Damper

FIELD: machine building.

SUBSTANCE: damper consists of cylinder chamber filled with fluid, of piston installed inside cylinder chamber, of rod connected to piston and of accumulator. The accumulator facilitates generation of damping force produced by the piston rod due to fluid flow from the side of compression in the cylinder chamber. One coil of spiral damping groove is formed on internal periphery of the cylinder chamber within the ranges of piston stroke. Width of the damping groove is constant along its whole length. Depth of the damping groove is gradually diminishes along the spiral in the direction whereto the piston rod is pushed out. The length of the piston along axial line is less, than pitch of the damping groove.

EFFECT: simplified design and more efficient control of damping force of damper.

6 cl, 7 dwg

 

The technical FIELD

The present invention relates to a shock absorber, which enables the creation of a piston rod of the damping force by controlling the output fluid flow from the compression in the cylinder chamber by moving the piston in the cylindrical chamber and which absorbs mechanical shock attached to the piston rod, by means of the damping force.

PREREQUISITES TO the CREATION of INVENTIONS

The absorber, which is previously well-known document 1 (published examined Japanese application for a utility model registration No. S62-194946), or similar shock absorber provide a cylindrical chamber in the pipe, while the cylindrical chamber encloses a fluid, the piston dividing the cylinder chamber into two chambers, and a piston rod, one end of which is connected to the piston, and the other end comes out of the tube and the absorber enables the creation of a piston rod of the damping force by controlling the output flow of a viscous fluid from the compression in the cylinder chamber due to the sliding of the piston in the cylindrical chamber.

What is described in the document 1 as a prior art, relates to a shock absorber, which controls the output fluid flow from the compression cylindrical the chamber due to the movement of the piston, when this cylinder, sealed at one end, designed with double walls, a large number of through holes located on the surface of the inner wall of the cylinder, formed with a predetermined pitch in the direction along the axis of the cylinder, and a viscous fluid, which creates an obstacle when the piston moves in the inner cylinder in its axial direction can flow outward from the inner cylinder through the through-hole.

Further, what is described in the document 1 as the invention is that the inner tube is located inside the outer pipe with a specified gap, this viscous liquid is enclosed in the chamber for fluid between the two pipes and into the cylindrical chamber in the inner tube, the connecting channel connecting the chamber for liquid and a cylindrical chamber has a throttle valve, and, in addition, the cross-sectional area of the channel to flow between the outer periphery of the piston and the inner periphery of the inner tube gradually becomes smaller in the direction in which you push the piston through the implementation of the inner periphery of the inner tube cone, so that there was a gradual decrease its internal diameter in the direction in which you push the plunger.

However, this type of shock absorber, which can the be managed by the quantity of liquid, resulting in dependence on the stroke of the piston is so designed that the fluid produced by the compression in the cylinder chamber when the piston rod moves in the direction of vtalkivaniya due to mechanical impact, attached to the piston rod will be moved between the inner pipe and outer pipe, so the cylindrical pipe shall be constructed with double walls, which leads to the problem lies in the fact that some parts become large, and the construction becomes complicated. In addition, when the inner periphery of the inner tube provided with a tapering portion, the accuracy of forming the tapered surface has a significant influence on the cross-sectional area of the path of flow defined by the gap between the outer periphery of the piston and the inner periphery of the inner tube, so that in this case there is a problem, which consists not only of the necessity of high precision manufacturing tapering surface, but also in the difficulty of precise control of the damping force, attached to the piston rod.

The INVENTION

The technical problem according to the present invention is that the shock absorber having the cross-sectional area of the channel to flow between the outer periphery of the piston and in the morning the periphery of the pipe, this cross-sectional area gradually decreases in the direction in which you push the piston to the linear increase of the load attached to the fluid passing between the outer periphery of the piston and the inner periphery of the cylindrical chamber, in fact, proportional to move the piston rod in the direction of pushing of the impact through a simple process of creating a damping groove on the inner periphery of the tube, and for allowing precise control of the damping force, attached to the piston rod.

In order to solve the above problem, the present invention created a shock absorber comprising a cylindrical chamber formed in the pipe and fill with fluid, a piston located in the cylinder chamber so that it can be freely displaced in the direction along the axial line of the cylindrical chamber, a piston rod, one end of which is connected with the piston, and the other end comes out of the tube, and the battery, providing for the establishment of a piston rod of the damping force by overriding fluid from the compression in the cylinder chamber when the piston rod is pushed into the tube of the shock impact and displace the piston.

On the inner periphery of the cylindrical chamber formed by one turn of the spiral of the damping groove, cant consider is Ino centerline so, so she passed within the stroke range of the piston, the width of the damping groove is constant along its entire length, the damping depth of the groove gradually decreases along a helix in the direction in which you push the plunger, and the length of the piston in the direction along the axial line is set smaller than the step of the damping groove.

According to the above shock absorber made in accordance with the present invention, it becomes possible to linearly increase the load attached to the fluid passing between the outer periphery of the piston and the inner periphery of the cylindrical chamber, in fact, proportional to move the piston rod in the direction of pushing of the impact through the relatively simple process of forming one turn of the spiral of the damping groove, the depth of which gradually decreases on the inner periphery of the pipe, and the possibility of application to the piston rod of precisely controlled damping force.

In the present invention it is preferable that the width of the damping groove along the centerline was performed essentially equal or greater length of the piston, and also to the bottom wall of the damping groove was flat.

In the present invention one step damping grooves can be formed in the stroke range of the piston, the piston can be held in to the CA stem in a floating state.

In the present invention it is preferable that the outer end of the cylindrical chamber, serving to give direction to the rod in the cylindrical chamber was connected to the camera, which forms the battery, and the camera inside provide pliable compressible and expandable elastic element.

BRIEF DESCRIPTION of DRAWINGS

Figure 1 shows a view in vertical cross-section of the shock absorber according to the present invention.

Figure 2 presents a view in vertical cross section of the above shock absorber in a state where it absorbs shock.

Figure 3 presents a detailed view of the cylindrical chamber.

4 shows a view in cross-section along line IV-IV in figure 3.

Figure 5 presents a view in cross-section along line V-V in figure 3.

Figure 6 presents a graph showing the relationship between the effective cross-sectional area of the channel for passage of a flow generated by the damping groove, and the stroke of the piston in the shock absorber according to the present invention.

Figure 7 presents a graph showing the relationship between the length and depth of the damping groove in the shock absorber according to the present invention.

The PREFERRED embodiment of the INVENTION

Next, with reference to figures 1 to 7 will be described an implementation option is instrukcii according to the present invention. As shown in figures 1 and 2, the shock absorber 10 according to this variant has a cylindrical tube 11. In the half pipe 11 (head side) in the direction of its axial line And formed a cylindrical chamber 12, the piston 13, which is connected with the rod 14, is inserted into the cylindrical chamber 12 together with the rod 14 in the direction of the axial line a, so that he had the opportunity slip, and a cylindrical chamber 12 separated by a piston 13 to the first cylindrical chamber 12A from the side of the rod 14 and the second cylindrical chamber 12V on the other side. Both ends of the cylindrical chamber 12 is blocked by the flange portion 20b of the bearing housing 20 formed on the first end side of the housing 20 in the direction of its axial line a, and the tube 17, a screw into the hole 11C of the end face 11a of the head side of the tube 11, the inner diameter of the cylindrical chamber 12 is virtually constant over the entire length in the direction of the axial line a, except for parts of the damping groove 16.

Part 14a of small diameter which is formed at the end portion of the piston rod 14, which is the basis, freely installed in the center hole 13A of the piston 13, and the guide 22 of the cylindrical spring is rigidly fixed by a nut 25 at the top part 14a of small diameter, and the piston 13 is held in a floating condition between the stepped part 14 at one end part 14a of small diameter and the guide 22 of the spring by means of the part 14a of small diameter.

The rod 14 of the piston along the centerline And in the pipe 11 passes through vulcabras bearing body 20 from the other half (rod side) of the pipe 11, the seal 23, which is located along the inner perimeter on the second end side of the bearing housing 20 in the direction of the axial line a, and the cover 21 mounted at the end face 11b of the tube 11 from the side of the rod, with the upper part of the rod 14 of the piston acts on the outside of the pipe 11.

Bearing housing 20 forms part 20A to the direction of the piston rod 14 and is rigidly attached to the pipe 11 by clamping between the cover 21 of the rod, and a stepped part 11d in the pipe 11, and between the bearing housing 20 and the cover 21 of the rod by clamping rigidly secure the seal 23.

The camera 24 with an elastic element, forming a battery 31 formed between the outer periphery of the bearing housing 20 and the inner periphery of the pipe 11, while it is provided with pliable compressible and expandable elastic element 19 formed, for example, from an element with closed pores. Between a part of the outer periphery of the flange portion 20b of the bearing housing 20 and part of the inner periphery of the pipe 11 is provided with a connecting channel 26 that interconnects the chamber 24 containing the elastic element, and the first cylindrical chamber 12A, and the first and second cylindrical chambers 12A and 12B, in the connection channel 26 and in which the Amer 24 and an elastic element is enclosed fluid 30, preferably viscous liquid 30, such as oil.

Incidentally, the first and second cylindrical chambers 12A, 12B are connected to each other through the clearance between the outer periphery of the piston 13 and the inner periphery of the pipe 11, a small gap between the inner periphery of the piston 13 and the outer peripheral portion 14a of the rod 14 of the piston having a small diameter, and a damping groove 16 that will be described later.

In the case of this configuration, when the execution of the process, when the rod 14 of the piston being pushed inside the pipe 11 through the load F in the cylindrical chamber 12 is further from the position shown in figure 1, comes only a portion of the rod 14 of the piston (the male part). At this time, the liquid 30 in the amount corresponding to the amount of incoming portion of the rod 14 of the piston to flow from the cylindrical chamber 12 into the chamber 24 and an elastic element through the connecting channel 26 and will be placed in the chamber 24 with the elastic member by the possibility of compression of the elastic element 19, this will be compensated by the change of volume of the cylindrical chamber 12.

In the process, when the piston rod 14 protrudes from the pipe 11, the reverse of the above process, the liquid 30 to be released from the chamber 24 with an elastic element to repopulate the cylindrical chamber 12.

Between the sheet guiding part 22A on the periphery of the guide 22 for spring and planting 1st place for the holding of the spring, located at the end with the head side of the cylindrical chamber 12 in the pipe 11 is installed return spring 18, and the piston 13 and rod 14 of the piston will be forced filed a return spring 18 in the direction in which the rod 14 of the piston acts on the outside of the pipe 11. Return spring 18 will be compressed when the piston rod 14 will be applied mechanical shock in the direction of vtalkivaniya that helps to reduce the impact.

It should be noted that the gap between the outer periphery of the second end side of the bearing housing 20 and the inner periphery of the pipe 11 is compacted by installing the O-ring 28, and the gap between the inner periphery of the second end side of the bearing housing 20 and the outer periphery of the rod 14 of the piston seal by seal 23. In addition, the gap between the outer periphery of the tube 17, is rigidly fixed by screwing in the pipe 11 at its end 11a with the head side, and the inner periphery of the pipe 11 is compacted by means of O-ring 29. Further, on the outer periphery of the pipe 11 in fact, throughout its length to provide a mounting threaded portion 27, the shock absorber 10 attach configuration by mounting the threaded part 27 so that its position can be adjusted when it is installed at a certain about is the equipment.

On the cylindrical inner periphery 15 of the cylindrical chamber 12 has one line helical damping groove 16, is inclined relative to the axial line of the cylindrical chamber 12 so as to surround the axial line A. This damping groove 16 is made to control the flow of fluid 30 caused by sliding of the piston 13 in the cylinder chamber 12, and to create the rod 14 of the piston of the damping force. As follows from the expanded view in figure 3, this damping groove 16 formed in part of the inner periphery 15 of the cylindrical chamber 12, and this portion corresponds to the stroke range of the piston 13 so as to be rotated at least once on the inner periphery 15 of the cylindrical chamber 12 from serving for the direction of the rod outer end portion to the head-end side, that is to take place within the stroke range of the piston 13 in the order of one step.

The damping groove 16 has a flat bottom 16A and the left and right side walls 16b, the vertical relative to the flat bottom 16A of the groove, and the width W1 of the groove, i.e. its width W1 in the direction orthogonal to the spiral of the damping groove 16, is constant along the entire length of the damping groove 16. The depth D of the damping groove 16 is gradually reduced along this spiral groove 16 in the direction in which the push rod 14 of the piston that p is shown in the enlarged view on the graph according to Fig.7. In addition, the width W2 of the damping groove 16, that is, the width W2 in the direction of the axial line a, is formed so that it was in fact equal to or greater than the length L of the piston 13 in the direction of the axial line A. it is Preferable that the width W2 of the damping groove 16 in the direction of the axial line was formed so that it ranged from 1 to 2 lengths L of the piston 13. Thus, it is obvious that the length L of the piston 13 is smaller than the step of the damping groove 16.

It should be noted that although the angular part of the damping groove 16, in which the bottom portion 16A, the left and right side walls 16b of the groove are connected to each other, on the figures, given by way of example, have a sharp corner, this corner may have a gentle arc shape.

Thus, the channel flow in which the fluid 30 that is located in the cylindrical chamber 12, will flow in the direction of the axial line a, when the piston 13 makes a move, that is the channel for passage of a flow in which the fluid 30 flows between the first cylindrical chamber 12A and the second cylindrical chamber 12, formed by the damping groove 16 between the piston 13 and the inner periphery of the cylindrical chamber 12. In this case, the fluid 30 flows into the damping groove 16 around the piston 13 in the direction of the axial line And, turning in the direction along damping to the skill sets 16, but not linearly in a direction parallel to the centerline And along the outer peripheral surface of the piston 13. That is, the fluid 30 flows in a spiral direction in the form of a mixed flow generated from the rotating flow and in the direction of the axial line, and due to viscous braking fluid 30, at this time, the piston 13 will be applied braking force.

In addition, since the damping groove 16 crosses diagonally peripheral surface of the piston 13, a channel for passage of a thread formed in an oblique direction so that the length of the channel is greater than a channel for passage of a flow going directly in the direction of the axial line a, and braking force will be correspondingly increased. In addition, as the fluid 30 flows not directly in the direction parallel to the axial line a, And in the spiral direction, the braking force will be increased. Consequently, it becomes possible to effectively create a braking force through the use of a piston with a short length. Further, since the depth of the damping groove 16 is gradually reduced in the direction in which the push rod 14 of the piston, it is possible to control the flow of fluid 30 flowing through the channel in the damping groove 16, to a greater extent and, accordingly, it is possible to control the output flow of the liquid is t 30 from the second cylindrical chamber 12, while on the rod 14 of the piston creates a corresponding damping force and mechanical shock attached to the rod 14 of the piston can be amortized.

In addition, since the damping groove 16 is formed so that it passes around the inner periphery 15 of the cylindrical chamber 12, at least one turn, can be prevented uneven wear on the outer periphery of the piston 13.

In the absorber, constructed as described above, when the damper is in a degraded state in which the piston 13 and rod 14 are in the extended position at the end of the rod, the outer periphery of the piston 13 facing the side of the damping groove 16, in which the maximum depth and the cross-sectional area of the channel for flow connecting the second cylindrical chamber 12B and the first cylindrical chamber 12A, the maximum. In this state, when a mechanical shock F attached to the end of the rod 14 of the piston in the direction of vtalkivaniya, it will be transferred to the piston 13 and moves the piston 13 in the direction of vtalkivaniya, this will create pressure fluid 30 in the second cylindrical chamber 12, and the liquid 30 under pressure flows to the side of the first cylindrical chamber 12A mainly through the damping groove 16 having the maximum area is the cross-section.

In this regard, although the fluid 30 flows through the gap between the outer periphery of the piston 13 and the inner periphery of the pipe 11, and the gap between the inner periphery of the piston 13 and the outer peripheral portion 14a of the rod 14 of the piston, which has a small diameter, the amount is small and the flow of fluid 30 in the damping groove 16 mainly be involved in the regulation of the damping forces.

The liquid 30, which flows into the first cylindrical chamber 12A, partially passes into the chamber 24 and an elastic element through the connecting channel 26 and is absorbed by the elastic element 19. As the fluid 30 flows in the channel having the maximum cross-sectional area, to the piston rod 14 is applied to a relatively small damping force.

The magnitude of the cross-sectional area of the channel for passage of a stream that is formed between the outer periphery of the piston 13 and the inner periphery 15 of the cylindrical chamber 12 by means of the damping groove 16, actually gradually decreases in proportion to the fly rod 14 of the piston in the direction of vtalkivaniya, as shown in an enlarged scale on the graph according to Fig.6, since the depth of the damping groove 16 on the inner periphery 15 of the pipe gradually becomes smaller toward the head side. Therefore, the flow of liquid 30, the current from the second cylindrical chamber, 12V to pervotselinnikam chamber 12A, decreases in fact proportional to move the rod 14 of the piston to the head side and the damping force gradually decreases.

Figure 2 shows the state in which the rod 14 of the piston is at half stroke in the direction of vtalkivaniya, and in this state, the fluid flow 30, the current in the channel to flow is greatly reduced, according to the course of the rod 14 of the piston to the head-side damping force gradually increases, while continuing to absorb mechanical shock, and eventually leads to stopping of the piston rod 14. Figure 1 is a piston 13, which is located at the end of its stroke, indicated by dashed lines.

After the mechanical shock applied to the piston rod 14, is absorbed, and the rod 14 and piston 13 is stopped, when excluding the impact of a shock load, the rod 14 of the piston begins to slowly move in the direction of its protrusion through the energy of the return spring 18. At this time, since the depth of the damping groove 16 that faces the outer periphery of the piston 13, is increased in accordance with the stroke of the piston 13, the moving speed of the piston rod 14 becomes higher, and the rod 14 is returned to its initial position.

If it is desirable to carry out rapid action when returning the piston rod 14 may be a check valve, for example, in the channel, on espacenet inside the piston 13 in the direction of the axial line, when this check valve provides fluid flow 30 to pass only from the first cylindrical chamber 12A to the second cylindrical chamber 12B.

1. The absorber containing:
cylindrical chamber formed in the pipe and filled with a liquid;
a piston located in a cylindrical chamber with a possibility of free movement in the direction along the axial line of the cylindrical chamber;
the piston rod, one end of which is connected with the piston, and the other end comes out of the tube;
battery, providing for the establishment of a piston rod of the damping force by overriding fluid from the compression in the cylinder chamber when the piston rod is pushed into the pipe by impact forces and the movement of the piston
in which on the inner periphery of the cylindrical chamber formed by one turn of the spiral damping grooves inclined relative to the axial line, so that it was held within the stroke range of the piston, the width of the damping groove is constant over the entire length of the damping groove, the depth of the damping groove gradually decreases along a helix in the direction in which the push rod piston and the length of the piston in the direction along the centerline is less than the step of the damping groove.

2. The shock absorber according to claim 1, in which the width of campfire the soup groove along the centerline in fact equal to the length of the piston or larger.

3. The shock absorber according to claim 1 or 2, in which the bottom wall of the damping groove is made flat.

4. The shock absorber according to any one of claims 1 and 2, in which one step of the damping groove formed in the stroke range of the piston.

5. The shock absorber according to any one of claims 1 and 2, in which the piston is held at the end of the rod in a floating state.

6. The shock absorber according to any one of claims 1 and 2, in which the outer end of the cylindrical chamber, a guide rod connected with the camera, forming the battery, and this camera contains within pliable extensible and compressible elastic element.



 

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3 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: inclination angle of relationship between resistance force modulus and deflection speed modulus of an elastic member is changed if current resistance force modulus differs from the specified value. The specified value of resistance force is changed depending on current deflection of the elastic member. The specified current value of resistance force is set so that it is directly proportional to modulus of current deflection of elasticity force, which is corrected to resistance force vector, of the elastic member of its static value. The device for implementing the method represents a hydraulic telescopic damper, in which the resistance force, the modulus of which depends on the modulus of deflection variation speed, is created during the suspension deflection variation. As per the first version, the damper includes a bar fixed at the compression chamber bottom. The bar has a four-sided variable cross-section in the working section of its length. At the damper compression, the bar is retracted into inner cavity of the stock. As per the second version, the damper includes two bars, as well as a compensating chamber that is separated from the compression chamber with a partition wall and partially filled with liquid. The bars are made in the form of a rotation body and installed inside the first and the second guide elements respectively with possibility of longitudinal movement.

EFFECT: preventing resonance, and minimising the resultant force acting on the under-spring mass of the transport vehicle.

17 cl, 10 dwg

FIELD: machine building.

SUBSTANCE: shock absorber includes a housing, a cylinder, a stock, a piston-valve, a sleeve-governor, a rod with tracks, which is telescopically installed in the stock, a bottom valve, and a guide of the stock. Tracks on the rod are screw-shaped and have constant or variable angle of twist to the stock axis. When moving on the rod track, the guide stop turns the sleeve-governor; at that, holes in the stock are covered, thus changing the quantity of bypassed liquid. As per the first version, in the shock absorber the rod end is fixed in the bottom valve zone against being turned and against axial movement. As per the second version, in the shock absorber the rod end is fixed in the bottom valve zone against axial movement. Shock absorber includes an additional valve with channels adjoining the bottom valve holes. When moving on the rod track, the guide stop that is additionally made on the stock turns the rod; at that, holes in the additional valve are covered, thus changing the quantity of bypassed liquid.

EFFECT: obtaining automatic adjustment of a shock absorber force depending on a stock position, as well as providing the possibility of readjustment of the shock absorber without its removal.

2 cl, 3 dwg

Shock absorber // 2570243

FIELD: machine building.

SUBSTANCE: shock absorber contains a cylinder with work fluid. The piston is inserted in the cylinder and separates the cylinder to two chambers. The piston rod is connected with the piston. The damping valve is installed in the first channel. The through section regulation mechanism is installed in the piston and regulates the through section of the second channel based on the piston rod position. The damping force decreases for tension and increases for compression in the set rod position at large extension. The damping force increases for tension and decreases for compression in the set rod position at small extension. In the shock absorber under the second option the damping force decreases for tension and compression in set rod position at small extension. In the shock absorber under the third option the damping force decreases for tension and compression in set rod position at large extension. The damping force increases for tension and decreases for compression in the set rod position at small extension. The shock absorber under the 4th option is installed between the wheel and body of the vehicle. Mechanism regulating the vehicle height is installed in parallel with the shock absorber.

EFFECT: extension of dampening characteristics.

16 cl, 25 dwg

Hydraulic damper // 2628552

FIELD: machine engineering.

SUBSTANCE: hydraulic damper (10) contains the piston valve (22) fixed at the end of the piston rod (11), the base valve (27), the tank chamber (15). The base valve includes the compression side channel (31). The first coil spring (28) is provided between the first valve (24) and the base valve, and the second coil spring (23) is provided between the first valve and the piston valve. The compression side channel is closed by the first valve near the maximum compression state, reducing the oil flow rate, entering the tank chamber. The second valve (33), passing through the first valve centers and the base valve, regulates the oil flow rate, entering the tank chamber (15), when the pressure is equal to or exceeds the specified level of the pressure in the oil chamber (21b). In the second embodiment, the third valve is provided on the lower part of the first valve.

EFFECT: damping force characteristic change.

3 cl, 30 dwg

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