RU2528969C2 - Method and device of simulation of strike characteristics during practicing strikes on simulators in martial arts - Google Patents

Abstract

FIELD: sports.

SUBSTANCE: method is to convert the strike energy in the elastic deformation of the working part of the device through the transformation of bias ξ of the receiver to the strike load F (ξ) in accordance with the diagram of deformation δ of the split subject under the action of the strike load F (δ). The device comprises a mechanical transducer located between the receiver of strikes and the elastic working part, which is rigidly connected to the receiver of strikes and movably - to the elastic working part. In the proposed method and the device the offset of the receiver of strikes is provided under the action of the strike load, as close as possible to the deformation in destruction of potential objects of strike impact, which enables to simulate using non-destructive method the strike load for using in competitions on breaking solid objects (samples) with hands or feet (test "tamesivari"), and in improving the technique and efficiency of the strikes, strengthening striking limbs, hardening the striking surfaces of the trainees in various types of martial arts, or in the system of army hand-to-hand combat.

EFFECT: increased efficiency of strikes in martial arts, in particular in preparation of martial artists to tests or competitions on breaking solid objects with hands or feet.

6 cl, 7 dwg

Description

1. The technical field

The invention relates to the field of development of simulators designed to increase the effectiveness of strikes in martial arts, in particular when preparing martial artists for tests or competitions in breaking solid objects with their hands or feet (tameshivari test).

2. The level of technology

There are many devices and devices designed for practicing and increasing the effectiveness of strikes - paws fixed on hands, pillows fixed on a wall or racks, training bags (Lyalko V. Trainers in martial arts. Under. Red A.E. Taras. Minsk: Horvest Publishing House, 1998, p. 177-210).

These devices, as a rule, have constant rigidity, therefore the nature (diagram) of the dependence of the shock load on the deformation (displacement) of the device in the zone of contact with the shock limb has the same form (a straight line or an arc close to it). When the kinetic energy of the shock limb is varied, the initial angle of inclination of the diagram is preserved, only the amplitude of the shock load changes.

A well-known sports simulator for practicing the striking technique “Shilov tuning fork” adopted by the applicant for the closest analogue both in terms of the device and the method implemented by this device (utility model patent RU No. 955534 of 07/10/2010).

The known method includes the operation of regulating the level of rigidity of the working part of the simulator, striking the shock receiver, converting the impact energy into elastic deformation of the working part.

The known device comprises a base, a shock receiver connected to an elastic working part, a stiffness regulator of the working part.

A disadvantage of the known method and device is that the simulation of loads in a known manner and device does not ensure the identity of the loads in a wide range of their changes, in particular loads when splitting objects.

In a known manner and device, it is also impossible to reproduce (simulate) shock characteristics (change in shock loads in the process of displacement of the shock receiver) that are completely identical to characteristics in the conditions of destruction of objects, in particular, the specific phase of a sharp shock discharge that exists at the final stage of destruction any objects, especially if it is necessary to set up the equipment and practice the blow in order to split the objects.

3. The invention

3.1. Statement of the technical problem

The technical problem is aimed at eliminating the shortcomings of the known technical solutions by modeling on simulators in a wide range of changes in shock loads, most fully corresponding to shock loads when cracking objects.

In the proposed method and device for its implementation, the shock receiver is displaced under the influence of shock loading, as close as possible to deformation during the destruction of potential shock objects.

The solution to the problem is achieved due to the fact that the simulation of shock loads acting on the shock receiver of the simulator is performed by transforming the displacement of the receiver into deformation of the elastic working part using the transducer and minimizing the influence of inertial effects associated with the movement of cracked objects and the receiver during impacts.

3.3. Enumeration of figures.

The proposed solution is illustrated by the diagrams presented in figure 1 - figure 7:

figure 1 - diagram of the staffing test of destructive impact of a martial artist when splitting solid objects (test "tamesivari"), characterized by a deformation diagram δ during destruction of objects under the action of a load F (δ); figure 2 is a characteristic phased diagram of the change in shock load (F) depending on the deformation (deflection) (δ) of the object when it splits in a standard test; figure 3 is a diagram of a simulator for practicing impacts (prototype diagram) non-destructive method with a shock receiver, mounted on an elastic working part in the form of a cantilever bent beam; figure 4 - a simulator device with simulation of impact characteristics by a non-destructive method with two rigidly fixed and spaced (apart with a gap) flat elastic elements; figure 5 - device simulator with simulation of shock characteristics with spring elastic elements; Fig.6 is a diagram of the deformation of flat elastic elements of the device shown in Fig.4, under the action of loads, with a displacement diagram ξ under the action of the load F (ξ); Fig.7 is a diagram of the balance of forces transmitted from the shock receiver to the spring elastic elements of the device shown in Fig.5, where 1 is the shock receiver, 2 is the rod, 3 is the base, 4 is the elastic element, 5 is the rod; 6 - converter; 7 - upper cone of the converter; 8 - stiffness regulator, 9 - panel, 10 - lower cone of the transducer, 11 - destruction of the object to be broken at the limit value Fp, 12 - supporting elements of the regular power test, 13 - supporting element of the stiffness regulator (arm of the moment of force), 14 - contact with the elastic element 4 of the control element 17 at the limit value of Fp, 15 - hard-fixed connection, 16 - slipping of the transducer 6 between the elastic elements 4 at the limit value of the load Fp, 17 - control element; 18 - zone of elastic deformation in the diagram, 19 - the first stage of fracture of the sample in the diagram; 20 - the second stage of destruction with a sharp discharge of the load on the diagram; F is the load acting on the object to be broken or the shock receiver, Fп is the maximum load on the object to be broken within its elastic deformation, Fp is the maximum breaking load, F (δ) is the functional relationship between the load and the deformation of the object to be broken; F (ξ) is the functional relationship between the load and the shock receiver displacement, R1 is the reaction force of the support element of the stiffness regulator, R2 is the compression force of the elastic element, Rl is the reaction force of the left support, Rp is the reaction force of the right support, δ is the deformation of the object to be broken, δп is the limiting value of the elastic deformation of the object, δр is the maximum deformation of the object in the process of destruction, ξ is the displacement of the shock receiver, the displacement of the transducer, h is the thickness of the flat elastic element, t is the overlap ("overlap") of the transducer and flat GoGo element in the initial state, d - the height of the transducer, L - length of the free (nezaschemlennoy) portions of the flat elastic member, S - distance from the controller to the end part of the elastic plate member under load, α, β - taper angles.

3.4. Features.

In contrast to the known method, the energy of impacts is converted into elastic deformation of the working part by transforming the displacement ξ of the receiver into shock load F (ξ) in accordance with the deformation diagram δ of the split object under the action of the breaking load F (δ).

In this case, transformation can be carried out by a converter providing a predetermined functional relationship between the displacement of the shock receiver ξ, the deformation of the elastic working part and the shock loads F (ξ) acting on the shock receiver. In addition, when implementing the method, it is desirable to ensure that the conditions Mn = 0.4-0.6 Mp, where Mn is the mass of the receiver and the parts of the device moving with it, and Mp is the mass of the item to be destroyed.

In the device for implementing the method of modeling shock characteristics, in contrast to the known between the shock receiver and the elastic working part, a mechanical transducer is formed, profiled in the zone of contact with the working part, the transducer is rigidly connected to the shock receiver and movably with the elastic working part (for converting the displacement impact receiver into deformation of the elastic part with a given load force acting on the receiver), which ensures the transformation of the receiver displacement ξ into shock load F (ξ) in Compliant with the diagram of deformation δ object to be split by the action of the fracture load F (δ).

The elastic working part and the converter of the device can have various options.

In particular, the elastic working part of the device can consist of two elastic elements in the form of flexible flat rectangular plates placed in the same plane at a fixed distance from each other, the plates are cantilevered pressed from the bottom to the panels fastened to the base, the stiffness regulators in the form of pressure bars with the possibility longitudinal movement of the regulators along the plates, the shock receiver is rigidly connected using a rod, which can freely move along the axis, with a profiled transducer in the form of a rectangular plates with a given height, with a longitudinal size of the lower face greater than the distance between the plates and two side faces facing the plates located at a given angle to the vertical, and the plate in the initial state freely rests the lower face on the plates with a certain and the same amount of overlap with each plates.

Also, in particular, the elastic working part of the device can consist of two or several spring-loaded rods axially symmetrical towards each other, integrated in the base, the ends of the rods in contact with the transducer, which in the contact zone with the rods has the form of two truncated cones in series with different taper angles , the angle of the upper cone is less than the angle of the lower cone, the height of the lower cone is chosen equal to the elastic deformation of the destructible object, the total height of the two cones d It must be equal to the maximum deformation of the destructible object, the stiffness regulator is a screw plug with a lead-in section for winding part of the spring elastic element, the spring stiffness is selected so that the maximum load on the shock receiver when it is shifted down is equal to the value of the destructive load on the object.

The method and device allows you to play (simulate) shock loads that occur during the impact destruction of broken objects.

Under the action of the load, the object being broken begins to deform (dashed lines in Fig. 1). The relationship of the load F with the strain (deflection of the central part) δ of the destructible object, for example a board, has three characteristic zones (phases), indicated in Fig. 2 by numbers 18, 19, 20. In the zone of elastic deformation (plot 18), the sample is still destroyed does not start, the deformation grows to a value of δп in proportion to the load to its value of Fп. In section 19 (fracture zone), deformation increases with a slight increase in load. Actually, in this zone the diagram has the form of an arc, which can be approximated by a straight line segment (shelf). After reaching the maximum (destructive) value of the load Fp, corresponding to the deformation δ _p , the phase 20 of a sharp load shedding (shown by a dotted line) occurs. The movement of the shock limb in the conditions of this phase of destruction continues under loads tending to zero.

On the device selected as a prototype (figure 3), you can simulate only the load zone 18 of the destructible element. By changing the position of the stiffness regulator 8 of the elastic working part, it is possible to vary the angle of inclination of the straight line of the diagram in this zone.

Device Example 1

The inventive device with flat elastic elements (figure 4) includes a base 3, a shock receiver 1, an elastic working part, a stiffness adjuster 8 of the elastic working part. The elastic working part consists of two elastic elements in the form of two flexible flat rectangular plates 4, placed in the same plane at a fixed distance from each other. The plates are cantilevered pressed from below to the panels 9, mounted on the base, by the stiffness regulators in the form of pressure bars with the possibility of longitudinal movement of the regulators along the plates. The shock receiver is rigidly connected by means of a rod 2, which can be freely displaced along the axis, with a profiled transducer 6 in the form of a plate with a given height, with a longitudinal size of the lower face greater than the distance between the plates and two side faces facing the plates located at a given angle to verticals. The plate in the initial state freely rests with the bottom face on the plate with a certain and the same amount of overlap with each of the plates.

Device Example 2

A device with spring elastic elements (Fig. 5) also includes a base 3, a shock receiver 1, a rod 2, an elastic working part, a stiffness adjuster 8. The elastic working part consists of two or several spring-loaded rods 5 axially symmetrical towards each other, integrated in the base , the ends of the rods are in contact with the transducer, which in the zone of contact with the rods has the form of two consecutively truncated cones 7 and 10 with different taper angles (the upper angle is less than the lower), the height of the lower Nusa 10 is chosen equal to the value of the elastic deformation of the destructible object, the total height of the two cones must be equal to the maximum deformation of the destructible object, the stiffness regulator is a screw plug 8 with a lead-in section for winding part of the spring elastic elements 4, the spring stiffness must be selected so that the maximum the load on the receiver when it was shifted down was equal to the value of the breaking load.

A device with flat elastic elements (figure 4) works as follows.

At the moment of contact of the shock limb with shock receiver 1, the displacement ξ of the receiver and transducer 6 rigidly connected to it begins. The displacement of the transducer leads to the bending of flat elastic elements with the appearance of interaction forces proportional to the displacement. As the elements (plates) bend, the distance between them increases. Until this distance is equal to the length of the lower face of the transducer, the diagram F (ξ) will be a straight line segment (the first stage of the displacement of the receiver and transducer), similar to section 18 of the diagram of the destructible object F (δ) (Fig. 2). At the next stage of displacement, the side faces of the transducer slip along the ends of the plates. In this case, the plates continue to bend, but the increase in the interaction forces between the transducer and the elastic elements as the transducer is displaced occurs with a smaller gradient than in the first stage. The diagram F (ξ) in the second stage has the form of a straight line having a smaller angle of inclination to the horizontal compared with the plot in the first stage (similar to zone 19 of Fig. 2). When the distance between the ends of the plates is equal to the length of the upper face of the plate, the transducer is forced through the plates with relatively little force, with a sharp decrease in the impact load to zero (like zone 20 in FIG. 2). Thus, using the inventive device, it is possible, unlike the prototype, to simulate the nature of the change in shock load like a diagram of an object being destroyed. By purposefully setting the dimensions of the transducer and setting the level of plate stiffness by the regulator, it is possible to provide, experimentally or by calculation, not only qualitative, but also quantitative identity of the diagrams F (ξ) and F (δ).

The principle of the calculation approach for determining the values of the determining parameters can be explained using the scheme of Fig.6. In this diagram, solid lines show the initial position of the transducer and plates, and dashed lines show their position when the distance between the ends of the plates is equal to the length of the lower edge of the plate, which corresponds to the boundary of the transition from the first stage of the transducer to the second shift. At this boundary, from the conditions for the identity of the diagrams F (ξ) and F (δ), it follows that the displacement of the transducer, equal to the deflection of the plates, should be ξ = δп, and the load on each of the plates is equal to Fп / 2. The amount of overlap t is selected from the condition

t = L-S. For an elastic cantilevered clamped plate of thickness h, width b, and length L, the relationship between the deflection and the load at this boundary is expressed by the well-known formula:

$$\xi =\delta P=2\mathrm{<figure-callout\; id="3"\; label="F\; P\; L"\; filenames="00000006.png,00000007.png"\; state="\{\{state\}\}">F\; </figure-callout>}P{L}^{}{}^3/\mathrm{<figure-callout\; id="3"\; label="E\; b\; h"\; filenames="00000006.png,00000007.png"\; state="\{\{state\}\}">E\; </figure-callout>}b{h}^{}{}^3,(\mathrm{one})$$

where E is the modulus of elasticity of the plate material.

For a specifically selected plate, for example, of a steel alloy with a known modulus of elasticity, it is possible, on the basis of formula (1), to calculate the length of the non-clamped part of the plate that determines the location of the stiffener

$$L=h{\left(\delta PEb/2FP\right)}^{\mathrm{one}/3}(2)$$

If we assume that the shape of the curved part of the plate is close to the arc of a circle, then this part can be considered as half the arc of a segment of height ξ and a chord equal to 2S. In this case, using the well-known formulas for the segment elements, we can calculate the difference between the length of the arc and the chord, which should be equal to the double value of the overlap (2t). By such a value, the length of the lower face of the plate should be greater than the initial fixed distance between the plates. Thus, according to the above calculation scheme, it is possible to determine (select) the parameters of the transducer and the elastic working part, at which the diagrams F (ξ) and F (δ) are identical in the first section. According to a similar scheme, it is possible to determine the height of the plate d and the angle of inclination of its side faces α, at which the required conditions (ξ = δр, F = Fp) are realized at the boundary of the second and third sections.

In a device with spring elastic elements (figure 5), the force on the rod varies in proportion to its displacement. In the particular case of performing the lower cone of the transducer with an angle at the apex equal to π / 2 (Fig. 7), the displacement of the rod in contact with this cone is equal to the displacement of the transducer ξ. To ensure the identity of the diagrams F (ξ) and F (δ), the total height of the transducer d should be equal to δр, and the height of the lower cone (d-с) = δp. The force on each rod in contact with the upper boundary of the lower cone should be equal to Fп / 2, the maximum force in contact with

the upper cone (in the region of its upper boundary) - Fp / 2. The required stiffness k of the spring elastic element can be calculated from the dependence k = Fп / 2δп. The cone angle β of the upper cone should be less than π / 4 (in this case, the slope of the line segment in the second section of the diagram F (ξ) will be less than in the first section). In order to avoid possible ledges in the diagram, the transition boundary of the converter cones should be rounded.

The authors of this application conducted a study of the dependence F (δ) during the destruction using a press of boards made of coniferous wood with typical dimensions of 330 × 210 × 24 mm. According to the research results, the limiting average value of the elastic deformation of the board δp is 6 mm at a load of Fp = 900 N (92 kgf). The maximum deformation of the board δp reaches 14 mm with a breaking load of Fp = 1075 N (110 kgf). In accordance with the calculations according to the above methods, on a device with flat elastic elements, it is possible to provide a diagram F (ξ) close to the diagram F (ξ) for a board, with the following option (other options are possible) the ratio of the dimensions of the transducer (plate) and elastic elements (plates):

 plate size in plan 50 × 50 mm  the angle of inclination of the side faces β 5 °  plate height d 5 mm  plate thickness h (hardened steel 65G) 0.6 mm  plate width b 50 mm  length of the non-crimped part L 25 mm  the amount of overlap of the plate and panel t 2.0 mm

By shifting the regulator, it is possible to smoothly reduce or increase the maximum value of the load at which the transducer is pushed through the plates.

Implementation example.

To verify the claimed technical solutions, a device model was made with flat elastic elements in the form of hardened plates of steel alloy with a thickness of 1 mm and a width of 150 mm. The shock receiver was combined with the transducer and had the dimensions of a broken board. With dimensions of the length of the non-clamped part of the plate 35 mm and the overlap of 2 mm, experiments were carried out to shock punch the transducer through elastic elements with a falling load of 2 kg. By the same method, control tests were carried out with breaking a stack of two boards (according to estimates, at the indicated dimensions of the device model, the impact characteristics of the destruction of such a stack of boards should be reproduced). The experiments showed that the values of the bursting energy of the transducer and the destruction of the boards were close to each other.

The present invention can be used in various types of martial arts or in the system of army hand-to-hand combat in preparation for trials or competitions in breaking solid objects (samples) with hands or feet (tameshivari test), improving the technique and effectiveness of strikes, strengthening shock limbs, hardening shock surfaces.

Claims (6)

1. The method of modeling shock characteristics when practicing blows on simulators in martial arts, including the operations of regulating the stiffness of the elastic working part, striking the shock receiver, converting the energy of the blows into the elastic deformation of the working part, characterized in that the energy of the blows is converted into the elastic deformation of the working part by transforming the receiver bias ξ into the shock load F (ξ) in accordance with the deformation diagram δ of the split object under the action of the breaking load F (δ). 2. The method according to claim 1, characterized in that the transformation is carried out by a mechanical transducer providing a predetermined functional relationship between the displacement of the shock receiver ξ, the deformation of the elastic working part and the shock loads F (ξ) acting on the shock receiver. 3. The method according to claim 1, characterized in that, when implementing the method, the condition Mn = (04-0.6) Mp is provided, where Mn is the mass of the receiver and the parts of the device moving with it, and Mp is the mass of the item to be destroyed. 4. A device for modeling shock characteristics when practicing blows on simulators in martial arts, containing a base, a shock receiver, an elastic working part, a stiffness regulator for the elastic working part, characterized in that a mechanical transducer profiled in the contact zone is placed between the shock receiver and the elastic working part working part, the transducer is rigidly connected to the shock receiver and movably - with an elastic working part. 5. The device according to claim 4, characterized in that the elastic working part consists of two elastic elements in the form of flexible flat rectangular plates placed in the same plane at a fixed distance from each other, the plates are cantilevered pressed from below to the panels fastened with the base, the regulators rigidity in the form of clamping bars with the possibility of longitudinal movement of the regulators along the plates, the shock receiver is rigidly connected using a rod, which can freely move along the axis, with a profiled transducer in the form of a straight line angular plate with a given height, with a longitudinal size of the lower face greater than the distance between the plates and two side faces facing the plates located at a given angle to the vertical, and the plate in the initial state freely rests the lower face on the plate with a certain and the same amount of overlap with each from the plates. 6. The device according to claim 4, characterized in that the elastic working part consists of two or several spring-loaded rods axially symmetrically facing each other, integrated in the base, the ends of the rods contacting the transducer, which in the contact zone with the rods has the shape of two successively truncated cones with different taper angles, the angle of the upper cone is less than the angle of the lower cone, the height of the lower cone is chosen equal to the amount of elastic deformation of the destructible object, the total height of the two cones to be equal to the maximum deformation blasted object regulator stiffness is a screw cap with a lead-in portion for winding part of the spring of the elastic member, the spring stiffness is selected so that the maximum load stress on the bumps receiver during its downward displacement is equal to the value of the breaking load on the subject.

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