KR100696952B1 - A damper using magneto-rheological fluid for controlling damping performance non-symmetrically - Google Patents

A damper using magneto-rheological fluid for controlling damping performance non-symmetrically Download PDF

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Publication number
KR100696952B1
KR100696952B1 KR1020050043838A KR20050043838A KR100696952B1 KR 100696952 B1 KR100696952 B1 KR 100696952B1 KR 1020050043838 A KR1020050043838 A KR 1020050043838A KR 20050043838 A KR20050043838 A KR 20050043838A KR 100696952 B1 KR100696952 B1 KR 100696952B1
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South Korea
Prior art keywords
tension
cylinder
compression
flow path
chamber
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KR1020050043838A
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Korean (ko)
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KR20060121586A (en
Inventor
재 우 박
백운경
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부경대학교 산학협력단
에스앤티대우(주)
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Priority to KR1020050043838A priority Critical patent/KR100696952B1/en
Publication of KR20060121586A publication Critical patent/KR20060121586A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32Details
    • F16F9/53Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
    • F16F9/535Magnetorheological [MR] fluid dampers

Abstract

The present invention relates to an asymmetric damping performance controlled damper using a magneto-rheological fluid, which is compressed in a cylinder during a compression and tensile stroke by an impact continuously applied from the outside such as vibration transmitted from a road surface. The apparent viscosity of the magnetic fluid that is moved between the seal and the tension chamber is controlled by the strength of the electromagnetic field formed by the electromagnet solenoid so that the damping force is varied, but through a check valve installed in the piston valve during compression stroke. The second flow path is formed so that the damping performance of the tension stroke and the compression stroke is asymmetrically controlled, and the volume compensation due to the entry and exit of the piston rod during the compression and tension stroke is rapidly performed every time by the action of the diaphragm installed in the compression chamber. Stick Slip (Stick S) It is possible to provide fast time response characteristics by remarkably reducing time delay caused by friction accompanying lip).
The present invention is a cylindrical cylinder having a diameter and a length of a predetermined size; A hollow rod (Hollow Rod) of a predetermined length, which is fitted into the cylinder from an upper outer side of the cylinder and has a cavity having a diameter in a longitudinal direction along an inner center line; A rod guide configured to guide the hollow rod in a linear state while being fitted and coupled to an upper end of the cylinder while maintaining an accurate straightness; It is fixedly coupled to the inner end of the hollow rod and partitions the cylinder into a lower compression chamber and an upper tension chamber, and generates an electromagnetic field during compression and tension stroke by the action of an electromagnet solenoid installed along the outer circumferential surface. It controls the flow of the filled magnetic fluid fluid and forms a first flow path by a gap formed between the outer circumferential surface of the electromagnet solenoid and the inner circumferential surface of the flux ring, and the magnetic fluid fluid of the compression chamber flows to the tension chamber only during the compression stroke. A second valve having a second valve formed therein; The second flow path is opened while being pushed upward by the pressure of the magnetic fluid filled in the compression chamber during the compression stroke in the state of being installed inside the second flow path formed inside the piston valve, and in the tension chamber during the tension stroke. A check valve for closing the second flow path while being pushed downward by the pressure of the filled magnetic fluid; It is installed to be closed to have a volume compensation chamber of a predetermined volume therein from the inner lower end of the cylinder and includes a diaphragm (Diaphragm) to extend and compress according to the tension and compression stroke of the piston valve.
Electromagnet solenoid, piston valve, flow path, check valve, diaphragm

Description

Asymmetric damping performance controlled damper using magnetofluid fluid {A DAMPER USING MAGNETO-RHEOLOGICAL FLUID FOR CONTROLLING DAMPING PERFORMANCE NON-SYMMETRICALLY}

1 is a perspective view showing a partial cross-sectional view showing an asymmetric damping performance controlled daffer using a magnetorheological fluid according to an embodiment of the present invention;

2 is a front cross-sectional view of FIG.

3 is an enlarged cross-sectional perspective view of the main part of FIG. 1;

Figure 4 is a perspective view showing a partial cross-sectional view showing an asymmetric damping performance controlled damper using a magnetic fluid in accordance with another embodiment of the present invention,

5 is a front sectional view of FIG. 4;

6 is an enlarged cross-sectional perspective view of the main portion of FIG. 4;

7 is a perspective view showing a partial cross-sectional view showing a diaphragm applied to the asymmetric damping performance controlled damper using a magnetic fluid according to the present invention,

8 is an enlarged cross-sectional view illustrating an operating state of the asymmetric damping performance controlled damper using the magnetic fluid fluid in the compression stroke according to an embodiment of the present invention;

Figure 9 is an enlarged cross-sectional view showing the operating state of the tension stroke of the asymmetric damping performance controlled damper using a magnetic fluid according to an embodiment of the present invention,

10 is an enlarged cross-sectional view illustrating an operating state of the asymmetric damping performance controlled damper using the magnetic fluid fluid during compression stroke according to another embodiment of the present invention;

FIG. 11 is an enlarged cross-sectional view illustrating an operating state of the asymmetric damping performance controlled damper using a magnetic fluid according to another embodiment of the present invention at tension stroke.

* Description of the symbols for the main parts of the drawings *

20: cylinder 30: hollow rod

31: cavity 32: electric wire

40: rod guide 50: piston valve

51: electromagnet solenoid core 52: solenoid coil

55a, 56a: Orifice 58: 2nd flow path

60: check valve 70: diaphragm

The present invention relates to an asymmetric damping performance controlled damper using magnetofluidic fluid, and more particularly, to a compression chamber and a tension chamber in a cylinder in a process in which a compression and tension stroke is performed by an impact continuously applied from the outside, such as a vibration transmitted from a road surface. The apparent viscosity of the magnetic fluid that is moved between the chambers is controlled by the strength of the electromagnetic field formed by the electromagnet solenoid so that the damping force is variable, but is separated through a check valve installed in the piston valve during compression stroke. The flow path is formed so that the damping performance of the tension stroke and the compression stroke is asymmetrically controlled, and the volume compensation due to the entry and exit of the piston rod in the compression and tension stroke is performed rapidly every time by the action of the diaphragm installed in the compression chamber. Stick Slip The present invention relates to an asymmetric damping performance controlled damper using magnetofluidic fluid which can significantly reduce the time delay caused by friction and provide fast time response characteristics.

In general, the damper serves to attenuate vibration or impact force applied from the outside and is widely applied to various industrial fields such as a vehicle suspension system.

On the other hand, the suspension system of the vehicle connects the axle and the body so that vibrations or shocks transmitted from the road surface to the axle during the driving are not directly transmitted to the body, thereby preventing damage to the cargo on the vehicle and the vehicle, and providing a comfortable ride for passengers. It is one of the important devices to be able to give.

In order to perform such an operation precisely, the suspension system is made of an electronic control method, a chassis spring for mitigating vibration or shock applied from the road surface, and a stabilizer for preventing rolling of the vehicle. And a damper for controlling the free vibration of the chassis spring to give an improved ride comfort.

On the other hand, the damper constituting the suspension of the vehicle absorbs the free vibration generated by the shock applied to the chassis spring and at the same time to attenuate quickly to convert the energy of the vertical motion into thermal energy, electronically controlled The hydraulic damping variable variable damper is mainly applied to the current value of the vehicle so that the damping force can be automatically or arbitrarily converted to improve driving stability, steering stability, and ride comfort.

As an example of such a conventional hydraulic damping force variable damper, a hydraulic solenoid valve type has been applied.

The time response characteristic of the conventional hydraulic solenoid valve type damper is 30 to 50ms, which is superior to the discrete damping force variable damper driven by a passive damper or step motor using oil or gas, but the time response characteristic is still relatively high. The problem is that it's slow.

In this case, when the response time is slow, the shock absorber does not absorb the vibration transmitted from the road surface in a short time and is transmitted to the vehicle body as it is, or it only serves to attenuate the aftershock after the main vibration. There is a problem that causes them to complain about the price-performance ratio.

In addition, the conventional hydraulic solenoid valve-type damper has a problem that the structure is quite complicated, it is difficult to adjust the damping performance because it is made in the form of mounting the hydraulic solenoid valve to the existing gas damper.

In order to improve the performance of the electronically controlled suspension system, a damper having a faster time response characteristic of 10 ms or less is required.

Accordingly, in recent years, the apparent viscosity of the magnetic fluid fluid that is moved between the compression chamber and the tension chamber in the process of compressing and tensioning due to the impact continuously applied from the outside such as vibration transmitted from the road surface to the electronically controlled suspension system is applied to the electromagnet solenoid. A damper using a magneto-fluidic fluid that is controlled by the strength of the electromagnetic field formed by the variable damping force has been applied.

However, in the conventional electronically controlled suspension system using a damper using a magnetofluidic fluid, a separate valve is not provided in the damper using the magnetofluidic fluid, and the magnetofluid fluid is formed through the same annular gap (gap) during tension stroke or compression stroke. As the damping force is adjusted according to the strength of the magnetic field formed by the electromagnet solenoid, the tensile damping force control region and the compressive damping force control region are designed to be almost symmetrical.

However, in reality, in the suspension of a vehicle, the tension damping area requires a relatively large damping force, and the compression damping area requires a relatively small damping force compared to the tension damping area, so that the tensile to compression damping performance ratio is 3: 1. Tuned.

Therefore, in order to be able to construct an efficient electronically controlled suspension system, it is required to secure a certain region at a relatively large damping force and to compress a predetermined region at a small damping force.

On the other hand, the most important performance of the electronically controlled suspension system using a damper using magnetofluidic fluid is the time response characteristic. Floating pistons applied to the dampers using the conventional magnetofluidic fluid are magnetic fluidity by O-rings. Since the fluid and nitrogen gas is separated to move along the inner wall surface of the cylinder as the piston rod enters and exits, there is a problem that time delay due to friction cannot be avoided.

Therefore, in order to improve such a time delay shape, it is necessary to polish the inner wall of the cylinder, adjust the hardness of the O-ring fitted to the floating piston, or install a teflon band to help the sliding piston slide. Several methods were sought.

However, in any case, the friction can be reduced, but since the friction can not be eliminated fundamentally, there is a problem that it is difficult to improve the time delay phenomenon.

The present invention is to solve such a conventional problem, the object is to move between the compression chamber and the tension chamber in the cylinder in the process of compression and tensile stroke by the impact applied continuously from the outside, such as vibration transmitted from the road surface While the apparent viscosity of the magnetic fluid is controlled by the strength of the electromagnetic field formed by the electromagnet solenoid, the damping force is varied, but a separate second flow path is formed through a check valve installed in the piston valve during compression stroke. Therefore, it is to provide an asymmetric damping performance controlled damper using magnetofluidic fluid which allows the damping performance during tension and compression strokes to be controlled asymmetrically.

Another object of the present invention is to make the volume compensation according to the entry and exit of the piston rod during compression and tension stroke to be made quickly every time by the action of the diaphragm installed in the compression chamber, so that the time delay by friction accompanying stick slip It is to provide an asymmetric damping performance controlled damper using magneto-fluidic fluid that can significantly reduce the speed and provide fast time response characteristics.

In order to achieve the above object, the asymmetric damping performance controlled damper using a magnetic fluid according to the present invention comprises a cylindrical cylinder having a diameter and a length of a predetermined size; A hollow rod (Hollow Rod) of a predetermined length, which is fitted into the cylinder from an upper outer side of the cylinder and has a cavity having a diameter in a longitudinal direction along an inner center line; A rod guide configured to guide the hollow rod in a linear state while being fitted and coupled to an upper end of the cylinder while maintaining an accurate straightness; It is fixedly coupled to the inner end of the hollow rod and partitions the cylinder into a lower compression chamber and an upper tension chamber, and generates an electromagnetic field during compression and tension stroke by the action of an electromagnet solenoid installed along the outer circumferential surface. It controls the flow of the filled magnetic fluid fluid and forms a first flow path by a gap formed between the outer circumferential surface of the electromagnet solenoid and the inner circumferential surface of the flux ring, and the magnetic fluid fluid of the compression chamber flows to the tension chamber only during the compression stroke. And a separate second flow passage formed therein; and a piston valve formed therein; and a pressure of the magneto-fluid fluid filled in the compression chamber during the compression stroke in the state of being installed inside the second flow passage formed in the piston valve. Open the second flow path while pushing upward, and in the tension stroke, As with self-check by the pressure of the flow fluid pushed to the bottom to close the second flow valve; It is installed to be closed to have a volume compensation chamber of a predetermined volume therein from the inner lower end of the cylinder and includes a diaphragm (Diaphragm) to extend and compress according to the tension and compression stroke of the piston valve.

In the present invention, the second flow path formed inside the piston valve is tensioned through the inner surface of the lower end of the hollow rod screwed to the center line of the piston valve and the upper surface of the upper plate in a state that penetrates and is formed along the vertical center line of the piston valve body. Has a feature configured to communicate with the yarn.

In the present invention, the second flow path formed inside the piston valve is formed in a diagonal direction toward the upper edge of the piston valve body in a state formed in a predetermined depth upward from the bottom of the vertical center line of the piston valve body and formed on the upper surface of the upper plate. It is characterized in that it is configured to communicate with the tension chamber through the orifice.

In the present invention, the check valve is a spherical body fitted into the inlet portion of the second flow path formed in the center of the bottom surface of the piston valve; It is characterized in that the support spring for supporting the spherical body with an elastic force that always acts downward in the state of being fitted inside the second flow path corresponding to the upper side of the spherical body.

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

1 is a perspective view showing a partial cross-sectional view showing a control asymmetric damping performance using a magnetic fluid fluid according to an embodiment of the present invention, Figure 2 is a front sectional view of Figure 1, Figure 3 is an enlarged cross-sectional perspective view of the main part of Figure 1 to be.

4 is a perspective view showing a partial cross-sectional view showing a damped performance controlled damper using a magnetic fluid according to another embodiment of the present invention, Figure 5 is a front sectional view of Figure 4, Figure 6 is an enlarged main portion of Figure 4 Sectional perspective view.

7 is a perspective view showing a partial cross-sectional view showing a diaphragm applied to the asymmetric damping performance controlled damper using the magneto-fluidic fluid according to the present invention.

8 is an enlarged cross-sectional view illustrating an operating state of the asymmetric damping performance controlled damper using the magneto-fluidic fluid according to an embodiment of the present invention during compression stroke, and FIG. 9 is a magneto-fluidic fluid according to an embodiment of the present invention. This is an enlarged cross-sectional view showing the operating state of the asymmetric damping performance controlled damper at tension stroke using.

FIG. 10 is an enlarged cross-sectional view illustrating an operating state of the asymmetric damping performance controlled damper using a magnetic fluid fluid according to another embodiment of the present invention during compression stroke, and FIG. 11 is a magnetic fluid fluid according to another embodiment of the present invention. This is an enlarged cross-sectional view showing the operating state of the asymmetric damping performance controlled damper at tension stroke using.

Referring to this, the asymmetric damping performance controlled damper using the magneto-fluidic fluid 10 according to the present invention is a change in the apparent viscosity of the magnetic fluid fluid is moved between the compression chamber and the tension chamber by the strength of the electromagnetic field formed by the electromagnet solenoid The damping force is variable according to the above, but a separate second flow path is formed through a check valve installed in the piston valve during the compression stroke so that the damping performance of the tension stroke and the compression stroke is asymmetrically controlled.

In addition, the present invention is to ensure that the volume compensation according to the entry and exit of the piston rod in the compression and tension stroke is made quickly every time by the action of the diaphragm installed in the compression chamber to prevent time delay due to friction accompanying the stick slip (Slip Slip) It is significantly reduced to provide fast time response.

To this end, the asymmetric damping performance controlled damper 10 using the magnetofluidic fluid according to the present invention has a cylindrical cylinder 20 having a predetermined size and a hollow rod having a predetermined length fitted into the cylinder 20. 30, a rod guide 40 coupled to the upper inner side of the cylinder 20, a piston valve 50 coupled to an inner end of the hollow rod 30, and an interior of the piston valve 50. The check valve 60 is installed in a separate second flow path formed in the diaphragm 70 is installed in the cylinder 20 corresponding to the lower side of the piston valve 50.

In the present invention, the interior of the cylinder 20 is divided into the compression chamber 21 and the tension chamber 22 by the piston valve 50 and the diaphragm 70, the compression chamber 21 and the tension chamber 22 ) Is configured to be filled with magnetofluidic fluid 23.

The cylinder 20 has a cylindrical shape having a predetermined diameter and length, the lower end of which is closed and the upper end is opened, and an annular fastening rib 24 is formed along the inner circumferential surface of the upper end.

In addition, a separate cap 25 may be covered on the outer side of the upper end of the cylinder 20 if necessary, and a spring seat for supporting a lower end of the spring 26 at a predetermined height on the outer circumferential surface of the cap 25. 27) can be fixed and installed.

The hollow rod 30 is fitted into the interior of the cylinder from the upper outer side of the cylinder 20, the fastening screw portion is formed on the outer peripheral surface of the upper end.

In addition, a cavity 31 having a predetermined diameter is formed in the hollow rod 30 along a longitudinal center line, and an electric wire 32 for supplying external power is provided in the cavity 31. It is fitted and installed.

The outer circumferential surface of the wire 32 is wrapped with an insulating material 33, the connector 34 is coupled to the lower end. The grommets seal 35 is installed around the connector 34 to prevent leakage.

On the other hand, the rod guide 40 is fitted inside the upper end of the cylinder 20 in order to guide the hollow rod 30 to move linearly while maintaining the correct straightness.

The rod guide 40 is a disk-shaped rod guide main body 41 having a predetermined diameter and height, and a magneto-fluid fluid buried on the outer surface of the hollow rod 30 by being fitted to the bottom surface of the rod guide main body 41. Oil seal 42 to remove the 23 to prevent leakage, the support plate 43 for supporting the oil seal 42, the oil leakage is installed on the outer peripheral surface of the bushing 44 and the rod guide body 41 of the Teflon material It consists of a protective O-ring 45.

In addition, a rod insertion hole 46 into which the hollow rod 30 is fitted is formed at the center of the rod guide body 41, and a bushing 44 of Teflon material having excellent wear resistance is formed on an inner circumferential surface of the rod insertion hole 46. It is fitted and installed.

The oil seal 42 made of a rubber material is configured such that the hollow rod 30 is fitted through the center portion thereof.

The support plate 43 serves to support the oil seal 42 at the bottom of the oil seal 42.

The leakage preventing O-ring 45 serves to prevent leakage of the magnetofluidic fluid 23 in the tension chamber 22 during the tension stroke to the outside of the cylinder 20.

In the present invention, the piston valve 50 fixed and coupled to the inner end of the hollow rod 30 partitions the inside of the cylinder 20 into a lower compression chamber 21 and an upper tension chamber 22. The damping force is varied in such a way that the apparent viscosity of the magnetofluidic fluid 23 flowing between the compression chamber 21 and the tension chamber 22 is changed by generating an electromagnetic field during the tension stroke.

The piston valve 50 has an electromagnet solenoid core 51 formed in an axisymmetric type, a solenoid coil 52 provided on an outer circumferential surface of the electromagnet solenoid core 51, and a circumference of the electromagnet solenoid core 51. A flux ring 54 covered with a gap 53 at a predetermined interval, and an upper plate 55 and a lower plate 56 which are tightly coupled to the upper and lower surfaces of the electromagnet solenoid core 51; , Teflon band 57 is provided on the outer peripheral surface of the flux ring 54.

The electromagnet solenoid core 51 has a rod fixing groove 51a having a predetermined depth in which the lower end of the hollow rod 30 is fitted in the center of the upper surface of the electromagnet solenoid core 51.

The connection path 51b of a predetermined size is formed at a portion from the rod fixing groove 51a to the solenoid coil 52.

The electromagnet solenoid core 51 is designed in the axisymmetric shape to minimize the magnetic losses, and the electromagnet solenoid to mitigate the saturation of the magnetic flux density in the electromagnet solenoid core 51 in accordance with the induced power (Ampere × turns) The core 51 is constructed so that there is no hole in the center so that the cross-sectional area is maximized.

The solenoid coil 52 is configured to be mounted after being sealed by an injection molding in a wound state.

One end of the solenoid coil 52 is electrically connected to the connector 34 of the electric wire 32 through the lower end of the hollow rod 30 inserted through the connecting passage 51b and fitted into the rod fixing groove 51a. .

At this time, the (-) pole is drawn out through the connecting passage 51b in an insulated state by the injection molding, and is connected to the electric wire 32 inside the lower end of the hollow rod 30, and the (+) pole is the electromagnet solenoid core. 51 is grounded to itself.

The flux ring 54 is installed by covering a gap 53 at a predetermined interval from the outer circumferential surface of the electromagnet solenoid core 51.

The upper plate 55 is coupled in close contact with the upper surface of the electromagnet solenoid core 51, and a through hole into which the hollow rod 30 is fitted is formed at the center thereof.

In addition, a plurality of orifices 55a (Orifice) having a predetermined angle range are formed at an upper surface edge corresponding to a position corresponding to the gap 53 formed between the outer circumferential surface of the electromagnet solenoid core 51 and the inner circumferential surface of the flux ring 54. Is formed.

On the other hand, the lower plate 56 is coupled in close contact with the bottom surface of the electromagnet solenoid core 51, by the gap 53 formed between the outer peripheral surface of the electromagnet solenoid core 51 and the inner peripheral surface of the flux ring 54 A plurality of orifices 56a having a predetermined angular range are formed at the upper surface edge corresponding to the position corresponding to the first flow path.

The teflon band 57 is excellent in wear resistance, and is fitted in the center of the outer circumferential surface of the flux ring 54.

Meanwhile, in the present invention, a separate second flow path 58 is formed in the piston valve 50 so that the magnetofluidic fluid 23 of the compression chamber 21 flows toward the tension chamber 22 only during the compression stroke. do.

In the second flow passage 58, the second flow passage 58 is opened while being pushed upward by the pressure of the magnetofluid fluid 23 filled in the compression chamber 21 during the compression stroke. A check valve 60 is installed to close the second flow path 58 while being pushed downward by the pressure of the magnetofluid fluid 23 filled in the seal 22.

As shown in FIGS. 1 to 3, the second flow path 58 formed in the piston valve 50 according to the exemplary embodiment of the present invention passes through and is formed along a vertical center line of the piston valve body. It is configured to communicate with the tension chamber 22 through the inner surface of the lower end of the hollow rod 30 screwed to the center line of the piston valve 50 and the upper plate 55.

In addition, the second flow path 58 formed inside the piston 50 in a state formed in a predetermined depth upward from the bottom of the vertical center line of the piston valve according to another embodiment of the present invention is shown in Figs. As described above, the piston valve body is formed in a diagonal direction toward the upper edge of the valve body and is configured to communicate with the tension chamber 22 through an orifice 55a formed on the upper surface of the upper plate 55.

Meanwhile, in the present invention, the check valve 60 corresponds to a spherical body 61 fitted inside the inlet of the second flow path 58 formed at the center of the bottom surface of the piston valve 50, and corresponds to an upper side of the spherical body 61. It is composed of a support spring 62 for supporting the spherical body 61 with an elastic force that always acts downward in the state of being fitted inside the second flow path (58).

In the present invention, the diaphragm 70 is fixedly installed in a closed state at the lower end of the compression chamber 21 of the cylinder 20, and a volume compensation chamber 71 of a predetermined volume is formed therein to form the piston valve 50. It is configured to perform volume compensation while stretching and compressing according to the tension and compression stroke of.

The operation of the present invention made as described above is as follows.

8 to 11, the asymmetric damping performance controlled damper 10 using the magneto-fluidic fluid according to the present invention is applied to the suspension of the vehicle wires inserted into the cavity 31 in the hollow rod 30 As the external power is applied to the solenoid coil 52 through 32, the inner power is directed from the inner side to the outer side between the solenoid coil 52 and the inner circumferential surface of the flux ring 54 wound along the circumferential surface of the electromagnet solenoid core 51. An electromagnetic field is formed.

 As the vehicle travels in such a state, as the shock and vibration transmitted from the road surface are transmitted to the cylinder 20, the hollow rod 30 and the piston valve 50 continuously repeat the compression stroke and the tension stroke.

In the compression stroke in which the hollow rod 30 and the piston valve 50 are moved to the compression chamber 21, as shown in FIGS. 8 and 10, the magnetic fluid 23 in the compression chamber 21 is a piston valve. (50) After entering the orifice (56a) of the lower plate 56 constituting the first flow path consisting of a gap 53 formed between the outer peripheral surface of the electromagnet solenoid core 51 and the inner peripheral surface of the flux ring 54 It is moved into the tension chamber 22 through the orifice 55a on the upper plate 55.

 In this way, the magnetic fluid 23 is formed in the gap 53 between the electromagnet solenoid core 51 and the flux ring 54 and the orifices 55a and 56a formed on the upper and lower plates 55 and 56 (i.e., , The first flow path is attenuated by changing the apparent viscosity of the magnetofluidic fluid 23 by the electromagnetic field formed between the electromagnet solenoid core 51 and the flux ring 54.

On the other hand, the spherical body 61 constituting the check valve 60 provided in the second flow path 58 by the pressure in which the magnetic fluid 23 filled in the compression chamber 21 acts upward in the compression stroke as described above. ) Is moved upward while compressing the support spring 62, the second flow path 58 is opened.

As such, when the second flow path 58 is opened, the magnetofluidic fluid 23 extends through the inner space of the lower end of the second flow path 58 and the hollow rod 30 and the upper surface of the upper plate 55. Will be moved into.

In addition, in the tension stroke in which the hollow rod 30 and the piston valve 50 are moved to the tension chamber 22, as shown in FIGS. 9 and 11, the magnetic fluid 23 in the tension chamber 22 After entering the orifice 55a of the upper plate 55 constituting the piston valve 50, the lower plate (via the gap 53 formed between the outer circumferential surface of the electromagnet solenoid core 51 and the inner circumferential surface of the flux ring 54) It is moved into the compression chamber 21 through the orifice 56a on 56.

 In this way, the magnetic fluid 23 is formed in the gap 53 between the electromagnet solenoid core 51 and the flux ring 54 and the orifices 55a and 56a formed on the upper and lower plates 55 and 56. 1 passage) is attenuated by changing the apparent viscosity of the magnetofluidic fluid 23 by the electromagnetic field formed between the electromagnet solenoid core 51 and the flux ring 54.

 In this tension stroke, the spherical body 61 is returned to its original state due to the downward pressure of the magnetofluid fluid 23 in the tension chamber 22 and the restoring force of the support spring 62 constituting the check valve 60. As the return is made, the second flow path 58 is closed.

On the other hand, the vibration is generated in the vertical direction according to the state of the road surface when the vehicle is running, and thus the volume compensation according to the vertical reciprocating movement of the hollow rod 30 and the piston valve 50 constituting the shock absorber is the cylinder 20 Compensated by the action of the diaphragm 70 installed therein.

That is, the diaphragm 70 is compressed and stretched to change the volume of the volume compensation chamber 71 when a volume change occurs due to the entering / exiting operation of the hollow rod 30 and the reciprocating motion of the piston valve 50. Is rewarded instantly every second.

When the hollow rod 30 is moved in and out according to the compression and tension stroke, the magnetic fluid 23 buried on the surface of the hollow rod 30 is removed by the action of the oil seal 42 constituting the rod guide 40. It will not leak.

In addition, due to the up and down vibration transmitted from the road surface, excessive pressure is formed in the damper during the process of tension and compression stroke, and the leakage of the magnetofluidic fluid 23 may be expected. In particular, in order to construct an electromagnet solenoid Since the electric wire 32 is connected through the cavity 31 formed at the center of the 30, the phenomenon in which the magnetic fluid 23 may leak may occur.

However, in the present invention, as the grommet seal 35 is installed around the connector 34 formed at the lower end of the electric wire 32, leakage of oil is prevented.

According to the present invention, a separate second flow path is formed inside the piston valve, and a check valve is installed in the second flow path to open the second flow path only during the compression stroke, thereby moving the asymmetric damping performance region. Can be implemented.

In addition, since the second flow path opened by the check valve in the compression stroke is designed so as not to interfere with the magnetic path of the electromagnetic induction magnetic field, the reliability of the operation can be ensured, and the time caused by friction by applying the diaphragm instead of the conventional floating piston. The response characteristic is not affected.

Claims (4)

  1. A cylindrical cylinder having a diameter and a length of a predetermined size;
    A hollow rod (Hollow Rod) of a predetermined length, which is fitted into the cylinder from an upper outer side of the cylinder and has a cavity having a diameter in a longitudinal direction along an inner center line;
    A rod guide configured to guide the hollow rod in a linear state while being fitted and coupled to an upper end of the cylinder while maintaining an accurate straightness;
    It is fixedly coupled to the inner end of the hollow rod and partitions the cylinder into a lower compression chamber and an upper tension chamber, and generates an electromagnetic field during compression and tension stroke by the action of an electromagnet solenoid installed along the outer circumferential surface. It controls the flow of the filled magnetic fluid fluid and forms a first flow path by a gap formed between the outer circumferential surface of the electromagnet solenoid and the inner circumferential surface of the flux ring, and the magnetic fluid fluid of the compression chamber flows to the tension chamber only during the compression stroke. A second valve having a second valve formed therein;
    It is formed inside the piston valve, so as to communicate with the tension chamber through the upper surface of the lower plate and the upper plate of the hollow rod screwed to the center line of the piston valve in a state penetrating and formed along the vertical center line of the piston valve body. In a state in which the second flow path is configured, the second flow path is opened while being pushed upward by the pressure of the magnetic fluid filled in the compression chamber during the compression stroke, and the pressure of the magnetic fluid filled in the tension chamber during the tension stroke. A check valve for closing the second flow path while pushing downward;
    It is installed so as to have a volume compensation chamber of a predetermined volume therein from the inner lower end of the cylinder and includes a diaphragm (Diaphragm) to perform a volume compensation action while expanding and compressing according to the tension and compression stroke of the piston valve. Asymmetric damping performance controlled damper using magnetic fluid.
  2. delete
  3. A cylindrical cylinder having a diameter and a length of a predetermined size;
    A hollow rod (Hollow Rod) of a predetermined length, which is fitted into the cylinder from an upper outer side of the cylinder and has a cavity having a diameter in a longitudinal direction along an inner center line;
    A rod guide configured to guide the hollow rod in a linear state while being fitted and coupled to an upper end of the cylinder while maintaining an accurate straightness;
    It is fixedly coupled to the inner end of the hollow rod and partitions the cylinder into a lower compression chamber and an upper tension chamber, and generates an electromagnetic field during compression and tension stroke by the action of an electromagnet solenoid installed along the outer circumferential surface. It controls the flow of the filled magnetic fluid fluid and forms a first flow path by a gap formed between the outer circumferential surface of the electromagnet solenoid and the inner circumferential surface of the flux ring, and the magnetic fluid fluid of the compression chamber flows to the tension chamber only during the compression stroke. A second valve having a second valve formed therein;
    It is formed in the piston valve, formed in a diagonal direction toward the upper edge of the piston valve body in the state formed in a predetermined depth upward from the bottom of the vertical center line of the piston valve body and is tensioned through an orifice formed on the upper plate upper surface In the state of being installed inside the second flow path configured to communicate with the seal, the compression flow is pushed upward by the pressure of the magnetofluid fluid filled in the compression chamber to open the second flow path, and in the tension stroke A check valve that closes the second flow path while being pushed downward by the pressure of the fluid fluid;
    It is installed so as to have a volume compensation chamber of a predetermined volume therein from the inner lower end of the cylinder and includes a diaphragm (Diaphragm) to perform a volume compensation action while expanding and compressing according to the tension and compression stroke of the piston valve. Asymmetric damping performance controlled damper using magnetic fluid.
  4. The method according to claim 1 or 3,
    The check valve includes a spherical body fitted into the inlet of the second flow path formed in the center of the bottom surface of the piston valve;
    Asymmetric damping performance controlled damper using a magnetic fluid fluid, characterized in that the support spring for supporting the spherical body with an elastic force that always acts downward in the state of being fitted inside the second flow path corresponding to the upper side of the spherical body.
KR1020050043838A 2005-05-24 2005-05-24 A damper using magneto-rheological fluid for controlling damping performance non-symmetrically KR100696952B1 (en)

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KR100935179B1 (en) * 2008-07-29 2010-01-06 주식회사 브이원 One direction viscos damper
KR101222645B1 (en) 2011-04-26 2013-01-21 현대로템 주식회사 Particle agitating apparatus for smart fluid damper with the same
CN103470674A (en) * 2013-09-30 2013-12-25 湘潭大学 Inner-channel vehicle suspension system magnetorheological damper
CN109404466A (en) * 2018-10-30 2019-03-01 广州澳森液压元件有限公司 A kind of vehicular shock absorber that can be generated electricity

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US8141689B2 (en) * 2007-10-09 2012-03-27 Bwi Company Limited S.A. Magnetorheological (MR) piston ring with lubricating grooves
KR20100007018A (en) 2008-07-11 2010-01-22 에스앤티대우(주) Piston valve assembly and continuous damping control damper comprising the same
CN101915281A (en) * 2010-07-19 2010-12-15 谭和平 Single-rod magnetorheological damper with one-way channel
CN103352956B (en) * 2013-06-19 2015-09-23 重庆大学 The MR damper of asymmetric controllable damping characteristic
CN103758911B (en) * 2014-01-27 2016-02-10 安徽柳工起重机有限公司 The magnetorheological hydro pneumatic suspension orifice valve of vehicle

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KR100935179B1 (en) * 2008-07-29 2010-01-06 주식회사 브이원 One direction viscos damper
KR101222645B1 (en) 2011-04-26 2013-01-21 현대로템 주식회사 Particle agitating apparatus for smart fluid damper with the same
CN103470674A (en) * 2013-09-30 2013-12-25 湘潭大学 Inner-channel vehicle suspension system magnetorheological damper
CN109404466A (en) * 2018-10-30 2019-03-01 广州澳森液压元件有限公司 A kind of vehicular shock absorber that can be generated electricity

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