Vibro-impact tool with ultrasonic excitation

 

(57) Abstract:

The invention relates mainly to manual instruments with ultrasonic agitation for vibro-impact surface treatment, accompanied by plastic deformation. Vibro-impact tool with ultrasonic excitation includes a housing, an elastic vibration protection strip, the excitation source consisting of a magnetostrictive transducer and waveguide transformer is located inside the housing and having regard to him the possibility of the reciprocating stroke, and the clip with strikers mounted coaxially with the waveguide transformer, and an air cooling system. The excitation source is fixed in the sleeve installed on a related body sliding guides, while between the outer surface of the bushing and the inner surface of the housing has a gap. This increases the functional efficiency of the instrument while reducing harmful vibration exposure of the operator. 1 C.p. f-crystals, 10 ill.

The invention relates mainly to manual instruments with ultrasonic agitation for vibro-impact surface treatment, accompanying athelney (scanning) relaxation-hardening and passivating treatment, for example, the heat-affected zones and joints welded joints, surfaces of steel structures exposed to atmospheric, water and soil corrosion, as well as for stamping, riveting, removing scale and rust, chipping, dismantling mechanical joints with strong interference, such as a shaft sleeve and a screw-nut, particularly subjected during operation of the corrosive effect.

Known tool for hardening of steel parts vibrating ball [1]. Kinematic scheme of this tool suggests an oscillatory movement of the ball-striker between the workpiece surface and the source of vibration excitation, representing electroacoustic magnetostrictive transducer connected to the acoustic waveguide transformer, to the working end of which a ball-PEEN is pressed by means of a spring mechanism.

To achieve the specified lower technical result prevents the following. This tool requires a fixed position relative to the workpiece surface with the presence of a well-defined gap between the ball and the surfaces on which he performs oscillatory peremeshenie hold a fixed position would be difficult. In the absence of a fixed position can occur simultaneous mechanical contact between the workpiece surface, the ball-striker and the working face of the excitation source, regardless of the phase of the oscillatory displacement of the latter, which will be the nature of the collisions.

Sources of energy for each collision in the process of repeated shocks (multidrop process) in this case will be:

movement of the center of mass of the tool in the direction of the shock, if there is a positive component of the gravity vector in this direction;

symmetric, elastic vibrations of the excitation source relative to the nodes of the standing acoustic waves initiated it electroacusticas Converter;

external force applied to the tool body is the force with which the operator presses the tool to the processing object, doing work against the forces of inertia of the tool as it "bounces" after each collision with the surface.

In the process, the energy of the collisions is allocated on the treated surface, where it produces the work of plastic deformation, and the instrument in the form of kinetic energy once ATSC what oratorum, holding the tool during operation and representing to him the external force. This may cause the operator vibration disease. The harmful effects of vibration will be greater, the greater will be the amplitude or magnitude 2 vibrational forces transmitted through the instrument.

Known megabaytovy tool for ultrasonic impact treatment of welded joints [2], which can be used as manual [3, 4] , consisting of a source of excitation of the ultrasonic magnetostrictive transducer with the hub and attached the working body in the form of glass (clip) into which is inserted deforming elements (tools, jaunty) in the form of a stepped cylindrical rods with freedom of axial movement, and held from falling out of the cage by thickening on the inner end. In operation the tool is pressed against the processing surface so that some of the strikers is in mechanical contact with its outer end with the treated surface, and an inner, thicker end with an end face of the hub (acoustic waveguide transformer), that is, due to its rigidity transmits energy source wosb the rebound of the tool at the expense of the energy of the collision, which has not trashdolls on the plastic deformation and movement of the object and is part of the kinetic energy at the beginning of the collision is proportional to the square of Newtonian coefficient of restitution R:

E = 0,5 um2impR2,

where vimp- the speed of the tool at the beginning of the occurred collision;

m is the mass of the instrument.

The absence of this instrument cushioning and damping elements determines the same drawback as that of the previously described analog - excessive rigidity, causing a weak vibration protection. In moments of repeated mechanical contact elements of the tool between themselves and with the object being processed through the system hard links: die - hub - acoustic junction (mount of the excitation source to the housing in the plane of the node vibrational displacement of the acoustic waveguide transformer) - case, the operator will feel the vibration. It should be noted that when the tool during operation is held or moved relative to the object to be processed using any technical means, excluding the part of the operator, harmful vibrazioni.

Known hand-held ultrasound tool (prototype) to strain hardening and relaxation treatment [5], containing the excitation source in the form of a magnetostrictive transducer rigidly connected with the transformer oscillatory velocity (acoustic waveguide transformer), placed in a sealed housing with a lid. Free volume between the inner wall of the housing and the excitation source is used for circulation of cooling fluid through which it is removed and carried away the heat generated during operation of the excitation source. In this tool to reduce vibrations, as high - and low-frequency arising at work and affecting the operator, the excitation source is connected with the tool body by means of elastic sealing rings located between it and the tool body near the plane of the node vibrational displacement of the transformer vibrating speed. In addition, the tool is provided with pnevmoskleros installed in the cover in alignment with the transducer, on which he leans back end. The source of excitation is the possibility of axial reciprocating movement, in which e is and pneumonia acts as shock absorber. The length of this travel set size pnevmostartery.

Factor hindering the achievement of specified following technical result when using this taken as a prototype of an ultrasonic impact tool, is based on the fact that the lower level of vibro-impact loads experienced by the operator when working with this tool, is achieved mainly due to the dissipation of kinetic energy bounces on the viscous friction and the sliding friction of the elements of its design. It is ineffective against vibration protection and, in addition, reduces the mechanical coefficient of performance (COP) of the instrument.

This circumstance can argue as follows (Fig.1, 2). When working vibro-impact tool with ultrasonic excitation can be distinguished elementary cycle single blowc[0,tr,2] consisting of a stage of mechanical contact of the tool with the object being processed and the phase in which this contact is missing, and Boiky can freely and chaotically to vibrate without exerting force action on any object or tool, as they have negligible mass. The period of time of mechanical contacti[t0the center of mass will change its direction of motion [ti,1, ti,2] . The period of rebound is also divided into two similar phase [ti,2, tr,1] and [tr,1,tr,2]. Period of timea[tr,1, t*i,1], where t*i,1the time inversion of the velocity vector that characterizes the movement of the movable part of the instrument to the object, ad[ti,1, tr,1]- from object. The first is characterized by the dissipation of part of the kinetic energy of the rebound and transformation of another part of the potential energy, which in the second period of time is doing work for the resumption of mechanical contact is required for the next stage of energy transfer of the excitation source through jaunty, that is, moves the tool toward the workpiece object.

Mechanical model describing the influence of the properties of structural elements taken as a prototype tool for the reaction F(t) held by the operator in the case of this tool, can be represented in the form of circuit shown in Fig. 3. It should be noted that the magnitude of the displacement x of the movable part of the tool is small and comprise, for example, 0.04 to 2 mm depending on the phase of the oscillatory speed of the working end face of the waveguide transformer during Nacho offset 20 μm, the amplitude of the oscillatory velocity of 4.5 m/s, the module of elasticity of the processed material 21011N/m2and the radius of curvature of the working surface brisk 2.5 mm, which can be calculated using, for example, the model hit Hertz-Sterman [6, 7]. The elastic element 1 in the diagram - absorber - presents shear elasticity seals and elastic resistance pnevmostartery its deformation. The latter is mainly the stiffness of the shell pnevmostartery, as it may change under the pressure of the end face of the excitation source its shape, little by changing its volume. The damping properties of the structure are characterized by cataracta 2, which is represented by the friction in the gland seal and the internal friction in the coolant, accompanying the change of its volume inside the housing under the action of the reciprocating movements of the excitation source. It is clear that this volume change creates additional flow of coolant in the channels of the cooling system, as the fluid is an incompressible substance. Due to friction on the seals and internal friction in the coolant is the dissipation of kinetic energy of the rebound. The shock absorber and damper (cataract) skachivaemoe on the elastic deformation of the shock absorber is stored in the form of potential energy. Efforts to overcome the friction on the elements of the system is lost as heat. In the period of time of removal of the center of mass of the moving parts of the tool from the object is also the transformation of a part of its kinetic energy to potential energy as the coolant inside the housing has a static excess pressure Pexldue to which, obviously, to overcome the hydraulic resistance of the channels of the cooling system its running. In a period of rapprochement with the object stored energy position and the shock absorber is spent on restoring the original volume of fluid between the excitation source and the body of the instrument. Performed in this work is also work against the forces of viscous friction of the coolant in the channels of the cooling system and sliding friction on the seals. Thus, to protect the operator from vibration impact loads is here largely due to the dissipation of kinetic energy within the system during its insignificant accumulation. This tool along with the loss of energy loses its functional efficiency. It is obvious that increasing this efficiency is possible in such a system only by increasing gestkoe. This will inevitably entail an increase in the vibration exposure of the operator.

Known electroacoustic transducers with air cooling, which can serve as excitation sources for ultrasonic impact tool [8] . However, information describing the design of vibro-impact tools, air cooled, not detected. Using the same design of the prototype without its changes with air cooling of the excitation source instead of the water will not get the expected technical result as a lip seal used in the prototype, including to prevent leakage of the cooling liquid can act as a guide reciprocating movement only with significant friction losses. Tightness, provide seals for air cooling unnecessary.

It is known that the efficiency of multigenic processes depends on the energy conservation in the system and the maximum with the minimum scattering [7]. In the case of systems with ultrasonic excitation of high dissipative coefficient of the tool can lead to the degeneration of the system with "free" brisk in with kontaktnyh processes more effective at reducing harmful vibration impacts are elements with higher mechanical compliance.

The technical result is an increase functional efficiency of the instrument (mechanical efficiency) while reducing harmful vibration exposure of the operator or the technical means to control the operation of the tool if it is used as part of the technical system. The result is achieved by changing the mechanical schematic and design tool so that while ensuring energy recovery rebounds in the process was provided and increased mechanical flexibility of moving the movable part relative to the body.

This technical result of the invention is achieved in that in the known vibro-impact tool with ultrasonic excitation, comprising a housing, a source of excitation, consisting of series-connected electro-acoustic magnetostrictive transducer and waveguide acoustic transformer is located inside the housing and having regard to him the possibility of the reciprocating stroke of a given length, the clip with strikers mounted coaxially with the acoustic waveguide transformer and cooling system, the cooling system of the air, and istochniku the outer surface of the sleeve and the inner surface of the housing has a gap. Sliding guides is made in the form of pins, which are incorporated into the slots of the housing and at least one of them laid in a groove in the sleeve, and the length of the groove in the sleeve greater than the length of its guide on the magnitude of the reciprocating stroke of the excitation source.

In the claimed tool (Fig.4) elastic element I, physically represented by the elasticity of the air inside the enclosure, which is in contrast to the coolant of the prototype is compressible medium. The role of the friction element, similar to the corresponding element of friction of the prototype, which is the energy dissipation, performs the element II, represented by parts of the structure, providing a slide with a reciprocating movement of the sleeve relative to the housing guide, and the viscosity of the air. It is clear that this element of friction significantly reduces the force of friction compared to cataracta prototype containing a sealing device, as the latter also performs the role of seals and these two functions conflict with each other in terms of accomplishing its objectives, and the air compared to water can be considered as a viscous environment. Elastic and viscous elements in the schema are included in series is a, may, with time to relax at the expense of the messages of the internal space of the tool with the surrounding space through the gap between the housing and the sleeve, i.e. the movement of the movable part of the instrument is the sum of the deformations of the shock absorber and damper. Thus, the work done in the prototype, as against elastic resistance to deformation of the components of the system, and against the frictional forces on them, which depend on the strain rate, this is mainly against resistance elements having a greater ductility, that is basically against the pressure and elasticity of the air. Under high strain rates that occur in the area of the object of the invention (see Fig. 1, 2) it favors the accumulation of energy in the system and its recovery. This achieves the efficiency of the tool.

In relation to vibration protection properties to show the materiality of the differences between the claimed tool from the prototype allows a quantitative comparative analysis of the solutions of the differential equations of motion of the centers of the movable mass relative to the reaction forces still held corps. Because of prototype, the displacement of the movable part is equal to the strain amortizatio the account of the differential equations of motion for them will be accordingly:

,

,

where m is the mass of the moving parts of the tool;

- coefficient of friction damper;

D is the rigidity of the shock absorber.

The corresponding solutions of the equations of motion relative to the reaction force with regard to static forces, ensuring the clamping of the tool to the object during operation:

,

,

where

constants;

the reaction force at the beginning of the rebound;

v=-vimpR is the velocity of the center of mass of the movable part at the beginning of the rebound;

Pex[q]- excess air inside the claimed tool;

Pex[l]- excessive pressure of the coolant in the case of the prototype;

S - the area of the piston - moving parts of the tool in the plane of the seals in the prototype and in the plane of the guides have declared tools;

Fpn- power pressure pnevmostartery at the end of the transducer excitation source from the prototype.

The value of the rigidity of the pneumatic shock absorber of the claimed tool moves within the xmax- maximum distances rebound, which, as noted above, for real instruments with ultrasonic excitation units are millimeters, can be nom.

The force characteristic of the shock absorber in such small movements can rely linear. Let the power of the static pressure on the moving parts from the gas and the liquid from the prototype and the claimed instrument is equal. In other words, in the case of the prototype instead of the fluid is air, which exerts on the movable part of the same pressure as the coolant together with pnevmoskleros. However dampers and friction coefficients of cataracts, the initial velocity and mass of the moving parts of the compared tools are also equal. This formulated the least favorable conditions for a comparison of the claimed device, which makes the comparison results are unconditional.

Graphs of F(t) for the prototype (number of curves: 1 - at = 10 kg/s; 2 = 15 kg/c; 3 = 20 kg/s and the claimed instrument (number of curves: 4 - at = 10 kg/c; 5 - at = 15 kg/c; 6 - when = 20 kg/c is shown in Fig. 5. Thus D = 130 kg/s2; m = 1,53 kg; v =3.5 m/s; PexqS = Pexl+Fpn=60 H.

From the graphs it is seen that ceteris paribus, in a time interval of t= 100 MS greater than the actual value cycle (see Fig. 1,2), the values of the reaction forces of the body more to the mechanical scheme of the 2 - if = 15 kg/c; 3 = 20 kg/c;

Fixed and variable components of the reaction forces of the body have the form, respectively:

,

,

where average values of response communications at the destruction of the center of mass of the tool from the object and intimacy with him respectively,

< / BR>
the corresponding impulses.

The selected criteria comparison - difference fixed and variable components - can be written as functions of the duration of cycle

,

.

The variable component of the reaction is vibrating force acting on the operator through the restraint of the tool during operation: the handle housing. Therefore, the second expression which is a function of the difference of the vibration forces of the prototype and the claimed tool, characterized by improved vibration protection properties of the tool when using the claimed design.

The graphs of the functions Fst() and () are given in Fig.7 and 8, respectively, for the same parameters as F(t) and F(t). All the curves in the graphs lie above the time axis and it is shown that the static force and vibration force, which will test the operator when working with vibro-impact tool, the prototype certainly higher than the declared invenia absolute values, shown in the graphs are the smallest possible. That is, the analysis shows the advantages of only mechanical diagram (Fig.4) of the claimed device. If to take into account the quantitative differences in real settings, such as: the difference between the viscosities and densities of the cooling fluid and air; the coefficients of friction in the seals, designed essentially for seals and guides, which are devices to reduce friction, and to consider the exclusion from the scheme of the rigidity of pnevmostartery, the benefits will be more significant.

From the foregoing it is seen that in the claimed tool vibration exposure of the operator, of course, is reduced, which also meets the required technical result.

Thus, a comparison of the claimed tool prototype, which is essentially the closest analogues of the technical solution, characterizing known to the applicant, the prior art shows that the tool has a set of distinctive features, significant in relation to the specified technical result.

Fig.1 is a graph of the audio signal recorded when working savingon MK-6 with a frequency of 44 kHz and a sound card Sound Blaster 16 Pro Creative Labs., with the following parameters:

the mass of the moving parts of the tool 1,53 kg;

- applied force 60 N;

the amplitude of oscillatory displacement 17 microns;

- the oscillation frequency of 22 kHz;

the material of the object to be processed steel SP;

the radius of curvature of the working surface brisk 2.5 mm

Fig. 2 - fragment multicargo process duration T, selected from the graph in Fig. 1 the increase of the time scale and illustrating the phase of the cycle the shock process.

Fig. 3 - scheme of mechanical design adopted for the prototype of vibro-impact tool with ultrasonic agitation.

Fig. 4 is a diagram of a mechanical model of the claimed design of vibro-impact tool with ultrasonic agitation.

Fig. 5 - graphics time functions reaction forces corps of vibro-impact instruments with ultrasonic agitation, collected under the scheme of the prototype (1, 2, 3) and the claimed tool (4, 5, 6) with the parameter values used in the calculation:

the mass of the moving parts of the tool 1,53 kg;

- speed in the beginning of the rebound to 3.5 m/s;

- applied force 60 N;

- the stiffness of the shock absorber 130 kg/s2;

the coefficients of friction for cataract curves 1,4-10 x instruments with ultrasonic agitation, collected under the scheme of the prototype and the requested tool. Parameter values are the same. Coefficients of friction for cataract curves 1-10 kg/s; 2-15 kg/s; 3-20 kg/s

Fig. 7 graphic functions according to the difference of the permanent components of the reaction forces for vibro-impact instruments with ultrasonic agitation, collected under the scheme of the prototype and the claimed tool from the cycle time of a single blow. Parameter values are the same. The coefficients of friction cataract (damper) for curves 1-10 kg/s; 2-15 kg/s; 3-20 kg/s

Fig.8 graphic functions according to the difference of the vibration reaction forces for vibro-impact instruments with ultrasonic agitation, collected under the scheme of the prototype and the claimed tool from the cycle time of a single blow. Values of parameters and constants are the same. Coefficients of friction for cataract curves 1-10 kg/s; 2-15 kg/s; 3-20 kg/s

Fig.9 is an example of the General appearance of the claimed design of vibro-impact tool with ultrasonic excitation. The ratio of the conditional.

Fig.10 - the same cross section.

Declared vibro-impact tool with ultrasonic excitation (Fig.9, 10), includes a housing 1, the excitation source consisting of posledovati) 2 and the waveguide acoustic transformer 3, located inside the housing and having regard to him the possibility of the reciprocating stroke of a given length L1race 4 with 5 strikers and the air cooling system.

The tool differs in that the excitation source is fixed in the sleeve 6, is located inside the housing with a gap 7 and the sliding guides 8, made in the form, for example, rectangular keys, which are incorporated in through the slots of the housing 9, and at least one of them laid in a hollow groove 10 in the sleeve, and the length of the groove in the sleeve exceeds the length of its guide on the magnitude of the reciprocating stroke of the excitation source inside L1. In the above example, the construction of the instrument has three guide - pins and all three laid in corresponding slots in the sleeve.

Napravlyayus are held in end-to-end the body groove worn in it by the casing 11, which is fixed with curly nuts 12. Freeplay L2the sleeve is additionally limited by a spring-damper 13.

Cooling air is supplied through the orifice 14, which is secured in one of the two channels 15, available at the base of the handle of the tool 16. The second end of the channel screwed W which constitute together with the gap 7 between the sleeve and the casing of the air cooling system of the excitation source.

Through the second channel in the base of the handle removed wires 18 electroosmotic excitation source.

In the handle 16 of the tool is a switching device with a trigger switch 19 system remote start-stop ultrasonic generator supplying the excitation source.

The excitation source is fixed in the sleeve, screwed in her transition pipe 20, the flange 21 of the waveguide acoustic transformer through the elastic strip 22.

Clip 4 strikers 5 screwed on the other end of the reducer by means of a cap nut 23 held together by a retaining ring 24, and able loosened the nut to be rotated at a desired angle relative to the handle of the tool. In the design of the holder is fixed relative to the excitation source in the axial direction motionless, as the second analogue. The clip can also be attached to the body, as is done in the prototype.

For convenience of Assembly of the tool casing consisting of two parts connected by a plug connection 25.

The tool works as follows.

After the filing of the cooling air which enters the toolbar is it through the gap 7 between the housing 1 and the sleeve 6, the movable part of the tool, consisting of a source of excitation 2,3, sleeve 6, of the reducer 20, the strips 22, the holder 4 with the nut 23 and the locking ring 24, the progressive moves in the direction from the housing under the action of excess pressure arising inside the instrument. Rotational movement of the sleeve within the housing, which could result in entanglement and breakage of the lead wires 18 electroosmotic excitation source, prevents keyed connection, consisting of the guides 8, the grooves 9 in the housing and 10 in the sleeve. The length of longitudinal travel of the movable part of the instrument is limited to the value of L1that the length of the slots in the sleeve is greater than the length of the guides. This eliminates the loss of the movable part of the tool from the housing under the action of excess pressure of air inside the instrument.

After starting the generator by pressing the trigger switch 19 excitation source 2,3 begins to oscillate relative to the nodes of the vibrational displacement of the standing wave, one of which is in the plane of the flange 21. In this case, if the contact of the front (working) end of the waveguide transformer 3 with 5 strikers missing, missing and vibray wave, offset relative to the center of its mass. From the transverse high-frequency vibrations caused by transverse oscillation mode of the source, a housing secured shear elasticity of the elastic strips 22.

If the tool body, for example, through the handle 16 and the casing 11 of the applied external force, the source, jaunty and the object to be processed are in mechanical contact with a force equal to the external force. Under these conditions, as described above, is initiated multiday process. If the external force exceeds the force of the air pressure on the movable part of the tool, resulting in a free play of the L2<Lis selected, the inner end of the sleeve 6 is in mechanical contact with a spring shock absorber 13. The total stiffness of the shock absorber is increased by the value of the stiffness of the spring, thereby attenuated shock loads on the guide and the inner edges of the slots when the rebound.

Since the middle of each collision, the energy stored in the system during impact due to the elasticity which is in mechanical contact with the object to be processed, striker (Boykov) 5 and the excitation source 2,3, return is displaced is a, and in the case of "choice" free running L2- pressure on the shock absorber 13, while working against the elastic forces, i.e. the transformation of the kinetic energy of your moving mass in the potential energy of their situation. When this part of the work done against friction on the guides 8. Part of the volume of air in the instrument, when it is displaced through the gap 7 between the casing and the sleeve. This process takes place practically without energy dissipation, since the viscosity of air is small. After the force of air pressure (or air pressure and spring shock absorber) will balance the force of inertia of the moving parts of the tool, the air inside will begin to restore its original volume, giving the Bush and all that therein is fixed, the acceleration of the opposite sign. In this part of work will also be done against friction. It is clear that the pulses of the reaction force of the tool body when removed from the object and intimacy with him will not be equal. The difference of average values of reaction forces will scale vibrational forces experienced by a stationary part of the tool housing and respectively holding it by the operator. But, as shown above, this force is less than the PR is 2">

The most favorable mode of operation of the instrument is such that when the operator shall hold the tool within the free motion of the movable part of the L2. In this case, against the inertia of the moving parts of the tool during its rebound will only friction and air pressure and spring force will be excluded from the process.

Generally stated, the tool can operate in three modes:

1. The most favorable mode without the participation of the spring, which was mentioned above - nominal mode.

2. The mode in which the free play of the L2selected and participates elasticity of the spring shock absorber.

3. The mode in which the entire course of L1selected and there is no attenuation and damping of shock and vibration impact load is transmitted to the operator through almost hard link: die 5 - waveguide transformer 3 - flange 21 gasket 22 to the outer edges of the grooves 10 of the sleeve 6 of the guide 8 to the inner edge of the grooves 9 of the case 1 - case 1 - arm 16 and the casing 11. This mode is similar to the second of the analogues.

It is obvious that the size of L1and L2should be selected so as to provide the operator the ability to easily implement mode AC go into mode 3.

In the proposed tool can also be used in other technical means of protection of the operator beyond the claims of the present invention:

1. Use the design of the circuit breaker remote start generator-triggered mode 2.

2. Mechanical restriction of free running due to the length Boykov, for which the ferrule with the strikers must be secured to the tool body, as is done for the prototype.

In the second case, you can refuse the use of a spring shock absorber at all, but you lose some of the benefits associated with the loss of the stationary form of the profile of the working body of the tool - holder with the strikers. This can make it difficult to use when handling certain objects with the developed surface relief.

Sources of information

1. Mukhanov, I. I., Y. Golubev M. Hardening of steel parts ball, vibrating with ultrasonic frequency // Bulletin of engineering. - 1966. - 11. - S. 52-53.

2. Badalyan Century BC , Kazantsev C. F., Statnikov E. W., ( E. M. the Mechanism of ultrasonic impact treatment of welded joints // Bulletin of engineering. - 1979. - 8. -S. 56-58.3.

3. RF patent 20ptx2">

6. The [Y. N. Mechanics of deformable solids. - M.: Nauka, 1988. - 712 S.: ill.

7. Panovko J., introduction to theory of mechanical shock. - M.: Nauka, 1977. - 224 S.

8. Ultrasonic technological kits type USTC 18/22. Technical conditions TU 3444-001-01172039-95. State reregistration room 012/002248.

9. Vagapov I. K. Nonlinear effects in ultrasonic processing. - Minsk: Science and technology, 1987. - 159 S.

10. Bykhov I. I. fundamentals of theory of vibrating equipment. - M.: Nauka, 1969.2

1. Vibro-impact tool with ultrasonic excitation, comprising a housing, an elastic vibration protection strip, the excitation source consisting of a magnetostrictive transducer and waveguide transformer is located inside the housing and having regard to him the possibility of the reciprocating stroke, and the clip with strikers mounted coaxially with the waveguide transformer and cooling system, characterized in that the cooling air, and the excitation source is fixed in the sleeve installed on a related body sliding guides, while between the outer surface of the bushing and the inner surface of the housing has a gap.


 

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