A bilateral magnetic force-driven low reaction force double-body vibration penetration device

Abstract

The present invention relates to a bilateral magnetic force-driven low reaction force double-body vibration piercing device. The upper ends of the first vibration group and the second vibration group of the device are connected by an upper spring, and the lower ends of the first vibration group and the second vibration group are connected by a lower spring. The upper spring and the lower spring are thin plate springs, and the outer ring and the inner ring of the thin plate spring are connected in a vortex shape. The device uses an electromagnet to alternately attract and release the upper armature and the lower armature, so that the first vibration group connected to the upper armature and the lower armature and the second vibration group connected to the electromagnet form relative motion, and the first tool and the second tool alternately impact hard rock in sequence to achieve the effect of breaking hard rock. The present invention solves the problem that existing hard rock drilling devices cannot achieve low power consumption, low heat generation, low reaction force and high tunneling rate.

Description

Technical Field

[0001] The present invention relates to the technical field of hard rock tunneling devices, and particularly to a double-sided magnetic drive type low reaction force double-body vibration penetration device. Background Art

[0002] Hard rock drilling is usually carried out by driving a drill bit with a rotary motor. This drilling method has high energy consumption and a complex structure, and a large amount of heat will be generated during the drilling process, which will damage the physical properties of the internal structure of the rock. The impact work and tunneling rate of the single-sided magnetic drive type low reaction force double-body vibration penetration device are low. Different rocks have different densities. For rocks with high density, not only a vibration penetration device with low power consumption, low heat generation, and low reaction force is required, but also a larger impact work and tunneling rate are needed. However, the existing hard rock drilling devices cannot achieve low power consumption, low heat generation, low reaction force, and high tunneling rate. Summary of the Invention

[0003] Object of the Invention: The present invention provides a double-sided magnetic drive type low reaction force double-body vibration penetration device, aiming to solve the problem that the existing hard rock drilling devices cannot achieve low power consumption, low heat generation, low reaction force, and high tunneling rate.

[0004] Technical Solution:

[0005] A double-sided magnetic drive type low reaction force double-body vibration penetration device, wherein the upper ends of the first vibration group and the second vibration group of the device are connected by an upper spring, and the lower ends of the first vibration group and the second vibration group are connected by a lower spring. The upper spring and the lower spring are thin plate springs, and the overall shape of the thin plate spring is circular, which is divided into an outer ring and an inner ring, and the structure of the outer ring and the inner ring is connected in a vortex shape;

[0006] The first vibration group includes a housing, an upper end cover, a lower end cover, an upper armature, a lower armature, a sensor bracket, and a first tool. The upper part inside the housing is fixedly clamped with the upper armature, the lower part inside the housing is fixedly clamped with the lower armature. The upper end of the housing is fixedly connected with the upper end cover and the sensor bracket in sequence. The outer ring of the upper spring is fixedly pressed between the upper end of the housing and the upper end cover. The lower end of the housing is fixedly connected with the lower end cover, and the outer ring of the lower spring is fixedly pressed between the lower end of the housing and the lower end cover. The end of the lower end cover is fixedly connected with the first tool;

[0007] The second vibration group includes a central column, an electromagnet, an upper spring pressing cover, a lower spring pressing cover, and a second tool. The inner ring of the upper spring is fixedly sleeved on the upper end of the central column, the electromagnet is fixedly sleeved in the middle of the central column, the lower spring is fixedly sleeved on the lower part of the central column, the bottom end of the central column is fixedly connected with the second tool, and there is an initial gap of 1.0 - 2.0 mm between the electromagnet of the second vibration group and both the upper armature and the lower armature.

[0008] Further, the upper end of the central column is threadedly connected with an upper spring gland. A sleeve and an upper spring gasket are sequentially arranged above the top end of the inner skeleton. The sleeve is sleeved on the central column. The upper spring gasket presses the inner ring of the upper spring against the upper spring gland. Below the lower end surface of the central column, a lower spring gland is tightly connected. The lower spring gland presses the inner ring of the lower spring against the lower end surface of the central column.

[0009] Further, the electromagnet includes an inner skeleton, an outer skeleton, a coil, and a packing block. The middle part of the central column is fixedly sleeved with the inner skeleton. The inner skeleton is divided into upper and lower winding areas. Packing blocks are clamped at both the upper and lower ends of the inner skeleton. Coils are wound on both the upper and lower winding areas. An outer skeleton is fixedly sleeved on the outer periphery of the inner skeleton where the coil is wound. The outer skeleton and the inner skeleton are fixedly connected.

[0010] Further, a gap is left between the first tool and the second tool. The outer sides of the first tool and the second tool adopt a zigzag structure. The tops of the first tool and the second tool adopt a cone head structure with a chip removal groove.

[0011] Preferably, there is an initial gap of 1.5 mm between the electromagnet of the second vibration group and both the upper armature and the lower armature.

[0012] The present invention has the following beneficial effects: The device of the present invention has a simple structure, low energy consumption, and is convenient to disassemble. Different from the rotary drilling method, the linear drive generates less heat, and the drilling efficiency is high. The bearing structure is cancelled, and lubrication is not required, so it can be applied to complex environments such as aerospace. The unilateral magnetic force-driven low-reaction force double-body vibration penetration device has a lower impact work and tunneling rate because one side of the magnetic force is used as the driving force and the spring force on the other side is used as the rebounding force, so its application range is limited. By adopting bilateral magnetic force drive, the driving force is provided by the electromagnet on both sides, with a large impact work and a high tunneling rate, a wide practical range, applicable to most hard rocks, and low power consumption, low heat generation, low reaction force and high tunneling rate. Description of the Drawings

[0013] Figure 1 Axonometric view of the embodiment of the present invention;

[0014] Figure 2 Partial cross-sectional view of the embodiment of the present invention;

[0015] Figure 3 Cross-sectional view of the first vibration group of the present invention;

[0016] Figure 4 Cross-sectional view of the second vibration group of the present invention;

[0017] Figure 5 Schematic diagram of the upper spring on the scroll line of the parts of the present invention;

[0018] Figure 6 Schematic diagram of the lower spring on the scroll line of the parts of the present invention;

[0019] Figure 7 Schematic diagram of the driving unit of the present invention;

[0020] Figure 8 Schematic diagram of the machine structure;

[0021] Figure 9 Signal waveform diagram of two vibration groups;

[0022] Figure 10 Working waveform diagram of two vibration groups;

[0023] Figure 11 Relationship diagram of electromagnetic force with current and air gap;

[0024] Figure 12 Relationship diagram of tunneling rate with frequency and duty cycle under 1A current;

[0025] Figure 13 Relationship diagram of tunneling rate with frequency and duty cycle under 1.5A current;

[0026] Figure 14 Relationship diagram of tunneling rate with frequency and duty cycle under 2A current;

[0027] Annotations in the figure: 1. First machine tool, 2. Lower end cover, 3. Lower spring, 4. Lower armature gland, 5. Lower armature, 6. Outer skeleton, 7. Coil, 8. Outer shell, 9. Upper armature gland, 10. Upper end cover, 11. Sensor bracket, 12. Upper anti-collision sleeve, 13. Upper spring gland, 14. Upper spring, 15. Upper spring gasket, 16. Sleeve, 17. Upper armature, 18. Inner skeleton, 19. Cushion wood, 20. Central column, 21. Lower spring gland, 22. Lower anti-collision sleeve, 23. Second machine tool, 24. Electromagnet, 25. Winding area. Detailed implementation manners

[0028] The present invention will be further described below with reference to the accompanying drawings.

[0029] As shown by Figures 1-4 , a bilateral magnetic force driven low reaction force double-body vibration penetration device uses electromagnets to alternately attract and release the lower armature 5 and the upper armature 17 respectively, so that the first vibration group connected to the upper and lower armatures and the second vibration group connected to the electromagnet form relative motion. The upper ends of the first vibration group and the second vibration group of the device are connected by the upper spring 14, and the lower ends of the first vibration group and the second vibration group are connected by the lower spring 3. There is an initial gap of 1.0 - 2.0 mm between the armature of the first vibration group and the electromagnet of the second vibration group. Preferably, there is an initial gap of 1.5 mm between the armature of the first vibration group and the electromagnet of the second vibration group. If the gap is too large, the driving force provided by the electromagnetic force will be too small; if the gap is too small, the impact stroke will be insufficient and the tunneling effect will be poor.

[0030] Working principle: The double-sided magnetic drive double-body vibration penetration device uses electromagnets 24 to alternately attract and release the lower armature 5 and the upper armature 17 respectively, so that the first vibration group connected to the upper and lower armatures and the second vibration group connected to the electromagnets form an alternating impact motion. When the upper coil is energized, the electromagnet attracts the upper armature 17, that is, the second vibration group moves upward, and the first vibration group generates an impact downward; when the lower coil is energized, the electromagnet 24 attracts the lower armature 5, that is, the first vibration group moves upward, and the second vibration group generates an impact downward. The double-sided magnetic drive provides a greater impact work and tunneling rate.

[0031] Both vibration groups of this device are driven to make alternating downward impact motions by electromagnetic forces, and the electromagnetic force is much greater than the restoring force of the spring; the initial gap between the double-sided electromagnets and the upper and lower armatures is 1.5 mm, and the actual distance of each impact is 3 mm from the upper armature to the lower armature. The impact work of this device is much greater than that of the existing devices; therefore, under the conditions of low power consumption and low heat generation, this device can achieve a good tunneling and crushing effect.

[0032] The spring can not only reset but also position, improving the utilization rate of the part functions. During the tunneling process, due to the existence of the spring, a large part of the reaction force will be offset, so the device has good low reaction force characteristics. The upper spring 14 and the lower spring 3 are thin plate springs. The overall thin plate spring is circular, divided into an outer ring and an inner ring, and the structure of the outer ring and the inner ring is connected in a vortex shape; Figure 5 and Figure 6 are the structural diagrams of the upper and lower thin plate springs. This spring is a plate spring different from the traditional spring. This spring is used as a flexible support. Due to its strong radial support ability, it plays a radial positioning role. The spring adopts a vortex wire thin plate spring different from the traditional spring, which has the advantages of small volume, light weight, and large radial stiffness. The thickness of the thin plate spring is 1.5 mm. The vortex wire spring can well avoid stress concentration. The maximum stress of the vortex wire plate spring when it reaches the working limit position is less than the tensile strength of the spring material. And the axial stiffness of the spring is 24 N / mm, and the radial stiffness is 94 N / mm, which can play a good supporting role and has a certain restoring force. Since the working state of the spring required by this device is to deform repeatedly up and down many times, the vortex wire spring has good fatigue life and can meet the working conditions of this device.

[0033] Such as Figures 1-3As shown in the figure, the first vibration group includes a housing 8, an upper end cover 10, a lower end cover 2, an upper armature 17, a lower armature 5, an upper armature gland 9, a lower armature gland 4, a sensor bracket 11, and a first tool 1. The housing 8 is non-magnetic and only serves to support the whole. The upper armature 17 is fixedly clamped at the upper stop of the inner side of the housing 8 and is fixedly pressed by the upper armature gland 9; the lower armature 5 is fixedly clamped at the lower stop of the inner side of the housing 8 and is fixedly pressed by the lower armature gland 4. The upper end of the housing 8 is fixedly connected with the upper end cover 10 and the sensor bracket 11 in sequence. The outer ring of the upper spring 4 is fixedly pressed between the upper end of the housing 8 and the upper end cover 10. The lower end of the housing 8 is fixedly connected with the lower end cover 2. The outer ring of the lower spring 3 is fixedly pressed between the lower end of the housing 8 and the lower end cover 2. The first tool 1 is fixedly connected to the end of the lower end cover 2 by screws.

[0034] As Figures 1-2 shown in Figures 3 and 4, the second vibration group includes a central column 20, an electromagnet 24, an upper spring gland 13, a lower spring gland 21, and a second tool 23. The main body of the second vibration group is the central column 20. The inner ring of the upper spring 14 is fixedly sleeved at the upper end of the central column 20. The electromagnet 24 is fixedly sleeved in the middle of the central column 20. The lower spring 3 is fixedly sleeved at the lower part of the central column 20. The bottom end of the central column 20 is fixedly connected with the second tool 23 by two hexagon socket head cap screws.

[0035] The upper end of the central column 20 is threadedly connected with the upper spring gland 13. An upper anti-collision sleeve 12 is sleeved outside the upper spring gland 13. A sleeve 16 and an upper spring gasket 15 are arranged in sequence above the top of the inner skeleton 18. The sleeve 16 is sleeved on the central column 20; the sleeve 16 is used to press the inner skeleton 18 and make the spring parallel to the upper end of the housing. The inner ring of the upper spring 14 is pressed between the upper spring gasket 15 and the upper spring gland 13. The lower spring gland 21 is pressed and connected by two screws below the lower end face of the central column 20. The inner ring of the lower spring 3 is pressed between the lower spring gland 21 and the lower end face of the central column 20. A lower anti-collision sleeve 22 is sleeved outside the lower spring gland 21.

[0036] The electromagnet 24 includes an inner skeleton 18, an outer skeleton 6, a coil 7, and a spacer 19. The inner skeleton 18 is fixedly sleeved in the middle of the central column 20. As Figure 7 shown in the figure, the inner skeleton 18 is divided into upper and lower winding areas 25. Stoppers are provided at the upper and lower ends of the inner skeleton 18 and the spacer 19 is clamped. The spacer 19 is used to prevent the coil 7 on the inner skeleton 18 from falling off. The gap between the upper and lower winding areas is 8 mm, which can effectively prevent the magnetization generated when the upper and lower coils are energized from affecting each other's areas. Coils 7 are wound on both the upper and lower winding areas 25. An outer skeleton 6 is fixedly sleeved on the outer periphery of the inner skeleton 18 where the coil 7 is wound. The outer skeleton 6 and the inner skeleton 18 are fixedly connected by screws. The inner skeleton 18, the outer skeleton 6, the coil 7, and the spacer 19 form the electromagnet 24.

[0037] A 0.2-mm gap is left between the first tool 1 and the second tool 23 to prevent relative friction between the two tools. As Figure 8 shown, the outer sides of the first tool 1 and the second tool 23 adopt a zigzag structure of 1.5 mm × 1.5 mm, and the tops of the first tool 1 and the second tool 23 adopt a tapered head structure with chip removal grooves. The first tool 1 and the second tool 23 alternately impact the hard rock in sequence to achieve the effect of crushing the hard rock.

[0038] Assembly method:

[0039] The driving mechanism of this device consists of an electromagnet, an upper armature 17, and a lower armature 5. The upper armature 17 and the lower armature 5 are respectively stuck on the shoulders inside the housing 8 and are tightly fixed by an upper armature gland 9 and a lower armature gland 4 respectively. The lower end cover 2 is connected to the first tool 1 by screws. The coil 7 of the second vibration group is wound around an inner skeleton 18 made of soft iron. The inner skeleton 18 protrudes from the shoulders above and below for jamming a spacer 19, and the outer side is fixedly connected to an outer skeleton 6 by screws to form an electromagnet. The electromagnet is sleeved on the central column 20 through the inner shoulder of the inner skeleton 18, and is tightly fixed on the inner shoulder of the inner skeleton 18 in sequence through a sleeve 16, an upper spring washer 15, and an upper spring gland 13. The second tool 23 is connected to the central column 20 by two hexagon socket head cap screws. The upper spring 14 is placed on the upper spring washer 15, is pressed tightly by the upper end cover 10, and is threadedly connected and locked with the central column 20 through the upper spring gland 13. The lower spring 3 is pressed tightly by the lower end cover 2, and the lower spring gland 21 and the lower end face of the central column 20 are fixed by two screws to fix the lower spring 3. The upper spring gland 13 and the lower spring gland 21 are respectively sleeved with an anti-collision sleeve 12 and a lower anti-collision sleeve 22. To provide balanced force, the masses of the first vibration group and the second vibration group are basically the same. The first vibration group and the second vibration group are flexibly supported by the upper spring 14 and the lower spring 3 and are provided with a restoring force. The first tool 1 and the second tool 23 alternately impact the hard rock in sequence to achieve the effect of crushing the hard rock.

[0040] Usage method, the steps are as follows:

[0041] Step 1: Connect a 24-V switching power supply to the two drivers to supply power to the two drivers. The two drivers are respectively connected to the coils 7 wound on the upper side and the lower side of the inner skeleton 18; and one port of the two drivers is connected to the D / A port of DSpace. Use Simulink software to build the working block diagram of this device and control the working conditions of this device through DSpace.

[0042] Step 2: Energize the coils 7 wound on the upper and lower sides of the inner skeleton 18 respectively. There should be a delay in the energization time of the upper and lower coils 7, and the delay time is the time when the square wave signal is 0, or it can be adjusted through the square wave signal. According to different vibration objects, adjust the frequency of the square wave signal to adjust the working frequency of the device, and adjust the magnitude of the current passing through by adjusting the amplitude of the square wave signal.

[0043] During operation, the device drives the first vibration group and the second vibration group through two drivers. The upper coil 7 and the lower coil 7 are energized alternately in sequence. When the upper coil 7 is energized, the coil 7 and the soft iron skeleton form an electromagnet, and the electromagnet attracts the upper armature 17 by magnetic force, that is, the first vibration group makes a downward impact movement. At the same time, the upper spring 14 and the lower spring 3 are axially deformed by force to store energy. When the upper coil 7 is de-energized, the electromagnet returns to its original position by relying on the restoring force of the upper spring 14 and the lower spring 3. Similarly, when the lower coil 7 is energized, the coil 7 and the soft iron skeleton form an electromagnet, and the electromagnet attracts the lower armature 5 by magnetic force, that is, the second vibration group makes a downward impact movement. At the same time, the upper spring 14 and the lower spring 3 are axially deformed by force to store energy. When the lower coil 7 is de-energized, the electromagnet returns to its original position by relying on the restoring force of the upper spring 14 and the lower spring 3. Working repeatedly like this, the first vibration group and the second vibration group move relative to each other continuously, driving the first tool 1 and the second tool 23 at the end to alternately impact the hard rock.

[0044] The two drivers are controlled by the square wave signal of the control block diagram built by Simulink software, as Figures 9-10 , Figure 9 is the signal waveform diagram of the two vibration groups, Figure 10 is the working waveform diagram of the two vibration groups. When the square wave signal is 1, that is, the coil is energized; when the square wave signal is 0, that is, the coil is de-energized. Among them, the first vibration group is directly fed with the square wave signal, and there is a certain phase difference between the square wave signals of the two vibration groups. The second vibration group adds a delay signal relative to the first vibration group to ensure that the energization drives of the two vibration groups alternate with each other. After the first vibration group starts working by being fed with the square wave signal, the second vibration group starts working by being fed with the square wave signal after a delay for a period of time, that is, the first vibration group and the second vibration group work alternately.

[0045] The time when neither the first vibration group nor the second vibration group is energized is represented by the duty cycle of the square wave signal, that is, 1 - 2*(duty cycle). When the duty cycle is 50%, the time when neither of the two vibration groups is energized is 0%; when the duty cycle is 40%, the time when neither of the two vibration groups is energized is 20%. Adjust the frequency of the square wave signal to adjust the working frequency of the device, and adjust the magnitude of the current passing through by adjusting the amplitude of the square wave signal.

[0046] When ensuring that the electromagnet is not magnetically saturated, the greater the current, the greater the electromagnetic force. However, the wire diameter of the coil affects the magnitude of the current that can be passed through. This device uses a copper coil with a diameter of 0.38 mm, and the maximum input current does not exceed 2 A. The magnitude of the frequency is determined by the resonance frequency of the rock to be broken. The duty cycle is used to determine the interval time between the energizations of the two vibration groups, leaving a certain interval time to ensure that the vibration group returns to the initial position relying on the restoring force of the spring.

[0047] Figure 11 This is a graph showing the relationship between the electromagnetic force (i.e., the driving force) of this device and the current and air gap. At a certain current, the smaller the air gap between the upper and lower armatures and the electromagnet, the greater the electromagnetic force used as the driving force. The smaller the air gap, the greater the electromagnetic force (driving force), that is, the greater the force towards the tunneling direction, which is beneficial to improving the tunneling effect. This device uses the electromagnet to separately attract and release the upper and lower armatures to achieve the impact purpose, and relies on the electromagnetic force as its driving force. Figure 11 This is a graph showing the relationship between the electromagnetic force of this device and the current and air gap. The greater the current, the greater the driving force of this device. At a certain current, the smaller the air gap between the upper and lower armatures and the electromagnet, the smaller the electromagnetic force. The smaller the working air gap, the greater the driving force of this device, that is, the greater the force towards the tunneling direction; within one working cycle of this device, the greater the tunneling depth, the greater the driving force, which is beneficial to improving the rock-breaking effect of this device.

[0048] To verify the tunneling and rock-breaking ability of this device, analysis is carried out through experiments. By adjusting different currents, frequencies, and different duty cycles, tunneling and rock-breaking experiments on refractory bricks with a certain strength are conducted. Figures 12-14 These are the relationships between the tunneling rate of this device and the frequency and duty cycle when passing currents of 1 A, 1.5 A, and 2 A respectively. Among them, when the current amplitude is 1 A, the duty cycle is 50%, and the tunneling frequency is 50 Hz, the tunneling rate is the highest, which is 13.5 mm / min. When the current amplitude is 1.5 A, the duty cycle is 40%, and the tunneling frequency is 40 Hz, the tunneling rate is the highest, which is 16.5 mm / min. When the current amplitude is 2 A, the duty cycle is 40%, and the tunneling frequency is 30 Hz, the tunneling rate is the highest, which is 17.8 mm / min. The parameters of an input current amplitude of 2 A, a duty cycle of 40%, and a frequency of 30 Hz are the optimal tunneling parameters.

Claims

1. A bilateral magnetic force-driven low-reaction double-body vibration penetration device, characterized in that: The upper ends of the first vibration group and the second vibration group of the device are connected by an upper spring (14), and the lower ends of the first vibration group and the second vibration group are connected by a lower spring (3). The upper spring (14) and the lower spring (3) are thin plate springs. The thin plate spring is circular as a whole and is divided into an outer ring and an inner ring, with a vortex connection structure between the outer ring and the inner ring; The first vibration group includes a housing (8), an upper end cover (10), a lower end cover (2), an upper armature (17), a lower armature (5), a sensor bracket (11) and a first tool (1). The upper part inside the housing (8) is fixedly clamped with an upper armature (17), and the lower part inside the housing (8) is fixedly clamped with a lower armature (5). The upper end of the housing (8) is sequentially fixedly connected with an upper end cover (10) and a sensor bracket (11). The outer ring of the upper spring (14) is fixedly pressed between the upper end of the housing (8) and the upper end cover (10). The lower end of the housing (8) is fixedly connected with a lower end cover (2), and the outer ring of the lower spring (3) is fixedly pressed between the lower end of the housing (8) and the lower end cover (2). The end of the lower end cover (2) is fixedly connected with a first tool (1); The second vibration group includes a central column (20), an electromagnet (24), an upper spring gland (13), a lower spring gland (21), and a second tool (23). The upper end of the central column (20) is fixedly sleeved with the inner ring of the upper spring (14). The middle part of the central column (20) is fixedly sleeved with an electromagnet (24). The lower part of the central column (20) is fixedly sleeved with a lower spring (3). The bottom end of the central column (20) is fixedly connected with a second tool (23). There is an initial gap of 1.0 - 2.0 mm between the electromagnet of the second vibration group and both the upper armature (17) and the lower armature (5); The upper end of the central column (20) is threadedly connected with an upper spring gland (13). Above the top of the inner skeleton (18), a sleeve (16) and an upper spring gasket (15) are arranged in sequence. The sleeve (16) is sleeved on the central column (20); The inner ring of the upper spring (14) is pressed between the upper spring gasket (15) and the upper spring gland (13). A lower spring gland (21) is tightly connected and pressed below the lower end face of the central column (20), and the inner ring of the lower spring (3) is pressed between the lower spring gland (21) and the lower end face of the central column (20); The electromagnet (24) includes an inner skeleton (18), an outer skeleton (6), a coil (7), and a packing block (19). The middle part of the central column (20) is fixedly sleeved with an inner skeleton (18). The inner skeleton (18) is divided into two upper and lower winding areas (25), and packing blocks (19) are clamped at both the upper and lower ends of the inner skeleton (18). Coils (7) are wound on both the upper and lower winding areas (25). An outer skeleton (6) is fixedly sleeved on the outer periphery of the inner skeleton (18) where the coil (7) is wound. The outer skeleton (6) and the inner skeleton (18) are fixedly connected.

2. The double-sided magnetic force-driven low-reaction force double-body vibration and penetration device according to claim 1, wherein: There is a gap between the first tool (1) and the second tool (23). The outer sides of the first tool (1) and the second tool (23) adopt a zigzag structure, and the tops of the first tool (1) and the second tool (23) adopt a cone head structure with a chip removal groove.

3. The bilateral magnetic force-driven low-reaction force double-body vibration penetration device according to claim 1, wherein: There is an initial gap of 1.5 mm between the electromagnet of the second vibration group and both the upper armature (17) and the lower armature (5).

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