JPS5822677A - Vibration interruption type handle device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a vibration-isolating handle device which can be attached to a hand-held vibrating machine such as a tamper-28/mer-drill, and which can reduce the harmful vibrations generated by such machines. This invention relates to a g1 cut-off type handle device that can sufficiently prevent vibrations from being transmitted to a grip member lζ, which is a dollar part.

Conventionally, anti-vibration measures for hand-held vibrating machines such as tampers and electric drills have been made by using elastic or elastic members such as vibration-proof rubber or springs between the vibration source of the vibrating machine and the handle. This was the key to insulating the vibrations by interposing the

However, with this method, it is not possible to expect a vibration insulating effect against violent vibrations of comparatively high frequencies such as those caused by tampering, and it is difficult to prevent harmful vibrations that cause vibration disasters such as white wax. there were. Furthermore, even if a certain degree of vibration insulation effect can be achieved, the use of anti-vibration rubber, springs with small spring constants, etc. will make operation softer, causing the problem that vibrating machines will wobble and cannot be operated properly. Ta.

The present invention has been devised to effectively solve the above-mentioned conventional problems, and an object of the present invention is to:

It is an object of the present invention to provide a vibration isolation type handle device that can almost completely isolate harmful vibrations even though it is substantially rigidly connected to a vibrating machine such as a tamper or a hammer drill.

First, in order to facilitate understanding of the vibration isolation effect of the device according to the present invention, prior to a detailed explanation of the present invention, the principle of the present invention will be explained in comparison with the principle of a conventional vibration isolator.

FIG. 1 shows a principle diagram of the vibration system of a conventional vibration isolator. In the figure, 1 is a vibration source that vibrates in the vertical direction at a frequency ω and an amplitude XI.A cantilever-shaped spring 2 with a spring constant is connected to the vibration source 1, and the free end of the spring 2 , mass M...ndle 3 is provided.

When the vibration source 1 vibrates, this vibration is transmitted to the handle 3 via the spring 2, and the handle 3 is vibrated. If the amplitude of the handle 3 is represented by X, the amplitude - ratio f is expressed as a function of frequency ω by the following equation.

Here, ω7=1 to j, which is the natural frequency of the handle 3. (The vibration response curve of equation 0 is the song 111m in Figure 3.The horizontal axis of the graph in Figure 3 is the ratio (frequency ratio) between the excitation frequency - and the natural frequency -0. does not become small.In other words, the vibration damping effect can only be obtained when the excitation frequency ω is very high.The natural frequency,
If rl- is made smaller, it is possible to have a vibration damping effect even for vibrations with an excitation frequency ω in a lower frequency range, but in order to make rl- smaller by 1.6 stones, K is made smaller 4, or M must be increased. When K is made small,
The operation of the knob 3 relative to the vibration source ICζ becomes soft, causing the vibration source 1 to wobble, and increasing M increases the weight. Turns out it's impossible.

FIG. 2 shows a principle diagram of the vibration system of the present invention. In the vibration system of the present invention, a single impact damper type weight 4 having a mass m is attached to the spring 2 of the conventional vibration absorber shown in FIG. The weight 4 contains a large number of small balls 5 that move while randomly colliding with each other when subjected to vibration.

In the vibration system shown in FIG. 82, the relationship between the amplitude Xi at the point of force U distribution and the amplitude X of the handle 3 of mass M is as follows.

μ is the mass ratio between the mass M of 7 dollars 3 and the quality tm of the weight 4, and μ>'1 (M>m). In addition, k is the spring constant of spring 2 from the excitation point to the attachment point of weight 4, and α
is the spring constant ratio α × 1.

As a specific example, α=0.55. (2
) The vibration response curve of the equation is as shown in FIG. The curve has two resonance points λ! , λ2 (λ1 × λ2). As is clear from the comparison with song #a, it can be seen that the vibration isolation characteristics of song 1jb are extremely superior to song 1ja on the higher frequency side than the resonance point λ2, which is around λ-3.

For example, when λ=10, the amplitude ratio of curve a is approximately 1. .

On the other hand, in the curve, H8ooI of about 8°
This vibration amplitude has decreased.

In the case of a cantilever-shaped spring, the spring constant is K=3E given 3 (E; Young's modulus, Ii moment of inertia), /! , ;
Since α=0.55(=(0,8
2) In 3), the attachment point of weight 4 is 0.821 from the acceleration point.
As a result of numerical calculation to find the optimal value so that the resonance point 22 is on the low frequency side as much as possible, α and μ are respectively O55〈α(0,55゜×μ
It was found that a value of about 3 is good. In other words, if the weight 4 is attached to the spring 2 at a position of about 0.81 from the excitation point, and the mass m is 3 ~ of the mass M of 7 dollars 3, as shown in Figure 3. A vibration response characteristic similar to that of the curve can be obtained.

However, by attaching weight 4, the high frequency side 1
A second resonance point 22 appears and countermeasures are required. The weight 4 vibrates violently at the resonance point λ2. Therefore, instead of making the weight 4 an integrated object, a large number of movable small balls 5 are filled in the weight 4 as shown in Fig. 2, and the small balls 5 violently collide with other small balls 5 at the resonance point. By causing random motion while moving, the peak of the vibration response curve at the resonance point λ21 can be removed, and the vibration energy of the imaging source 1 is converted into thermal energy and absorbed by the collision between the small balls 5. be able to.

In addition, at frequencies above the resonance point 22, the amplitude of the weight 4 becomes small, and the weight 4 vibrates as an integral body, and the curve shown in Fig. 3 becomes equal, resulting in excellent vibration isolation as shown in Fig. 4. characteristics can be obtained.

Below, an example will be shown in which the present invention is applied to Titanpa Ichiban, which is a vibrating machine for putting gravel under sleepers and compacting it for track maintenance work.

In FIG. 5, 10 is a drive motor that vibrates a tamping plate 11 for compacting gravel, and the drive motor 10fζ is equipped with leaf springs f2 and 13, respectively. The tip portions are connected to both end portions of the rod 16, respectively. The leaf springs 12 and 13 are
In order to damp vibrations from the motor 10, it is formed to be appropriately curved as shown in the figure. A grip member 17 serving as a handle is connected to one end of the rod 16.

A vibrating mass 15 is also provided on the leaf spring 12I.

As shown in an enlarged view in FIG. 6, the vibrating mass body 15 is composed of a large number of rigid balls 19 and a split casing 18 serving as a housing section for accommodating these rigid balls 19. hard ball 19
is 80 to 90% of the closest packing inside the casing 18.
When the casing 18 vibrates, the hard balls 19 move against each other (Iζ
A space is formed within the casing 18 for the movement of the rigid ball 19. Furthermore, the hard balls 19 are made of several types with different diameters so that the movement of the hard balls 19 is more random.

In this embodiment, the drive motor 10 is the vibration source,
Board? The folding rack 12 corresponds to the connecting member. Moreover, the rigid sphere 19 is a small mass body.

Next, the operation of this embodiment will be described.

The tamping plate 11 is violently vibrated by the operation of the drive motor 10, and the gravel is compacted by inserting the vibrating tamping plate 11 into the gravel. On the other hand, the intense vibrations of the drive motor 10 are transmitted to the rod via the leaf springs 12 and 13, but in the tamper, the tip of the leaf spring 13 is designed so as not to vibrate. , the rod 16 and the grip member 11 are vibrated up and down using the tip of the leaf spring 13 as a fulcrum.

By the way, when comparing the vibration system of this embodiment with the vibration system shown in FIG. 2, the plate spring 12 of this embodiment corresponds to the spring 2 of FIG. 2, and the grip member 17... corresponds to It can also be seen that the vibrating mass body 15 corresponds to the weight 4.

Therefore, if the mass of the vibrating mass body 15 and its mounting position on the leaf spring 12 are set to optimal values based on the above-mentioned theoretical explanation, excellent vibration as shown in FIG. 3 can be achieved. This shows blocking characteristics.

Furthermore, when the vibrating mass body 15 vibrates the casing 18, the rigid spheres 19 violently collide with other rigid spheres 19 or the wall of the casing 1B, repeating random shooting or movement, so that the original vibration with respect to the resonance frequency of the grip member 17 is , thermal energy (heat generation) is dissipated in the rigid sphere 19 or the casing 18 due to the impact force caused by the collision of the rigid sphere 19.

Therefore, the harmful original vibrations are absorbed by the vibrating mass body 15 without being transmitted to the grip member 17, and ultimately, extremely excellent vibration isolation characteristics as shown in FIG. 4 can be obtained.

In the above embodiment, a spherical rigid body (-sphere 19) was used as the small mass body, but it may be replaced with a ring-shaped steel toric body 22 as shown in FIG. (This may be in the shape of a rond. In short, it is sufficient that the small mass bodies have a large density and collide violently with each other due to the vibration of the casing 18. Depending on the amplitude of the casing 18, etc., the small mass bodies A good vibration insulation effect can be obtained by selecting and adjusting the filling rate, its size, shape, etc. appropriately.Furthermore, as described above, the vibrating mass body 15 is a hard sphere 19.
Since heat is generated by the collision between the rigid ball 19 and the casing 18, the casing 18 is heated as shown in FIG.
Heat dissipation fins 20 and casing 18 wall [this through hole 2] are provided on the outer wall.
1 may be provided to provide a heat dissipation effect. Furthermore, the casing 18 may have any shape.

Below, the results of a vibration experiment of the device of the present invention conducted using the tamper shown in FIG. 5 are shown in FIG. 9A.

Shown in B and C. FIG. 9 A, B, and C are grip members 1, respectively.
7 shows the vibration acceleration transmitted to 7.

9A shows a case where nothing is attached to the leaf spring 12 as in the conventional case, and FIG. 9B shows a case where an integral weight having the same mass as the vibrating mass body 15 is attached at the position of the mass body 15. Furthermore, FIG. 9C shows a vibrating mass body 15 as shown in FIG.
It shows the vibration acceleration when the is installed. As is clear from the figure, in the case of the one-piece weight (this also has a good vibration isolation effect), in the case of the vibrating mass body 15, an even more excellent vibration isolation effect is observed, and It was confirmed that vibration can be almost completely blocked.

As is clear from the above explanation, according to the present invention, harmful vibrations can be almost completely blocked out even though the handle is substantially rigidly connected to vibrating machines such as tampers and hammer drills. The transmission of vibration to the grip member, which is the main part of the grip, becomes extremely weak, making it possible to prevent vibration disasters such as white wax.

[Brief explanation of drawings]

FIG. 1 is a principle diagram showing the vibration system of a conventional vibration isolator, FIG. 2 is a principle diagram showing the vibration system of the present invention, and FIG. 3 is a diagram showing the principle of the vibration system of the present invention. FIG. 4 is a graph showing the vibration response curve of a conventional vibration isolator and the vibration response curve of the device of the present invention, and FIG. 5 is a schematic front view showing an embodiment in which the device of the present invention is applied to a tamper. Figure 6 is a partially cutaway enlarged perspective view of section A in Figure 5;
The figure is a perspective view showing another embodiment of the vibrating mass body, FIG. 8 is a perspective view showing an example of the small mass body, and FIGS. 9A, B, and C show vibration acceleration transmitted to the grip member of the tamper. is a graph showing the measurement results obtained when no vibrating mass body was added to the leaf spring, when an integral weight was added, and when a vibrating mass body was added. - In the figure, 1 and 10 are vibration sources (10 is a drive motor), 2.12 is a connecting member (2 is a spring, 12 is a leaf spring), 3.1T is a grip member (3 is a handle), 4 and 15 are Vibrating mass body (4 is weight), 5, 19.
22G/J% mass body (5 is a small sphere, 19 is a hard sphere, 22 (
The torus 18 is a housing portion (casing). Patent applicant: Makoto Minamidate - Seto - Registered patent attorney: Nobuo Kinutani

Claims (1)

[Claims] A connecting member connected to a vibration source and extending therefrom, a grip member provided at the tip of the connecting member, and an intervening member positioned between the grip member and the vibration source. The vibrating mass body is composed of a plurality of rigid small mass bodies and a housing portion that accommodates each of the small mass bodies while allowing movement of each of the small mass bodies. Features a vibration-isolating type nodle device.