuff 28 and provided with a rod eye 29, to which the casing 30 is rigidly attached. On the outer surface of the casing there is a circular groove in which a protective ring 31 is installed, which protects the sub-cavity “G” from abrasive particles and snow.

The hydraulic damper of the first stage of spring suspension of the vehicle operates as follows.

On the vehicle, the hydraulic damper is attached with its eyes 2 and 29 to the sprung masses of the first stage of spring suspension. When the vehicle is moving, the sprung masses in the first stage of spring suspension make oscillating movements of harmonic and shock types, while the eyes 2 and 29 of the hydraulic damper move among themselves, the rod 5 with a spring-loaded piston 4 moves reciprocally relative to the cylinder 3 and the damper makes compression moves and stretching.

During compression, when the piston 4 in harmonic motion moves to the bottom 19, the pressure of the working fluid 27 in the piston cavity "A" increases, however, the forces acting on the piston 4 do not exceed the preload of the upper spring 17. The piston 4 does not move relative to the rod 5 and the working fluid under pressure squeezes the ball 8 with the spring 9 in the piston 4 and the working fluid 27 through the throttle compression 7 and through the Central passage hole in the adjusting nut 10 enters the over-piston cavity "B", then flows through the throttle throttle 24 into the radial channel 25 in the guide sleeve 21, then into the overflow tube 26 and into the annular cavity "B". When the working fluid 27 passes through the throttles of compression 7 and tension 24, viscous friction forces are realized that prevent the piston 4 from moving with the rod 5 and, therefore, prevent the sprung parts of the rolling stock from oscillating during compression. When impacted by rail irregularities, such as rail joints, on the first stage of spring suspension of the vehicle, the speed of movement of the piston 4 increases abruptly and, accordingly, the pressure of the working fluid 27 in the under-piston cavity "A" increases abruptly. Under increased pressure of the working fluid 27, the piston 4 overcomes the efforts of the preload of the upper spring 17 and moves upward relative to the rod 5. When the piston 4 is displaced, the volume of the piston cavity "A" of the cylinder 3 increases, which limits the increase in pressure of the working fluid 27 in this cavity, and, therefore, limits the strength of the inelastic resistance of the damper. When the piston 4 is displaced upward relative to the rod 5, the lower row of radial holes 15 in the rod 5 communicates with the piston cavity "A" and the working fluid 27 from this cavity through the lower row of radial holes 15, through the cavity "D" of the through hole 13 and the upper row of radial holes 14 flows into the above-piston cavity “B” of cylinder 3 in a volume substantially larger than only through the compression throttle 7. The total effect of the displacement of the piston 4 relative to the rod 5 and the effective flow of fluid 27 through the radial holes 15, 14 from the piston cavity "A" in the cavity above the piston "B" provides effective limitation of the working fluid 27 pressure increases in the subpiston chamber "A". From here, the transmission of shock to the sprung masses of the vehicle is limited at a permissible maximum level. This acceptable level is determined by the calculation method, is determined by the stiffness of the upper spring 17, which abuts the piston from above, by its preload, and the dimensions of the radial holes 15, 14. By installing springs 17 with different stiffness and preload, the sizes of the radial holes 15, 14 in the proposed damper can be effectively adjust the pressure of the working fluid 27 and, therefore, the maximum inelastic strength of the damper during compression. This limits the unwanted transmission of shock from the rail to the rolling stock when the vehicle is moving.

During the stretching during harmonic vibrations of the sprung masses in the first stage of spring suspension, the rod 5 with the piston 4 moves to the guide 21, while the compression throttle 7 in the piston 4 is closed by a ball 8, therefore, the pressure of the working fluid 27 increases in the nadporshnevy cavity B. Working fluid 27 from the over-piston cavity "B" under pressure flows through the expansion throttle 24 into the radial channel 26 in the guide sleeve 21, then into the overflow tube 26 and into the annular cavity "B". With the passage of the working fluid 27 through the stretching throttle 24, the inelastic resistance forces of the damper during the stretching are realized. At the same time, the pressure in the sub-piston cavity "A" decreases and the pressure drop in this cavity and in the annular cavity "B" opens the inlet valve 20 in the bottom 19 and the working fluid 27 through this valve flows from the annular cavity "B" into the piston cavity "A" and fills it for the effective functioning of the damper in the next compression step. When impact from the rail joints or turnouts on the wheel and on the axle box of the vehicle increases the speed of movement of the piston 4 and, accordingly, the pressure of the working fluid 27 in the nadporshnevy cavity "B" increases. The pressure of the working fluid 27, the piston 4 overcomes the preload of the lower spring 18 and moves downward relative to the rod 5. In this case, the volume of the above-piston cavity "B" of the cylinder 3 increases by the amount of this displacement, which limits the increase in pressure of the working fluid 27 in this cavity during stretching, and, therefore, limits the inelastic resistance of the damper at an acceptable level. When the piston 4 is displaced downward relative to the rod 5, the circular groove of the piston 11 is aligned with the lower row of radial holes 15 in the rod 5 and the working fluid 27 from the over-piston cavity "A" through the upper radial holes 14, through the cavity "D" of the through hole and the lower radial holes 15 begins to flow from the over-piston cavity “B” of the cylinder 3 into the under-piston cavity “A” of the cylinder in a volume substantially larger than only through the expansion throttle 24 and, thereby, even more effectively limits the pressure increase of the working fluid 27 in the over-piston "B" fins during stretching. An increase in the amount of working fluid 27 passing from the above-piston cavity "B" of the cylinder 3 into the under-piston cavity "A" limits the increase in pressure and, consequently, the increase in resistance forces during tension during the maximum permissible level. The total effect of the displacement of the piston 4 relative to the rod 5 and the effective flow of fluid 27 through the radial holes 14, 15 from the supra-piston cavity "B" to the sub-piston cavity "A" provides an effective limitation of the pressure increase of the working fluid 27 in the sub-piston cavity "A". By installing a spring 18 with different stiffness and preload, the dimensions of the radial holes 14, 15, in the proposed hydraulic damper, it is possible to effectively control the pressure of the working fluid 27 and, therefore, the maximum inelastic resistance of the hydraulic damper during tension during impact on the vehicle.

The maximum value of the inelastic resistance forces of the hydraulic damper of the first stage of spring suspension is limited from the conditions of the strength of the connecting elements of the damper, the safety conditions of the vehicle and ensuring the smooth running of the car or locomotive.

The casing 30 and the protective ring 31 protect the subcavity cavity "G" from abrasive and snow particles. Prevention of abrasive particles protects the surface of the stem 5 and cuff 28 from premature wear or damage, and the prevention of snow particles eliminates sub-casing ice formation. The sleeve 28 seals the stem 5 against leakage of the working fluid 27, the piston ring 6 seals the piston 4, and the rubber ring 23 protects the threaded connection of the nut 22 and the housing 1 from leakage of the working fluid 27.

Due to structural differences, the proposed damper of the first stage of spring suspension most effectively limits the resistance forces developed by the damper during impact action on compression and tensile moves, which ensures the necessary smoothness of the vehicle.

The proposed hydraulic damper of the first stage of the spring suspension of the vehicle can be used on railway cars, locomotives, trams and subway cars.

Claims (3)

1. The hydraulic damper of the first stage of the spring suspension of the vehicle, comprising a housing with a base and a cylinder coaxially placed in the housing, in which the piston with the rod is mounted to move, the piston is mounted to move relative to the rod and spring loaded from above and below by springs, an internal cavity the cylinder is divided by the piston into the supra-piston and sub-piston cavities, which are filled with a working fluid, the annular cavity between the cylinder and the body is filled with a working fluid partially bone, the bottom cylinder is closed by the bottom, and the top is closed by the guide sleeve, there is a compression throttle in the piston, there is a tension throttle in the guide sleeve, while the rod is passed through the central hole in the guide sleeve, and the entire cylinder-piston group of parts is fixed in the housing by a ring nut, case and the stem are provided with eyes, an inlet valve is mounted in the bottom, and a tensile throttle is connected through a radial channel in the guide sleeve to an overflow tube extending into the annular cavity, distinguishing The fact that the piston has a circular groove along the inner diameter, which is connected by vertical channels to the piston cavity of the cylinder, and the rod end has a through axial hole with a threaded outlet, equipped with rows of upper and lower radial holes at different levels. 2. The damper according to claim 1, characterized in that at least one row of radial upper holes of the rod at its level has an exit to the supra-piston cavity and at least one row of radial lower holes of its level has an exit to the sub-piston cavity . 3. The damper according to claim 1, characterized in that the through hole from the end of the rod is closed by a bolt.

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