KR101844386B1 - A vibration absorber - Google Patents

A vibration absorber Download PDF

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Publication number
KR101844386B1
KR101844386B1 KR1020150175619A KR20150175619A KR101844386B1 KR 101844386 B1 KR101844386 B1 KR 101844386B1 KR 1020150175619 A KR1020150175619 A KR 1020150175619A KR 20150175619 A KR20150175619 A KR 20150175619A KR 101844386 B1 KR101844386 B1 KR 101844386B1
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KR
South Korea
Prior art keywords
vibration
frequency
dynamic damper
brake
present
Prior art date
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KR1020150175619A
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Korean (ko)
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KR20170068760A (en
Inventor
진봉만
김재홍
지우진
Original Assignee
삼성중공업 주식회사
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Priority to KR1020150175619A priority Critical patent/KR101844386B1/en
Publication of KR20170068760A publication Critical patent/KR20170068760A/en
Application granted granted Critical
Publication of KR101844386B1 publication Critical patent/KR101844386B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B17/00—Vessels parts, details, or accessories, not otherwise provided for
    • B63B17/0081—Vibration isolation or damping elements or arrangements, e.g. elastic support of deck-houses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/30—Mounting of propulsion plant or unit, e.g. for anti-vibration purposes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/04—Frequency effects

Abstract

A dynamic damper is provided. The dynamic damper includes a housing, an elastic member fixedly coupled to the housing inside the housing, a mass coupled to the elastic member, and a brake for restraining or restraining vibration of the mass.

Description

A vibration absorber

The present invention relates to a dynamic damper, more particularly, to a dynamic damper for absorbing vibration of a machine or a ship.

Mechanisms or structures, such as ships, may experience vibration due to operation. This can lead to unwanted noise, or cumulative fatigue at the joints can cause equipment or instrument failure.

In order to absorb such vibration, a dynamic damper is used which absorbs a part of vibration generated by attaching to a machine or a ship where vibration occurs.

Korean Patent Publication No. 10-2015-0010259

However, although the resonance frequency of the object is generally shifted to a different frequency by reducing the natural frequency of the object, it is necessary to completely suppress the resonance at the shifted resonance frequency it's difficult.

When the operating frequency of a ship or machine is changed, for example, when increasing the RPM of a ship, the frequency of the excitation acting on the ship or machine is matched to the shifted natural frequency of the ship or machine to which the damper is attached. , Which has the difficulty of causing unexpected resonance or vibration.

Accordingly, an object of the present invention is to provide a dynamic damper capable of suppressing vibration of a ship or a machine mechanism whose operating frequency is changed.

The problems to be solved by the present invention are not limited to the above-mentioned problems, and other matters not mentioned can be clearly understood by those skilled in the art from the following description.

According to an aspect of the present invention, there is provided a dynamic damper comprising: a housing; An elastic member fixedly coupled to the housing within the housing; A mass coupled to the elastic member; And a brake for restraining or restraining the vibration of the mass body.

The hinge further includes a hinge fixed to the inside of the housing, and a rod rotatably connected to a hinge having one end connected to the mass body and the other end fixed to the inside of the housing.

On the other hand, the brake restrains the rod from rotating relative to the hinge.

According to an aspect of the present invention, there is provided a dynamic asynchronous system including: a dynamic damper attached to an object and including a brake for restraining or restraining a mass coupled to an elastic member; A vibration sensor for measuring an excitation frequency of the object; And the operation of the brake based on the excitation frequency measured by the vibration sensor.

The controller releases the brake when the excitation frequency is within a preset resonance range.

Specifically, when the first resonance range, the second resonance range and the third resonance range are sequentially arranged and the excitation frequency is within the first resonance range or the third resonance range, the brake is activated, And releases the operation of the brake when the frequency is within the second resonance range.

1 is a block diagram illustrating a general dynamic damper structure.
2 is a frequency characteristic graph showing a change in the frequency characteristic according to the dynamic damper attachment.
3 is an exemplary sectional view of a dynamic damper according to an embodiment of the present invention.
4 is a graph of frequency characteristics when the brake of the dynamic damper restrains vibration of a mass according to an embodiment of the present invention.
5 is a graph of a frequency characteristic when the brake of the dynamic damper according to the embodiment of the present invention does not constrain vibration of a mass.
FIG. 6 is a block diagram showing a dynamic damper system composed of a dynamic damper according to an embodiment of the present invention.
7 is a flowchart showing an operation process of the dynamic absorption system according to an embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS The advantages and features of the present invention, and the manner of achieving them, will be apparent from and elucidated with reference to the embodiments described hereinafter in conjunction with the accompanying drawings. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Is provided to fully convey the scope of the invention to those skilled in the art, and the invention is only defined by the scope of the claims. Like reference numerals refer to like elements throughout the specification.

Unless defined otherwise, all terms (including technical and scientific terms) used herein may be used in a sense commonly understood by one of ordinary skill in the art to which this invention belongs. Also, commonly used predefined terms are not ideally or excessively interpreted unless explicitly defined otherwise.

Also, terms used herein are for the purpose of illustrating embodiments and are not intended to limit the invention. In the present specification, the singular form includes plural forms unless otherwise specified in the specification. It should be understood that the terms comprising and / or comprising the terms used in the specification do not exclude the presence or addition of one or more other elements, steps and / or operations in addition to the stated elements, steps and / use. And "and / or" include each and any combination of one or more of the mentioned items.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings.

1 is a block diagram illustrating a general dynamic damper structure.

2 is a frequency characteristic graph showing a change in the frequency characteristic according to the dynamic damper attachment.

Referring to Fig. 1, an exemplary dynamic damper 20 can be attached on a vibrating body 10 where vibrations occur. The exemplary dynamic damper 20 can be interpreted as a vibration system in which the mass M is coupled to the spring S and reciprocating with a constant period. For example, when the vibrating body 10 on which vibration is generated is regarded as one main vibration system, the dynamic damper 20 attached thereto can be interpreted as a supplementary vibration system. By attaching the dynamic damper, the characteristics of the vibration system of the vibrator 10 and the dynamic damper 20 as a whole can be changed.

Referring to FIG. 2, what is shown in the area (a) is the frequency characteristic of the object when the exemplary dynamic damper 20 is not attached. As shown in area (a), an object generally has a typical natural frequency, which is known as a function of the stiffness (elastic) modulus and mass of the object. That is, as shown in the region (a), the mass has the first natural frequency (nf 1 ), and when the object is excited at the same frequency as the first natural frequency (nf 1 ) . ≪ / RTI >

Next, what is shown in the area (b) is the overall frequency characteristic when the exemplary dynamic damper 20 is attached to an object. As shown in the region (b), the object and the dynamic damper as a whole form one main vibration system having a second natural frequency (nf 2 ), and the dynamic damper has an auxiliary vibration system having a third natural frequency (nf 23 ) As shown in Fig. The object to which the dynamic damper is attached can be reduced in the degree of resonance and vibration as compared with the case where the dynamic damper is not attached, but it can still include the possibility of vibration due to resonance.

3 is an exemplary cross-sectional view of a dynamic damper 100 according to an embodiment of the present invention.

3, the dynamic damper 100 according to an embodiment of the present invention includes a housing 102, an elastic member 130, a mass body 112, and a brake 140.

The housing 102 may be formed of a rigid material, such as metal, for example, and may itself serve as a support for supporting the dynamic damper 100 according to an embodiment of the present invention.

The elastic member 130 may be indirectly fixed to the housing 102 directly or via other components.

The elastic member 130 may be, for example, a metal spring, and may be, for example, a coil spring or a leaf spring.

The mass body 112 may be coupled to one end of the elastic member 130. The movement of the mass body 112 can compress or decompress the elastic member 130. Accordingly, the mass body 112 can repeat the reciprocating periodic motion for compressing or decompressing the elastic member 130 at a predetermined frequency or period. That is, the reciprocating period of the mass body 112 inside the housing 102 is determined by the elasticity (stiffness) coefficient of the elastic member 130 and the pendulum of the pendulum (where the pendulum is connected to the rod 110 connected to the mass body 112 and the mass body 112) Sum). Accordingly, the mass body 112 performs a cyclic reciprocating motion for compressing or decompressing the elastic member 130 at regular intervals.

In one embodiment of the present invention, the dynamic damper 100 further includes a rod 110 having one end connected to the mass body 112 and the other end rotatably connected to the hinge 120 fixed to the housing 102 .

Accordingly, the mass body 112 and the rod 110 connected to the mass body 112 may be composed of a pendulum that performs pendulum movement with the hinge as the central axis.

In some cases, the extension length of the rod 110 may be interpreted as being sufficiently long relative to the amplitude of the mass 112, and the mass 112 and the rod 110 may be interpreted as having a linear periodic reciprocating motion .

The brake 140 can restrict the reciprocating motion of the mass body 112, that is, restraining or releasing the vibration. That is, the brake 140 restrains the vibration of the mass body 112, thereby preventing the mass body 112 from cyclically moving inside the housing 102. [ In one embodiment of the present invention, the masses 112 are connected to the rods 110 so that the brakes 140 act on the rods 110 or the friction discs 114 formed at the ends of the rods, Thereby restraining the pendulum motion or the vibration of the pendulum 112. That is, the brake 140 may be a friction type brake or disc brake, and may be a friction type brake 140 that restrains the rod 110 from rotating with respect to the hinge 120. However, the present invention is not limited thereto, and the brake 140 may be a means capable of restraining the movement of the mass body 112 and the rod 110. In another embodiment of the present invention, the brake 140 may comprise a kind of latch, and in another embodiment the brake 140 may be comprised of an electromagnet that acts to increase the friction force by applying a magnetic force.

When the brake 140 restrains the vibration of the mass body 112, the vibration absorber 100 will act only as a mass attached to any object and perform the desired dynamic absorption function, for example, shifting of the natural frequency .

On the other hand, when the brake 140 does not restrain the vibration of the mass body 112, the dynamic absorber 100 according to an embodiment of the present invention acts as a secondary vibration system, so that a desired dynamic absorption function, Shifting of the frequency can be performed.

That is, according to one embodiment of the present invention, the dynamic damper 100 can be operated in two modes of restraining or restraining the vibration of the mass body 112, whereby the dynamic damper 100 can be operated The frequency characteristic can be varied in two modes.

4 is a graph of a frequency characteristic when the brake 140 of the dynamic damper 100 restrains the vibration of the mass body 112 according to an embodiment of the present invention.

5 is a graph of frequency characteristics when the brake 140 of the dynamic damper 100 according to an embodiment of the present invention does not restrain the vibration of the mass body 112. FIG.

4, in the constraint mode in which the brake 140 of the dynamic damper 100 according to the embodiment of the present invention constrains the vibration of the mass body 112, the dynamic damper 100 can be used only as one mass And the object to which the dynamic damper 100 is attached and the dynamic damper 100 can have the fourth natural frequency (nf 4 ) corresponding to the combined mass. The object to which the dynamic damper 100 and the damper 100 are attached exceeds the required allowable value when excited by the first resonance frequency range RR1 which means a certain frequency range from the fourth natural frequency nf 4 It can oscillate with magnitude or amplitude.

5, in the restraint mode in which the brake 140 of the dynamic damper 100 according to the embodiment of the present invention does not restrict the vibration of the mass body 112, The object to which the dynamic damper 100 is attached and the main vibration system constituted by the dynamic damper 100 have the fifth natural frequency nf 5 and the auxiliary vibration system constituted by the dynamic damper 100 is the sixth And may have a natural frequency (nf 6 ). That is, in the restraining mode, the dynamic absorber 100 and the object can have two natural frequencies, and the second resonant frequency range RR2, which is a certain frequency range from the fifth natural frequency nf 5 , the natural frequencies of claim 3 when having the resonance frequency range (RR3), copper reducer 100 and the dynamic damper (100) is attached to the object, which means a certain frequency range from (nf 6) is greater than the tolerance required size or It can oscillate with amplitude.

The object causing vibration may be, for example, a ship whose operating frequency fluctuates from low RPM to high RPM. In this case, even if the dynamic damper 100 is attached to any mechanical device attached to the ship or ship and the frequency characteristic shown in Fig. 4 is changed to the frequency characteristic shown in Fig. 5, There may still be a problem of vibration and vibration due to vibration.

However, according to one embodiment of the present invention, depending on whether the brake 140 is operated, the object to which the dynamic damper 100 is attached may have the frequency characteristic shown in Fig. 4 or the frequency characteristic shown in Fig. 5 The mode can be changed. Accordingly, for example, when the RPM of the ship is a low RPM section or a high RPM section, that is, a frequency section out of the first resonance frequency range RR1, the brake 140 is operated, To have the frequency characteristics as shown in Fig. Or when the RPM of the ship is a frequency within the first RPM range RR1, that is, the second resonant frequency range RR2 and the third resonant frequency range RR3, the brake 140 is deactivated So that the object to which the dynamic damper 100 is attached can have a frequency characteristic as shown in Fig.

Accordingly, the dynamic damper 100 according to an embodiment of the present invention can be attached to an object whose operating frequency is variable, so that it is possible to smoothly perform resonance and avoid excessive vibration.

FIG. 6 is a block diagram showing a dynamic damper system composed of a dynamic damper 100 according to an embodiment of the present invention.

Referring to FIG. 6, the dynamic damping system according to an embodiment of the present invention includes a controller 200, a vibration sensor 300, and a dynamic damper 100.

The dynamic damper 100 corresponds to the dynamic damper 100 according to the embodiment of the present invention described above, and a repeated description thereof will be omitted.

The vibration sensor 300 senses the vibration of the vibrating object and can sense the vibration frequency. For example, the vibration sensor may be a kind of pressure sensor, and may transmit a pressure change due to the vibration to the controller 200 as a vibration signal.

The controller 200 can receive the vibration signal from the vibration sensor 300 and can measure the vibration frequency or vibration frequency which is excited by the object from the vibration signal received. For example, when the vibration sensor 300 is a pressure sensor that senses a pressure change, the controller 200 can detect the peak period of the received vibration signal as the vibration period of the object.

The controller 200 can control whether the brake 140 of the dynamic damper 100 operates according to the measured frequency. For example, the controller 200 may operate or maintain the brake 140 if the measured frequency is not in the first resonant frequency range RR1 of FIG. The controller 200 also determines whether the measured frequency is within the first resonant frequency range RR1 in Figure 5 and if the second resonant frequency range RR2 and the third resonant frequency range RR3 are not, You can unbind or keep the unblocked state.

Thus, in the dynamic damping system according to the embodiment of the present invention, the mode of the dynamic damper 100 can be changed in accordance with the variable exciting frequency, and the occurrence of resonance or vibration can be suppressed.

7 is a flowchart showing an operation process of the dynamic absorption system according to an embodiment of the present invention.

Referring to FIG. 7, the dynamic aspiration system according to an embodiment of the present invention may operate the brake 140 in a low RPM state, for example, at the start of a ship (S10).

Then, the vibration sensor 300 can continuously measure the excitation frequency or the vibration frequency (S20).

Thereafter, the controller 200 can confirm whether the measured excitation frequency or oscillation frequency is within the first resonance range (S30).

If the measured excitation frequency is within the first resonance range, the controller 200 can release (disengage) the brake 140 (S20), and then measure the excitation frequency S20) can be done again.

If the measured excitation frequency is not within the first resonance range, the controller 200 can check whether the measured excitation frequency is within the second resonance range or the third resonance range (S50).

If the measured excitation frequency is within the second resonance range or the third resonance range, the controller 200 can operate or maintain the brake 140 (S60). Then, step S20 of measuring the excitation frequency may be performed again.

If the measured excitation frequency is not within the second resonance range or the third resonance range, step S20 of measuring the excitation frequency can be performed again.

The vibration damping system according to the embodiment of the present invention can continuously confirm the vibration frequency of the object to which the dynamic damper 100 is attached. Accordingly, the frequency characteristic mode of the dynamic damper 100 can be actively changed in response to the fluctuation of the vibration frequency.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, You will understand. It is therefore to be understood that the above-described embodiments are illustrative in all aspects and not restrictive.

100: Dynamic absorber 102: Housing
112: mass body 120: hinge
130: elastic member

Claims (6)

delete delete delete A dynamic damper attached to the object and including a brake for restraining or restraining the vibration of the mass by the elastic member;
A vibration sensor for measuring an excitation frequency of the object; And
And a controller for controlling the operation of the brake based on the excitation frequency measured by the vibration sensor,
Wherein the controller releases the operation of the brake to generate vibration of the mass body when the excitation frequency is within a predetermined resonance range. delete 5. The method of claim 4,
A first resonance range, a second resonance range and a third resonance range are sequentially arranged,
The controller comprising:
When the excitation frequency is within the first resonance range or the third resonance range, activates the brake,
And releases the operation of the brake when the excitation frequency is within the second resonance range.
KR1020150175619A 2015-12-10 2015-12-10 A vibration absorber KR101844386B1 (en)

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Application Number Priority Date Filing Date Title
KR1020150175619A KR101844386B1 (en) 2015-12-10 2015-12-10 A vibration absorber

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KR101844386B1 true KR101844386B1 (en) 2018-04-03

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019014384A (en) * 2017-07-07 2019-01-31 株式会社豊田中央研究所 Vehicle body vibration control device
KR102534272B1 (en) * 2019-01-20 2023-05-17 김상호 A permanent magnet free electric cylinder
WO2021164938A1 (en) * 2020-02-17 2021-08-26 Fm Energie Gmbh & Co.Kg Adaptive tuned mass damper for damping low excitation frequencies

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR200150309Y1 (en) * 1995-05-31 1999-07-01 이해규 Absorbing vibration equipment of gravity pendulum type
JP2004035163A (en) * 2002-07-02 2004-02-05 Mitsubishi Electric Corp Guiding device for elevator
JP2015127261A (en) * 2013-11-26 2015-07-09 三菱電機株式会社 Elevator controller and elevator control method

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR200150309Y1 (en) * 1995-05-31 1999-07-01 이해규 Absorbing vibration equipment of gravity pendulum type
JP2004035163A (en) * 2002-07-02 2004-02-05 Mitsubishi Electric Corp Guiding device for elevator
JP2015127261A (en) * 2013-11-26 2015-07-09 三菱電機株式会社 Elevator controller and elevator control method

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