KR20110055038A

KR20110055038A - Rotary oil damper

Info

Publication number: KR20110055038A
Application number: KR1020090111899A
Authority: KR
Inventors: 이해만
Original assignee: 이해만
Priority date: 2009-11-19
Filing date: 2009-11-19
Publication date: 2011-05-25

Abstract

PURPOSE: A rotary oil damper is provided to ensure gentle rotation of a rotator by preventing sudden movement of the rotator due to the self weight or external forces. CONSTITUTION: A rotary oil damper comprises a casing(110) which is fixed on a base and accommodates oil, a rotating member(120) which is coupled to a hollow(111) of the casing on an end and to a rotator on the other, and a piston which is inserted in a coupling groove(123) and moved in the axial direction as being rotated along with the rotating member within the hollow of the casing. The piston pressurizes oil in the hollow of the casing by the axial motion. An air gap(g) is formed on the outer periphery of the piston and the inner periphery of the casing to allow the flow of oil.

Description

Rotary oil damper

The present invention relates to a rotary oil damper, and more particularly, to a rotary oil damper for preventing stable rotation of a rotating body rotating a predetermined section by its own weight or external force.

In general, the rotating body hinged to be rotated within a certain radius with respect to the main body, such as a bidet cover or piano cover is closed by its own weight at a certain angle or more when opened and closed by the user, the weight of the rotating body is In the case of heavy, the opening and closing speed is accelerated to impact the noise and breakage while colliding with the main body, the user had to be inconvenient to hold the rotating body to open and close completely.

Therefore, various dampers having a deceleration function have been proposed and applied to prevent a sudden rotation of a rotating body that is rotated within a certain radius to prevent shock noise and damage and to ensure stable operation.

Dampers having a deceleration function according to the prior art include a spring damper using an elastic body and a rotary oil damper using a fluid resistance.

The spring damper is a spring using the elastic force of the spring, the rotor is not completely closed, the phenomenon is slightly lifted up and the noise caused by the spring with the problem that the reliability of the operation is not guaranteed due to the spring elastic force deterioration in the long-term use There was a downside.

In order to improve the disadvantage of the spring damper, a rotary oil damper has been proposed, and the rotary oil damper is configured by coupling a rotator into a casing filled with viscous oil having high fluid resistance, and rotating the casing and the rotator. It consists of a structure constituting a control valve for generating a different resistance force according to the direction.

By the way, the existing rotary oil damper has the advantage that can solve a number of problems with the spring damper, while the speed is lowered gradually when descending has a disadvantage that a big shock occurs when reaching the final target point. Therefore, when the viscous force of the oil is increased to reduce the impact, the rotational speed of the rotating body becomes too slow, and when rotating in the opposite direction, a lot more force is required, which makes the operation difficult.

The present invention is to solve the problems of the conventional rotary oil damper as described above, an object of the present invention is to maintain a constant descent speed of the rotating body even at low viscosity, a rotary that can provide a smooth operation ability To provide an oil damper.

The present invention for achieving the above object, in the rotary damper for rotatably connecting the rotating body with respect to the base in a predetermined angle range, the hollow casing is fixed to the base, the oil is contained therein and; A rotating member having one end rotatably coupled to the hollow portion of the casing and the other end coupled to the rotating body to rotate together with the rotating body; One end is inserted into the coupling groove formed in the rotating member and installed to move in the axial direction while rotating in conjunction with the rotating member in the hollow part of the casing, thereby pressurizing oil in the hollow part of the casing by the axial movement. And a piston having an air gap formed between an outer circumferential surface and an inner circumferential surface of the casing, thereby providing a rotary oil damper.

According to the present invention, the pressure is constantly changed by moving in the casing of the rotary oil damper to the opposite direction of the movement of the piston inside the casing by the axial movement of the piston, so that the rotational movement of the rotor relative to the base is smooth. It is smooth and stable even with low viscosity oils.

Hereinafter, exemplary embodiments of the rotary oil damper according to the present invention will be described in detail with reference to the accompanying drawings.

1 to 5 show a first embodiment of a rotary oil damper according to the invention. Rotary oil damper of the present invention is a device for interconnecting a rotating body (not shown) that rotates in a predetermined angle range with respect to the base (not shown), such as bidet, piano, notebook, etc., the casing is fixed to the base (not shown) ( 110, a rotatable member 120 rotatably installed on the casing 110 and having one end coupled to the rotating body (not shown) and rotating together with the rotating body, and a rotating member inside the casing 110. A piston 130 for compressing and flowing the oil contained in the casing 110 while moving in the axial direction by the rotational movement of 120, and a compression for elastically supporting the piston 130 in the casing 110 It is configured to include a spring (160). Reference numeral 180 is a stop ring that is coupled to the open end of the casing 110 to prevent the rotating member 120 is separated out of the casing 110.

One end of the casing 110 is closed, the other end is formed of a hollow cylindrical body formed to be open. On the inner circumferential surface of the hollow part 111 of the casing 110, a plurality of guide protrusions 112 for axial movement of the piston 130 are formed spirally.

The rotating member 120 is formed to extend in an outward direction to the rotating portion 121 and the one end of the rotating portion 121 is rotatably coupled to the inside of the hollow portion 111 of the casing 110, the rotating body ( It is composed of a coupling portion 122 coupled to (not shown) (see FIG. 1). On the outer circumferential surface of the rotating part 121 of the rotating member 120, a rubber packing 125 having a ring shape for preventing leakage of oil is mounted. In addition, a coupling groove 123 into which the outer end of the piston 130 is inserted is formed at the center of the rotating part 121. The coupling groove 123 has a track shape corresponding to one end of the piston 130, that is, a shape in which both sides are chamfered. Therefore, when the rotating member 120 rotates, the piston 130 rotates together with the rotating member 120.

A plurality of spiral guide grooves 132 are formed on the outer circumferential surface of the piston 130 to be inserted corresponding to the spiral guide protrusion 112 of the casing 110. Therefore, when the piston 130 is rotated by the rotational movement of the rotary member 120, the piston 130 is rotated in the casing 110 by the action of the guide protrusion 112 and the guide groove 132. As it moves, it moves in the axial direction. Of course, in this embodiment, the helical guide protrusion 112 is formed on the inner circumferential surface of the casing 110 for the axial movement of the piston 130, the spiral guide protrusion 112 is inserted into the outer circumferential surface of the piston 130. The helical guide groove 132 is formed, but on the contrary, the guide groove may be formed in the casing 110 in a helical manner, and the guide protrusion may be formed in the piston 130 in a helical manner.

Between the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110 is formed a fine void (g) through which the oil can flow when the piston 130 moves in the axial direction.

In addition, an oil passage 131 through which oil flows along the axial direction from the inner end to the outer end is formed in the central portion of the piston 130. The oil passage 131 is formed in a shape in which a plurality of holes having different diameters are continuously connected, and an outer end thereof communicates with the coupling groove 123 of the rotating member 120. In the oil passage 131, a check valve 140 is installed to selectively open and close the oil passage 131 according to the axial movement of the piston 130. That is, the check valve 140 functions to block the flow of oil when the piston moves in the pressurizing direction, and to allow the flow of oil when the piston moves in the opposite direction to the pressurization direction.

In this embodiment, the check valve 140 is fixed to the inside of the oil passage 131 and the mounting bracket 141 is formed in the center and the opening, the opening and closing of the oil passage 131 on the outside of the mounting bracket 141 Ball 142 and the compression coil spring 143 for elastically supporting the ball 142 with respect to the mounting bracket 141. Therefore, the ball 142 of the check valve 140, when the piston 130 moves in the axial direction in front of the casing 110 to compress the oil to close the oil passage 131 by the pressure of the oil, the piston When the 130 moves in the axial direction to the rear of the casing 110, the elastic force of the compression coil spring 143 by the pressure of the oil transmitted from the coupling groove 123 of the rotating member 120 to the oil passage 131 inside. It wins and moves to open the oil passage 131.

In addition, the piston 130 is formed to penetrate radially outward from the front portion of the check valve 140 to piston the oil in the oil flow path 131 when the oil flow path 131 is blocked by the check valve 140. A first bypass hole 133 is guided to the outer circumferential surface of the 130. When the oil passage 131 is closed by the check valve 140, the first bypass hole 133 induces oil to the rear of the sealing member 150 to be described below, and the outer peripheral surface and the casing of the piston 130. Through the gap (g) between the inner circumferential surface of the 110 to allow the flow toward the coupling groove 123 of the rotating member 120.

In addition, a sealing member 150 having a ring shape is coupled to the outer circumferential surface of the front end of the piston 130. The sealing member 150 is made of an elastic material such as rubber or silicon to elastically contact the inner circumferential surface of the hollow part 111 of the casing 110 to limit the flow of oil. The sealing member 150 may block the flow of oil during the forward and backward movement of the piston 130 by using a general O-ring, etc. Alternatively, when the piston 130 moves in the direction of pressurizing oil Strongly adhered to the inner circumferential surface of the casing 110 to prevent the flow of oil, when the piston 130 is moved in the opposite direction of the pressing direction may be configured to allow the flow of oil while the adhesive force with the inner circumferential surface of the casing 110 is released. .

For example, as shown in FIGS. 4 and 5, the sealing member 150 may have a ring-shaped packing part 151 having a 'U'-shaped cross section, and the packing part 151 may be open. It is formed on the outer surface of the open end at a predetermined interval along the circumferential direction to form a plurality of flow allowance grooves 152 to form a passage in which the oil flows when the piston 130 moves in the pressing direction in the contraction direction To make. When the sealing member 150 is made in this manner, when the piston 130 moves forward of the casing 110 to pressurize the oil, the outer circumferential surface of the sealing member 150 is opened to the outside by the pressure of the oil, and the casing 110 is opened. When the piston 130 moves to the rear of the casing 110, the oil flowing from the rear to the front shrinks the outer peripheral surface of the sealing member 150 while the piston 130 moves to the rear of the casing 110. Since the oil is to flow through the sealing member 150 will also be able to flow.

The rotary oil damper configured as described above operates as follows.

As shown in FIG. 2, when the rotating body (not shown) rotates in the open state, the rotating member 120 rotates together with the rotating body (not shown). The piston 130 is rotated together with the rotation of the rotating member 120, wherein the spiral guide groove 132 formed on the outer surface of the piston 130 by the spiral guide protrusion 112 of the casing 110 The piston 130 is guided so as to overcome the elastic force of the compression spring 160 and move axially in front of the casing 110.

As the piston 130 rotates and moves in the axial direction, the volume inside the casing 110 is gradually reduced, thereby compressing the oil inside the casing 110.

At this time, since the flow of oil is blocked through the outer peripheral surface of the front end portion of the piston 130 by the sealing member 150 as described above, the oil inside the casing 110 is sheared by the oil flow path 131 of the piston 130. After being introduced through the unit, it is guided to the outer circumferential surface of the piston 130 through the first bypass hole 133 on one side of the check valve 140, and the outer circumferential surface of the piston 130 and the casing at the rear of the sealing member 150 ( It flows backward through the gap (g) formed between the inner circumferential surface of the 110 is collected in the coupling groove 123 of the rotary member 120.

As described above, in a state in which the rotating body (not shown) rotates so that the piston 130 moves forward of the casing 110 (as shown in FIG. 3), the user rotates the rotating body in the opposite direction as before. When the rotating member 120 rotates in the opposite direction as before, the piston 130 moves axially backward in the casing 110.

Accordingly, the oil contained in the coupling groove 123 of the rotating member 120 is compressed to the front of the casing 110 through the oil channel 131 while opening the check valve 140 on the oil channel 131. Simultaneously with the flow, it flows forward through the space g between the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110. A portion of the oil flowing forward through the air gap g between the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110 is introduced into the first bypass hole 133, and the remaining portion is the sealing member 150. Rather through the sealing member 150 through the flow allowance groove 152 of the) is gathered to the front of the casing (110). At this time, the compression spring 160 makes the piston 130 more smoothly by applying an elastic force to the piston 130 to the rear of the casing 110.

On the other hand, the rotary oil damper of the above-described embodiment through the first bypass hole 133, the oil is formed in the radial direction of the piston 130 when the piston 130 moves forward of the casing 110 to pressurize the oil It is configured to flow. However, as shown in the second embodiment in FIG. 6, the second bypass hole 134 is formed to penetrate in the axial direction on the outer side of the oil passage 131 of the piston 130 and the front of the piston 130. An oil receiving groove 135 is formed in the portion to communicate with the second bypass hole 134 so that the oil flows when the oil passage 131 is blocked by the check valve 140 when the piston 130 moves forward. It may be to flow into the coupling groove 123 of the oil receiving groove 135 and the rotating member 120 through the 2 bypass hole 134. Of course, in the first and second embodiments described above, only one of the first bypass hole 133 and the second bypass hole 134 is formed in the piston 130, but the first and second pistons 130 are formed in the piston 130. The bypass hole 133 and the second bypass hole 134 may be formed together.

In addition, Figure 7 shows a third embodiment of the rotary oil damper according to the present invention, the rotary oil damper of the third embodiment is the same as the rotary oil dampers of the first and second embodiments described above, but the piston 130, The first bypass hole 133 (see FIG. 2) and / or the second bypass hole 134 (FIG. 6) is not formed, and the check valve 140 (FIG. 2 and FIG. 2) is formed in the oil flow path 131. 6), the difference is that the orifice hole 136 having a small diameter is formed in the oil passage 131.

In the rotary oil damper of the third embodiment configured as described above, when the piston 130 moves forward of the casing 110 to pressurize the oil inside the casing, the oil is slowly rearward through the orifice hole 136 of the oil passage 131. Oil that is filled in the coupling groove 123 of the rotating member 120 and, on the contrary, is filled in the coupling groove 123 of the rotating member 120 when the piston 130 moves to the rear of the casing 110. The orifice hole 136 of the oil channel 131 and the air gap g between the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110 are moved and filled in front of the casing 110.

FIG. 8 shows a fourth embodiment of a rotary oil damper according to the present invention, wherein the rotary oil damper of this embodiment has a first bypass hole 133 (see FIG. 2) and / or a second bypass in the piston 130. 6 is different from the rotary oil dampers of the first and second embodiments in that the hole 134 (see FIG. 6) is not formed and the sealing member 150 is not mounted on the outer circumferential surface of the front end of the piston 130.

The rotary oil damper of this fourth embodiment is the oil between the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110 when the piston 130 moves forward of the casing 110 to pressurize the oil inside the casing 110. Slowly flows backward through the gap to fill the inside of the coupling groove 123 of the rotating member 120, on the contrary, when the piston 130 moves to the rear of the casing 110, the coupling groove 123 of the rotating member 120 The oil filled inside the casing (ga) between the oil passage 131 and the outer circumferential surface of the piston 130 and the inner circumferential surface of the casing 110 while opening the shank valve 140 of the oil passage 131 is the casing ( It is filled in front of the flow 110.

Embodiments of the above-described rotary oil damper are described for the purpose of helping the understanding of the present invention, and the present invention may be variously modified and implemented within the scope of the appended claims.

1 is an exploded perspective view showing the configuration of a first embodiment of a rotary oil damper according to the present invention.

2 and 3 are cross-sectional views of the rotary oil damper of FIG.

4 is a perspective view of an embodiment of a sealing member of the rotary oil damper of FIG. 1.

5 is a cross-sectional view of the sealing member of FIG. 4.

6 is a cross-sectional view showing the construction of a second embodiment of a rotary oil damper according to the present invention.

Figure 7 is a cross-sectional view showing the configuration of a third embodiment of a rotary oil damper according to the present invention.

Figure 8 is a cross-sectional view showing the configuration of a fourth embodiment of a rotary oil damper according to the present invention.

Explanation of symbols on the main parts of the drawings

110: casing 112: guide protrusion

120: rotating member 123: coupling groove

130: piston 131: oil euro

132: guide groove 133: the first bypass hole

134: second bypass hole 135: oil receiving groove

136: orifice hole 140: check valve

150: sealing member 151: packing part

152: allowable groove 160: compression spring

Claims

In the rotary damper for rotatably connecting the rotor to the base in a certain angle range,

A hollow casing fixed to the base and accommodating oil therein;

A rotating member having one end rotatably coupled to the hollow portion of the casing and the other end coupled to the rotating body to rotate together with the rotating body;

One end is inserted into the coupling groove formed in the rotating member and installed to move in the axial direction while rotating in conjunction with the rotating member in the hollow part of the casing, thereby pressurizing oil in the hollow part of the casing by the axial movement. And a piston having an air gap formed between an outer circumferential surface and an inner circumferential surface of the casing, the rotary oil damper comprising: a piston;

The rotary oil damper according to claim 1, further comprising an elastic member installed in the hollow portion of the casing to elastically support the piston to impart an elastic force in a direction opposite to the pressing direction of the piston.

The helical guide groove or guide protrusion is formed on the inner circumferential surface of the casing, and the guide protrusion or the guide protrusion of the casing is inserted into the outer circumferential surface of the piston to guide the guide groove. The guide groove is formed in a spiral, the piston is guided by the guide groove and the guide projections, the rotary oil damper, characterized in that to move in the axial direction while rotating.

According to claim 1, When coupled to the outer circumferential surface of the piston when the piston moves in the direction of pressurizing oil strongly adheres to the inner circumferential surface of the casing to prevent the flow of oil, when the piston moves in the opposite direction of the pressing direction and the inner circumferential surface of the casing Rotary oil damper, characterized in that further comprising a sealing member for allowing the flow of oil while the adhesion is released.

The seal member of claim 4, wherein the sealing member is formed in a ring-shaped packing portion having a 'U'-shaped cross section open toward the pressing direction, and is formed at regular intervals along the circumferential direction on the outer surface of the open end of the packing portion. Rotary oil damper, characterized in that it comprises a plurality of flow allowance grooves to form a passage in which the oil flows when the movement in the direction opposite to the pressing direction.

The rotary oil damper according to claim 1, wherein an oil passage communicating with a coupling groove of the rotating member is formed in the central portion of the piston so as to penetrate in the axial direction from the front end to the rear end of the piston.

7. The rotary oil damper according to claim 6, wherein the oil passage has an orifice hole whose diameter is sharply reduced.

7. The rotary of claim 6, wherein the oil passage further comprises a check valve that prevents the flow of oil when the piston moves in the pressurizing direction and permits the flow of oil when the piston moves in the opposite direction to the pressurization direction. Oil damper.

The piston of claim 8, wherein the piston has a first bypass hole formed to penetrate radially outward from the front portion of the shank valve to guide oil to an outer circumferential surface of the piston when the oil channel is blocked by the shank valve. Rotary oil damper characterized by the above-mentioned.

The second bypass of claim 8 or 9, wherein the piston is axially penetrated from the outside of the oil passage to guide the oil into the space between the piston and the rotating member when the oil passage is blocked by a check valve. And an oil receiving groove formed in communication with the hole and the front of the second bypass hole.