KR100494651B1 - Rotary type oil damper - Google Patents

Abstract

The present invention relates to a rotary oil damper, in the conventional rotary oil damper, because there is no section in which the damping force should not be generated among opening and closing sections such as a lid, and the same damping force is generated from the beginning to the end in the section where the damping force is applied. When the lid is closed, the lid cannot be completely closed, and when assembling each part after injecting oil, assembly of the damper becomes cumbersome, as it impairs the assembly work such as oil flows out during the assembly process. There was also. According to the present invention, the damping force does not occur in the non-occurring opening section in which the damping force does not occur until the rotor starts to open in the state where the rotor is completely closed in the horizontal position and reaches the vertical position so that the user can lightly open the rotor. Damping force that is flipped back in the vertical position In the open section, the damping force is generated so that the rotor does not collide with the fixed body rapidly so that the rotor can be opened safely without collision, and the vertical position in the position where the rotor is flipped back The damping force does not occur in the closing section, so no damping force is generated, so that the user can lightly close the rotor, and the damping force is generated in the closing section where the damping force is reached from the vertical position to the position just before the horizontal position. The rotor closes slowly and stops at the moment when the rotor reaches the position just before the horizontal position. As the ping force rapidly increases, the rotor temporarily stops for a moment, and then the damping force gradually decreases in the damping force dividing section where the rotor reaches the horizontal position, and the rotor is safely closed without colliding with the stationary body. As the damping force is completely dissipated when the rotor reaches the horizontal position, the user can open and close the rotor lightly without any force in opening and closing the rotor, and the rotor is opened and closed safely by various damping forces for each section. will be.

Description

Rotary Oil Damper {ROTARY TYPE OIL DAMPER}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary type oil damper, and more particularly, to a rotary oil damper for optimally capping a lid by dividing a closed section such as a lid into several sections having different damping forces.

In general, a rotary damper is used to control the closing force in a process of opening and closing a rotating element, for example, a cover of a piano or a kimchi refrigerator, a lid, a door, and the like, so that the cover or the door does not close rapidly.

Conventional rotary dampers include an elastic member-type rotary damper using an elastic member such as a spring, and a rotary oil damper for imparting a damping force using a viscous fluid.

The elastic member rotary damper, as in Korean Patent Application Publication No. 88-14508, is provided between the casing, a shaft rotatably inserted into the casing, and one end protrudes between the casing and the shaft to provide damping force to the shaft. It is composed of an elastic member to give.

Since the damping force is generated in both directions (clockwise and counterclockwise), the elastic member-type rotary damper cannot be adopted when the damping force is required only in one direction, and the spring is used as the use continues. Since there is a change in the elastic force of the elastic member there was a problem that can not maintain the desired damping force.

In addition, the conventional rotary oil damper is a hollow casing having a chamber having both ends open as shown in US Patent No. 5,635,655, and a protrusion is radially inserted into a portion of the casing rotatably inserted in one end thereof and protruded in the chamber. And a movable valve which is operated in a state in which the outer circumferential surface is in close contact with the inner circumferential surface of the casing in conjunction with the projection of the shaft, and a stopper which protrudes inside the casing to stop the rotation of the movable valve; A stopper member for closing both ends of the casing, and a viscous fluid filled in the chamber, and fluid passages having different cross-sectional areas are formed on both side walls of the movable valve, and the protrusions have a larger cross-sectional area than the fluid passages. The branches had fluid passages formed therein.

In such a rotary oil damper, when the protrusion rotates, when the viscous fluid in one region of the chamber partitioned by the protrusion and the movable valve flows to the other region through the fluid passage formed in the protrusion and the movable valve, the fluid passage resists the flow of the viscous fluid. It acts as a damping force.

Therefore, ideally, both end faces of the projection and the movable valve should be in close contact with the inner surfaces of both closure members so that the flow of the viscous fluid should not occur between the protrusions and the movable valve.

However, O-rings and the like cannot be used because both end faces of the projection and the movable valve must be rotated while being radially disposed with respect to the inner side surfaces of the both end closure members. Because it has to rotate in a state, a certain tolerance must be given, and thus internal leakage of viscous fluid is inevitably generated between both regions between the projections and both end faces of the movable valve and the inner side faces of the both end closure members.

When the flow of the viscous fluid between the two areas between the projections and the both end surfaces of the closure member and the inner surface of the closure member, the damping force set according to the cross-sectional area of the fluid passage formed in the movable valve is not accurately exhibited.

Also, in the related art, the internal leakage of the viscous fluid between the two regions between the both end surfaces of the protrusion and the movable valve and the inner surface of the both end cap members can be ignored so that the internal leakage can be ignored. The method to do is adopted.

However, in this case, as the cross-sectional area of the fluid passage increases, a large damping force cannot be obtained, and in order to increase the damping force, there is a problem in that the size of the entire damper must be increased.

In addition, as a conventional rotary oil damper, as in Korean Patent No. 208,746, a first compression chamber and a second compression chamber are formed in a housing to process a flow path so that fluid flows between them, and communicate with the first compression chamber to accommodate the pinion portion. Threads are formed respectively, and the first compression chamber houses the first plunger and closes it with a flow path adjustment opening. In the second compression chamber, the second plunger is stored together with the spring and the adjustment screw is closed to cover the pinion unit. The part was accommodated, the pinion part was assembled so as to be engaged with the rack of the first plunger, and the pinion part was fitted with a lever.

However, in the conventional rotary oil damper, since the first compression chamber and the second compression chamber must be provided, the size of the damper is not only large but also the plunger must be installed in the first compression chamber and the second compression chamber, respectively, thereby increasing the number of parts. There was a problem such as that cumbersome.

In addition, in the conventional rotary oil damper, there is no section in which the damping force should not be generated among opening and closing sections such as the lid, and in the section where the damping force is applied, the same damping force is generated from the beginning to the end. There was also a problem that could not be closed.

In addition, all the above-described types of dampers are to assemble each part after injecting oil first when assembling the dampers, thus causing troubles in assembling work such as oil flows out during the assembly process. .

Accordingly, it is an object of the present invention to provide a rotary oil damper that allows the closing operation of the lid to be optimally performed by dividing the closing section of the lid into several sections in which damping force is generated differently.

Another object of the present invention is to provide a rotary oil damper which can achieve a desired damping force by avoiding internal leakage of oil during a damping operation.

It is yet another object of the present invention to provide a rotary oil damper which makes it easy to inject oil and improve assembly productivity.

In order to achieve the object of the present invention, the front portion of the cylindrical portion is sealed with a hard plate portion and the rear portion is formed of a damper body having an open cylinder; A first compartment plate inserted into an internal space of the damper body to form an oil injection space between the damper body and a shaft hole formed at a center thereof; A second compartment plate inserted into an inner space of the damper body at a rear side of the first compartment plate to form an oil escape space between the first compartment plate and a shaft hole formed at a center thereof; A sealing plate inserted into an inner space of the damper body at a rear side of the second partition plate to seal a rear opening of the damper body and having a shaft hole at a center thereof; A rotating shaft rotatably installed through the shaft hole of the first partition plate, the second partition plate, and the sealing plate, and having a rear end protruding to the rear of the sealing plate; A pair of wings protruding from both outer peripheral surfaces of the distal end of the rotary shaft to be in intimate contact with the inner circumferential surface of the cylindrical portion, the hard plate portion, and the first partition plate in the oil injection space; A pair of valve balls formed in the first compartment plate to connect the oil injection space and the oil escape space; the valve balls are opened when the lid shaft rotates in the rotary shaft, and the valves when the lid shaft rotates in the lid shaft. A check valve having a valve ball for closing the ball; An arc-shaped space connecting hole formed in an arc shape at a predetermined angle section from a position spaced a predetermined angle from the valve hole in the first partition plate to connect the oil injection space and the oil escape space; It is formed in an arc shape with a constant width in a predetermined angle section on the front of the first partition plate, one end portion is in communication with the space connecting hole and gradually formed shallower from the one end portion thereof, the other end portion of the second partition plate An arcuate orifice groove closed by; There is provided a rotary oil damper, characterized in that the configuration.

The wing is in contact with an approximately c-shaped cross section in which an engaging groove is formed by an arc portion having an arc-shaped contact surface in close contact with the inner circumferential surface of the cylindrical portion of the damper body and a pair of wall portions extending in the center direction of the rotation shaft from both sides of the arc portion. The pad is inserted and coupled.

Guide protrusions parallel to the rotating shaft are formed on both side surfaces of the wing, and guide grooves corresponding to the guide protrusions are formed on the inner side of the coupling groove of the contact pad.

The coupling groove of the contact pad is formed to gradually increase in the circumferential width toward the center side of the rotation shaft.

An oil injection hole communicating with the ball receiving space of the valve body is formed in the hard plate portion of the damper main body, and further includes a closing member for closing the oil injection hole.

The oil injection hole includes a screw hole having a threaded portion formed on an inner circumferential surface thereof, and a counterbore hole formed on the front side of the screw hole, and the closing member has a screw that is fastened to the screw hole and a head inserted into the counterbore hole. O-ring is inserted between the gongbobore ball and the head to maintain the airtightness.

Hereinafter, the rotary oil damper according to the present invention will be described in detail according to the embodiment shown in the accompanying drawings.

1 is a perspective view of a rotary oil damper according to the present invention, Figures 2a and 2b is an exploded perspective view of the rotary oil damper according to the present invention viewed from the rear and front, respectively, Figure 3 is the end of the rotary oil damper according to the present invention 4 is a cross-sectional view taken along the line IV-IV of FIG. 3A, and FIG. 5 is a cross-sectional view taken along the line V-V of FIG. 3A.

1 to 5, 10 is a damper body, 20 is a first compartment plate, 30 is a second compartment plate, 40 is a closed plate, 50 is a rotating shaft, 60 is a blade, and 70 is a check valve.

The damper body 10 includes a cylindrical portion 11 and a hard plate portion 12 formed integrally with the front portion of the cylindrical portion 11, as shown in Figs. 2A and 2B, 3A and 3B. It is formed in a cylindrical shape, the rear portion is open.

The support shaft 13 for supporting the rotating shaft 50 is protruded from the center of the rear surface of the damper body 10 of the damper body 10, and the female screw portion 14 is formed on the inner circumferential surface of the open portion side.

On the outer circumferential surface of the rear end of the damper main body 10, a fixing bracket 15 for fixing to the fixed body 1 on which the rotating body 2 such as a cover is rotatably installed is integrally formed. The bracket 15 has a threaded through hole 15a through which the set screw 3 passes.

As shown in FIGS. 3A and 3B, the first partition plate 20 is inserted into an internal space of the damper body 10 to form an oil injection space S1 between the hard plate portions 12. The shaft hole 21 is formed in the center part.

As shown in FIGS. 2A and 2B, and FIGS. 3A and 3B, the second partition plate 30 is inserted into the interior space of the damper body 10 at the rear side of the first partition plate 20. The oil escape space S2 is formed between the first partition plate 20, and the shaft hole 31 is formed at the center thereof.

A plurality of spacer protrusions 32 are formed on a front surface of the second partition plate 30 so as to form an oil escape space S2 between the rear surface of the first partition plate 20.

1 to 4, the sealing plate 40 seals the rear opening of the damper body 10, and a shaft hole 41 is formed in the center thereof.

On the outer circumferential surface of the sealing plate 40, a male screw portion 42 screwed to the female screw portion 14 of the damper body 10 is formed.

As shown in FIGS. 2A to 3B, the rotation shaft 50 may be configured to form shaft holes 21, 31, and 41 of the first partition plate 20, the second partition plate 30, and the sealing plate 40. The front end surface penetrates the rear surface of the hard plate portion 12 of the damper body 10, and the rear end portion thereof is installed to protrude to the rear of the sealing plate 40.

A support groove 51 into which the support shaft 13 of the damper body 10 is fitted is formed at the front end of the rotation shaft 50.

The bushing 52 is inserted between the support shaft 13 and the support groove 51. The bushing 52 is made of synthetic resin material to minimize friction.

The rear end of the rotary shaft 50 is formed with a square portion 53 for preventing the idle when coupled to the rotary body 2, such as a lid.

For example, in coupling the rotating body 2 to the rotating shaft 50, as shown in Figs. 13, 15 and 17, the brackets 4, 5 and 6 may be coupled to the rotating body 2. In this case, the square portion 53 is inserted into the square grooves 4a, 5a, 6a formed in the brackets 4, 5, 6.

The pair of vanes 60, as shown in Figures 2a to 4 protruding to the outer peripheral surface of the front end portion of the rotary shaft 50, the inner peripheral surface of the cylindrical portion 11 in the oil injection space (S1) It is in close contact with the hard plate portion 12 and the first partition plate 20.

As shown in FIGS. 2A to 4 and 8, the wing 60 has a contact pad 61 having a substantially c-shaped cross section, respectively. The contact pad 61 has an arc portion 62 having an arc-shaped contact surface 62a which is in intimate contact with the inner circumferential surface of the cylindrical portion 11 of the damper body 10, and a rotation shaft 50 on both sides of the arc portion 62. Coupling groove 64 is formed by a pair of wall portions 63 extending in the center direction of ().

As shown in FIG. 8, the contact pad 61 may be coupled to the blade 60 so as to be movable in a radial direction of the rotation shaft 50. The reason for this is described later.

To this end, the width of the circumferential direction of the coupling groove 64 gradually increases toward the center of the rotation shaft 50, and forms the thickness of the wing 60 thinner toward the outer circumferential direction.

In addition, the guide protrusions 65 and the guide grooves 66 are formed on both side surfaces of the blade 60 and the inner surface of the coupling groove 64 in a direction parallel to the rotation shaft 50, respectively.

The guide protrusion 65 and the guide groove 66 guide the contact pad 61 in a direction parallel to the rotation axis 50 with respect to the blade 60, while the contact pad 61 is radial in the blade 60. In addition to being formed to flow in the contact pad 61 is formed so as not to be separated randomly with respect to the radial direction of the wing (60). That is, the radial width of the guide groove 66 is formed to be wider than the radial width of the guide protrusion (65).

The check valve 70 is formed in the first partition plate 20, as shown in Figs. 2a to 4 and 7, a pair for connecting the oil injection space (S1) and the oil escape space (S2) Of the valve hole 71, the pair of valve bodies 72 formed in the damper body 10, and the valve body 72 are rotated in the lid opening direction of the rotary shaft 50. The valve ball 71 is opened and the valve ball 76 is closed to close the valve ball 71 when the rotary shaft 50 rotates in the cap closing direction.

The pair of valve bodies 72 are rotationally symmetrical with respect to the center of the rotation shaft 50, and the cylindrical portion 11 on both sides of the inner surface of the hard plate portion 12 relative to the rotation shaft 50 Along the inner circumferential surface of the rotation axis 50 is formed extending in parallel with the ball receiving space 73 is formed therein to connect the ball receiving space 73 and the oil injection space (S1) on the side facing the wing (60) An oil flow hole 74 is formed and a ball entrance 75 is formed at the rear end thereof to communicate with the valve hole 71.

The valve ball 76 is accommodated in the ball receiving space 73 of the pair of valve body 72 is installed to open and close the pair of valve holes 71 through the ball inlet (75).

The valve ball 76 is pushed toward the valve hole 71 by the pressure of the oil even if it is not elastically supported by a separate spring to act as a check valve, but in the ball receiving space 73 of the valve body 72. Compression springs 77 for elastically supporting the valve ball 76 toward the valve hole 71 may be inserted.

As shown in FIGS. 2A to 5 and 9 to 11, the first compartment plate 20 has the oil injection space S1 and the oil escape at a predetermined angle from the position spaced from the valve hole 71. An arc-shaped space connecting hole 81 communicating with the space S2 is formed through a predetermined width.

One end portion communicates with the space connecting hole 81 at a predetermined angle section on the front of the first partition plate 20 and is gradually formed in shallow depth from one end thereof, and the other end thereof is the second partition plate 30. The circular arc orifice groove 82 is closed by a) is formed to a predetermined width.

In the middle of the orifice groove 82 is formed a neck portion 83 narrowing the width.

When applying the rotary oil damper of the present invention to the damping of the piano cover, for example, as shown in Figure 9, the angular interval from the center of the valve hole 71 to one end of the space connecting hole 81 is 20 The angle interval from the one end of the space connecting hole 81 to the one end of the orifice groove 82 is 41 °, and the angle interval from the one end of the orifice groove 82 to the neck 83 is It is preferable to set it as 70 degrees, and to set the angular space from the neck part 83 to the other end of the orifice groove 82 to 19 degrees.

2A, 2B, 5, in order to accurately match the ball inlet 75 and the valve hole 71 of the valve body 10 when assembling the first partition plate 20 with respect to the damper body 10. As shown in FIGS. 7 and 10, positioning protrusions 16 are formed on both sides of the inner circumferential surface of the cylindrical portion 12 of the damper main body 10, and the outer periphery of the first partition plate 20 is formed. Positioning grooves 22 corresponding to the positioning projections 16 are formed.

The positioning projection 16 may be formed at any position irrespective of the valve body 72, but is preferably formed along the inner circumferential surface of the damper body 10 on the upper surface of the valve body 72.

As shown in FIGS. 2B, 3B and 7, the oil injection hole 17 communicating with the ball receiving space 73 of the valve body 10 is provided in the hard plate portion 12 of the damper body 10. And the oil injection hole 17 is closed by the closing member 18.

The oil injection hole 17 is composed of a screw hole portion 17a having a female threaded portion formed on an inner circumferential surface thereof, and a counterbore portion 17b formed on the front side of the screw hole portion 17a, and the closing member 18 includes the screw. A screw having a screw portion 18a fastened to the study 17a and a head portion 18b inserted into the counterbore portion 17b is used.

In addition, an O-ring 19 is inserted between the counterbore 17b and the head 18b to maintain airtightness.

As shown in FIGS. 1 and 2A, 3A, and 3B, a tool insertion for inserting a tool when turning the sealing plate 40 to the valve body 10 is fastened to the rear surface of the sealing plate 40. Grooves 43 are formed.

O-ring grooves 33 and 34 are formed around and around the axial hole 31 on the rear surface of the second partition plate 30, respectively.

In sealing the rear opening of the damper main body 10 with the sealing plate 40, the flange portion 91 in close contact with the rear surface of the second partition plate 30 extends rearward from the flange portion 91. A bushing 90 having a bushing portion 92 inserted between the shaft hole 41 of the sealing plate 40 and the outer circumferential surface of the rotating shaft 50 is used, and each of the O-ring grooves 33 and 34 has an o-ring 93, 94 is inserted so that the O-ring 93 is in close contact with the flange portion 91 and the O-ring 94 is in close contact with the sealing plate 40 to maintain airtightness.

Assembly of the rotary oil damper according to the present invention configured as described above is made as follows.

In the state in which the sealing member 18 and the O-ring 19 are removed from the oil injection hole 17 formed in the hard plate portion 12 of the damper body 10, the valve ball ( Insert 76). At this time, if necessary, after inserting the compression spring 77 before inserting the valve ball 76, the valve ball 76 is inserted.

The rotary shaft 50 is inserted into the inner space of the damper body 10 in a state in which the contact pad 61 is coupled to the wing 60 so that the support groove 51 is inserted into the support shaft 13 and supported.

In coupling the contact pad 61 to the blade 60, the blade 60 is inserted into the coupling groove 64 of the contact pad 61, and at the same time, the guide protrusion 65 formed on the blade 60 is the coupling groove. To be fitted into the guide groove (66) formed in (64).

Since the guide groove 66 has a radial width that is wider than the radial width of the guide protrusion 65, the contact pad 61 is guided in a direction parallel to the rotation axis 50 with respect to the blade 60, and also has a radius. While being able to flow in the direction it is coupled in a state that does not leave at random in the radial direction.

The first partition plate 20 is inserted into the interior space of the damper body 10 so that the oil injection space S1 is formed in the interior space of the damper body 10. At this time, the rear end portion of the rotation shaft 50 comes out through the shaft hole 21 of the first partition plate 20.

In addition, the damper body 10 and the first partition plate 20 are set by the positioning grooves 22 formed at the outer periphery of the first partition plate 20 and the positioning protrusions 16 formed on the damper body 10. It is precisely coupled to the relative position.

At the rear side of the first partition plate 20, the second partition plate 30 is inserted into the interior space of the damper body 10 so that the spacer protrusions 32 closely contact the rear surface of the first partition plate 20. The oil escape space S2 is formed between the rear surface of the first compartment plate 20 and the front surface of the second compartment plate 30. At this time, the rear end of the rotating shaft 50 to come out through the shaft hole 31 of the second partition plate 30.

O-rings 93 and 94 are respectively inserted into the O-ring grooves 33 and 34 of the second partition plate 30, and the bushing 90 is inserted into the flange portion 91 so that the O-ring 93 can be pressed. Be sure to

Align the male screw portion 42 of the sealing plate 40 with the female screw portion 14 of the damper body 10, and turn the sealing plate 40 in the screw tightening direction so that the sealing plate 40 is fastened to the damper body 10. do. At this time, the clamping force of the sealing plate 40 is directly applied to the O-ring 94, the O-ring 93 is applied through the flange portion 91 of the bushing 90 is in a state capable of maintaining airtightness.

Thereafter, oil is injected into the oil injection space S1 through the oil injection hole 17, and the oil injection hole 17 is closed by the closing member 18. At this time, the screw portion 18a of the sealing member 18 is fastened to the screw hole 17a of the oil injection hole 17, and the head portion 18b of the sealing member 18 is the counterbore portion of the oil injection hole 17. It will be in the state inserted in 18b. In addition, the oil injected by inserting the O-ring 19 between the counterbore 18b and the head 18b does not leak arbitrarily.

Therefore, since the oil injection to the oil injection space (S1) is completed after the assembly of all the parts of the damper is completed, the oil does not flow out during the assembly process, it is possible to facilitate the assembly of the damper.

Hereinafter, a process of installing the rotary oil damper of the present invention on the fixed body and the rotating body will be described.

FIG. 13 and FIG. 14 show an example in which the rotary oil damper of the present invention is applied to a GP type rotor. FIG. 15 and FIG. 16 show an example in which the rotary oil damper of the present invention is applied to a console type rotor. And FIG. 18 shows an example in which the rotary oil damper of the present invention is applied to an UP-type rotating body. The damper main body 10 includes a fixing screw 3 passing through the fixing bracket 15 of the fixing body 1. Fixed by fastening to the side surface and fixed to the side surface of the rotating body 2 with a fixing screw 7 and having a square groove 4a, 5a, 6a parallel to the horizontal surface of the rotating body 2, Installation is completed by inserting the square part 53 of the rotating shaft 50 into square groove 4a, 5a, 6a using 5,6.

Each of these rotors 2 is only to change the relative angle of the square portion 53 and the blade 60 of the rotary shaft 50, the damping action is made the same, so the operation will be described below in common.

Hereinafter, the operation of the rotary oil damper of the present invention will be described.

12A illustrates a state of the rotation shaft 50, the blade 60, the check valve 70, the space connecting hole 81, and the orifice groove 82 when the rotor 2 is closed in a horizontal state. As shown in the drawing, the wing 60 is in a state where the oil distribution hole 74 side of the valve body 72 is located.

In this state, when the rotary body 2 is lifted, the rotating shaft 50 and the blade 60 start to rotate clockwise, and in the clockwise direction of the blade 60, the oil in the oil injection space S1 is pressurized and the blade ( On the counterclockwise side of 60), negative pressure is generated.

At this time, the oil pressurized in the clockwise side of the wing 60 is escaped to the oil escape space (S2) through the space connecting hole 81, the oil escape space (S2) by the negative pressure in the counterclockwise direction of the wing (60). Oil of the thrust) pushes the valve ball 76 through the valve hole 71 and the counter-clockwise side oil of the wing 60 through the ball entrance 75, the ball receiving space 73 and the oil distribution hole 74 Damping force is not generated because it is introduced into the injection space (S1).

This damping force non-occurrence opening section starts from (a) of FIG. 12 and proceeds until the wing 60 reaches the space connecting hole 81 as shown in (b) of FIG. 12.

On the basis of the rotating body 2 rotatably supported by the fixed body 1 by the rotary oil damper of the present invention, the damping force non-occurring opening section from (a) to (b) of FIG. 12 is a rotating body. (2) is set to a section that opens up to a vertical position in a horizontally closed state.

Therefore, the user only needs to bear the weight of the rotating body 2 to open the rotating body 2 from the horizontal state to the vertical state, so that it can be easily opened without great force.

Subsequently, when the rotating body 2 exceeds the vertical state, even if the user releases the hand from the rotating body 2, the rotating body 2 continues to be flipped by the weight of the rotating body 2, and the wing 60 is a space connecting hole 81. ) And the cross-sectional area of the space connecting hole 81 remaining on the clockwise side of the wing 60 is gradually reduced, the oil of the oil injection space (S1) through the space connecting hole 81 oil escape space ( Since the flow resistance increases in the process of escaping to S2), a damping force is generated such that the rotor 2 does not collide with the fixed body 1.

The collision preventing damping force generation opening section starts from (b) of FIG. 12 when the wing 60 passes through the space connecting hole 81 and reaches the valve body 72 as shown in (c) of FIG. 12. Proceeds to.

In the state of FIG. 12C, since the cross-sectional area of the space connecting hole 81 remaining on the clockwise side of the wing 60 is "0", the largest damping force is generated during the process of opening the rotating body 2. In this state, the rotating body 2 does not collide with the fixed body 1 at the open end by this action.

When the rotating shaft 50 and the wing 60 is rotated counterclockwise in the state of Fig. 12 (c) in the state that the rotor 2 is fully opened to the retracted position, the counterclockwise direction of the wing 60 In the oil in the oil injection space (S1) is pressurized and negative pressure is generated in the clockwise direction of the wing (60).

The oil pressurized in the counterclockwise direction of the blade 60 flows into the oil escape space S2 through the space connecting hole 81, and in the clockwise direction of the wing 60, the oil in the oil escape space S2 is negatively affected by negative pressure. It is introduced into the oil injection space (S1) through the space connecting hole 81 so that the damping force does not occur.

This damping force non-occurrence closing section starts from (c) of FIG. 12 and proceeds until the wing 60 escapes the space connecting hole 81 as shown in (b) of FIG. 12.

Referring to the rotating body 2 rotatably supported by the fixed body 1 by the rotary oil damper of the present invention, the damping force non-occurring closing section from (c) to (b) of FIG. 12 is a rotating body. (2) is set to a section that closes to the vertical position in the state of being flipped back.

Therefore, the user only needs to bear the weight of the rotating body 2 to close the rotating body 2 to the vertical state in the state of being rolled back, so that it can be easily closed without great force.

After that, if the rotor 2 is beyond the vertical state, even if you remove the hand from the rotor 2 will continue to be closed by the weight of the rotor 2,

Since the wing 60 reaches the orifice groove 82, the oil pressurized in the counterclockwise direction of the wing 60 flows into the ball receiving space 73 through the oil error hole 74 and opens the valve ball 76. It is pushed up and the valve ball 76 closes the valve hole 71 through the ball inlet 75 so that the oil in the oil injection space S1 cannot escape to the oil escape space S2, and the oil injection space ( S1) is connected to the space connecting hole 81 only through the orifice groove 82, so that the escape path is narrowed, so that a damping force for slowly rotating the rotor 2 is generated.

The damping force generation closing section starts from (b) of FIG. 12 and proceeds until the wing 60 reaches the neck portion 83 of the orifice groove 82 as shown in (d) of FIG. 12.

In addition, since the orifice groove 82 has the deepest depth of the portion connected to the space connecting hole 81 and the depth of the portion close to the valve body 72 is the shallowest, as shown in FIG. Is the smallest of the damping force generated in the damping force generation closing section when the orifice groove 82 and the space connecting hole 81 at the boundary portion, the damping force is gradually generated toward the valve body 72 side.

Therefore, in the process of rotating the rotating body 2 from the vertical position to the horizontal position by its own weight, the rapid closing operation of the rotating body 2 does not occur and is closed gradually.

In the state where the rotor 2 reaches the position immediately before reaching the horizontal position, as shown in FIG. 12 (d), the blade 60 reaches the neck portion 83 of the orifice groove 82, and this neck In the part 83, since the width | variety is abruptly reduced, the damping force becomes large rapidly, and the rotating body 2 momentarily pauses.

After the momentary closing section, the wing 60 is out of the neck portion 83 and a smaller damping force than the damping force in the neck portion 83 is generated, and then the wing 60 is orifice groove 82 again. In the process of reaching the end of the depth, the depth gradually becomes shallow, but since the oil remaining on the counterclockwise side of the wing 60 is almost escaped, the damping force is reduced, but the rotor 2 does not use the damper. Compared to the case, since the damping force is generated, the rotor 2 is gradually closed.

In this damping force decrement closing section, damping force is generated so that the rotor 2 does not collide with the fixture 1 so that the rotor 2 does not collide with the fixture 1 rapidly. do.

As shown in FIG. 12A, when the wing 60 reaches the valve body 72, all of the oil in the oil injection space S1 flows in the clockwise direction of the wing 60. Since no oil remains on the counterclockwise side of the damping force, the rotor 2 is completely closed.

Here, the moment the blade 60 passes through the neck portion 83, that is, the position where the rotor 2 pauses momentarily is set to a position where the rotor 2 is lifted by approximately 20 degrees from the horizontal, the rotor The closing operation of (2) can be completed smoothly.

On the other hand, since the contact pad 61 is coupled to the wing 60, the wing 60 is the inner peripheral surface of the cylindrical portion 11 of the damper body 10 and the rear surface of the hard plate portion 12 and the first partition plate 20 The contact is in close contact with the front of the internal leakage does not occur.

In addition, since the contact pad 61 is coupled to the blade 60 so as to be movable in the radial direction of the rotation shaft 50, the contact pad 61 is a cylindrical portion of the damper main body 10 due to the pressure applied to the oil. (11) Since it is pressed in the direction in close contact with the inner circumferential surface, it is possible to more reliably prevent internal leakage.

In addition, guide protrusions 65 parallel to the rotating shaft 50 are formed on both side surfaces of the blade 60, and guide grooves 66 corresponding to the guide protrusions 65 on the inner surface of the coupling groove 64 of the contact pad 61. ) Is formed, and the radial width of the guide groove 66 is wider than the radial width of the guide protrusion 65, so that the guide protrusion 65 and the guide groove 66 is a contact pad (61) While contacting the blade 60 in a direction parallel to the rotation axis 50 and the contact pad 61 flows radially with respect to the blade 60 to prevent the internal leakage while assembling the contact pad during the assembly operation The 61 is not detached arbitrarily with respect to the radial direction of the blade 60, and assembling operation becomes convenient.

As described above, in the present invention, the damping force does not occur in the non-occurring opening section in which the damping force does not occur in the open position when the rotor starts to open in the state where the rotor is completely closed in the horizontal position, thereby allowing the user to lightly open the rotor. Damping force generation in which the rotor leans back from the vertical position In the open section, the damping force is generated so that the rotor does not collide rapidly with the fixed body, so that the rotor can be opened safely without collision, and the rotor is turned backward Damping force does not occur in the non-occurring closing section from to vertical position, allowing the user to lightly close the rotating body, and damping force in the closing section generating damping force from the vertical position to the position just before the horizontal position. Occurs and the rotor closes slowly and stops momentarily when the rotor reaches its position immediately before the horizontal position. In the liver, the damping force increases rapidly and the rotor temporarily stops for a moment, and then the damping force gradually decreases in the damping force closing section where the rotor reaches the horizontal position so that the rotor can safely close without colliding with the fixed body. Finally, when the rotating body reaches the horizontal position, the damping force is completely dissipated, so the user can open and close it lightly without opening and closing the rotating body. The effect is to open and close.

1 is a perspective view of a rotary oil damper according to the present invention.

2 is an exploded perspective view of a rotary oil damper according to the present invention;

Figure 2a is an exploded perspective view seen from the rear of the rotary oil damper,

2b is an exploded perspective view of the rotary oil damper viewed from the front;

3 is a longitudinal side view of a rotary oil damper according to the present invention;

Figure 3a is a longitudinal side view along the line passing through the wing,

Figure 3b is a longitudinal side view along the line passing through the check valve,

4 is a cross-sectional view taken along the line IV-IV of FIG. 3A.

5 is a cross-sectional view taken along the line VV of FIG. 3A.

6 is a cross-sectional view taken along the line VI-VI in FIG. 3A.

7 is a cut perspective view of the damper body.

8 is a cross-sectional view showing a rotating shaft, the blade and the contact pad.

9 is a front view of the first compartment plate.

10 is a rear view of the first compartment plate.

11 is an exploded cross-sectional view of the oil distribution hole and the orifice groove of the first partition plate.

12 is an operational state diagram of the rotary oil damper of the present invention.

Figure 13 is a combined state of the G.P type rotary body and the bracket to which the rotary oil damper of the present invention is applied.

Figure 14 is an operating state of the rotating body showing an example in which the rotary oil damper of the present invention is applied to the G.P type rotating body.

Figure 15 is a combined state of the console-type rotating body and the bracket to which the rotary oil damper of the present invention is applied.

Figure 16 is an operating state of the rotating body showing an example of applying the rotary oil damper of the present invention to the console-type rotating body.

Figure 17 is a coupling state of the U.P type rotor and the bracket to which the rotary oil damper of the present invention is applied.

18 is an operational state diagram of a rotating body showing an example in which the rotary oil damper of the present invention is applied to a U.P type rotating body.

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

1: fixed body 2: rotating body

10: damper main body 11: cylindrical part

12: hard plate portion 13: support shaft

15: Fixing bracket 16: Positioning protrusion

17: oil injection hole 18: closing member

20: first compartment plate 22: positioning groove

30: second compartment 32: spacer projection

40: sealing plate 50: rotating shaft

60: wing 61: contact pad

64: coupling groove

65: guide protrusion 66: guide groove

70: check valve 71: valve ball

72: valve body 73: ball receiving space

74: oil distributor 75: ball entrance

76: valve ball 77: compression spring

81: space connector 82: orifice groove

83: neck

90: bushing 91: flange

92: bushing 93,94: O-ring

Claims (18)

A damper body formed in a cylindrical shape in which the front portion of the cylindrical portion is closed by the hard plate portion and the rear portion is opened; A first compartment plate inserted into an internal space of the damper body to form an oil injection space between the damper body and a shaft hole formed at a center thereof; A second compartment plate inserted into an inner space of the damper body at a rear side of the first compartment plate to form an oil escape space between the first compartment plate and a shaft hole formed at a center thereof; A sealing plate inserted into an inner space of the damper body at a rear side of the second partition plate to seal a rear opening of the damper body and having a shaft hole at a center thereof; A rotating shaft rotatably installed through the shaft hole of the first partition plate, the second partition plate, and the sealing plate, and having a rear end protruding to the rear of the sealing plate; A pair of wings protruding from both outer peripheral surfaces of the distal end of the rotary shaft to be in intimate contact with the inner circumferential surface of the cylindrical portion, the hard plate portion, and the first partition plate in the oil injection space; A pair of valve balls formed in the first compartment plate to connect the oil injection space and the oil escape space; the valve balls are opened when the lid shaft rotates in the rotary shaft, and the valves when the lid shaft rotates in the lid shaft. A check valve having a valve ball for closing the ball; An arc-shaped space connecting hole formed in an arc shape at a predetermined angle section from a position spaced a predetermined angle from the valve hole in the first partition plate to connect the oil injection space and the oil escape space; It is formed in an arc shape with a constant width in a predetermined angle section on the front of the first partition plate, one end portion is in communication with the space connecting hole and gradually formed shallower from the one end portion thereof, the other end portion of the second partition plate An arcuate orifice groove closed by; Rotary oil damper, characterized in that it comprises a. According to claim 1, wherein the outer peripheral surface of the rear end of the damper body is integrally formed with a fixing bracket having a fixing screw hole for fixing to a fixed body rotatably installed, such as a cover, the rear end of the rotary shaft Rotating oil damper, characterized in that the square is formed to prevent the idle when coupled to the rotating body. 2. The rotary oil damper according to claim 1, wherein a support shaft for supporting the rotation shaft is protruded from a center of the hard plate portion of the damper body, and a support groove for fitting the support shaft is formed at the tip of the rotation shaft. 4. The rotary oil damper according to claim 3, wherein a bushing is inserted between the support shaft and the support groove. The method of claim 1, wherein the check valve, An oil flow that connects the ball receiving space and the oil injection space on the side facing the wing is formed in the ball bearing space formed therein is formed extending in parallel to the rotation axis along the inner circumferential surface of the cylindrical portion on the inner side of the hard disk portion relative to the rotation axis A ball is formed and the rear end portion is formed with a ball inlet communicating with the valve ball and a pair of valve body disposed in a rotationally symmetrical type with respect to the center of the rotating shaft, A rotary oil damper, characterized in that it comprises a valve ball which is accommodated in each ball receiving space to open and close the valve ball through the ball entrance. The rotary oil damper according to claim 1, wherein a neck portion of which the width is narrowed is formed in the middle of the arc-shaped orifice groove. According to claim 1 or 6, wherein the interval from the center of the valve hole to the beginning of the space connection hole is 20 °, the formation section of the space connection hole is 41 °, at the end of the communication connection portion The section to the neck portion is 70 °, the section from the neck portion to the end of the orifice groove is a rotary oil damper, characterized in that 19 °. The rotary oil damper of claim 1, wherein a spacer protrusion is formed on a front surface of the second compartment plate to form an oil escape space between the first compartment plate. 2. The rotary oil damper according to claim 1, wherein positioning grooves are formed at both sides of the outer circumferential surface of the first partition plate, and positioning protrusions corresponding to the positioning grooves are formed at both sides of the inner circumferential surface of the cylindrical portion of the damper body. . 10. The rotary oil damper of claim 9, wherein the positioning protrusion is formed at one side of the valve body. The rotary oil damper of claim 10, wherein the positioning protrusion is formed at a position in which the pair of valve bodies are symmetrically rotated with respect to the center of the rotating shaft. According to claim 1, wherein the wing is formed with an engaging groove formed by a circular arc portion having an arc-shaped contact surface in close contact with the inner peripheral surface of the cylindrical portion of the damper body and a pair of wall portions extending in the direction of the center of the rotation shaft on both sides of the arc portion; Rotary oil damper, characterized in that the contact pad of the approximately U-shaped cross section is inserted. The rotary oil damper of claim 12, wherein guide protrusions parallel to the rotation shaft are formed on both side surfaces of the wing, and guide grooves corresponding to the guide protrusions are formed on an inner surface of the coupling groove of the contact pad. The rotary oil damper according to claim 12 or 13, wherein the engaging groove of the contact pad is formed such that its circumferential width gradually increases toward the center side of the rotating shaft. The rotary oil damper of claim 1, wherein an oil injection hole communicating with the ball receiving space of the valve body is formed in the hard plate portion of the damper main body, and further includes a closing member for closing the oil injection hole. . The oil injection hole of claim 15, wherein the oil injection hole comprises a screw hole having a threaded portion formed on an inner circumferential surface thereof, and a counterbore hole formed on a front side of the screw hole, and the closing member is disposed on the screw portion and the counterbore hole fastened to the screw hole. Rotating oil damper, characterized in that the screw having a head to be inserted, the O-ring for maintaining the airtightness between the gongbobore ball and the head. The rotary oil damper of claim 1, wherein the damper body and the sealing plate are coupled by a female screw portion formed on the inner circumferential surface of the rear end of the damper body and a male screw portion formed on the outer circumferential surface of the sealing plate. 18. The bushing according to claim 17, further comprising: a flange portion in close contact with a rear surface of the second partition plate; a bushing portion extending rearward from the flange portion and inserted between the shaft hole of the sealing plate and the outer peripheral surface of the rotating shaft; And an O-ring inserted between the rear surface of the partition plate and the front surface of the flange portion, and the O-ring inserted between the front surface of the sealing plate, the rear surface of the second partition plate, and the inner circumferential surface of the damper body.