KR200345011Y1 - Hydraulic damping hinge - Google Patents

Abstract

The present invention discloses a hydraulic buffer hinge that is used in conjunction with the spring hinge to control the speed at which the door is closed. The present invention is fixed to the door frame having a first hinge bracket fixed to the door and having a cylinder at one side end spaced apart from each other, and an intermediate cylinder coaxially interposed between the upper and lower cylinders of the first hinge bracket on one side end of the intermediate cylinder. A second hinge bracket having a plurality of guide protrusions of a predetermined length in the center of the inner circumference, an upper hinge bush fixed in the upper cylinder, a part of which is inserted into the intermediate cylinder, and has multi-threaded screws in the inner circumference, and an inner circumference of the upper hinge bush A slider having a multi-threaded screw on the outer periphery and having a guide groove to which the guide protrusions are coupled to the outer periphery of the head, and a hydraulically assembled oil in a small diameter portion having a smaller diameter on the inner periphery and assembled in the intermediate cylinder at the lower side of the guide protrusion. The piston rod and the piston rod whose upper end is fixed to the slider through the chamber and the upper and lower ends of the hydraulic chamber are hermetically sealed. A piston unit positioned in the middle of the piston rod so as to be airtightly assembled to the small diameter portion of the chamber, and having a piston body having a flow path for communicating with the upper and lower portions of the hydraulic chamber partitioned by an upwardly elastically biased piston body, and a lower portion of the intermediate cylinder. And a lower hinge bush that is engaged and partially inserted into the lower cylinder.

Description

Hydraulic damping hinge

The present invention relates to a hinge that supports the door to be opened and closed with respect to the door frame, and more specifically, used with the spring hinge, which is closed by hydraulic pressure when the opened door is automatically closed by restoring elasticity of the spring. This invention relates to a hydraulic shock absorbing hinge that provides a speed control to prevent the door from closing rapidly and to change the speed when the door opening is lower than a certain angle so that the door can be locked. .

As is known, the hinge is used to construct a so-called opening door by rotatably supporting one side end of the door to one side of the corresponding door frame so that the door can be rotated and opened about one side end thereof.

Such a hinge is usually composed of two hinge brackets each having a cylinder at one end and mounted on the door and the door frame, and hinge pins which are commonly fitted to the cylinders of these hinge brackets and connect both.

However, such a common hinge simply connects the door so as to be able to rotate open and close to the door frame, so that both opening and closing operations of the door have to be performed by an external force.

Accordingly, after the door is opened by adding a spring to the hinge, a spring hinge is provided that is automatically closed by restoring elasticity of the spring even if no additional force is applied.

However, in the case of the spring hinge can close the door automatically, the door is suddenly closed by the restoring elasticity of the spring to cause severe impact noise, the spring hinge is combined with the hydraulic buffer hinge to open the door It is common to have a gentle control of the closing speed of the hydraulic buffer hinge when it is closed by a spring.

Such a hydraulic buffer hinge can be found, for example, in Korean Utility Model Registration No. 0219473.

Utility Model Registration No. 0219473 discloses that as the piston head is raised when the door is opened, the oil in the upper hydraulic chamber is quickly moved to the lower hydraulic chamber through the main valve chamber of the large flow path provided in the piston head. On the contrary, when the spring hinge closes the door, the main valve chamber is blocked by the ball, and as the piston head descends, the oil in the lower hydraulic chamber moves to the upper hydraulic chamber through a small fluid passage formed on the wall of the cylinder, so that the door closes at a gentle speed. When the door is almost closed, the piston head enters the expansion portion of the cylinder inner circumference so that the oil moves simultaneously with the fluid passage through the gap between the piston head and the cylinder so that the door is completely closed.

However, the conventional hydraulic buffer hinge has a plurality of fluid passages for moving the oil to cover opening and closing of the doors, respectively, and the structure is complicated. In particular, a small fluid passage for controlling the closing speed of the door has a side wall of the cylinder. Because it is formed in the fabrication, it is very difficult to manufacture and there is a high possibility that it may not work smoothly due to pressure loss when leakage occurs.

In addition, Korean Utility Model Registration No. 0288374 also provides a safety hinge for gently controlling the closing speed of the door by the spring hinge, which is equipped with a neoprene that changes the volume in accordance with the pressure of the fluid caused by oil or air bubbles Malfunctions + can be prevented, but this also has a double structure so that the oil passages for opening and closing the doors are opened and closed respectively, which is complicated and difficult to manufacture, and the closing speed is constant. There is a high possibility of being locked.

The present invention was devised to solve the above-mentioned conventional problems, and when the door is closed by the restoring force of the spring hinge, the door is gradually closed by hydraulic pressure, thereby minimizing the occurrence of noise due to the sudden closure of the door. The purpose of the present invention is to provide a hydraulic buffer hinge that can secure the locking of the door by giving a speed change when the opening degree reaches a certain angle or less.

Another object of the present invention is to provide a hydraulic shock absorbing hinge that can be easily manufactured and assembled with a simple structure, and can operate stably even if some leakage occurs.

1 is an exploded perspective view showing a hydraulic buffer hinge according to the present invention,

Figure 2 is a cross-sectional view of the coupled state of FIG.

3 is a cross-sectional view taken along line III-III of FIG. 2;

4 is a cross-sectional view taken along the line IV-IV of FIG. 2;

Figure 5 is a partial cutaway exploded side view showing the hydraulic chamber unit;

6A and 6B are cross-sectional views respectively showing a closed state and an open state of the present invention hydraulic buffer hinge;

7A to 7D are cross-sectional views of main parts for explaining the operation of the present invention.

<Description of Symbols for Main Parts of Drawings>

10: first hinge bracket 11, 12: upper and lower cylinders

20: 2nd hinge bracket 21: intermediate cylinder

22: guide protrusion 30: upper hinge bush

33: multi-threaded screw 40: slider

41: multi-threaded screw 43: guide groove

50: hydraulic chamber 50a, 50b: upper and lower hydraulic chamber

51a: small diameter 54: V packing

60: piston unit 61: piston body

62: piston rod 63: euro

63a: taper euro 64: compressed coil spring

65: flow adjustment ball 69: adjustment bolt

D: Door F: Door Frame

Hydraulic buffer hinge according to the present invention for achieving the above object, the first hinge bracket is fixed to the door, having a cylinder at one side end upper and lower intervals; A second hinge bracket having a middle cylinder coaxially interposed between the upper and lower cylinders of the first hinge bracket at one side end, and fixed to the door frame, the second hinge bracket having a plurality of guide protrusions of a predetermined length in an inner circumference of the intermediate cylinder; An upper hinge bush fixed in the upper cylinder of the first hinge bracket so that a part of the body is rotatably inserted into the intermediate cylinder, and having multi-threaded screws in the inner circumference thereof; A slider having a multi-threaded screw coupled to an inner circumference of the upper hinge bush at an outer circumference and having a plurality of guide grooves in which the guide protrusions of the intermediate cylinder are coupled to the outer circumference of the lower head; An oil chamber (30) which is assembled in the intermediate cylinder so as to be positioned below the guide protrusion, and has a predetermined length of a small diameter portion having a smaller diameter at a predetermined position of the inner circumference, and is filled with oil; A piston rod which penetrates the upper and lower ends of the hydraulic chamber in an airtight state and the upper end thereof is connected to the slider, and a piston body which is located in the middle of the piston rod so as to be airtightly assembled so as to be airtightly assembled in the small diameter portion of the hydraulic chamber; A piston unit having a flow path for communicating the upper and lower portions of the hydraulic chamber partitioned by the piston body; And a lower hinge bush coupled to the lower portion of the intermediate cylinder to fix the position of the hydraulic chamber and a part of the lower hinge bush rotatably inserted into the lower cylinder of the first hinge bracket.

According to one preferred feature of the present invention, a tapered portion provided to narrow upward in a portion of the flow path of the piston unit, a flow adjusting ball which is accommodated in the tapered portion and elastically biased toward its small diameter, and a piston rod It includes a valve means consisting of an adjusting bolt to form an adjustment hole so as to communicate with the flow path at the top of the upper end of the adjustment bolt to press the ball in the anti-elastic direction by being screwed in the axial direction.

Accordingly, the present invention enables a quick opening of the door as well as closes slowly when the open door is closed by a spring hinge, but closes only quickly for a certain degree immediately before the closing, thereby minimizing noise due to sudden closing. Can be locked securely.

In addition, it can be easily manufactured and assembled as a relatively simple structure compared to the prior art, and when the door is opened and closed, the oil is moved through a single flow path provided in the piston and the gap between the piston and the hydraulic chamber, so that even if there is a slight leakage The bar can be operated to have a great effect on improving the reliability, durability and manufacturability of the hydraulic buffer hinge.

Such specific features and other advantages of the present invention will become more apparent from the following description of the preferred embodiments with reference to the accompanying drawings.

1 to 4, the hydraulic shock-absorbing hinge according to the present invention, the first cylinder is fastened to the door (D), for example, having the upper cylinder 11 and the lower cylinder 12 coaxially spaced apart from one side end up and down The hinge bracket 10 and the intermediate cylinder 21 positioned between the upper and lower cylinders 11 and 12 of the first hinge bracket 10 at one side end thereof are fastened to, for example, the door frame F. 2 the hinge bracket 20, the upper hinge bush 30 for rotatably connecting the upper cylinder 11 and the intermediate cylinder 21, the slider 40 is coupled to the upper hinge bush 30 to move up and down; The hydraulic chamber 50 is fixed in the intermediate cylinder 21 of the second hinge bracket 20 so as to be positioned below the slider 40, and is connected to the slider 40 to move up and down inside the hydraulic chamber 50. It consists of a lower hinge bush 70 for rotatably connecting the piston unit 60 and the lower cylinder 12 and the intermediate cylinder 21.

The upper cylinder 11 and the lower cylinder 12 are integrally welded to one side end of the first hinge bracket 10, and a plurality of fastenings for fastening with the door D are disposed at appropriate positions of the first hinge bracket 10. Holes 13 are formed.

Preferably, a fixing bush 14 for fixing the upper hinge bush 30 is inserted into the upper cylinder 11 to be fixed by a bolt 16 fastened in a radial direction thereof. In the inner circumference of the plurality of assembly grooves 15 are arranged radially and formed in the longitudinal direction.

The intermediate cylinder 21 is integrally welded to one side end of the second hinge bracket 20 so as to be coaxially interposed between the upper and lower cylinders 11 and 12 of the first hinge bracket 10. A plurality of guide protrusions 22 for guiding the slider 40 to move up and down are radially disposed at a predetermined angle on the inner circumference of the intermediate cylinder 21 to form a predetermined length along the axial direction.

A plurality of fastening holes 23 for fastening with the door frame F are also formed in the second hinge bracket 20.

The upper hinge bush 30 is provided with a plurality of assembly protrusions 31 fitted in the assembly grooves 15 of the fixing bush 14 on the outer circumference thereof to be coupled to the inside of the fixing bush 14, and a part of the body is upper. It protrudes below the cylinder 11 and is inserted in the upper side of the intermediate cylinder 21. The lower end of the upper hinge bush 30 is formed with a flange 32 for rotatably contacting and supporting the inner circumference of the intermediate cylinder 21.

The lower surface of the flange 32 is supported in contact with the upper end of the guide projection 22 of the intermediate cylinder 21, the upper surface is supported by the C-shaped fixing ring 34 coupled to the inner circumference of the intermediate cylinder 21 to fix the position do. This is to preserve the durability of the upper cylinder 11 by allowing the fixed ring 34 to support the axial force acting upon the rise of the slider 40.

The inner circumference of the upper hinge bush 30 is provided with a multi-threaded screw 33 so that the slider 40 coupled to it according to the opening and closing operation of the door D can be lifted with sufficient stroke.

The slider 40 has a multi-threaded thread 41 corresponding to the multi-threaded screw 33 of the upper hinge bush 30 on the outer circumference thereof and is assembled to the inner circumference of the upper hinge bush 30 by screwing. The lower end of the slider 40 is integrally provided with a large diameter head 42 in sliding contact with the inner circumference of the intermediate cylinder 21, and the guide protrusion 22 of the intermediate cylinder 21 is provided on the outer circumference of the head 42. A plurality of guide grooves 43 for movably inserting are formed in the axial direction.

In the center of the head 42 side of the slider 40, an assembling hole 44 into which the upper end of the piston rod 62 of the piston unit 60 to be described later is formed to have an appropriate depth. Accordingly, preferably in the center of the slider 40 is formed with a guide hole 45 for easy operation of the flow rate adjustment bolt 69 of the piston unit 60 described later.

As shown in FIG. 5, the hydraulic chamber 50 is inserted into the interior of the intermediate cylinder 21 so as to be positioned below the guide protrusion 22 of the intermediate cylinder 21 to be fixed by the lower hinge bush 70. do. That is, the hydraulic chamber 50 has a lower end in contact with the lower hinge bush 70 fastened to the lower end of the intermediate cylinder 21 while the upper end thereof is in contact with and supported by the lower end of the guide protrusion 22. It is mounted in).

The hydraulic chamber 50 is composed of a cylinder 51 filled with oil therein and upper and lower end caps 52a and 52b for sealing both ends of the cylinder 51. On the inner circumference of the cylinder 51, a small length 51a having a diameter smaller than the inner diameter is provided at a predetermined position.

Each end cap 52a, 52b is hollow so that the piston rod 62 of the piston unit 60 can pass therethrough, and a plurality of O-rings 53 are formed on the outer circumference for airtightness. It is provided and screwed to the inner circumference of the cylinder (51). In addition, a so-called V-packing 54 having a V-shaped cross section for inserting the piston rod 62 in an airtight state is fitted to the inner circumference of the end caps 52a and 52b, and is fixed by a hollow tan bolt (55). do.

The piston unit 60 is a piston body 61 which is elevated in the cylinder 51 of the hydraulic chamber 50, and a piston which penetrates both ends of the cylinder 51 and connects the piston body 61 to the slider 40. It consists of the flow path 63 which communicates the upper hydraulic chamber 50a and the lower hydraulic chamber 50b of the hydraulic chamber 50 partitioned by the rod 62 and the piston body 61. As shown in FIG.

The piston body 61 has an O-ring 61a for airtightness on the outer circumference thereof and is coupled in the small diameter portion 51a of the cylinder 51, and is compressed between it and the lower end cap 52b of the hydraulic chamber 50. It is elastically biased upward through the coil spring 64. As shown in FIG. In the center of the piston body 61, a tapered flow path 63a is formed in which the diameter decreases toward the upper side.

The upper end of the piston rod 62 is welded to the center of the upper surface of the piston body 61 and the upper end is fitted into the assembly hole 44 of the slider 40 through the upper end cap 52a of the hydraulic chamber 50. The rod 62a and the lower rod 62b are welded to the center of the lower surface of the piston body 61 and penetrate the lower end cap 52b of the hydraulic chamber 50.

An upper hydraulic chamber 50a and a lower hydraulic chamber 50b of the hydraulic chamber 50 communicate with the taper flow path 63a of the piston body 61 at the lower end of the upper rod 62a and the upper end of the lower rod 62b. Connecting flow paths 63b and 63c are formed.

On the other hand, preferably, the ball 65 for adjusting the flow rate is fitted in the taper flow path 63a of the piston body 61, and the ball 65 is a C ring 66 assembled on the inner circumference of the tapered flow path 63a. ) Is biased toward the small diameter of the tape flow path 63a in the closing direction by the spring 67 supported by the &lt; RTI ID = 0.0 &gt;

In the center of the upper rod 62a, an adjustment hole 68 is formed so as to communicate with the flow path 63b, and the flow adjustment ball 65 is pressed in the semi-elastic direction to the taper flow path 63a. Flow adjustment bolt 69 for adjusting the opening degree of the screw is provided with an O-ring (69a) for airtightness on the outer periphery.

The lower hinge bush 70 is screwed into the lower portion of the inner circumference of the intermediate cylinder 21 to fix the position of the hydraulic chamber 50, and the lower portion of the body protrudes downward of the intermediate cylinder 21 so that the first hinge bracket It is assembled rotatably in the lower cylinder 12 of (10). The lower hinge bush 70 is configured to be hollow so that the lower rod 62b of the piston unit 60 can pass therethrough.

Meanwhile, upper and lower caps 80 and 90 for assembling the upper and lower cylinders 11 and 12 of the first hinge bracket 10 to the outside are respectively assembled. Each cap 80, 90 has a plurality of hooks 81, 91 and is elastically assembled to the engaging grooves 11a, 12a formed in the inner circumference of the upper and lower cylinders 11, 12.

Next, the operation of the hydraulic buffer hinge according to the present invention configured as described above will be described with reference to Figures 6a to 7d.

6A shows a state in which the door D is closed, and the slider 40 is mostly escaped from the upper hinge bush 30 so that the head 42 is positioned at the lower end of the guide protrusion 22 of the intermediate cylinder 21. In this state, the piston unit 60 is lowered and the piston body 61 is released from the small diameter portion 51a of the hydraulic chamber 50 while compressing the compression coil spring 64. The upper hydraulic chamber (50a) and the lower hydraulic chamber (50b) of the) will be in communication.

At this time, the ball 65 mounted on the taper flow path 63a of the piston body 61 is in close contact with the lower end of the flow rate adjustment bolt 69 by the spring 67.

In this state, as shown in FIG. 6B, when the door D is opened, the upper hinge bush 30 fixed in the upper cylinder 11 of the first hinge bracket 10 rotates together with the door D, thereby screwing it. The combined slider 40 is raised.

That is, the upper hinge bush 30 is a fixing bush fixed to the inner cylinder of the upper cylinder 11 of the first hinge bracket 10 to which the assembly protrusion 31 of the outer periphery thereof is fastened to the door D. 14, the slider 40 is not rotated and the slider 40 has a guide groove 43 formed on the outer circumference of the head 42 on the inner circumference of the intermediate cylinder 21 of the second hinge bracket 20. Since both of the screws are coupled in a state where the guide protrusion 22 cannot be rotated by inserting the guide protrusion 22, when the door D is opened, thrust is generated upward in the slider 40, so that the slider 40 guides the intermediate cylinder 21. Will rise along (22).

At the same time, as the compression coil spring 64 is restored to its initial state of elasticity, the piston body 61 is pushed upward. Accordingly, the oil in the upper hydraulic chamber 50a of the hydraulic chamber 50 flows in the flow path ( The door D is opened by moving to the lower hydraulic chamber 50b through 63.

At this time, as shown in Fig. 7a, as shown in Fig. 7a, the upper and lower hydraulic chambers 50a are moved to a state where a predetermined gap is formed between the outer circumference of the piston body 61 and the inner circumference of the hydraulic chamber 50 ( Since the position of the ball 65 does not change because the pressure difference is small in 50b), the opening degree of the taper flow path 63a is kept constant, but the gap and the flow path in which oil is formed between the inner circumference of the piston body 61 and the hydraulic chamber 50 ( 63) It opens simultaneously because it flows simultaneously.

Then, as shown in FIG. 7B, when the piston body 61 enters and comes into close contact with the small diameter portion 51a of the hydraulic chamber 50, the oil flows only through the flow path 63, but the pressure of the upper hydraulic chamber 50a is relatively increased. The ball 65 is lowered while compressing the spring 67, so that the opening degree of the flow path 63 becomes large, so that quick opening is also possible.

On the other hand, when the external force applied to the door (D) in the state in which the door (D) is open as shown in Figure 6b, the door (D) is rotated in the closing direction by the restoring elasticity of the spring hinge (not shown). Then, as the upper hinge bush 30 is rotated at the same time, the slider 40 screwed thereto is guided to the guide protrusion 22 of the intermediate cylinder 21 to descend, thereby lowering the piston unit 60 simultaneously.

When the piston unit 60 is lowered in this way, the oil in the lower hydraulic chamber 50b of the hydraulic chamber 50 moves to the upper hydraulic chamber 50a. At the beginning of closing, the moving flow rate is small, and the closing is completed slowly. In a certain opening degree section immediately before, since the flow rate is large, the door is closed quickly, thereby ensuring a reliable locking of the door D.

That is, at the beginning of closing, as shown in FIG. 7C, the piston body 61 moves in a state of being in close contact with the small diameter portion 51a of the hydraulic chamber 50, so that the oil in the lower hydraulic chamber 50b flows into the flow path ( 63 only flows through and the hydraulic pressure acts in the closing direction to the flow path adjusting ball 65 so that the door D is gradually closed because the opening degree of the tapered flow path 63a is kept constant.

And just before the closing, as shown in Fig. 7d, the piston body 61 descends out of the small diameter portion 51a of the hydraulic chamber 50 to form a gap therebetween, so that the oil in the lower hydraulic chamber 50b is piston. Through the gap between the outer circumference of the body 61 and the inner circumference of the hydraulic chamber 50 and the flow path 63 at the same time is to close quickly.

Therefore, the noise generated due to the sudden closing operation is effectively suppressed, and the risk of being injured by a finger or the like due to carelessness is minimized, and the door D can be reliably locked.

In addition, since the oil moves both through one flow path 63 of the piston unit 60 when the door D is opened and closed, the oil moves through the gap formed between the piston body 61 and the hydraulic chamber 50. Even if there is oil leakage, there is almost no pressure loss during operation to ensure stable operation.

On the other hand, the closing speed of the door (D) is appropriately controlled by adjusting the opening degree of the taper flow path 63a by adjusting the position of the ball 65 by tightening or releasing the adjusting bolt 69.

As described above, according to the hydraulic shock absorbing hinge according to the present invention, while the door is opened quickly while ensuring the quick opening of the door is closed in most of the opening gradually closes only for a certain degree immediately before the completion of the closing noise Minimized, safety accidents such as a finger injury between the door frame and the door is effectively suppressed, as well as to securely lock the door.

In addition, it can be easily manufactured and assembled as a relatively simple structure compared to the prior art, it is also possible to minimize the malfunction caused by leakage.

Therefore, the present design has an excellent effect of greatly contributing to the improvement of reliability, durability, and manufacturability of the hydraulic shock absorbing hinge.

Claims (6)

A first hinge bracket fixed to the door, the first hinge bracket having a cylinder spaced at an upper side and a lower side of one side end; A second hinge bracket having a plurality of guide protrusions of a predetermined length in a central direction on an inner circumference of the intermediate cylinder having a middle cylinder interposed coaxially between the upper and lower cylinders of the first hinge bracket at one side end; ; An upper hinge bush fixed in an upper cylinder of the first hinge bracket so that a portion of the body is rotatably inserted into the intermediate cylinder, and having multi-threaded screws in an inner circumference thereof; A slider having a multi-threaded screw coupled to an inner circumference of the upper hinge bush at an outer circumference, and having a plurality of guide grooves in which the guide protrusions of the intermediate cylinder are coupled to a lower head circumference at a center thereof; A hydraulic chamber which is assembled in the intermediate cylinder so as to be positioned below the guide protrusion, has a small diameter portion smaller in diameter at a predetermined position in the inner circumference, and is filled with oil; A piston rod which penetrates the upper and lower ends of the hydraulic chamber in an airtight state and is positioned in the middle of the piston rod so as to be assembled in an airtight state to the small diameter portion of the hydraulic chamber by an upper end thereof connected to the slider. And a piston unit having a flow path for communicating the upper and lower portions of the hydraulic chamber partitioned by the piston body; And A lower hinge bush coupled to a lower portion of the intermediate cylinder to fix the position of the hydraulic chamber, and a portion of which is rotatably inserted into the lower cylinder of the first hinge bracket. 2. The taper portion according to claim 1, wherein a taper portion provided to be narrowed upward in a portion of the flow path of the piston unit, a flow adjusting ball accommodated in the taper portion and elastically biased toward a small diameter thereof, and an upper end of the piston rod in the flow path. A hydraulic shock absorbing hinge comprising a valve means consisting of an adjusting bolt which forms an adjusting hole so as to communicate with and maintains airtightness and is screwed in an axial direction to press the ball in a semi-elastic direction. The method of claim 2, wherein the piston unit, A piston body having the tapered flow path in the center thereof, the piston body having the flow control ball therein; a lower piston rod joined to the lower surface of the piston body with a taper flow path connecting the lower hydraulic chamber of the hydraulic chamber; and a tapered flow path. And an upper piston rod coupled to the upper surface of the piston rod by coupling the adjusting bolt to an inner circumference while having a flow path connecting the upper hydraulic chamber of the hydraulic chamber. The hydraulic chamber according to any one of claims 1 to 3, wherein A cylinder having a small diameter portion to which the piston body is coupled at a predetermined position of the inner circumference, two hollow end caps each of which is screwed in a hermetic state to both ends of the cylinder, and mounted on the inner circumference of each end cap to seal the piston rod Hydraulic buffer hinge, characterized in that made of V-packing to be inserted into. The hydraulic shock absorbing hinge according to claim 1, wherein a flange is provided at a lower end of the upper hinge bush, and a support ring for contacting and supporting the upper surface of the flange of the upper hinge bush is mounted on an inner circumference of the intermediate cylinder. The hydraulic shock absorbing hinge according to claim 2 or 3, wherein the slider has a guide hole through which the adjustment bolt passes.