RU2611282C1 - Sleeve vibration isolator and method of its manufacturing - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: vibration isolator comprises an annular mounting flange (5), a pair of truncated cone-shaped elastic-damping elements (8), a sleeve (9) with the poppet flange (11). The elastic-damping elements are made from a coil, wound from springy metal wire with turn pitch being equal to the coil diameter, and pressed into a cone shape. The spiral is made of a pair of interconnected links (131, 132) with a spring wire of different diameters. The method comprises the step to draw a spiral between the turns of the equal diameter of the corresponding spiral. Dosed wound on a mandrel smaller diameter helix, spiral wound over it a larger diameter cross weave with a resilient barrel member, followed by the moulding. The cone-shaped elastic-damping elements are impregnated with the greasing mixture.

EFFECT: increased reliability and an increase in the isolator resourse, providing vibration protection in the longitudinal and transverse directions.

2 cl, 9 dwg

Description

The present invention relates to transport engineering, mainly to aircraft and can be used for vibration isolation of blocks of computer systems, which require a reduction in vibration and shock load.

Known compressible elastic element of a non-magnetic metal wire of cylindrical shape. The wire is wound in a spiral with a step y between the turns, which is wound round to round into a coil on a mandrel in several layers, forming a cylindrical elastic element. The characteristics of the material of the wire and the elastic element are presented. A disadvantage of the known damping element is the insufficient bundle of spiral turns between them, which leads to insufficient stiffness of the damping element (US patent No. 4514458, NKI 428/222 from 04/30/1985 SPRING-LIKE MATERIAL FORMED OF COMPRESSED METALLIC WIRE).

A damping element is also known, wound from interconnected metal spirals of different diameters, first a spiral of a smaller diameter being wound round to round in several layers, and then a larger diameter coil being wound over it at an angle to a smaller spiral, and a winding method is presented. A disadvantage of the known damping element is the lack of cohesion of the coils of a smaller diameter spiral to each other, which leads to a decrease in the stiffness of the damping element and degrades its characteristics, the dynamic coefficient at the resonant frequency (EP No. 0447294, IPC F16F 1/362 from 03.03.1991, Manchon elastique anti -vibratoire notamment pour accouplement d'echapement et procede de realization d'un manchon elastique anti-vibratoire).

Known vibration insulator sleeve, adopted for the prototype, containing two elasto-damping elements made of metal rubber material, placed on an annular base on both sides with different compressive forces, restrictive washers mounted on the sleeve coaxially with the annular base and elastic-damping elements. In addition, between the annular base and one of the restriction washers, two preloaded unloading springs are introduced coaxially with them, one of which is cylindrical, covering, for the most part of its turns, the outer surface of the elastic-damping element and the other, a conical spring, installed in the inner central conical opening of the elastic-damping element, the coil of the smaller base tightly covers the outer surface of the shoulder of the restrictive washer, and most of the turns of the conical spring on the inner conical surface of the Central hole of the elastic-damping element, and the Central sleeve is made in the form of a mounting rod at the same time with a restrictive washer at one end with a threaded part at the opposite end, and the other restrictive washer through the Central hole is pressed with its inner shoulder on the mounting rod and secured with a nut with turnkey longitudinal grooves (Utility Model Patent No. 95048, IPC F16F 3/08 “Vibroinsulator sleeve” dated 06/10/2010). The disadvantage of the sleeve vibration damper is the wear of the damping element made of metal rubber, caused by its dry friction against the unloading springs, thereby reducing the resource.

The purpose of the invention is to increase reliability and improve its damping properties by increasing the stiffness of elastically damping elements in the longitudinal and transverse directions and to increase the resource.

This goal is achieved by the fact that the sleeve insulator containing a mounting ring flange with flanges on both sides, a pair of cone-shaped elastic damping elements with the same degree of stiffness, made of a spiral wound from a spring metal wire, with a pitch between the turns equal to its diameter, and the spiral consists from two interconnected links of different diameters, while a larger spiral link is wound on top of a smaller diameter spiral link, the base of a cone-shaped elastic damping The mounting elements are connected with the mounting ring flange on both sides, the central sleeve with protrusions mounted coaxially with the mounting ring flange and cone-shaped elastic damping elements, plate flanges with central holes mounted on opposite sides of the central sleeve on its protrusions.

Distinctive features of the proposed sleeve vibration isolator are that the cone-shaped damping elements are truncated with a transition at a large diameter into an annular base with a height equal to the height of the flanges of the mounting ring flange, and are rigidly fixed to its internal surfaces, and the smaller bases of the truncated cone-shaped elastic damping elements are rigidly fixed to the inner surfaces of the dish-shaped flanges and to the flanges made along their perimeters, truncated conical elastically the damping elements are made of a spiral wound from a spring metal wire with a pitch between the turns of the spiral equal to the diameter in the form of an elastic barrel-shaped element with subsequent crimping into an elastically damping element of a truncated conical shape, the spiral being made of a pair of interconnected links with different diameters of the spring wire and it is laid with an interference fit with weaving, and the link of a larger diameter of the spiral is laid on top of its smaller diameter, the central sleeve is expanded in holes in the disk-shaped flanges, and a groove is made in the middle of the central sleeve.

A method of manufacturing a sleeve vibration absorber is that an elastic damping element is wound from interconnected metal spirals of different diameters, with a smaller diameter coil being wound first on a mandrel and then a larger diameter spiral being wound over it.

The differences of the method are that first, before winding, both spiral links are stretched to a step between the turns equal to the diameter of the corresponding spiral link, then the stretched spiral links are wound on the mandrel cross-woven into an elastic barrel-shaped element, and the smaller spiral link is wound in a batch with different lengths and the filling height and is controlled by the number of turns of the mandrel, then the elastic barrel-shaped element is crimped in the form of a truncated cone-shaped elastic damping element and with a transition at its larger diameter into a ring-shaped base, the height of which is equal to the height of the flange of the mounting ring flange, while the length of the elastic barrel-shaped element is 2.8–2.9 times the height of the truncated cone-shaped elastic-damping element, and the larger diameter is correspondingly larger than the diameter of the ring-shaped base 1.2 to 1.3 times, in addition, a reliable glue rigid connection of the surfaces of smaller and ring-shaped bases of truncated cone-shaped elastic damping elements, respectively, with internal erhnostyami poppet flanges with collars made along the perimeter of the annular flange and fastening with their preload provides vibration shield products from axial and lateral loads.

Reliable adhesive bonding is facilitated by an increase in the area of the bonded surface due to the introduction of beads along the perimeter of the dish-shaped flanges and sandblasting of the bonded surfaces with their subsequent degreasing.

In addition, the truncated cone-shaped elastic damping elements are impregnated with a lubricant mixture of 100 ml of gasoline and 10 ÷ 20 mm ^{3 of} TsIATIM 221 lubricant.

The implementation of the differences of the invention in conjunction with the characteristics given in the characterizing part of the formula, ensures the achievement of a new technical effect of the vibration damper sleeve:

- high reliability of the sleeve vibration absorber by increasing the rigidity of truncated cone-shaped elastically damping elements and increasing the area of glued surfaces;

- increase the life of the sleeve vibration damper due to the impregnation of the truncated cone-shaped elastically damping elements with a lubricant mixture, thereby eliminating the spiral breaking due to friction during operation;

- ensuring effective vibration protection of the protected product from loads in both longitudinal and transverse directions.

The invention is illustrated by drawings.

In FIG. 1 shows an embodiment of a sleeve vibration isolator.

In FIG. 2 shows the design of the proposed vibration insulator sleeve.

In FIG. 3 shows a truncated cone-shaped elastic damping element.

In FIG. 4 is a diagram of a device for winding an elastic barrel-shaped element.

In FIG. 5 shows an elastic barrel-shaped element.

In FIG. 6 shows a device for crimping an elastic barrel-shaped element into a truncated cone-shaped elastic damping element.

In FIG. Figures 7-8 show the assembly of the sleeve vibration isolator and the central sleeve.

In FIG. 9 shows the frequency response.

The sleeve vibration isolator can be used according to the embodiment shown in FIG. 1.

Hub vibration insulators 3 are mounted to its fasteners 2 of the airplane block of computing systems 1 with bolts 4, and the fixing ring flange 5 of the sleeve vibration isolator is fixed to the aircraft platform 6.

When exposed to vibration and shock loads on the platform 6, and, consequently, on the sleeve insulators 3, a significant part of the vibration energy is dissipated due to the elastic properties of the sleeve insulators, thereby ensuring vibration isolation of the computing system unit 1.

The sleeve vibration damper 3 (FIG. 2) contains a mounting annular flange 5 with shoulders 7 on both sides of it, a pair of truncated cone-shaped elastic damping elements 8 with a ring-shaped base at a larger diameter, rigidly fixed with an adhesive joint to the mounting annular flange 5 and shoulders 7 from opposite sides with identical by pressing forces, the central sleeve 9 with protrusions 10 on both sides and disk flanges 11 with flanges 12 made along their perimeter, covering and rigidly fixed to their inner surface on reliable adhesive connection to the smaller bases of the truncated cone-shaped elasto-damping elements 8, in the center of each plate-shaped flange 11 holes are made in which the protrusions 10 of the central sleeve 9 are installed and expanded, with the truncated conical elasto-damping elements 8 being pressed.

In FIG. 3 is a truncated cone-shaped elastic-damping element 8 with the transition from the larger diameter annular base whose height h is the height of the shoulder 7 of the fastening of the annular flange 5, the diameter of the central aperture D _ukue truncated conical elastic-damping member 8 larger than the external diameter D _col central hub 9 by an amount δ to elimination of friction of the spiral on the surface of the Central sleeve 9 during vibration.

In FIG. 4, 5, 6, a method for manufacturing a truncated cone-shaped elastic damping element with a transition at a larger diameter into an annular base is presented.

Pre-stretched spirals wound from a spring metal wire (Fig. 4) made of two interconnected links 13 ₁ , 13 _{2 of} smaller d ₁ and larger d ₂ diameters and pitch between turns h ₁ and h _2, respectively, fit into the recess of the rotating around its axis of the roller 14 mounted on the bar 15, made with the possibility of vertically reciprocating movement, regulating the tension of the spirals 13 ₁ , 13 ₂ . Then the spiral passes into the hole 16 of the lever 17, made at its end, while the lever 17 with the hole 16 is made with the possibility of horizontal reciprocating motion with adjustable amplitude of movement.

A spiral 13 _{1 of} smaller diameter is tightly packed crosswise with weaving on a rotating cylindrical mandrel 18 in a dosage manner along the length and height of the winding. The length of the spiral winding corresponds to a given amplitude of horizontal movement of the lever 17 with the hole 16, and the height is controlled by the counter 19 of the number of revolutions of the cylindrical mandrel 18.

First, the minimum amplitude of movement of the lever 17 is set, which corresponds to the length l ₁ (Fig. 5) of the dosed winding of the spiral 13 _{1 of} smaller diameter, and the calculated height of the winding is controlled by the counter 19 of the number of revolutions of the mandrel 18. Then, with an increase in the amplitude of movement of the lever 17, the initial winding spiral with a length l _{1 is} wound crosswise with weaving the next dose of a spiral 13 ₁ with a length l ₂ , and the estimated filling height is controlled by the counter 19 reset using the button 20.

In this way, the entire length of the spiral 13 _{1 of} smaller diameter is wound crosswise in a metering manner with the weaving turn on a turn with a dose length of l ₃ and l ₄ . In conclusion, the entire link of the spiral 13 _{2 of a} larger diameter is wound crosswise with the interlacing of the coils.

Then, the elastic barrel-shaped element 21 is crimped into a truncated conical elastic-damping element 8.

The formed elastic barrel-shaped element 21 with its hole is installed in the central pin 22 of the crimping device 23 (Fig. 6), containing a matrix 24, including a base 25 with a central pin 22, made integral, and a glass 26 mounted on the base 25, the punch 27, the pressure surface 28, which is formed as a truncated cone with the height H _{of PP} presser _surface, at the height of a truncated cone-shaped elastic-damping element 8 by the amount of its annular base h _CO, the smaller diameter D _M and bolsheg A base _B are respectively equal diameters and the smaller bases of the truncated conical annular elastic-damping elements 8.

The barrel-shaped elastic damping element 21 mounted on the pin 22 close to the surface of the base 25 is pressed with an exposure of the punch 27 into a truncated cone-shaped damping element 8 with a ring-shaped base at a large diameter, while the punch 23 adjoins the surface 29 to the glass 26 of the matrix 24.

The assembly of the sleeve vibration absorber is carried out in the device 30 shown in FIG. 7.

The device 30 includes a channel-shaped bracket 31 with threaded holes made at the ends of its side walls, a pressure bar 32 with a central hole 33 made therein and a pair of holes at its ends 34 ₁ and 34 ₂ aligned with the threaded holes.

In the center of the base of the channel-shaped bracket 31, a hole is made into which the guide 38 is pressed in, and a rod 36 with a conical tip 37 is installed in the hole 33 of the pressure plate 32.

Before assembly, the inner surfaces of the mounting annular flange 5 with its shoulders 7 and plate-shaped flanges 11 with their shoulders 12 are sandblasted and then degreased.

The assembly begins with the fixing of the central sleeve 9 with the first disk flange 11, for which the protrusion 10 of the central sleeve 9 is installed in the hole of the disk flange 11 is installed on the guide 38 of the device 30 is fixed with bolts 35 ₁ and 35 _{2 of the} pressure plate 32 and is expanded with a conical tip 37 of the rod 36.

Then, a VK-9 adhesive layer is applied onto the inner surface of the first plate-shaped flange 11, the shoulder 12 and the surface of the mounting annular flange 5 and its shoulders 7, onto which the smaller base of the first truncated cone-shaped elasto-damping element 8 and the ring-shaped base of the second truncated cone-shaped elasto-damping element 8, are ring-shaped the base of the first truncated cone-shaped elastic damping element 8 is mounted on the opposite surface of the mounting ring element 8, and the smaller base of the second truncated cone-shaped elastic damping element 8 is mounted on the inner surface of the second disk flange 11.

The assembled package is installed by the inner diameter of the Central sleeve 9 on the guide 38 and is pulled together by pressing with bolts 35 ₁ and 35 _{2 of the} clamping plate 32.

After hardening of glue VK-9 in a heat chamber with a temperature of 60 ÷ 70 ° C and 2-hour exposure, the assembled package is dismantled and removed with a guide 38.

Then the final stage of assembly.

On the inner surface of the second plate-shaped flange 11 with its shoulder 12 and the opposite surface of the mounting annular flange 5 with its shoulders 7, VK-9 glue is applied, onto which the smaller base of the second truncated conical elastically damping element 8 and the annular base of the first truncated conical elastically-damping element 8 are applied, respectively.

The assembled package is installed by the inner diameter of the central sleeve 9 on the guide 38 and is pulled together by pressing bolts 35 ₁ , 35 _{2 of the} clamping plate 32. After the glue VK-9 has hardened and then removed from the device 30, the second protrusion 10 of the central sleeve 9 is expanded.

Preloading truncated cone-shaped elasto-damping elements is ensured by the implementation of the length L _C. the Central sleeve 9 (Fig. 8) from the ratio:

L _C.V. <2H _UKUE + S,

where L _C.V. - the length of the Central sleeve 9;

H _UKUE - the height of the truncated cone-shaped _{elastic damping} element with an annular base 8;

S is the thickness of the mounting annular flange 5.

Calculation and experimental method found that the length of the Central sleeve 9 should be less by 1.5-2 mm As shown in FIG. 8, a groove of length L _{C.B is} made on the outer diameter of the central sleeve 9 _. , which contributes to vibration isolation in the transverse direction.

For winding of truncated cone-shaped elasto-damping elements (UKUE) 8, metal wires of the EI708A VI TU 14-1-1597-75 brand with a diameter of d ₁ = 0.12 mm and d ₂ = 0.2 mm were used, and the density of the spiral structure of a truncated cone-shaped elasto-damping element 8 is in the optimal range of values of 1.9 g / cm ³ ... 2.0 g / cm ³ .

Vibroinsulator sleeve works as follows.

The mounting ring flange 5 through the openings of the sleeve isolator is fixed to the platform 6 (Fig. 1), which is a source of vibration loads, and with the help of a bolt 4 is attached to the computing system unit protected from vibration and shock loads 1. When the sleeve is exposed to the vibration isolator 3, vibration and shock loads from top to bottom in the longitudinal direction of the upper (Fig. 2) truncated cone-shaped elastic damping element (UKE) 8 is compressed and the lower UKUE 8 is stretched to the same amplitude. With the reverse impact of loads from the bottom up, the upper UKUE 8 is stretched, and the lower UKUE 8 is compressed. In this case, a significant part of the vibrational energy is dissipated due to the elastic properties of the spirals 13 ₁ and 13 _2. Similarly, when transverse loads are applied to the vibration isolator.

Due to the increased stiffness of UKUE 8, the resonant frequency of the vibration isolator decreases by 1.5–2 times, which is one of the main characteristics of the quality of the vibration isolator. In addition, the spread of the amplitude-frequency characteristics and the coefficient of dynamism is minimal, which ensures the optimal degree of vibration isolation at the attachment points.

Industrial application

Using the materials of the application, the authors developed documentation for shock absorbers AVP ÷ 15M, produced a batch of shock absorbers, tested for axial (tension, compression) UKUE and cantilever loads, and also removed the amplitude-frequency characteristics.

At a rated load of 15 kg, the resonant frequency at an axial load of 15 ÷ 16 Hz is a dynamic coefficient of 3.5 ÷ 4.0 static deflection at a minimum load:

- axial load - 1.8;

- console load - 1.55.

In addition, the minimum overall mass characteristics were obtained.

Thus, the proposed design of the sleeve vibration isolator and the method of its manufacture, as well as the obtained technical characteristics, can be used for vibration isolation, vibration suppression of blocks of computer systems of aircraft.

A manufactured batch of shock absorbers using application materials is being tested as part of an aircraft.

Information sources

1. Patent for utility model No. 95048, IPC F16F 3/08 “Vibroinsulator sleeve” dated 06/10/2010.

2. EP No. 0447294, IPC F16F 1/38 dated 03/05/1991 (Manchon elastique anti-vibratoire notamment pour accouplement d'echapement et procede de realization d'un manchon elastique anti-vibratoire).

3. US patent No. 4514458, NKI 428/222 from 04/30/1985 (SPRING-LIKE MATERIAL FORMED OF COMPRESSED METALLIC WIRE).

Claims (2)

1. Vibration insulator sleeve containing a mounting ring flange with flanges on opposite sides, a pair of cone-shaped elastic damping elements with the same degree of stiffness, made of a spiral wound from a spring metal wire with a pitch between the turns, and the spiral consists of two interconnected links of different diameters, in this case, a link of a larger diameter is wound over a link of a spiral of a smaller diameter, the bases of the cone-shaped elastic damping elements are connected from opposite sides with a fixing ring flange, a central sleeve with protrusions from opposite ends, mounted coaxially with a fixing ring flange and conical elastic damping elements, disk flanges installed from opposite ends of the central sleeve, characterized in that the conical elastic damping elements are truncated with a transition at a larger diameter in the ring the base with a height equal to the height of the flanges of the mounting annular flange, and are firmly fixed to its inner surfaces reliably m adhesive connection, and the smaller bases of the truncated cone-shaped elasto-damping elements are rigidly fixed to the inner surfaces of the dish-shaped flanges and to the flanges made along their perimeters with compression, the truncated cone-shaped elasto-damping elements are made of a spiral wound from a spring metal wire with a pitch between the spiral turns equal to , in the form of an elastic barrel-shaped element with subsequent crimping into a truncated cone-shaped elastic damping element, the spiral being made It consists of a pair of interconnected links with different diameters of a spring metal wire and is laid with an interference fit with a weave, and a link with a larger diameter of the spiral is laid on top of its smaller diameter, while the optimal type of spring metal wire was selected by the EI708AVI brand and its smaller diameter is 0.12 mm, and the larger diameter is 0.2 mm, which allows to achieve the optimal density of the spiral structure of the pressed truncated truncated cone-shaped elastic damping elements of 1.9 ÷ 2.0 g / cm ³ . 2. A method of manufacturing a sleeve vibration absorber, which consists in the fact that the elastic damping element is wound from interconnected metal spirals of different diameters, with a smaller diameter spiral being wound first on a mandrel, and then a larger diameter spiral being wound over it, characterized in that first, before winding both links of the spiral are stretched to a step between the turns equal to the diameter of the corresponding link of the spiral, then the extended links of the spiral are wound on the mandrel crosswise with weaving in ugly barrel-shaped element, with a smaller diameter spiral link being wound dosed with different lengths and filling heights with increasing spiral winding length from the middle and controlled by a counter by the number of mandrel revolutions, then the elastic barrel-shaped element is crimped in the form of a truncated cone-shaped elastic-damping element with a transition at its larger diameter an annular base with a height equal to the height of the flange of the mounting annular flange, while the length of the elastic barrel-shaped element is 2.8 ÷ 2.9 times greater is higher than the height of the truncated cone-shaped elastic damping element, and the larger diameter is respectively 1.2–1.3 times larger than the diameter of the ring-shaped base, the surfaces of the smaller and ring-shaped bases of the truncated cone-shaped elastic-damping elements are connected by reliable adhesive bonding to the inner surfaces of the corresponding disk flanges with perimeter flanges and mounting ring flange, the surfaces to be bonded are previously sandblasted and then degreased vaniem, a truncated cone-shaped elastic-damping elements are impregnated with 100 ml gasoline at 10 ÷ 20 mm ³ 221 CIATIM lubricant.

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