RU80208U1 - TRANSPORT HYDRAULIC DAMPER - Google Patents

Abstract

The utility model relates to transport engineering, namely to transport hydraulic vibration dampers, mainly to rail rolling stock. The transport hydraulic vibration damper comprises a housing with a base and a cylinder coaxially placed in the housing, in which the piston with the rod and the bottom is mounted to move, the internal cavities of the cylinder are filled with working fluid, the annular cavity between the cylinder and the housing is partially filled with fluid, the cylinder is closed with a bottom from the bottom, and closed by a guide sleeve on top. The rod is passed through the central hole in the guide sleeve, the entire cylinder-piston group of parts is fixed in the casing with a ring nut, the casing and the stem are equipped with fixing eyes. The same valve-throttle devices are mounted in the piston and the bottom, each of which includes a valve support with a central threaded hole, with passage and inlet openings and valve seats in the form of ring collars, on each support there is an inlet valve in the form of a disk, pressed by a spring of low stiffness to the inlet valve seat and the inlet blocking in the valve support, the safety valve and the throttle. The safety valve is made in the form of elastic plates overlapping the passage openings in the valve support and pressed against the safety valve seat by a coupling bolt screwed into the central threaded hole of the valve support, while the shank of the coupling bolt is equipped with a lock nut. There is a washer between the coupling bolt and the elastic plates. The technical result is an increase in the performance of the damper. 1 ill.

Description

The utility model relates to transport equipment, namely to hydraulic vibration dampers of rail rolling stock-wagons and locomotives. Hydraulic vibration dampers are designed to limit the movement of the sprung masses of moving cars and locomotives through viscous friction.

Known transport hydraulic vibration damper (RU No. 2075665, F16F 5/00, publ. 1997.03.20), comprising a housing with a base and a cylinder placed coaxially in the housing, in which a piston with a rod is mounted to move, the internal cavity of the cylinder is filled with a working fluid, the annular cavity between the body and the cylinder is partially filled with the working fluid, the cylinder is closed by the bottom from the bottom, and the guide from above, the rod is passed through the central hole in the guide, the entire piston and piston group of parts is fixed ana ring nut in the housing, the housing and stem of mounting lugs are provided in the piston and the bottom of the valve devices are mounted, each of which includes a valve support on which are mounted inlet and pressure relief valve. The throttle is made in the upper part of the cylinder and communicates the over-piston and compensation chambers. The safety valves are made in the form of balls overlapping the passage openings in the valve supports and pressed to this hole by pressure springs under the influence of control screws. The cylinder is completely, the remaining internal cavity of the absorber is partially filled with a working fluid, as a rule, mineral oil with a low pour point. Absorber Cylinder Inside

subdivided by a piston into a piston and a piston cavity. With the eyes, the vibration damper is attached to the sprung masses of the vehicle. During the movement of the rolling stock, the sprung masses oscillate, the rod with the piston of the damper moves reciprocally relative to the cylinder, acting on the working fluid alternately in the sub-piston and supra-piston cavities of the cylinder, while the hydraulic fluid under pressure with high resistance is displaced through the throttle from the supra-piston cavity into the compensation chamber. In the process of throttling, viscous friction forces are realized that limit the amplitude of oscillations of the sprung masses within the specified limits and provide the required smoothness of the vehicle. At increased piston displacement speeds, the pressure of the working fluid in the piston or supra-piston cavities of the cylinder increases significantly, as a result of which the safety ball valves open either in the bottom or in the piston, limiting at the calculated level the maximum resistance forces of the vibration damper during compression or extension, respectively.

The disadvantage of this vibration damper is the unsatisfactory operation of ball-type safety valves that have insufficient flow area, and when opened, these valves vibrate at a high frequency, which negatively affects the power characteristic of the damper and therefore impairs the smoothness of the vehicle. During vibration, the ball of the safety valve breaks the seat, which can lead to leaks in this valve, which reduces the performance of the hydraulic vibration damper. The design of the safety ball valve is very complicated, and the pressure spring is not reliable in operation, since during the intensive valve mode of operation of the damper

oscillations are deformed, broken, which leads to failure of the vibration damper.

Known vibration damper according to patent RU No. 2288387 F16F 5/00, publ. 2006.11.27, which contains a tank coaxially installed in it with the formation of a regenerative cavity, a cylinder with a bottom containing a check valve and a safety valve. From above, the cylinder is closed by a guide sleeve, through which the piston rod is passed through a central hole. Safety and overflow valves are mounted in the piston. Safety valves in the piston and in the bottom and overflow valves in the piston are made in the form of cones, pressed by pressure springs under the influence of control screws. Chokes are made in the form of opposed flats and through holes. The disadvantage of this damper is the unstable operation of the safety valves - when the valve is opened under the influence of high fluid pressure, the spring-loaded cone oscillates automatically, changing the fluid passage through the hole of the safety valve and thereby makes the power characteristic of the hydraulic vibration damper unstable, therefore, worsens the damping process of the vehicle. Overflow cone valves in the piston are unstable for the same reason. The multi-cycle operation of the safety valves during the accelerated operation of the hydraulic vibration damper at critical vehicle speeds wears out the cone and their seats, which reduces the performance of the vibration damper.

Known valve block for hydraulic vibration dampers of vehicles according to patent RU No. 2145010 F16F 5/00 publ. 2000.01.07, in which the safety valve is installed in the axial bore and contains a locking element in the form of a spring-loaded cone,

overlapping bypass channel. The cone shank is passed through a guide and an adjusting washer bounded by a thrust ring. The main disadvantage of this technical solution is the vibration of the cone when the valve is opened under the influence of high pressure of the working fluid - self-oscillations of the spring-loaded cone occur. The cross section of the bypass channel of the safety cone valve is not sufficient for efficient passage of the working fluid in the valve mode and, therefore, is not able to provide the required limitation of the working fluid pressure at the design level. Vibration of the cone valve and insufficient flow area of its passage channel reduce the performance of the hydraulic vibration damper. The design of the valve block is very complex, and the vibration of the cone breaks the seat and reduces the density, which also affects the performance of the valve block and the hydraulic vibration damper as a whole.

The closest in technical essence to the claimed object is the KVZ-LIIZhT hydro-absorber shown in the textbook for universities of railway transport (Cars: Textbook for universities railway transport / A.A. Shadur, I.I. Chelnokov, L.N . Nikolsky et al., Revised And add. - M.: Transport, 1980, p. 171), selected for the prototype. This hydraulic vibration damper is basic, since it has been produced by our industry for a long time and is used in railway transport. The damper comprises a housing with a base and a cylinder located in the housing, in which the piston with the rod is mounted to move, and the bottom, the internal cavity of the cylinder is filled with a working fluid, the annular cavity of the housing is partially filled with fluid, the cylinder is closed from the bottom by a bottom and a guide from above. the rod is passed with a minimum clearance through the central hole in the guide, the entire piston group

the parts are fixed in the casing with a ring nut, the casing and the stem are equipped with fixing eyes, valve supports are installed in the piston and the bottom along the threads, on which valve-throttle devices are mounted, each of which includes an inlet valve, a safety valve and a throttle. In the valve support there is a central threaded hole and saddles are made; for the inlet valve in the form of two landing annular collars, between which there are inlet openings; for the safety valve - in the form of a conical hole blocked by a ball. The ball is pressed against the seat with a bore by a spring with a screw to regulate the fluid pressure at which the safety valve opens. The inlet valve is made in the form of a disk overlapping the inlet openings in the valve support and spring-tightened to the saddle of this support.

The disadvantage of the vibration damper selected for the prototype is poor performance due to the high-frequency vibration of the ball of the vibration damper when the valve is opened under the pressure of the working fluid in the damper. This vibration degrades the power characteristic of the damper, often leads to valve spring breakdowns and breaks the seating surface of the seat. The flow areas of these valves are very small, because of which there is no effective limitation of the maximum viscous resistance forces at the calculated level.

Cylindrical springs pressing the ball or cone to the valve support seats are unreliable in operation due to the high vibration load and in the forced mode of operation of the damper break or deform. With high-frequency vibration of the ball, the seat of the safety valve breaks, which reduces the performance of the damper.

The objective of this technical proposal is to increase the operability of a hydraulic vibration damper by eliminating the high-frequency vibration of the safety valve, increasing the area of its passage section, and simplifying the design.

The problem is achieved in that in a transport hydraulic vibration damper comprising a housing with a base and a cylinder coaxially placed in the housing, in which the piston with the rod and the bottom is mounted to move, the internal cavity of the cylinder is filled with working fluid, the annular cavity between the cylinder and the housing is partially filled liquid, the bottom cylinder is closed by the bottom, and the top is closed by the guide sleeve, while the rod is passed through the central hole in the guide sleeve, the entire cylinder is piston a group of parts is fixed in the casing with a ring nut, the casing and the stem are equipped with fixing eyes, the same valve-throttle devices are mounted in the piston and bottom, each of which includes a valve support with a central threaded hole, passage and inlet openings and valve seats in the form of ring collars, Each support has an inlet valve in the form of a disk, spring-loaded to the seat of the inlet valve and overlapping the inlet openings in the valve support, safety valve and throttle. The safety valve is made in the form of elastic plates overlapping the passage openings in the valve support and pressed against the safety valve seat with a coupling bolt screwed into the central threaded hole of the valve support, while the bolt shank is equipped with a lock nut.

There is a washer between the coupling bolt and the elastic plates.

The proposed damper has the following design differences:

- the safety valve is made in the form of a set of elastic plates overlapping the passage holes in the valve support, and pressed against

the inlet valve seat in the valve support with a coupling bolt screwed into the central threaded hole of the valve support;

- there is a washer between the bolt and the elastic plates;

- a lock nut is screwed onto the shank of the coupling bolt.

The essence of the proposed utility model is illustrated by the drawing, where the figure shows a sectional view of a transport hydraulic vibration damper, where are indicated:

1 - case eye;

2, 24 - rubber sleeve;

3, 25 - metal sleeve;

4 - housing base;

Channel 5;

6 - bottom;

7, 35 - valve support with seats in the form of annular collars for valves;

8 - cylinder;

9, 34 - discharge channel in the valve support;

10 - a glass of the body;

11, 46 - a coupling bolt of the safety valve;

12, 44 - plate safety valve;

13.43 - inlet hole of the valve support;

14 - a piston;

15 - piston ring;

16, 41 - inlet valve disc;

17, 38 - spring low rigidity of the intake valve;

18 - a radial hole in the stock;

19 - a protective casing;

20 - rubber ring;

21 - ring nut of the housing;

22 - a flange;

23 - rod eye;

26 - locking screw;

27 - stock;

28 - clip;

29 - cuffs;

30 - a metal ring;

31 - guide sleeve;

32, 39 - lock nut;

33, 40 - throttle bore;

36, 42 - a persistent ring;

37, 45 - washer of the safety valve.

"A" is the piston cavity of the cylinder;

"B" - the piston cavity of the cylinder;

"B" - a regenerative chamber;

"G" - drain cavity;

"D" - nadklapanny cavity in the piston.

The claimed hydraulic vibration damper of the rolling stock comprises a housing including a housing eye 1, a base 4, a cup 10, rigidly connected by welding. A cylinder 8 is placed in the housing, in which the piston 14 with the piston rod 27 and the piston ring 15 is movably inserted. The piston rod with a minimum clearance is missing into the central hole of the guide sleeve 31, pressed by a nut 21 through the yoke 28 to the cylinder 8. The bottom of the cylinder has a bottom 6. In the bottom 6 and in the piston 14 are screwed identical threads valve 7 (35) having a central threaded hole and saddles in the form of annular collars. On the saddles are mounted the same inlet and the same

safety valves. Each inlet valve contains a disk 16 (41), overlapping the inlet openings 13 (43) and a spring of low rigidity 17 (38). The throttle hole 33 (40) is made in the form of a circular hole in the inlet valve disk 16 (41). Each safety valve contains plates 12 (44) that overlap the passage openings 9 (34), a washer 37 (45), a coupling bolt 11 (46), and a lock nut 32 (39). Ring shoulders limit the inlet and passage holes in the valve support 7 (35). The valve support is secured by a thrust ring 36 (42). The inner part of the cylinder is divided by a piston into the cavity "A" and "B". The annular cavity between the cylinder and the body — the regenerative chamber is indicated by the letter “B”, the intermediate cavity under the bottom is indicated by the letter “G”, and the cavity above the disk 16 in the piston is indicated by the letter “D”. At the base there is a channel 5 connecting the cavity "G" and "B". The channel is directed in such a way as to prevent air from entering the cavity “A” of the cylinder during the operation of the damper in a horizontal (inclined) position. On the outside of the damper on the housing from the side of the connecting channel 5 there is a mark "NCD". A radial channel 18 is made in the stem, connecting the cavity "D" with the above-piston cavity "B".

The under-piston “A” and the over-piston “B” cavities of the cylinder 8, the under-valve cavity “G” are completely filled with the working fluid (mineral oil). Recuperative chamber "B" is not completely filled with the working fluid. The damper rod 27 is sealed by a cuff 29 inserted into the yoke 28, and the body by a rubber ring 20, compressed by a nut 21 through a metal ring 30. The upper eye 23 is threaded to the rod 27 and fixed by the locking screw 26. A flange 22 is fixed to the eye 23, to to which the protective cover 19 is rigidly attached.

Hydraulic vibration damper as follows:

On the vehicle, a hydraulic vibration damper is attached by its eyes 1 and 23 to the sprung masses of the rolling stock. When the rolling stock moves, the sprung masses oscillate and the rod 27 with the piston 14 moves relative to the cylinder 8.

During compression at standard speeds of movement of the rod 27 with the piston 14, the working fluid flows from the damper cavity “A” through the inlets 13 in the valve support 35 in the piston 14, presses the disk 16 with a spring of low stiffness 17, and first gets into the supravalve cavity “G” , then through the radial channel 18 in the rod 27 flows into the above-piston cavity "B". The cavity "B" is closed by the guide 31, in which the clearance with the rod is very small and represents a very large obstacle to the liquid. Therefore, the fluid pressure in the sub-piston and supra-piston cavities increases depending on the speed of movement of the rod with the piston. Since the over-piston cavity "B" is smaller than the under-piston cavity "A", a part of the working fluid equal to the volume of the rod entering the cylinder will be pressed through the throttle hole 40 in the inlet valve disk 41 mounted on the valve support 7 in the bottom 6 under high pressure This volume of fluid through the inlet openings 43 enters the cavity "G" and, from there, through the channel 5 - into the regenerative cavity "B", which is not completely filled. When the working fluid flows at high speed through the throttle hole 40, the inelastic resistance of the damper is realized, which limits the amplitude of the vehicle’s vibrations. At excess speeds of the piston rod with an oversized pressure, the liquids are squeezed from the saddle of the valve support 7 of the plate 44 and the liquid through the passage openings 9

enters the cavity "G" and, from there, through channel 5 - into the regenerative cavity "B".

During the stretching of the damper in the above-piston cavity "B" under the influence of the moving piston 14, the pressure of the working fluid increases and it begins to throttle through the throttle hole 33, then passes through the inlets 13 in the valve support 36 into the cavity "A", when throttling is realized viscous friction, limiting the amplitude of oscillations of the sprung masses of the vehicle when the damper is stretched. The fluid coming from the cavity "B" cannot fill the cavity "A", since the cavity "B" is smaller than the cavity "A". Therefore, the pressure decreases in the cavity "A". The differential pressure in the cavity "A" and in the regenerative chamber "B" opens the inlet valve in the valve support 7: the disk 41 rises above the seat of the inlet valve, compressing a low spring 38. The fluid from the regenerative chamber "B" through channel 5, cavity "G" and the inlet 43 enters the cavity "A", thereby replenishing the lack of working fluid in this cavity during stretching. At excess speeds of the stem with the piston during stretching with increased fluid pressure in the cavity "B", the plates 12 are squeezed out of the seat of the safety valve of the valve support 35 in the piston 14 and the liquid enters the cavity "A" through the discharge holes 34. The use of locknuts 32 (39) allows screwing the valve support 7 (35) into the threaded holes of the bottom and piston by rotating the clamping bolt 11 (46) with a wrench. Thrust rings 36 (42) fix the valve supports in the piston 14 and in the bottom 6 from self-unscrewing.

The piston ring 15 seals the over-piston and under-piston cylinder cavities while moving the piston. The rubber ring 20 and cuffs 29 seal the body and damper rod, thereby preventing leakage of the working fluid from the vibration damper. Cover 19 s

the flange 22 protect the damper rod 27 from mechanical damage, and the cuff 29 from pollution. An eye 23 is threadedly connected to the stem 27, a screw 26 is installed to stop this threaded connection. Rubber bushings 2 and 24 in the eyes 1 and 23 reduce the transmission of high-frequency vibration to the sprung parts of the vehicle. Metal bushings 3 and 25 protect the rubber bushings and provide them with rated voltage. The guide 31 seals the over-piston cavity "B" of the cylinder 8.

In the claimed damper, the distinguishing features that contribute to increased efficiency are:

- plate safety valves, which when opened do not vibrate, as a result of which the power characteristic of the damper is improved and the safety of the footprint of the safety valve, and therefore the damper’s performance, is improved;

- the cross-sectional area of the proposed plate valve is much larger than the cross-sectional area of the known ball valve prototype, which effectively limits the maximum resistance forces developed by the vibration damper at the design level and, therefore, provides the required performance of the vibration damper;

- the shank of the coupling bolt is equipped with a lock nut, which prevents the coupling bolt from unscrewing during operation and allows the valve support to be unscrewed by rotating the head of the coupling bolt. Prevention of self-loosening of the coupling bolt helps ensure the operation of the damper;

- between the coupling bolt and the plates there is a washer that protects the plates from damage and mutual displacements when tightening the coupling bolt during valve assembly, which

contributes to the design performance of the proposed vibration damper;

- the design of the plate valve is much simpler than a ball or cone valve, since the plates are both locking and elastic elements of the valve, which simplifies the design in comparison with analogues and prototype.

In the proposed damper, the unreliable cylindrical spring of the safety valve is excluded from the design, which contributes to an increase in the operability of the damper.

Due to structural differences, the claimed hydraulic vibration damper has increased operability against the prototype and analogues, which helps to ensure the normalized smoothness of the vehicle during the overhaul periods of operation.

The use of a plate safety valve having a larger passage area than ball or cone valves makes the vibration damper suitable for use in the first stage of suspension of a vehicle where impacts prevail. Thus, the claimed vibration damper is operable in the first and second stages of spring suspension, which ensures its unification for use on all types of rolling stock.

The proposed vibration damper can be used on railway cars, locomotives, trams and subway cars, in automobile and tracked vehicles.

Claims (2)

1. Transport hydraulic vibration damper, 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, and the bottom, the internal cavity of the cylinder is filled with a working fluid, the annular cavity between the cylinder and the housing is partially filled with fluid, the cylinder is bottom closed by the bottom, and closed by a guide sleeve on top, while the rod is passed through a central hole in the guide sleeve, the entire cylinder-piston group of parts is fixed in the housing the ring nut, the body and the stem are equipped with fixing eyes, the same valve-throttle devices are mounted in the piston and the bottom, each of which includes a valve support with a central threaded hole, with passage and inlet openings and valve seats in the form of ring collars, on each support there is an inlet a valve in the form of a disk, spring-loaded to the inlet valve seat and blocking the inlet openings in the valve support, a safety valve and an orifice, characterized in that the safety valve n is made in the form of elastic plates overlapping the passage holes in the valve support and pressed against the safety valve seat with a coupling bolt screwed into the central threaded hole of the valve support, while the shank of the coupling bolt is equipped with a lock nut. 2. Transport vibration damper according to claim 1, characterized in that there is a washer between the coupling bolt and the elastic plates.