Vibration isolator of large carrying capacity

FIELD: machine building.

SUBSTANCE: invention refers to machine building industry. Vibration isolator includes a housing with a flange, two elastic sleeves from wire material of metal rubber, which are arranged in it with radial and axial preload, a cover and fastening parts. In a central hole of sleeves and the cover there arranged is a tightening screw with threaded ends, in which there are holes for cotter pins. A cylindrical wall of the housing projects on both sides of its base to the height of the sleeve in free state. Specified value of axial preload of elastic sleeves is created by tightening of a lower slotted nut, under which elastic washers are installed. Sharp edges of parts are rounded with radii. Parameters of elastic sleeves are determined so that at simultaneous action of weight force of the object and the force allowable in operation and determined by dynamic overload, which are accounted for by the vibration isolator, dynamic loading processes of the vibration isolator cannot interfere with "tails" of its field of elastic hysteresis loops.

EFFECT: achieving increase in carrying capacity and service life of a vibration isolator.

3 cl, 4 dwg

 

The invention relates to a vibration-insulating-metal devices, medium and large capacity, capable of working in a hostile environment, in vacuum, in terms of radiation and elevated temperature (up to 450°C).

Known vibration absorber (see Cats AS the Calculation provedeniya characteristics of vibration isolators of Mr material, abstract dissertatsii on competition of a scientific degree of candidate of technical Sciences. - Samara - 2007), comprising a housing, two tapered elastic sleeve of wire nonwoven Mr ("- Metal"), the cover, the Central sleeve, the clamping shoulder screw and fastener - washer, slotted nuts and cotter pins. On the housing, the cover and the center hub is made small concentric flange, which are centered bushings from Mr and creates a radial interference fit. Axially clamped in the sleeve of the Mr is created by twisting the lower slotted nut (if the axis of insulator vertical) to lock the cover to the flange of the clamping screw and the end of the Central sleeve in the lid, and in this position the nut splinters. The body of the insulator has a flange, to which the vibration absorber is attached to the base. Vibrotherapy object is placed on the cover and secured with a washer, a second slotted nut and cotter pin.

The vibration absorber can be used in spatial loading. Its elastic the sleeves are bilateral upregulating it stops at loading in all six degrees of freedom. Among its positive qualities should include its relatively small size and weight, simplicity of design and its manufacturing technology.

The technical nature of this vibration absorber closest to the proposed and adopted for the prototype.

However, this vibration absorber has a number of serious shortcomings.

Material Mr bad tensile and torsional and lateral vibrations of the object in the places of the elastic bushings where they are in contact with the centering shoulder, you may experience tensile stresses leading to local rupture of the material of the sleeves.

In the literature (see Cats AS the Calculation provedeniya characteristics of vibration isolators of Mr material, abstract dissertatsii on competition of a scientific degree of candidate of technical Sciences. - Samara - 2007), which describes the design of insulator not covered by the conditions that you must follow when creating a workable, heavily loaded of insulator with progesterone elements made of Mr material, satisfying THE customer, and not opened their physical meaning (see below).

Note that in the proposed design of insulator these conditions are met and claimed as a distinctive feature of the proposed design.

Elastic sleeve insulator made of unidirectional the pressing of the workpiece along the vertical axis of the sleeve. Therefore, the angles of inclination to the axis of the sleeve planes of the main mass of coils within its volume a little different from direct, and with considerable radial dynamic loads will be residual radial deformation, which will be to grow rapidly at the time.

Products of Mr material, made of unidirectional pressing, work best in compression in the direction of pressing.

The prototype of the upper elastic sleeve is much more loaded than the bottom, since the loading of insulator weight of the object it zagrujaetsa by the same process by which it was loaded when you create axial tension, and the lower elastic sleeve when it is unloaded and the result is less loaded condition even in comparison with the state of it after its axial tension.

As a result, when the dynamic loading of insulator loading the upper sleeve is described by the hysteresis loop, either partially or entirely lying on the "tails" of the field it progesteronic loops, which greatly impairs progesterone characteristics (UFH) of insulator, increases congestion and resonance frequency vibroisolating object, which in turn leads to the emergence of "shrinkage" of the bushing material and reduction of axial tension bushings. Moreover, as will become nurestan the e shrinkage and residual radial deformation increases the density of the material of the sleeves. In addition, due to the wear increases the friction on the contact surfaces of coils. All of this will lead to the fact that the working hysteresis loop of the vibration damper further will be "pushed out" to "tail" of the field, will increase srednetehnicheskoe the rigidity of the insulator, and hence the resonant frequency of the dynamic system "object - vibration isolators", the scattering coefficient of the insulator will be reduced and, consequently, will increase the dynamic loads acting on the object. Moreover, the intensity increases the adverse impact of these factors will continuously increase as the lamp. Naturally, the intensity increases these adverse factors strongly depends on the successful choice of the initial design parameters of the vibration damper.

The disadvantages of the prototype should also be attributed to the absence of elastic compensating for the loss of axial tension in the mean time, due to the rigid bonding of the cover with the Central bushing. As a result, as shown by the experience of the operation of the vibration damper, by reducing the axial preload decreases the force of tightening slotted nuts despite their kontrolka pins and occasionally have their paxathipatai and splitout.

Therefore, the task of development of insulator large capacity the spine (with the same range of capacities, as the prototype), which in torsional and lateral vibrations of the object would not happen "Zakus" material elastic sleeves and local break him axial "shrinkage" and radial residual shear deformation of the material Mr bushings in the process of elaboration would not require periodic peresasyvaniya slotted nuts and their spontania, with vibration absorber compared to the prototype would be the best UFH, and, therefore, the dynamic system vibrotherapy object - vibration isolators" would have a lower resonant frequency, and the object was affected would be less dynamic overload in the resonance zones, and in the above-resonance, and therefore, the proposed vibration absorber would be more life than the prototype.

The problem is solved in that a vibration absorber MSF heavy vehicles, comprising a housing with a flange placed therein with radial and axial tension two tapered elastic sleeve of the wire material MP, made unidirectional by pressing in the direction of the axis of the sleeve, the cover is placed in the Central hole of the sleeves and cap clamping screw with threaded ends that made the holes for the cotter pins, fasteners - washers, slotted nut and cotter pins, distinguished by the fact that the cylindrical wall of the housing will ustupaet on both sides of its base to the height of the sleeve in a free state, on tightening the screw is made of a round conical flange with an outer diameter less than the internal diameter of the cylindrical wall of the casing at two turns of the insulator in the radial direction and on the outer surface of the flange of the support platform, the clamping screw with a given radial preload is placed in the Central hole of the elastic bushing, the diameter of the inner bore of the case base on two radial stroke larger than the diameter of the smooth cylindrical portion of the clamping screw, the conical cover is centered on the clamping screw and the outer surface is planar support platform, and its outer diameter equal to the outer diameter of the conical flange of the clamping screw, the desired axial preload of the elastic bushings created tightening the lower slotted nut, which has one, two or more elastic washer, spring washer also installed under the second slotted nut, sharp edges of the elastic bushing, the cylindrical wall of the casing, cap, conical flange coupling screw, and the junction of the casing wall with its base and tapered flange with coupling screw rounded radii, the parameters of elastic sleeves, and therefore, the vibration damper is defined in such a way that, under the simultaneous action attributable to the vibration absorber of the weight of the object and permissible to operate the tion forces, due to the dynamic overload, dynamic loading processes of insulator would have been on the "tails" of his field progesterone loops.

The absence of the proposed vibration damper of the shoulder at the base, the lid and the flange of the clamping bolt, which in the prototype centered elastic sleeve and created in them the tightness, the presence of rounding sharp edges at the wall of the housing, the flange of the clamping bolt and the cover in contact with the material of the elastic sleeves, and rounding sharp edges themselves elastic bushings eliminates the possibility of "drafts" of the material of the sleeves and the emergence of local discontinuities in the material.

Compared with the prototype strain due to axial and radial tightness, more evenly distributed on all of the boundary surfaces of the bushings, which significantly improves UFH offer of insulator.

The required parameters of the proposed vibration damper are determined by calculation or experimentally, taking into account the fact that when the elastic bushings duplex upregulating stops, when the axial loading of insulator constant force G and cyclic strength with maximum amplitude, given the terms of reference, the vibration absorber must be loaded on the hysteresis loop without "tails", while the deformation of the bushings under the action of a constant force will be much more shall iformatsii these bushings under the action of only one constant force, as the center of the hysteresis loop under the action of a constant force will shift point with the ordinate G process with stiffness equal to the lower stiffness of the stiffness of the processes limiting the loop.

And although this condition will increase the outer diameter of the elastic bushings (approximately 10-15%) and, consequently, the overall dimensions of the insulator in the horizontal plane and its weight, a significant improvement UFH of insulator more than cover this deficiency, as it will decrease the resonant frequency of the system object - vibration isolators and dynamic overload at resonance, and hence the service life of the insulator.

Install spring washers under the slotted nut eliminates invalid loosening slotted nuts at the time, and therefore there is no need of Peresetsky and splintage these nuts at the time. Note that the more elastic washers installed under the lower slotted nut, the large tightening force is maintained during the same axial permanent deformation of the sleeves.

The lowest residual strain and its rate of accumulation in the mean time ceteris paribus get products from wire material MP running on cyclic compression. The time of accumulation of permanent deformation to an invalid size is determined by the Republic of the PC these products.

Therefore, to increase resource insulator serves vibration absorber MSF large payload, wherein the elastic sleeve is made of successive pressing of the workpiece in the radial and axial directions, and the degree of deformation of the workpiece at each of these operations phases pressing chosen so that the plane of coils of the main mass of coils in the volume of the sleeve is inclined to the vertical axis of the vibrator angles φ lying in the range of 45°≤φ≤α, where α is the angle equal to the half angle of the cone sleeve.

In this case, the portion of the shear deformation of the elastic bushings at their radial dynamic loading is reduced and decreases the slew rate of the residual shear strain of the sleeves, thereby increasing the service life of the insulator.

In addition, to simplify the design of the insulator and the technology proposed vibration absorber MSF large-capacity performed with a cylindrical elastic sleeves, and the tilt angles of the planes of the coils to the vertical axis of the sleeve from the main mass of coils of material sleeve little different from 45°, and the base, the cover and the flange of the clamping screw is made with flat support surfaces.

Design and manufacturing technology of the housing, the clamping screw and cover vibration absorber is simplified due to the simpler geometry of these parts.

Construction of the proposed vibration isolators are illustrated by the figures on which the mounting insulator to the object and the base is shown as "furnished" on the Assembly drawing thin solid line.

1 shows a frontal section of insulator IAH with a tapered elastic sleeve.

Figure 2 shows a frontal section of insulator IAH with a cylindrical elastic sleeve.

Figure 3 shows a top view of these vibration isolators.

Figure 4 presents a qualitative field progesterone loops of insulator. The process of static loading force of the weight attributable to the vibration absorber, and its working hysteresis loop under the influence of the maximum dynamic overload represents the main contour line.

The proposed vibration absorber MSF high capacity (figure 1) includes a housing 1 with a flange 2 and a conical base 3 placed therein with radial and axial tension two tapered elastic sleeve 4 of the wire material MP, made unidirectional by pressing in the direction of the axis of the sleeve, the cover 5, the clamping screw 6 with threaded ends 7, in which holes 8 under the splints placed in the Central hole 9 of the sleeves 4 and the cover 5 with a given radial preload on the bushings, fasteners elastic washer 10, slotted nuts 11 and W is linty 12. Cylindrical wall 13 of the housing 1 acts on both sides of the base 3, the height of the sleeve 4 in the free state. On tightening the screw 6 is made of a round conical flange 14 with an outer diameter less than the internal diameter of the cylindrical wall 13 of the housing 1 at two turns of the insulator in the radial direction and on the outer surface of the flange of the support platform 15. The diameter of the inner bore 16 of the base 3 of the housing 1 at two radial stroke larger than the diameter of the smooth cylindrical part 17 of the clamping screw 6. Conical cap 5 is centered on the clamping screw 6. On its outer surface is planar support platform 18 and its outer diameter equal to the outer diameter of the conical flange 14 of the clamping screw 6. The desired axial preload of the elastic bushings 4 created by tightening the lower slotted nut 11, which has one, two or more elastic washer 10. Elastic washer 10 is also installed under the second slotted nut 11.

Sharp edges of the elastic bushings 4, the cylindrical wall 13 of the housing 1, the cover 5, the conical flange 14 of the clamping screw 6, and the junction of the wall 13 of the housing 1 with its base 3 and the conical flange 14 with coupling screw 6 rounded radii.

The parameters of the elastic bushings 4 and, consequently, the insulator is defined in such a way that, under the simultaneous action coming belonging on the vibration absorber of the weight of the object and a valid operation forces due to the dynamic overload, dynamic loading processes of insulator would have been on the "tails" 19 (see figure 4) his field progesterone loops.

Vibration absorber flange 2 of the housing 1, having a form of a rectangle with four holes 20 for mounting screws (see figure 1 and 3), is mounted on the base 21 and fixed thereto by screws 22 and the elastic washers 23. Vibrotherapy object 24 by means of the clamping screw 6, the elastic washer 10, slotted nuts 11 and pin 12 is fixed on the vibration damper.

In addition, the elastic sleeve 4 can be produced by consecutive pressing of the workpiece in the radial and axial directions, and the degree of deformation of the workpiece at each of these phases pressing chosen so that the plane of coils of the main mass of coils in the volume of the sleeve is inclined to the vertical axis of the vibrator angles φ lying in the range of 45°≤φ≤α, where α is the angle equal to half the cone angle of the sleeve 4. The angles φ of inclination of the coils not shown.

Proposed construction of insulator MSF high capacity cylindrical elastic sleeve 25 (see figure 2)where the angles φ of inclination of the planes of the coils to the vertical axis of the sleeve main mass of coils of material sleeve 25 little different from 45°. The base 26 of the housing 27, the cover 28 and the flange 29 of the clamping screw 30 this is vibroisolation made with flat support surfaces.

The Assembly of the vibration damper (1) is as follows.

In case 1 set of the elastic sleeve 4. On the long threaded end of the clamping screw 6 screw until it stops in the smooth part of the clamping screw technological intake cone (not shown in figure 1), the smaller the diameter of which is smaller than the diameter of the Central hole of the sleeve 4 in the free state, and more equal to the diameter of the smooth portion of the clamping screw 6. With a given radial tensioning insert clamping screw 6 in the Central hole of the elastic bushing 4 to the stop flange 14 in the elastic sleeve 4. Sbencivu intake cone with the clamping screw 6. Consistently put on the lid 5, one, two or more elastic washer 10 and screw slotted nut 11, tighten it until a specified axial tension in the elastic sleeve 4, which is controlled by the size between the outer face slotted nut 11 and a flat base platform 18. Then install the cotter pin 12 and unbend its ends on the edge of the nut 11. On the other threaded end of the clamping screw 6 set elastic washer 10, screw slotted nut 11, install the cotter pin 12 and slightly bent on one end, so that he could not fall out during transportation and storage of the assembled insulator, but that the cotter pin is easily removed during installation.

Other proposed vibration isolators collect the camping similarly.

The proposed vibration isolators are as follows. When setting the object on the vibration isolators vibration absorber is loaded by the force G of the weight of an object attributable to the vibration absorber, the process 31 (see figure 4) and loaded condition of the insulator is determined by the point A (G, yarticle), where yarticle- static deformation of the insulator under the force G. While impact strength G and dynamic loads workflows of insulator will be described at a constant dynamic overload one, and shock load multiple progesterone loops 32 and the center of these loops from the unloaded condition of the insulator About (0, 0) the process of loading 33 with a stiffness equal to the stiffness of the process 34 with the lowest stiffness field progesterone loops, will shift the point O1(G, y1), where y1- deformation of the insulator under the force G while impact strength G and dynamic loads.

The operation of the vibration damper with amplitude deformations, large amplitude deformations, resulting from the impact of the maximum permissible dynamic loads (loading of insulator on the loop 35), will not necessarily lead directly to the failure of insulator, but will deteriorate its UFH, to increase dynamic overload, grow resonant frequency and Socrates the it resource with the higher intensity the farther its working loop "crawl" on "tail" 19 field progesterone loops.

The proposed vibration isolators are working with all kinds of dynamic loads acting on all six degrees of freedom. They have a carrying capacity that is five times greater, and damping, 2.5-3 times larger than the vibration isolators rubber progesterone elements (in terms of unit volume element). When a large load their dimensions will be substantially smaller than the dimensions of the vibration isolators same capacity with rubber progesterone elements. They are calculated and can be operated in a hostile environment, in conditions of radiation, vacuum and high temperature. Their advantages in comparison with the prototype described above.

1. Vibration absorber heavy vehicles, comprising a housing with a flange placed therein with radial and axial tension two conical or cylindrical elastic sleeve of the wire material-metal made unidirectional by pressing in the direction of the axis of the sleeve, the cover is placed in the Central hole of the sleeves and cap clamping screw with threaded ends that made the holes for the cotter pins, fasteners - washers, slotted nut and cotter pins, characterized in that the cylindrical wall of the housing protrudes from both side is n its base to the height of the sleeve in a free state, on tightening the screw made a round flange with an outer diameter less than the internal diameter of the cylindrical wall of the casing at two turns of the insulator in the radial direction, performed conical to conical elastic sleeves or cylindrical to cylindrical elastic sleeves, and on the outer surface of the flange of the support platform, the clamping screw with a given radial preload is placed in the Central hole of the elastic bushing, the diameter of the inner bore of the case base on two radial stroke larger than the diameter of the smooth cylindrical portion of the clamping screw, and cap, respectively, performed conical or cylindrical, centered on the clamping screw, and its outer surface is planar support platform and its outer diameter equal to the outer diameter of the conical flange of the clamping screw, the desired axial preload of the elastic bushings created by tightening the lower slotted nut, which has one, two or more elastic washer, spring washer also installed under the second slotted nut, sharp edges of the elastic bushing, the cylindrical wall of the casing, cap, conical flange coupling screw, and the junction of the casing wall with its base and tapered flange with coupling screw rounded radii, the parameters of elastic sleeves, and therefore the insulator is defined thus so while action attributable to the vibration absorber of the weight of the object and a valid operation forces due to dynamic overload, dynamic loading processes of insulator would have been on the "tails" of his field progesterone loops.

2. Vibration absorber of high capacity according to claim 1, characterized in that the elastic bushings are made sequential pressing of the workpiece in the radial and axial directions, and the degree of deformation of the workpiece at each of these operations phases pressing chosen so that the plane of coils of the main mass of coils in the volume of the sleeve is inclined to the vertical axis of the vibrator angles φ lying in the range of 45°≤φ≤α, where α is the angle equal to the half angle of the cone sleeve.

3. Vibration absorber of high capacity according to claim 2, characterized in that its cylindrical elastic sleeve is designed so that the angle of inclination of the planes of the coils to the vertical axis of the sleeve from the main mass of coils of material sleeve little different from 45°, and the base, the cover and the flange of the clamping screw is made with flat support surfaces.



 

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Vibration isolator // 2445527

FIELD: machine building.

SUBSTANCE: proposed device comprises barrel accommodating packs of elastic elements sequentially fitted therein. Barrel is made form elastic polymer and feature cylindrical top part and truncated cone bottom. Said packs are made from discrete raw animal material, for example, linter-feather mix. Gaskets made from elastic dense raw animal material, for example, leather or felt, are arranged between aforesaid packs. Barrel top part is closed by cover from slightly-elastic polymer provided with central hole arranged coaxially with barrel lengthwise axis.

EFFECT: higher damping properties.

1 dwg

FIELD: machine building.

SUBSTANCE: conic equi-frequent element is made as two internal and external flexible rings axially symmetrically arranged in parallel planes. The rings are rigidly interconnected by means of two symmetrical elastic and diametrically arranged elements with a through central slot symmetrically made inside the element. Side surface of the slot are conjugated on ends with surfaces created with through orifices on external and internal rings. Surfaces making the equi-frequent element are conic. Cavities formed with the flexible rings and symmetrical elastic diametrically arranged elements are filled with an elastic damping net element.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

2 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: disk equi-frequent element is made as two internal and external flexible rings axially and symmetrically arranged in parallel planes. The rings are rigidly interconnected by means of two symmetrical elastic and diametrically arranged elements with a through central slot symmetrically cut inside the element. The elements connecting internal and external rings have lines of curve and can be secured on the rings by welding, for example contact welding, of by means of fastening threaded elements or by glue connection. Cavities formed with internal and external rings are filled with damping net elements.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

2 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: disk flexible element is made as two flat flexible internal and external rings coaxially arranged. The rings are positioned in parallel horizontal planes and are rigidly interconnected by means of two flexible elements. The flexible elements are radially arranged in horizontal plane at angle within ranges of 10°÷80° in vertical plane. Cavities formed with the flexible rings and flexible radially arranged elements are filled with an elastic damping net element.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

4 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: disk flexible element is made as two flat flexible internal and external rings coaxially arranged. The rings are positioned in parallel horizontal planes and are rigidly interconnected by means of two flexible elements. The flexible elements are radially arranged in horizontal plane at angle within ranges of 10°÷80° in vertical plane. Cavities formed with the flexible rings and flexible radially arranged elements are filled with an elastic damping net element.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

4 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: disk equi-frequent element is made as two internal and external flexible rings axially and symmetrically arranged in parallel planes. The rings are rigidly interconnected by means of two symmetrical elastic and diametrically arranged elements with a through central slot symmetrically cut inside the element. The elements connecting internal and external rings have lines of curve and can be secured on the rings by welding, for example contact welding, of by means of fastening threaded elements or by glue connection. Cavities formed with internal and external rings are filled with damping net elements.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

2 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: conic equi-frequent element is made as two internal and external flexible rings axially symmetrically arranged in parallel planes. The rings are rigidly interconnected by means of two symmetrical elastic and diametrically arranged elements with a through central slot symmetrically made inside the element. Side surface of the slot are conjugated on ends with surfaces created with through orifices on external and internal rings. Surfaces making the equi-frequent element are conic. Cavities formed with the flexible rings and symmetrical elastic diametrically arranged elements are filled with an elastic damping net element.

EFFECT: raised efficiency of vibration isolation in resonance mode and simplification of design and assembly.

2 cl, 2 dwg

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