KR101512122B1 - Pendulum type friction damper - Google Patents

Abstract

Disclosed is a pendulum type frictional damper which prevents scratches on a sliding contact surface between the members; smoothly operates; and prevents the components from moving against each other as a moving prevention guiding target part and a moving prevention guiding part are arranged to prevent a frictional contact member and a concave member from moving against each other. The frictional damper comprises: a hollow part which accepts at least part of the concave member inside to allow the concave member to move in an inclined direction of the concave surface of the concave member; and a hollow guiding member joined to an elastic pressurizing unit to prevent the elastic pressurizing unit from moving with the concave member in the inclined direction of the concave surface by grasping the elastic pressurizing unit. The hollow guiding member is made of engineering plastic.

Description

[0001] The present invention relates to a pendulum type friction damper,

The present invention relates to an improvement of a damper, and more particularly, to a damper which is installed between two structures, such as a pier and a bridge deck, which are allowed to move relatively relative to each other so as to buffer and absorb shocks acting between two structures, The present invention relates to an improvement of a pendulum type friction damper which can be suitably used for supporting a pipe of a piston.

Recently, the intensity and frequency of earthquakes are increasing worldwide, and the importance of seismic design of major facilities such as bridges, buildings and nuclear power plants is increasing. Especially, when a large displacement occurs in the piping directly connected to the safety of a nuclear power plant, it can cause a great problem of the power plant. There is an increasing need for piping support technology to prevent damages caused by piping damage.

The vibration damping system for supporting the piping of the nuclear power plant as described above requires a buffering mechanism to stably support the piping to the supporting structure and to prevent damages of the piping by buffering and absorbing impact force such as earthquake.

In general, the oil buffer mechanism used in bridges is designed to move the oil filled cylinder and the cylinder in order to buffer and absorb the impact force acting between the two structures due to earthquakes and the like while receiving a constant load acting slowly between the two structures. A piston connected to the piston, and a piston connected to the orifice.

Such a conventional oil buffer mechanism is difficult to manufacture, maintain and repair because it has to keep the oil tightness in the cylinder, and thus is expensive and is not suitable for use in a nuclear power plant requiring stable performance over a long period of time.

In addition, since the viscosity of the oil is highly influenced by the temperature change, the conventional oil buffer mechanism is disadvantageous in that the performance varies depending on the temperature.

In addition, the conventional oil buffer mechanism has a problem that the shock absorbing performance is insufficient.

Also, the conventional oil buffer mechanism has a problem that it is difficult to adjust the damping performance.

The conventional oil buffer mechanism is disadvantageous for use as a device for supporting piping and the like of a nuclear power plant because of the disadvantages described above.

A registration docket for registration No. 10-1200692 (a friction damper, inventor Cho, Young-chul, reason, hereinafter referred to as "pre-registered invention") has been developed to solve the problems of the oil buffer mechanism. By way of citation of this prior-filed invention, the disclosure of which is incorporated herein by reference in its entirety as prior art.

The present inventor has found that the friction damper of the present invention solves all the problems of conventional oil buffering mechanisms and exhibits excellent performance and is suitable for use in supporting a piping of a nuclear power plant. However, There is a possibility of occurrence of shaking due to the initial clearance and abrasion of the contact surface. In the case where the metal parts on both sides of the contact part are not smoothly operated and scratches are generated and when trying to prevent scratches, And it is recognized that there is a need for improvement in productivity due to the provision of the sliding friction material at the friction portion.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a friction damper capable of suppressing the initial clearance between contact members, the initial clearance between the inner surface of the elongated hole formed on the surface member and the shaft member contact surface, .

It is another object of the present invention to provide a friction damper in which sliding contact between members is made smooth and the contact surface is not scratched so that the behavior is smooth.

Another object of the present invention is to provide a friction damper which can reduce the time and manpower required for installing a separate friction material.

Still another object of the present invention is to provide a friction damper having a bearing element suitable for piping support.

A pendulum type friction damper according to the present invention is a pendulum type damper comprising: a concave member having a concave surface having an inclined surface arranged on at least one of an upper surface and a lower surface; A frictional contact member having a convex curved surface formed thereon and allowing the concave member to move in a direction in which the concave surface is disposed in an oblique direction and a frictional contact member for elastically pressing the frictional contact member against the concave surface, And elastically pressing means for increasing the frictional force of the member so as to exert a force which interferes with movement of the concave member in the direction in which the concave surface is inclined with respect to the friction contact member,

And a hollow portion for accommodating at least a part of the concave member and allowing the concave member to move in a direction in which the concave surface is disposed in an inclined manner, wherein the elastic pressing means is engaged with the elastic pressing means such that the concave surface is inclined And a hollow guide member for holding the elastic pressing means so as not to move together with the concave member in a predetermined direction,

The hollow guide member is characterized by being made of engineering plastic.

The hollow guide member is provided with a connection portion,

The hollow guide member is divided into left and right parts, and two split bodies formed with coupling grooves at one end of which coupling parts are coupled are coupled with a coupling means in a state of interposing a part of the coupling parts into the coupling grooves, .

Wherein the concave member is formed with a flow preventing surface provided along a direction in which the concave surface is disposed obliquely,

The friction contact member may be provided with a flow preventing guide portion which is coupled to the inside of the flow preventing face to guide the inside of the flow preventing face.

Wherein the inside of the flow prevention surface is an elongated hole provided in the concave member in a direction in which the concave surface is inclined,

The flow prevention guide protrudes from the first convex curved surface and is inserted into the slot to prevent lateral movement of the concave member and guide the movement of the concave member in the longitudinal direction of the slot,

The elastic pressing means comprises:

A shaft member vertically passing through the slot;

An elastic body coupled to the outer circumferential surface of the shaft member and disposed outside the friction contact member with respect to the concave surface;

An elevating member coupled to the outer peripheral surface of the shaft member such that the elevating member can move up and down relative to the outer surface of the shaft member; And

And a pressing member coupled to the shaft member to press the elevating member against the elastic body.

A cover member is provided between the elastic body and the friction contact member so as to be movable up and down on the outer peripheral surface of the shaft member,

Wherein the cover member is formed with a semi-cylindrical recessed groove having a radius of curvature smaller than that of the rivet, which allows rotation of the friction contact member on a contact surface with the friction contact member, and wherein the first convex surface of the friction contact member A second convex surface having a radius of curvature corresponding to the concave groove is formed in the surface,

It is preferable that the guide member is provided with an elevation guide portion for guiding the up and down movement of the friction contact member and the cover member in a direction perpendicular to the moving direction of the concave member.

The friction contact member is preferably made of engineering plastic.

The friction contact member may be an ultrahigh molecular weight polyethylene (UPE) that does not have a separate sliding friction plate on its surface.

Wherein the concave surface is formed on both the upper surface and the lower surface of the concave member,

Wherein the frictional contact member includes an upper friction contact member contacting the upper surface side surface of the concave member and a lower friction contact member contacting the lower surface side surface of the concave member and vertically symmetrical with the upper friction contact member,

The elastic pressing means includes an upper elastic member and an upper elastic member for resiliently pressing the upper friction contact member against the concave member, a lower elastic member for elastically pressing the lower friction contact member against the concave member, It is preferable that the lifting member is provided.

An upper cover member is provided between the upper elastic member and the upper friction contact member so as to be movable up and down on the outer peripheral surface of the shaft member,

Wherein the upper cover member is formed with a concave groove having a radius of curvature smaller than that of the irregular surface that allows the upper friction member to rotate on the bottom surface thereof and that the upper surface of the upper friction member has a radius of curvature A second convex surface is formed,

A lower cover member coupled between the lower elastic member and the lower friction contact member so as to be movable up and down on the outer peripheral surface of the shaft member,

Wherein the lower cover member has a concave groove with a radius of curvature smaller than that of the lower surface of the lower cover member so as to allow rotation of the lower friction contact member on the upper surface and corresponds to the concave groove of the lower cover member on the lower surface of the lower friction contact member A second convex surface having a radius of curvature is formed,

Wherein the guide member is provided with a lifting / lowering guide portion for guiding upward and downward movement of the friction contact member in a direction perpendicular to the moving direction of the concave member,

The elevation guide portion also guides upward and downward movement of the upper cover member and the lower cover member in a direction perpendicular to the moving direction of the concave member,

And the second convex surface is a semi-cylindrical curved surface.

With respect to piping support, various devices are used for existing vibration and earthquake. The pendulum-type friction damper according to the present invention as described above is mainly related to a conventional snubber, different.

Conventional shock absorber (snubber) has a characteristic that when it is subjected to a constant temperature change, it performs a cushioning operation while a very small load is applied, and when the fast load such as an earthquake acts, it locks up within a very small displacement I have.

However, the pendulum type friction damper according to the present invention differs from the conventional snubber in its characteristics, and acts as a damper for dissipating the acting load while causing a certain displacement.

According to the present invention, there is provided a flow prevention surface for preventing flow between the frictional contact member and the concave member and a flow prevention guide for guiding the flow prevention surface, so that the components constituting the device are not shaken.

According to the present invention, a sliding contact surface between members does not cause a scratching phenomenon, and a close contact state can be maintained between the members, so that the behavior is smooth.

According to the present invention, the second convex curved surface is formed into a semi-cylindrical curved surface shape, so that the horizontal movement that occurs during the movement is minimized.

Industrial Applicability According to the present invention, since engineering plastic, especially ultra high molecular weight (UPE) having no friction plate on its surface can be used as a friction contact member, productivity and time and manpower for attaching a sliding friction plate can be reduced and productivity can be improved.

1 is a perspective view of a pendulum type friction damper according to the present invention,
Fig. 2 is a partially broken perspective view of the pendulum type friction damper shown in Fig. 1,
FIG. 3 is a longitudinal sectional view according to II of FIG. 1,
Fig. 4 is a plan sectional view taken along the line JJ in Fig. 1,
5 is a perspective view of the friction contact member,
6 is a perspective view of the cover member,
7 is a perspective view showing a state in which a pendulum type friction damper according to the present invention supports a pipe.

Before describing the embodiments of the present invention, experiments and studies conducted by the present inventors in connection with the present invention will be described.

Experimental and research contents of the present invention

1. FCD EUT Design

 end. FCD product

1) FCD (Friction concave damper): Anti-vibration system using principle of friction pendulum

2) After checking the performance of the EUT type,

3) Optimization of equipment with EUT Type 1, 2, 3

4) Design and manufacture stage of EUT

○ Design and manufacture of EUT Type 1 ~ 3

   I. Design and manufacture of EUT Type 1

1) EUT Type1 design

     ○ FPB (Friction Pendulum Bearing) Design of spring element to realize the vertical load on the friction pendulum structure

     ○ The shape of Type1 of EUT consists of 4 elements in total

     Four factors: - Friction pendulum element, which is the part where damping and restoring forces are realized.

                    - a spring element that implements a vertical load

                    - a compression clamping element that fixes the compression of the spring

                    - connecting elements connecting them

Figure 1. FCD Type1 Configuration

Figure 2. FCD Type1 Damper Construction

Type 1 device property Type1 Description Upper curvature 800 mm Lower curvature 200 mm MER-
Spring Outer diameter 43 mm Inner diameter 14 mm Height 26 mm Design displacement 100 mm Yield value 2.3 kN Effective stiffness 0.167 kN / mm

2) Manufacture of EUT Type1

     ○ Production drawings of Type 1

Figure 3 - 1. FCD Type1 Production Drawing 1

Figure 3-2. FCD Type1 Production Drawing 2

     ○ Production of Type 1

Figure 4. Production of FCD Type1

    All. Design and manufacture of EUT Type2

1) Design and manufacture of EUT Type2

     ○ Since Type 2 shape applies the principle of friction pendulum, it is the same as Type 1 that the device is composed of 4 elements.

     ○ Four elements: Friction pendulum element which is the part where attenuation and restoring force are realized.

                    Spring elements that implement a vertical load

                    A compression-fixing element for fixing the compression of the spring

                    Connecting elements connecting them

     ○ Type2 improvements

- Improved rolling resistance on the plate and body

- Removal of laminate from urethane

- Increase the length of MER-Spring for smooth behavior and decrease rigidity

- Decrease R value to prevent warping

Figure 5-1. FCD Type2 Configuration

Figure 5-2. FCD Type2 structure diagram

Type 2 device property Type1 Description Upper curvature 800 mm Lower curvature 200 mm MER-Spring Outer diameter 43 mm Inner diameter 14 mm Height 50 mm Design displacement 100 mm Yield value 2.8 kN Effective stiffness 0.170 kN / mm

2) Production of EUT Type2

     ○ Production drawings of Type 2

Figure 6. Production Drawing of Type 2 FCD Product

 ○ Production of Type2

Figure 7. Production of FCD Type2

  la. Design and manufacture of EUT Type3

1) Design and manufacture of EUT Type3

     ○ The configuration of the total 4 parts of the shape of Type 3 is the same as Type 1 and 2

     Four factors: - Friction pendulum element, which is the part where damping and restoring forces are realized.

                    - a spring element that implements a vertical load

                    - a compression clamping element that fixes the compression of the spring

                    Connecting elements connecting them

     ○ Improvements in Type3

- Two-stage configuration of the body minimizes the movement when moving

- In previous types, since the cylinder and cover are both made of iron, it is not smooth and scratching occurs. Therefore, Type3 is replaced with engineering plastic to reduce the resistance to slip to induce smooth behavior.

- In order to make the behavior more smooth than Type 2, the R value is reduced to form a hemispherical shape to minimize the number of horizontal movements

- Combine bearing and friction material

- Material of friction element: UPE

Figure 8. FCD Type3 Shape

Figure 9. Structure of FCD Type3

Type 3 device property Type1 Description Upper curvature 1000 mm Lower curvature 25 mm MER-
Spring Outer diameter 45 mm Inner diameter 12.5 mm Height 40 mm Design displacement 85 mm Yield value 4.8 kN Effective stiffness 0.170 kN / mm

Figure 10. FCD Type3 Production Drawing

Figure 11. FCD Type3 production

 2. Analysis of FEM of EUT

   end. FEM analysis EUT selection

     ○ Determined by Type3, the most optimized design among FCD products

     ○ EUT Type 3

- The body of the device has a two-stage structure, minimizing the occurrence of the movement

- Use spring elements to implement upper vertical loads that induce frictional forces.

- The R value of the spherical surface is the shape of the hemisphere.

- Bearing made by UPE

- Apply the principle of gravitational friction pendulum through induced friction

     ○ Type 3 design variables

Type 3 design variables division Contents Ansys  ABAQUS Upper curvature 1000mm Lower curvature 25mm 20mm Spring stiffness 1,565 N / mm Spring Line Compression Amount 22mm Coefficient of friction 0.12 Design displacement ± 85mm

Figure 12. EUT shape (Type 3)

   I. Ansys Device Interpretation

     ○ Analysis of the part where the behavior occurs

- Analysis of behavior of FCD by analysis of behavior through Ansys v15.0

- Part of the behavior analysis: The part where the actual damping and restoring force of the general friction pendulum damper is implemented

- Boundary condition: Center Rod and Cylinder are allowed to move in parallel direction and fixed to the vertical direction of face.

- Load condition: Apply 40mm forced displacement to center rod

Figure 13. Behavior analysis part of the device

Figure 14. Device boundary conditions

- Contact conditions

■ Apply Frictional Condition to Center Rod and Cylinder which contact bearing

■ Center Rod & Bearing Contact Condition

Frictional Condition; Center Rod = Target Surface

                     Bearing = Contact Surface

                     Frictional coefficient = 0.12

■ Cylinder & Bearing Contact Condition

Frictional Condition; Cylinder = Target Surface

                     Bearing = Contact Surface

                     Frictional coefficient = 0.12

Center Rod-Bearing Bearing-Cylinder Cylinder-Spring

Center Rod-Bearing Bearing-Cylinder Cylinder-Spring

Figure 15. Surface contact condition of device - Mesh calculation

 - Mesh calculation

■ If it is too short, close to the correct solution, but because it takes a long time and speed,

■ Use square elements for mapped faced meshing for speed and accuracy

Figure 16-1. Mesh shape of the device 1

Total Figure

Figure 16-2. Mesh shape of device 2

Number of Nodes and Elements per Part division Center Rod Bearing Cylinder Spring Node 2508 1242 1052 371 Element 1500 935 1462 240

- Ansys analysis result

Figure 17. Ansvs analysis result Stress comparison

Ansys analysis result Stress comparison division SM490 Center Rod Yield strength The tensile strength Allowable stress Stress 333.367 510.133 210 33.04 Safety factor - 6.4

■ Stress distribution shows symmetrically selected stresses. The maximum stress of the center rod is 33.04MPa, which is 6 times higher than the allowable stress.

■ Even stress distribution is judged to be good for durability of friction pendulum damper

Figure 18. Behavior equation of frictional pendulum damper and comparison of load hysteresis curve of analysis result

Comparison of design value and analytical value division Exam conditions EDC
(kN · mm) K _eff
(kN / mm) Nonlinear design value Displacement 40mm 774.073 0.172  Ansys interpreted value 767.263 0.170 error - 0.8% One%

■ EDC and k _eff are 0.8% and 1%, respectively, when compared with the design value by the theory of behavior and Ansys analysis value.

■ Analysis results of displacement of FCD device

Figure 19. Comparison of Ansys analysis results of displacement-dependent devices

Figure 20. Analysis and design value comparison at 20mm

Figure 21. Analysis and design value comparison at 40mm

Figure 22. Analysis and design value comparison at 90mm

Analysis result by displacement Test Type Qd ( kN ) EDC ( kN · mm ) K _eff ( kN / mm ) Damping (%) Translate design error Translate design error Translate design error Translate design error 20mm 4.8 4.9 2% 374.5 377.2 One% 0.286 0.288 One% 52.0 52.2 0% 40mm 4.9 4.9 0% 767.3 774.1 One% 0.170 0.170 0% 44.9 45.4 One% 90mm 4.9 4.9 0% 1896.1 1878.6 One% 0.119 0.118 One% 31.4 31.3 0%

■ Analysis results of displacement of FCD device

ㅇ Perform analysis by displacement to check the behavior characteristics of the device due to displacement

ㅇ Load hysteresis curve for 20mm, 40mm, 90mm behaves in the same way

When the displacement increases, the Qd is the same, but as the secondary stiffness increases from 0.046 to 0.065 as the stiffness becomes 90 mm, it is judged that the hardening occurs due to the increase of the displacement

ㅇ To show the validity of the nonlinearity of the behavior theory, ansys analysis value and design value with increase of displacement

ㅇ The error between the interpretation value and the design value is less than 2% at maximum, proving the validity of the behavior theory for the nonlinearity of the device.

■ Analysis result of spring surface pressure of FCD device

Figure 23. Comparison of Ansys analysis results for each device with spring pressure

Analysis results by surface pressure Test Type Qd
(kN) EDC
(kN mm) K _eff
(kN / mm) Damping
(%) 5mm compression 2.2 359.706 0.082 43.6 11mm compression 4.9 767.263 0.170 44.9 30 mm compression 13.1 2046.984 0.446 45.7

ㅇ Perform analysis to check the behavior characteristics of compression spring of device spring

ㅇ spring As a result of analysis on compression length of 5mm, 11mm, 30mm for 40mm, yield value

ㅇ The larger the compression amount, the lower the friction coefficient

ㅇ The behavior tendency according to the compression amount of the device spring was confirmed, and it is predicted that the friction coefficient decreases as the spring compression amount increases

     ○ Ansys analysis of non-behavioral part

- Interpretation part: the part of the structure where no behavior occurs, excluding the friction pendulum part in the FCD device.

- Boundary condition: The plug is used to fix the device to the tester using the bar.

- Load condition: Bearing load is applied to the maximum load that occurs because the load generated in the behavior is received at the cylinder position.

Figure 24. Boundary conditions for non-behavior devices

- Contact conditions and mesh calculation

■ Contact conditions

The Friction Pendulum is a cover part that catches the pendulum.

■ mesh calculation

Since there is no nonlinear element, it is not necessary to fine-tune the mesh (set to coarse size)

- Ansys analysis result

■ Displacement distribution

ㅇ The result of the analysis of the cover part of the device shows that the displacement occurs according to the direction of the bearing force force.

ㅇ As in the stress distribution, the end of the cover in the cylinder section is vulnerable to the load, but the fracture due to the maximum load does not occur.

■ Stress distribution

ㅇ Concentration of stress in support part

ㅇ Since the force is applied in the x direction, the stress is concentrated at both ends because the support suppresses the displacement due to the force.

ㅇ Compared with the maximum stress in the stress concentration area and the allowable stress of SM490 steel, the FCD device has a safety factor of 6

Ansys analysis result Stress comparison division SM490 Plug Cylinder Yield strength The tensile strength Allowable stress Stress 333.367 510.133 210 35.326 23.181 Safety factor - 5.9 9.1

Stress distribution Displacement distribution

Stress distribution

Figure 25. Non-behavior analysis result

Figure 26. Non-behavioral stress distribution over time

     ○ Device Analysis Conclusion

- Comparison with Ansys analysis to demonstrate the behavior of the device

- Design values according to behavioral theory and analysis results by finite element analysis show very close difference within 2%

- Confirm the reliability of the device by securing the safety factor 6 against the maximum stress occurring during the behavior through device analysis.

   All. ABAQUS device interpretation

    ○ Analytical model

Using the general purpose program ABAQUS

Figure 27. Analytical model

Figure 28. Model Details

Analytical material properties Anti-vibration component Modulus of elasticity (MPa) Poe Songbi Cap 205,000 0.3 Spring 42.5 0.46 Bearing Plate 205,000 0.3 Bearing 4000 0.4 Body 4000 0.4 Center Shaft 205,000 0.3 Concave Plate 205,000 0.3

    Contact conditions

Since the anti-vibration device acts as a component of several components, the definition of the contact surface is important in the analysis.

Figure 29. Definition of friction on contact surfaces

Contact surface conditions Contact surface definition Coefficient of friction Concave Plate - Body 0 Concave Plate - Bearing 0.12 Bearing - Bearing plate 0.12 Bearing plate - Spring 0 Spring - Cap 0 Center shaft - Cap, Spring, Bearing, Bearing plate 0

○ Load condition

Load condition introduced displacement control method

Figure 30. Load input method

    ○ Analysis result

Figure Bearing stress distribution Figure Bearing plate stress distribution

Figure Concave Plate stress distribution Figure Spring stress distribution

Figure Center Shaft stress distribution Figure Cap stress distribution

Figure 31. Stress distribution by ABAQUS analysis result

Figure 32. Results of ABAQUS analysis Stress distribution

Figure 33. ABAQUS analysis result Body stress distribution

ABAQUS analysis result stress comparison division SM490 Center Rod  ( Max ) Yield strength The tensile strength Allowable stress Stress 333.367 510.133 210 37.78 Safety factor - 5.56

Figure 34. Load hysteresis curve of analysis result

    - As a result, yielding load is 4.01kN and effective stiffness is 0.147kN / mm.

    - The maximum load generated at 40mm displacement is 5.862kN.

    - Perform analysis according to change of radius of curvature when spring compressive force is same.

- Even though the radius of curvature is different, the yield load is similar but the effective stiffness decreases as the radius of curvature increases.

- It is judged that the effective stiffness is caused by the difference in deformation due to the radius of curvature.

Figure 35. Spring 5 mm compression

Figure 36. Spring 10 mm compression

Figure 37. Spring 13.4 mm compression

3. EUT test

   end. Purpose of Testing

○ To design and manufacture a mechanical vibration damping system using friction pendulum principle and to analyze the test results through the behavior test to obtain information on the performance of the specimens for each type and to draw out improvements by taking into account the weak points and limitations.

   I. Exam contents

○ In order to realize the friction force in the 2-axis dynamic tester, the MER-Spring is fixed to the jig and then compressed. After the compression device is fixed to the tester, basic property test and dependency test are performed.

Figure 38. Two-axis dynamic tester

2-Axis Dynamic Tester Specification Maximum capacity Vertical: 100 kN, Horizontal: 50 kN Maximum displacement (stroke) Vertical: ± 75mm, Horizontal: ± 100mm Maximum speed Vertical: 100mm / sec, Horizontal: 200mm / sec
However, when using two axes simultaneously, vertical, horizontal 100mm / sec Metrics Load-displacement Measuring sensor A load cell (Interface 1020), a displacement sensor (LVDT 200mm) Size (Approx) 2350mm * 1170mm * 1650mm Weight (Approx) 1.5 ton

○ Behavior test by displacement

- In the case of a damper supporting piping in a nuclear power plant, it must be able to maintain its performance against shocks and vibrations that may be caused by thermal deformation due to dead load, thermal stress, and dynamic load.

- To verify that the damper maintains normal performance for various displacements, perform a test to check the behavior by varying the displacement.

     ○ Behavior test by velocity

-FCD device generates energy dissipation due to friction during movement.

- Most friction materials have friction coefficient varying according to slip speed

- The test is performed to confirm the behavior according to the speed.

     ○ Durability test

- The damper supporting the structure also operates during the normal operation of the nuclear power plant, so it should be easy to replace and maintain and to maintain its performance for a long time.

- In case of earthquake or dynamic load other than usual, displacement may occur several times in piping.

- Perform tests to ensure that the device can maintain normal performance after several tens of displacements.

   All. Test Methods

     ○ EUT Type 1 Test Method

- Install FCD device in 2-axis dynamic tester → Compress MER-Spring → Perform basic property test for 0mm ~ 85mm at velocity of 100mm / sec → Test for 6 cycle 20mm, 50mm for displacement characteristic test → Test for displacement 50mm Speed test 5 mm / sec and 100 mm / sec test

Type 1 Device Characteristics Test Type Test Type Test Methods Detailed test method Displacement dependence Test displacement 20mm - Test speed: 100mm / sec
- Displacement type: Sine Wave
- Number of roundtrips: 6 times 50mm Speed dependence Test speed 5mm / sec - Test displacement: ± 50mm
- Displacement type: Sine Wave
- Number of roundtrips: 6 times 100mm / sec

Figure 39. Type1 trial foreground

     ○ EUT Type 2 Test Method

- Install FCD device in 2-axis dynamic tester → Compress MER-Spring → Perform this characteristic test for 0mm ~ 85mm at speed of 100mm / sec → Perform 10 cycles for 40mm and 45mm test for displacement characteristic → Test for displacement 45mm , 5 cycle, 10 cycle, and 100 cycle tests were performed to confirm the durability against the speed of 100 mm / sec

Type 2 Device Characteristics Test Type Test Type Test Methods Detailed test method Displacement dependence Test displacement 40mm - Test speed: 100mm / sec
- Displacement type: Sine Wave
- Number of round trips: 10 times 45mm Durability test Number of tests 5cylce - Test displacement: ± 45 mm
- Test speed: 100mm / sec
- Displacement type: Sine Wave 10cycle 100cycle

Figure 40. Type 2 trial foreground

     ○ EUT Type 3 Test Method

- Install FCD device in 2-axis dynamic tester → Compress MER-Spring → Perform basic characteristic test for 0mm ~ 85mm at velocity of 100mm / sec → Perform test for 10 cycles for displacement 35mm → Test by speed for displacement 40mm Perform 1 mm / sec to 200 mm / sec test

Type 3 Device Characteristics Test Type Test Type Test Methods Detailed test method Basic test Test displacement 35mm - Test speed: 100mm / sec
- Displacement type: Sine Wave
- Number of round trips: 10 times Speed dependence Test speed 1mm / sec - Test displacement: ± 40 mm
- Displacement type: Sine Wave
- Number of round trips: 5 times 20mm / sec 100mm / sec 200mm / sec Durability test Number of tests 10,000 Cycle - Test displacement: ± 5 mm
- Test speed: 20mm / sec
- Displacement type: Sine Wave

Figure 41. Type 3 trial foreground

 4. EUT  Test analysis

   end. Type 1 test

○ Test results

Figure 42. Displacement 20mm Speed 100mm / sec Load Hysteresis Curve

Figure 43. Displacement 50mm Speed 100mm / sec Load Hysteresis Curve

Figure 44. Displacement 50mm Speed 5mm / sec Load Hysteresis Curve

Figure 45. Load-displacement hysteresis curve (Type1)

Type 1 test results division Exam conditions EDC
( kN · mm ) K _eff
( kN / mm ) Displacement mm ) speed( mm / sec ) One 20 100 193.695 0.168 2 50 100 601.681 0.117 3 50 5 493.401 0.083

Figure 46. Comparison of test values and design values

Comparison of test value, design value and analytical value division Condition Qd
(kN) EDC
(kN mm) K _eff
(kN / mm) Damping
(%) Test value 100mm / sec 2.4 193.695 0.168 46.0 Design value - 2.3 179.110 0.167 42.9 error - 4% 8% One% 7%

     ○ Analysis of test results

- When the displacement is 50mm, the behavior is not smooth and splashing occurs.

- The tendency of the hysteresis curve is not the same when comparing the tests according to displacement

- When the value of R is large, when the displacement occurs, the center axis of the bearing and the cylinder is not constant and the bending occurs due to the behavior, which is the cause of the non-smooth behavior

- Error between design value and test value is less than 10%, but improvement is needed for smooth behavior

   I. Type 2 test

     ○ Test results

Figure 47. Displacement 40mm Speed 100mm / sec Load Hysteresis Curve 10cycle)

Figure 48. Displacement 45mm Speed 100mm / sec Load Hysteresis Curve (10 cycles)

_

Figure 49. Displacement 45mm Speed 100mm / sec Load Hysteresis curve (5 cycle)

Figure 50. Displacement 45mm Speed 100mm / sec Load Hysteresis Curve (100 cycles)

Figure 51. Load-displacement hysteresis curve (Type 2)

Type 2 test results division Exam conditions EDC
( kN · mm ) K _eff
( kN / mm ) Displacement
( mm ) speed
( mm / sec ) Number of times
( cycle ) One 40 100 10 781.593 0.216 2 45 100 929.978 0.213

Figure 52. Comparison of test values and design values

Comparison of test value, design value and analytical value division Condition Qd
(kN) EDC
(kN mm) K _eff
(kN / mm) Damping
(%) Test value 100mm / sec 4.5 781.593 0.216 36.9 Design value - 4.8 774.073 0.170 45.4 error - 6% One% 27% 19%

     ○ Analysis of test results

- Smooth behavior for 40 mm displacement

- Unstable device during testing due to lack of fixed connection parts on the bottom and closing parts of the tester.

-Type2 shows that the effective stiffness is similar to 1% difference and the EDC increases with increasing displacement when comparing two tests with different displacement at the same speed and frequency. Confirm match

- It was judged that the part of the hysteresis curve of 100 cycles was caused by the error of the tester when tested and confirmed that the tester did not move smoothly even during the actual test.

- It is judged that the difference between the design value and the design value is due to the flexure occurring due to the increase of the displacement when compared with the design value.

- Improvements to Type 1 have been well applied and overall behavior is smooth, but the curvature is still needed to be reduced because the bouncing is still occurring.

   All. Type 3 test

○ Test results

Figure 53. Comparison of test values and design values

Comparison of test value and design value division Condition EDC
( kN · mm ) K _eff
( kN / mm ) Damping
(%) Test value Displacement 35mm 626.144 0.181 45.1 Design value 674.232 0.186 47.1 error - 7% 2% 4%

- Comparison with the hysteresis curves calculated from the load hysteresis curve and the behavior equation of the test for the test displacement of 35 mm

- The error between the test value and the design value was 7% for EDC, 2% for K _eff , and 4% for damping, all within 10%.

- After the basic characteristic test, the test is carried out to confirm the dependency on the speed.

- Speed dependence Test content: The MER-Spring was compressed at 30 kN and the design displacement was tested in 4 steps for 1 mm / sec, 20 mm / sec, 100 mm / sec and 200 mm / sec for 40 mm

Figure 54. Load displacement curve for 1 mm / sec

Figure 55. Load displacement curve for 20 mm / sec

Figure 56. Load displacement curve for 100 mm / sec

Figure 57. Load displacement curve for 200 mm / sec

Figure 58. Hysteresis curve with speed

Figure 59. Change in Qd value by velocity

Speed dependence test result Test Type Qd
(kN) EDC
(kN mm) K _eff
(kN / mm) Damping
(%) Growth rate
1 mm / sec 3.7 600.524 0.141 42.8 - 20 mm / sec 4.6 748.879 0.173 43.4 026. 100 mm / sec 5.1 855.564 0.197 43.8 0.11 200 mm / sec 5.1 862.273 0.203 43.6 0.01

Figure 60. 10,000 cycle durability test load hysteresis curve

Figure 61. Appearance of the device after 10,000 cycles durability test

     ○ Analysis of test results

- Test results confirm that the damping area increases from low to high speed

- When comparing the yield value (Qd) per speed, the yield value increases as the speed increases and the increase rate decreases as the speed increases

- Draw a trend line for the change of the yield value according to the speed to indicate the log format.

- Increasing the damping area increases the friction coefficient as the speed increases.

The change in effective stiffness with increasing speed at -1 mm / sec is due to the difference between the resilience of MER-Spring at low speed and the resilience of MER-Spring at high speed

- As the velocity increases, the hysteresis curve and the curving phenomenon occur on the hysteresis curve.

- The shaking and tilting of the behavior is judged by the influence of the inertia due to the acceleration generated in the test system.

- In order to eliminate the effect of inertia due to acceleration, the effect of inertia must be removed through the bare table test, which is a preliminary test before the test.

- In the durability test, clearance occurs due to the tolerance between the pins fixing the device, and some distortion occurs at the maximum displacement.

- When the device is removed after the durability test, it is confirmed that there is no abnormality of the device.

Figure 62. Comparison of Hysteresis Curve of EUT

Comparison of test value, design value and analytical value division Condition Qd
(kN) EDC
(kN mm) K _eff
(kN / mm) Damping
(%) Test value 100mm / sec 5.1 855.564 0.197 43.8 Design value - 4.9 774.073 0.172 45.5 ansys interpretation value - 4.9 767.263 0.170 44.9 Error (design value) - 4% 10% 14% 4%

- Design values and Ansys analysis values are similar to EDC and K _eff , but when compared with the test values, the yield value is 4%, EDC value is 10%, K _eff is 14%, and damping ratio is 4%

- The yield value is 6% difference. The difference between the EDC value and the EDC value is more than 10%. This is because it is judged that there is an error because the end part is splashed due to the inertia of acceleration. Judged

   la. conclusion

     ○ Optimization of device through 3 types of EUT

     ○ Improvement of defectiveness through performance test after production by type of EUT

     ○ In Type 1 and 2, engineering plastic was introduced in the cover of Type 3 to improve the smoothness due to scratches between the cylinder and the cover.

     ○ Unlike Type1, Type2 and Type3 have less stiffness due to increase of length of MER-Spring, and the behavior becomes smooth.

     ○ The R value in Type 3 is solved in the form of hemispherical bending caused by the previous type because the center point is the same when displacement occurs.

     ○ Type 3 test result showed smooth behavior, and the error between test value and design value was less than 10% when the displacement was 35mm,

     ○ Plan to consider the impact on future accelerator inertia.

As a result of research and experiments conducted by the present inventor, Type 3 exhibited the best performance.

FCD is a mechanical anti-vibration device based on the principle of friction pendulum. Until now, it has not been used as a damper alone, but it has been used as a spring element to realize the upper vertical load that induces frictional force for single use. And the friction pendulum principle is applied. The behavior equation of the device is as follows.

○ Additional spring compressions according to the height difference of the pendulum during the behavior are calculated and expressed as

○ In the case of a damper using friction pendulum principle, there is no need for a restoring force induction device to return to home position in case of earthquake or vibration.

○ Since the principle of gravity restoration is applied, there is no need to install a separate spring structure and it is easy to maintain because of its simple structure and structure.

○ Check the behavior of the product using the behavior equation of friction pendulum damper (load hysteresis curve derivation)

Figure 63. Principle of the behavior of friction pendulum damper

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings and the accompanying drawings.

Fig. 1 is a perspective view of a pendulum type friction damper according to the present invention, Fig. 2 is a partially broken perspective view of a pendulum type damper shown in Fig. 1, Fig. 3 is a longitudinal sectional view according to II of Fig. FIG. 5 is a perspective view of the friction contact member, and FIG. 6 is a perspective view of the cover member.

1 to 6, the pendulum type friction damper 100 according to the present invention includes a concave member 110. As shown in FIG. 2, a concave surface 112 is formed on the upper surface of the concave member 110. The surface 112 of the concave surface 112 is inclined in the longitudinal direction of the concave member 110. A concave surface 112 having a surface inclined in the longitudinal direction of the concave member 110 is formed on the bottom surface of the concave member 110 as well. In this embodiment, the concave surface 112 is formed on the upper surface and the lower surface of the concave member 110 in a vertically symmetrical manner.

In some cases, the concave surface 112 may be formed on only one of the upper surface and the lower surface of the concave member 110.

Preferably, the concave surface 112 is formed symmetrically with respect to the center of the concave surface 112 in the longitudinal direction of the concave member 110. The radius of curvature of the concave surface 112 formed in the concave member 110 of this embodiment is about 1000 mm. Accordingly, the corresponding surface of the friction contact member 120 that is in contact with the concave surface 112 is preferably formed of a first convex curve surface having a radius of curvature of about 1000 mm.

As shown in FIG. 2, at a central portion of the concave surface 112, a flow preventing surface 114 extending in the longitudinal direction of the concave member 110 is formed. The flow preventive surface 114 is formed in a slotted shape as a portion to be guided when the flow preventive guide portion 124 is inserted into the frictional contact member 120, which will be described later. When the flow prevention guide 124 is formed in a groove shape, the flow prevention surface 114 may be formed as a protrusion protruding upward or downward from the surface of the concave member 110. The slip-proof anti-flow-in surface 114 preferably allows passage of the shaft member 132, which will be described later.

 In addition, at one end of the concave member 110, a connection portion 116 in the form of a through hole for connecting to another structure is formed.

The friction damper 100 of this embodiment has a frictional contact member 120 of a substantially semi-cylindrical shape as shown in Figs. The frictional contact member 120 is a member that contacts the concave surface 112 of the concave member 110 and has a first convex surface 122 having a radius of curvature corresponding to the concave surface 112 on a surface contacting the concave surface 112, Respectively. The first convex surface 122 protrudes from the surface of the first convex surface 122 and is inserted into the flow preventive surface 114 in the form of a long hole to contact the inner circumferential surface of the long hole to guide the movement of the concave member 110, Is prevented from moving left and right. On the opposite surface of the first convex surface 122 is formed a second convex surface 126 having a semicylindrical surface.

A through hole 128 through which the shaft member 132 can pass is formed at the center of the friction contact member 120.

 The frictional contact member 120 presses the concave surface 112 in a state where the first convex surface 122 is in contact with the concave surface 112 to provide a frictional force while a frictional force is applied to the concave member 110 To move in the direction in which the concave surface 112 is disposed obliquely, here, in the longitudinal direction of the concave member 110.

As the frictional contact member 120, a member made of a steel material such as SM490 having sufficient strength to withstand the pressure of the elastic pressing means 130 may be used, but a high-strength engineering plastic may be used. As the engineering plastic, it is preferable that the friction surface has a hardness of 75D to 95D. Such engineering plastics include polyamide (PA), polyacetal, polyethylene terephthalate (PET), polysulfone resin (PSU), polyether sulfone (PES), poly Polyphenylene sulfide (PPSU), polyether imide (PEI), polyamide imide (PAI), polybenzimidazole (PBI) , Polyimide (PI), and polyether ether ketone (PEEK) may be used. The engineering plastic has a tensile elongation at break of 15% or more, a density of 1.14 - 1.15 g / cm 3, and a compressive strength of 950 - 1,100 kg / cm 2.

Particularly, as the friction contact member 120 in the present invention, ultra high molecular weight (UPE) which is one kind of engineering plastic is suitable.

In the case of using the friction contact member 120 made of engineering plastic instead of the metallic material, it is not necessary to provide a separate sliding member on the first convex surface 122. However, it is needless to say that a plate-like sliding member of a different sliding property may be provided on the surface of the friction contact member 120 according to need. In the case of using a friction member made of a metal material, it is preferable to use a friction member provided with a separate sliding member on its friction surface.

The frictional contact member 120 is in contact with the upper side frictional contact member 120a which is in contact with the upper surface side concave surface 112 of the concave member 110 and the lower side concave surface 112 of the concave member 110 And a lower friction contact member 120b. Preferably, the upper friction contact member 120a and the lower friction contact member 120b are vertically symmetric about the concave member.

As shown in Figs. 1 to 4, the friction damper 100 according to the present invention includes elastic pressing means 130. Fig. The elastic pressing means 130 elastically urges the friction contact member 120 to the surface member 110. When the friction contact member 120 is elastically pressed against the concave member 110, the frictional force of the friction contact member 120 with respect to the concave member 110 is increased. The concave member 110 is subjected to a force which interferes with the movement of the concave member 112 in the longitudinal direction of the concave member 110 with respect to the friction contact member 120 in the direction in which the concave surface 112 is inclined. In this state, when the concave member 110 is impacted in a direction in which the concave surface 112 is inclined, the impact can be buffered and absorbed by the frictional force acting between the concave member 110 and the friction contact member 120 .

The elastic pressing means 130 having the above function includes a shaft member 132 and an elastic body 134 that pass through the elongated hole 114 vertically. As the shaft member 132, a bolt having spiral at both ends is preferable. The elastic member 134 is disposed outside the friction contact member 120 with respect to the concave surface 112. When the shaft member 132 is provided at the center, it is preferable that a through hole through which the shaft member 132 can pass is formed in the elastic body 134. When the shaft member 132 is installed on both the left and right sides as shown in FIG. 9 of the present invention, the through hole for passing the shaft member 132 may not be formed in the friction contact member 120 and the elastic member 134 .

In this embodiment, the elastic body 134 includes an upper elastic member 134a and a lower friction contact member 120b for elastically pressing the upper friction contact member 120a against the concave member 110, And a lower elastic body 134b for resiliently pressing against the lower elastic body 134b.

As such an elastic body 134, a mass energy regulator spring made of polyurethane having a rubber hardness in a range of 80 A to 100 A is preferable.

Preferably, the resilient pressing means 130 is provided with a lifting member 136. The elevating member 136 is used to press the entire end surface of the elastic body 134 against the concave surface 112 by the pressing means 130 and has a larger sectional area than the elastic body 134. In this embodiment, the elevating member 136 is provided to press the entire cross section of the upper elastic body 134a and the lower elastic body 134b, respectively, and includes an upper elevating member 136a and a lower elevating member 136b do.

The elastic pressing means 130 is provided with a pressing member 138. This urging member 138 is for urging the elastic body 134 against the concave surface 112 of the concave member 110. In this embodiment, a bolt having a bolt head can be used as the shaft member 132 as shown in Figs. 3 and 4, and in this case, the pressing member 138 can be composed of a nut that is coupled to one end of the bolt . A bolt having spirals at both ends may be used as the shaft member 132. In this case, a nut that is respectively coupled to a spiral formed at both ends of the shaft member 132 is used as the pressing member 138. [

When it is not necessary to adjust the pressing force for pressing the elastic body 134 and the predetermined pressing force can be fixedly maintained, the pressing member 138 is fixed to the shaft member 132 so as not to move by welding, Of course.

In this case, the elastic pressing means 130 may be constituted by the shaft member 132, the elevating member 136 and a pressing member 138 such as a nut fixed to the shaft member 132, And a pressing member 138 which is fixed to the elastic member 132 by welding or the like and presses the elastic member 134 having a wider sectional area than the elastic member 134 in a compressed state.

2 to 4 and 6, a pendulum type friction damper 100 according to the present invention includes a cover member 140 for covering the friction contact member 120 and allowing the friction contact member 120 to tilt, Respectively.

The cover member 140 includes an upper cover member 140a and a lower cover member 140b that are movably coupled to the outer circumferential surface of the shaft member 132 between the upper elastic member 134a and the upper friction member 120a, And a lower cover member 140b coupled to the outer peripheral surface of the shaft member 132 between the lower friction member 120b and the lower friction member 120b so as to be movable up and down. Only one of the upper cover member 140a and the lower cover member 140b is provided when the elastic member 134 and the friction contact member 120 are provided on only one of the upper surface and the lower surface of the face member 110. [

Preferably, recessed grooves 141 are formed on the bottom surface or top surface of the upper and lower cover members 140a and 140b, each of which has a semi-cylindrical curved surface having a curvature radius smaller than that of the concave surface 112. The concave groove 141 is in surface contact with the second convex surface 126 of the upper and lower friction contact members 120a and 120b and has a radius of curvature of approximately 20 mm to 25 mm. At the center of the cover member 140, a through hole 145 through which the shaft member 132 can pass is formed.

In this embodiment, the upper cover member 140a and the lower cover member 140b are arranged in a vertically symmetrical manner, and the upper friction contact member 120a and the lower friction contact member 120b are arranged in a vertically symmetrical manner.

The upper cover member 140a and the lower cover member 140b as described above serve as a component of the elastic pressing means 130. [

1 to 4, the friction damper 100 according to the present invention preferably has a hollow guide member 150. The guide member 150 has a function of receiving a part of the concave member 110 and guiding the concave member 110 to move in a direction in which the concave surface 112 is inclined, So that the elastic pressing means 130 catches the elastic pressing means 130 such that the elastic pressing means 130 can not move in the direction in which the concave surface 112 is inclined with the concave surface member 110.

Of course, when the shaft member 132 is directly fixed to the object to be connected, it is preferable that the friction damper having the damping function without the guide member 150 is formed.

One side of the guide member 150 is formed with an elevation guide portion 152 for guiding the cover member 140 and the friction contact member 120 to move up and down in the direction perpendicular to the moving direction of the concave member 110 . The elevating guide portion 152 may be configured to guide the elevating member 136 to move up and down. The lifting guide 152 serves to guide the vertical movement of the cover member 140 and the friction contact member 120 directly or indirectly and at the same time the elastic pressing unit 130 is disposed in the longitudinal direction It does not let you move. The elevating guide 152 preferably serves to prevent the elastic pressing means 130 from moving in the width direction of the surface member 110. [

The guide member 150 is preferably made of a high-strength engineering plastic as described above. In this embodiment, the guide member 150 has a rectangular parallelepiped shape, and a connecting portion 154 having an opening for connecting to another structure is provided at one end thereof. The guide member 150 has two split bodies 150a and 150b which are divided into left and right sides and formed with coupling grooves 156 in which a part of the coupling portion 154 is coupled at one end to a coupling groove 156 And is coupled with a coupling means 158 such as a bolt in a face-to-face manner. As the connection portion 154, it is preferable to use a metal material.

7 is a perspective view showing a state in which a pendulum type friction damper according to the present invention supports a pipe.

7, the pendulum type damper 100 according to the present invention includes a rod restraint 12, a variable spring hanger 14 and the like, which support the pipe P to the upper structure 10, The connection part 116 of one side is connected to the clamp C surrounding the pipe P and the connection part 154 of the other side is connected to the supporting structure The damper 16 can be suitably used to prevent the pipeline P from being damaged by buffering and dissipating the impact force applied to the structure by an earthquake or an explosion and transmitting it to the pipeline P. [

The present invention is not limited to the embodiments described in the specification of the present application, but may be modified to include a cylindrical member in which the guide member is formed in the form of a cylindrical cylinder, A configuration in which the concave member is provided on both sides of the guide member and the through hole for passing the shaft member is not formed in the elastic member and the friction contact member or the like It can be understood that the present invention can be applied to various forms.

The present invention is likely to be used for supporting piping of a nuclear power plant, and it is possible to be used to buffer and dissipate the impact force acting between two structures of other bridges, building structures, or vehicles have.

100: friction damper 110: concave member
112: concave surface 114:
120: Friction contact member 122: First convex surface
124: flow prevention guide portion 126: second convex surface
130: Elastic pressing means 132:
134: elastic body 138: pressing member
140: cover member 150: guide member
150a, 150b: Split body 156: Coupling groove

Claims (9)

A first convex surface having a radius of curvature corresponding to the concave surface is formed on a surface which is in contact with the concave surface and is in contact with the concave surface, A frictional contact member for allowing the member to move in a direction in which the concave surface is inclined and a frictional contact member for elastically pressing the frictional contact member against the concave surface to increase the frictional force of the frictional contact member with respect to the concave member, And elastically urging means for urging the frictional contact member in a direction in which the concave surface is inclined,
And a hollow portion for accommodating at least a part of the concave member and allowing the concave member to move in a direction in which the concave surface is disposed in an inclined manner, wherein the elastic pressing means is engaged with the elastic pressing means such that the concave surface is inclined And a hollow guide member for holding the elastic pressing means so as not to move together with the concave member in a predetermined direction,
The hollow guide member is made of engineering plastic,
Wherein the concave member is formed with a flow preventing surface provided along a direction in which the concave surface is disposed obliquely,
Wherein the friction contact member is provided with a flow preventing guide portion which is coupled to the inside of the flow preventing surface to guide the inside of the flow preventing surface. The connector according to claim 1, wherein the hollow guide member is provided with a connecting portion,
The hollow guide member is divided into left and right parts, and two split bodies formed with coupling grooves at one end of which coupling parts are coupled are coupled with a coupling means in a state of interposing a part of the coupling parts into the coupling grooves, Wherein the first and second frictional dampers are rotatable. delete The flow control valve according to claim 1, wherein the inside of the flow prevention hole is a slot formed in the concave member in a direction in which the concave surface is inclined,
The flow prevention guide protrudes from the first convex curved surface and is inserted into the slot to prevent lateral movement of the concave member and guide the movement of the concave member in the longitudinal direction of the slot,
The elastic pressing means comprises:
A shaft member vertically passing through the slot;
An elastic body coupled to the outer circumferential surface of the shaft member and disposed outside the friction contact member with respect to the concave surface;
An elevating member coupled to the outer peripheral surface of the shaft member such that the elevating member can move up and down relative to the outer surface of the shaft member; And
And a pressing member coupled to the shaft member to press the elevating member against the elastic body. And a frictional contact member provided between the elastic member and the frictional contact member, wherein the frictional contact member includes a cover member that is movably coupled to the outer circumferential surface of the shaft member and permits the frictional contact member to tilt,
Wherein the cover member has a semi-cylindrical recessed groove having a radius of curvature smaller than the surface of the friction member, the radius of curvature corresponding to the recessed groove on the surface opposite to the first convexity surface of the friction- And the second convex surface of the second convex surface is formed,
Wherein the guide member is provided with an elevation guide portion for guiding the friction contact member and the cover member in the vertical direction in a direction perpendicular to the moving direction of the concave member. The pendulum type friction damper according to any one of claims 1, 2, and 4, wherein the friction contact member is made of engineering plastic. The pendulum type friction damper according to claim 6, wherein the friction contact member is an ultra high molecular weight (UPE) material having no separate friction plate on its surface. 8. The light emitting device according to claim 7, wherein the concave surface is formed on both the upper surface and the lower surface of the concave member,
Wherein the frictional contact member includes an upper friction contact member contacting the upper surface side surface of the concave member and a lower friction contact member contacting the lower surface side surface of the concave member and vertically symmetrical with the upper friction contact member,
The elastic pressing means includes an upper elastic member and an upper elastic member for resiliently pressing the upper friction contact member against the concave member, a lower elastic member for elastically pressing the lower friction contact member against the concave member, And a lifting member for lifting the friction damper. The sliding device according to claim 8, further comprising an upper cover member coupled between the upper elastic member and the upper friction contact member so as to be movable up and down on the outer peripheral surface of the shaft member,
Wherein the upper cover member is formed with a concave groove having a radius of curvature smaller than that of the concave surface allowing the upper friction member to pivot on the bottom surface thereof and a concave groove having a radius of curvature corresponding to the concave groove on the upper surface of the upper friction- Two convex curved surfaces are formed,
A lower cover member coupled between the lower elastic member and the lower friction contact member so as to be movable up and down on the outer peripheral surface of the shaft member,
Wherein the lower cover member has a concave groove with a radius of curvature smaller than that of the lower surface of the lower cover member so as to allow rotation of the lower friction contact member on the upper surface and corresponds to the concave groove of the lower cover member on the lower surface of the lower friction contact member A second convex surface having a radius of curvature is formed,
Wherein the guide member is provided with a lifting / lowering guide portion for guiding upward and downward movement of the friction contact member in a direction perpendicular to the moving direction of the concave member,
The elevation guide portion also guides upward and downward movement of the upper cover member and the lower cover member in a direction perpendicular to the moving direction of the concave member,
And the second convex surface is a semi-cylindrical curved surface.

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