KR100586262B1 - Hinge Apparatus for Heavy Door Having Automatic Return Function - Google Patents

Abstract

The present invention preserves the closing force of a large door through a pair of camshafts having different cam lead lengths without increasing the outer diameter of the device, and minimizes the opening force generated when the door is opened. It is related with a hinge device for a large door that can be easily opened.

The present invention includes a central body fixedly coupled to the first hinge; Passing first and second guides fixedly coupled to the upper and lower ends of the second hinge, respectively; First and second camshafts that rotate by relative external forces generated in the first and second guide barrels when the door is rotated; First and second guide pins; First and second piston rods which move up and down along the cylindrical body inner circumferential surfaces of the first and second camshafts respectively in association with rotation of the first and second camshafts; First and second pistons including flow paths communicating with the first and second upper and lower chambers, respectively; First and second check valves for controlling the amount of oil moving through the first and second upper and lower chambers; A plurality of sealing caps coupled to the upper and lower ends of the first and second guide barrels in a sealing state, respectively; It is characterized by consisting of an elastic member for elastically supporting the first and second piston.

Large door, return speed adjustment, cam lead angle

Description

Hinge Apparatus for Heavy Door Having Automatic Return Function}

1 is a longitudinal cross-sectional view of an automatic return hinge device for a large door according to a first embodiment of the present invention,

Figure 2a is a perspective view showing a pair of camshaft for guiding the piston rod to move up and down in accordance with the opening and closing of the door in the automatic door hinge for the large door shown in Figure 1,

Figure 2b is a view showing the position of the guide pin and the return spring in accordance with the operation of the hinge device in the lifting guide hole of the pair of camshaft shown in Figure 2a,

3A and 3B are enlarged views showing the operating states of the disk-shaped valve actuators of the parts “A” and “B” shown in Fig. 1, respectively.

4A and 4B are enlarged views showing another example of the check valve shown in FIGS. 3A and 3B, that is, a ball type valve movable member;

Figure 5a is a cross-sectional view of the piston and the return speed control unit showing the initial position where the first and second pistons are located at the bottom dead center and the top dead center, respectively;

FIG. 5B is a hydraulic flow chart when the pistons of the first and second pistons are lifted and lowered in the process of reaching the door opening angle from 0 ° to 15 ° according to the opening of the door.

5C is a hydraulic flow diagram when the second piston descends while the first piston is stopped while the door opening angle reaches 15 ° to 90 ° according to the opening of the door;

FIG. 5D is a hydraulic flow diagram when the second piston is raised with the first piston stopped until the door opening angle reaches 90 ° to 15 ° according to the closing of the door; FIG.

FIG. 5E is a hydraulic flow chart when the first and second pistons are simultaneously raised and lowered while the door opening angle reaches from 15 ° to 0 ° according to the closing of the door.

5F is a cross-sectional view of the piston and the return speed adjusting unit showing a state in which the door opening angle reaches 0 degrees according to the closing of the door and the first and second pistons are returned to their initial positions located at the bottom dead center and the top dead center, respectively;

6 is a partial cross-sectional view showing an elastic force setting unit for adjusting the elastic force of the return spring to the sealing cap shown in FIG.

7 is a longitudinal sectional view of a hinge device for a large door according to a second embodiment of the present invention;

8 is a longitudinal sectional view of a hinge device for a large door according to a third embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

10: first hinge 11: center torso

20: second hinge 21: first guide barrel

21a: first upper chamber 21b: first lower chamber

22a, 22b: first vertical guide groove 23: second guide barrel

23a: second upper chamber 23b: second lower chamber

24a, 24b: second vertical guide groove 30: first camshaft

31: shaft 31a: first spring pin

33: round body 34a, 34b: first lifting guide hole

41: first guide pin 43: second guide pin

51: first piston rod 51a: bending through hole

52, 55: Euro groove 53: First piston

53a: first central through hole 53b: coupling hole

54: first valve movable member 54a: small through hole

60: second camshaft 61: shaft

61a: second spring pin 63: round body

64a, 64b: 2nd lifting guide hole 81: 2nd piston rod

81a: Bending through hole 82, 85: Euro groove

83: second piston 83a: second central through hole

83b: coupling hole 84: second valve movable body

84a: small through hole 91: first end cap

91a: air discharge bolt 93: first sealing cap

95: second sealing cap 95a: air discharge bolt

100, 200, 300: Hinges 131 to 137: O-ring

950: push bolt 951: head

952: body portion 960: pressure plate

The present invention relates to a hinge device for a large door having an automatic return function, and in particular, by installing two camshafts having two closed hydraulic circuits and correspondingly different cam lead lengths, the outer diameter of the device is increased. A large cam that can easily open heavy large doors with a small force by preserving the closing force of the large doors while minimizing the opening force generated when the door is opened through a pair of cam shafts having different cam lead lengths. A hinge device for a door.

In general, the hinge device is a device that connects two members so as to open or contact each other about one axis as needed. As a representative example, a hinge device for a door and a frame (including a movable part in a horizontal direction) and a refrigerator There is a hinge for opening and closing (including a movable part in the vertical direction) used in mobile phones, laptops, and the like.

In this prior art, registered utility model No. 0181646 discloses an example in which a hinged door opening and closing device is configured by separately configuring a hydraulic door closer and a spring door closer and using them in combination with each other.

Thus, the hinge device using a combination of the spring method and hydraulic pressure has a problem because the force required to open the door increases in proportion to the increase in the opening angle of the door, especially when the user opens a large door.

Moreover, since the inertia force generated in the closing direction is increased in proportion to the opening angle of the door, the hinge device is closed at an excessive speed when the large door is closed, thereby causing a problem of injury to the user by a large large door that is quickly closed. there was.

In addition, Korean Patent No. 435188 discloses a spiral cam diagram that stabilizes the multi-step automatic return speed setting structure to accurately set the last closing of the door and prevent the door from overspeed when closing the door. A hinge device using a single camshaft having is disclosed.

However, the hinge device is mainly applied to a light weight small door that does not require a large closing force, such as a refrigerator or a kimchi refrigerator, and is applied to a large door with a large weight difference compared to the small door. There is a very difficult problem in reality because of the large lack.

If the hinge device has a proper damping force corresponding to the large door in consideration of the weight of the large door, it is necessary to increase the last closing force of the door in consideration of the weight of the large door. The outer diameter should be increased. That is, the damping force of the door must be increased by increasing the diameter of the chamber and the size of all components constituting the hydraulic circuit to have an appropriate damping force corresponding to the weight of the large door.

However, if the diameter of the hinge device is greatly increased in this way, as the opening force of the large door is continuously increased in proportion to the increase in the opening angle of the door, there is a serious problem that it is more difficult to open the heavy large door.

In addition, when the outer diameter of the hinge device is increased as described above, the center of the hinge device, that is, the center of rotation of the door, exceeds the door rotation center setting reference value generally set for smooth rotation of the door. A fatal problem arises.

In addition, when carrying a person or a bulky object passing around the door by a hinge device protruding badly from the door due to the increased outer diameter may cause a problem of walking.

Accordingly, the present invention has been made in view of the problems of the related art, and an object thereof is to provide an outer diameter of the apparatus by installing two camshafts having two closed hydraulic circuits and correspondingly different cam lead lengths. A pair of camshafts with different cam lead lengths without increasing the preservation of the closing force of the large door and minimizing the opening force required to open the door can easily open the heavy large door with little force. The present invention provides a hinge device for a large door.

That is, an object of the present invention is to apply to the door between the door opening angle of 0 ° to 15 ° by the cam diagram angle of the lifting guide hole for guiding the lifting and lowering of the pair of pistons at the time of opening the door and the structure of the hydraulic circuit. A large door is easily opened by a second opening force, which is the first opening force with the greatest force, and the piston is lowered by about one half of the first opening force by lowering one of the pair of pistons between 15 ° and 90 °. The present invention provides a hinge device for a large door that can be opened.

In order to achieve the above object, the present invention is a self-returning hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, respectively, which is automatically returned when the door is closed, the first hinge A central body having one circumferential surface fixedly coupled to the center; One or more circumferential surfaces are fixedly coupled to upper and lower ends of the second hinge so as to maintain a distance corresponding to the height of the central body, respectively, and the first and second vertical guide grooves and the third vertical guide grooves are respectively positioned at positions opposite to each other. A fourth vertical guide groove formed therein, the first and second guide passages having first and second chambers into which oil is charged, respectively; A pair of shafts are fixedly inserted into the central body so as to face each other, and a circular body extending in the pair of shafts is rotatably installed on the inner circumferences of the first and second guide barrels, respectively, along the outer circumferential surface of the cylindrical body. First and second elevating guide holes and third and fourth elevating guide holes each having a cam diagram formed in a spiral shape having a symmetrical moving structure in the through hole, and the first and second guide barrels when the door is rotated. First and second camshafts that are rotated by a relative external force generated in the; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; The central portions of the first and second guide pins are respectively penetrated through one end thereof so that the first and second vertical guide grooves and the third and fourth vertical guide grooves are linked to the rotation of the first and second cam shafts. First and second piston rods which are moved up and down along the circular body inner circumferential surfaces of the first and second cam shafts, respectively, in a sliding manner, and bent through-holes communicating with the outer circumferential portion at the other ends thereof, respectively; First and second coupling holes are formed at the center of one side and the other ends of the first and second piston rods are coupled, respectively, and the first and second central through holes communicating with the first and second coupling holes are formed at the other side. First and second pistons formed on the outer circumferential portion to be slidable along the inner circumference of the first and second guide barrels, and partitioning the first and second chambers up and down, respectively; The first and second pistons are formed in the first and second pistons to increase or decrease the flow amount of oil moving in the first and second upper / lower chambers according to the rise / fall of the first and second pistons. First and second check valves for controlling the piston's rising / falling speed; First and second sealing cap portions coupled to the upper and lower ends of the first and second guide cylinders in a sealing state, respectively, such that the insides of the first and second guide barrels form independent hydraulic closed circuits; First and second lower chambers respectively installed to elastically support the first and second pistons, the first and second pistons providing a restoring force for returning the first and second pistons to their original positions upon return of the door; It provides an automatic return hinge device for a large door, characterized in that composed of a second elastic member.

In addition, according to another feature of the present invention, in the automatic return hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, respectively, which is automatically returned when the door is closed, the center of the first hinge One surface is fixedly coupled to the inside, and the inner side is divided into the first and second chambers by the partition wall, and the first and second vertical guide grooves and the first and the second vertical guide grooves respectively at positions opposite to each other inside the first and second chambers. 3, the central body and the fourth vertical guide groove is formed; First and second fixed bodies each having one side coupled to upper and lower side ends of the second hinge, respectively, while maintaining a distance from which the central body can be inserted; Shafts are fixedly inserted into the first and second fixing bodies, respectively, and first and second circular bodies respectively detachably coupled to the shafts are rotatably inserted into the first and second chamber inner circumferences of the central body, respectively. When the first and second elevating guide holes and the third and fourth elevating guide holes each having a cam diagram consisting of spirally symmetrical moving structures along the outer circumferential surface of the circular body are formed through each other, and the door is rotated. First and second camshafts that are rotated by relative external forces generated in the first and second fixed bodies; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; An upper end portion is penetrated by the first and second guide pins, respectively, and along the first and second vertical guide grooves and the third and fourth vertical guide grooves in association with rotation of the first and second camshafts. First and second piston rods which are moved up and down along the inner circumferential surfaces of the first and second camshafts in a sliding manner, respectively, and have bent through holes at one end thereof, the bending through-holes communicating vertically with the outer circumference; First and second coupling holes are formed at the center of one side and the other ends of the first and second piston rods are coupled, respectively, and the first and second central through holes communicating with the first and second coupling holes are formed at the other side. First and second pistons formed on the outer circumference thereof so as to be slidable along the inner circumference of the central body, and simultaneously partitioning the first and second chambers up and down; The first and second pistons are formed in the first and second pistons to increase or decrease the flow amount of oil moving in the first and second upper / lower chambers according to the rise / fall of the first and second pistons. First and second check valves for controlling the piston's rising / falling speed; A pair of sealing caps coupled to the upper and lower ends of the central body in a sealing state, respectively, so that the first and second spaces of the central body form independent hydraulic closed circuits; An elastic member installed in each of the first lower chamber and the second upper chamber to elastically support the first and second pistons, and providing a restoring force for returning the first and second pistons to their original positions upon return of the door; It provides an automatic return hinge device for a large door, characterized in that configured.

Furthermore, according to another feature of the present invention, in the automatic return hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, respectively, which is automatically returned when the door is closed, the center of the first hinge One main surface is fixedly coupled to the upper and lower inner peripheral portions of the first and second vertical guide grooves and the third and fourth vertical guide grooves are formed in the vertical direction, respectively, the center having a chamber inside Torso; First and second fixed bodies each having one side coupled to upper and lower side ends of the second hinge, respectively, while maintaining a distance from which the central body can be inserted; Circular bodies fixedly inserted into the first and second fixed bodies respectively and detachably coupled to the shafts are rotatably installed on the inner circumference of the chamber of the central body, respectively, and are symmetrically moved along the outer circumferential surface of the cylindrical body. The first and second elevating guide holes and the third and fourth elevating guide holes each having a cam diagram made of a spiral shape of the structure are formed therethrough, and are formed in the first and second guide barrels when the door is rotated. First and second camshafts rotating by relative external force; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; As the central portion of the first guide pin penetrates through one end and cooperates with the rotation of the first camshaft, the first guide pin moves up and down along the cylindrical body inner circumferential surface of the first camshaft in a sliding manner along the first and second vertical guide grooves. The drop has a first piston rod; A first piston integrally formed at the other end of the first piston rod and having an outer circumference portion slidably coupled to an inner circumference portion of the central body; The central portion of the second guide pin is coupled to one end portion and is moved up and down along the cylindrical body inner circumferential surface of the second cam shaft in a sliding manner along the third and fourth vertical guide grooves in association with rotation of the second cam shaft. A second piston rod having a bent through hole at one end formed in communication with the outer circumference; Coupling holes are formed at the other end of the second piston rod is coupled to each other, the center through-hole is formed in communication with the coupling hole on the other side, the outer circumference is arranged so as to slide along the inner circumference of the chamber of the central body, respectively And a second piston for partitioning the chambers up and down at the same time; A check for controlling the rising / falling speed of the first and second pistons by increasing or decreasing the flow amount of oil which is formed in the second piston and moves mutually in the upper / lower chamber according to the rising / falling of the second piston. A valve; A pair of sealing caps coupled to the upper and lower ends of the central body in a sealing state; A large view, comprising: an elastic member installed in the upper chamber to elastically support the first and second pistons to provide a restoring force for returning the first and second pistons to their original positions upon return of the door; Provides an automatic return hinge device for fishing.

In the hinge device of the present invention configured as described above, the length of one of the pair of camshafts is longer than the other one, so that a pair of pistons are simultaneously opened by a pair of camshafts at an opening angle of 0 to 15 °. Preserves the closing force of the door without increasing the outer diameter of the device by raising and lowering and raising and lowering only to the piston connected to the long camshaft of the camshaft of the pair of camshafts at the opening angle of 15 to 90 °. At the same time, the door can be opened with less opening force than is necessary at the door opening angle from 0 to 15 °.

As described above, in the present invention, a pair of camshafts having different cam lead lengths and a pair of pistons coupled thereto are installed in a hinge type hinge device used for a large door, so that a pair of pairs can be installed at the beginning and end of opening the door. The piston can be raised and lowered at the same time to preserve the closing force of the door and at the same time reduce the opening force of the door to open the heavy and large doors with little force, and also to improve the reliability of the product by realizing the precise opening and closing of the door. Can be.

(Example)

Hereinafter, with reference to the accompanying drawings, preferred embodiments of the hinge device for a large door according to the present invention will be described in detail.

1 is a longitudinal cross-sectional view of a hinge device for a large door according to the first embodiment of the present invention, Figure 2a is to move the piston rod up and down in accordance with the opening and closing of the door in the hinge device for a large door shown in FIG. Figure 2b is a perspective view showing a pair of camshaft to guide, Figure 2b shows the position of the guide pin and the compression state of the return spring according to the operation of the hinge device for a large door in the lifting guide hole of the pair of camshaft shown in Figure 2a 3A and 3B are enlarged views showing the operating states of the disk-shaped valve actuators of the parts "A" and "B" shown in FIG. 1, respectively.

As shown in Figures 1 to 3b, the configuration of the hinge apparatus 100 for a large door according to the first embodiment of the present invention will be described in detail as follows.

First, the first embodiment of the present invention is formed in the center of the first hinge 10 which is fixed to the door frame is a central body 11 is fixedly coupled, the second hinge 20 is fixed to the door The first and second vertical guide grooves 22a and 22b and the third and fourth vertical guide grooves 24a and 24b are respectively fixedly coupled to the lower end and in the vertical direction at positions opposite to each other. The formed first and second guide cylinders 21 and 23 are formed.

In this case, the interval between the first and second guide barrels 21 and 23 is such that the center body 11 is inserted between the first and second guide barrels 21 and 23 without any play. It is preferable that the intervals correspond to the heights of.

Although the first and second hinges are stated to be fixed to the door frame and the door, respectively, for convenience of description, the present invention is not limited thereto, and when one of the first and second hinges is coupled to the door frame, the other one is fixedly coupled to the door. It is possible to use

In addition, the first and second guide barrels 21 and 23 are coupled to the first and second sealing caps 93 and 97 at one end facing the central body, respectively, to prevent leakage of oil charged into the inside. At the other end, first and second end caps 91 and 95 having air discharge bolts 91a and 95a coupled thereto are coupled.

On the other hand, the first and second cam shafts 30 and 60 rotated by the relative external force generated in the first and second guide cylinders 21 and 23 when the door is rotated, the pair of shafts 31 and 61 Circular bodies 33 and 63, which are fixed by spring pins 31a and 61a in the state inserted into the central body 11 so as to face each other, respectively, and which are respectively formed on the pair of shafts 31 and 61, are respectively formed. The inner peripheral parts of the 1st and 2nd guide cylinders 21 and 23 are rotatably provided.

At this time, the cylindrical body (33, 63) along the outer circumferential surface of the first and second elevating guide hole (34a, 34b) and the third, fourth elevating guide hole (64a) 64b) are respectively penetrated.

The first and second lifting guide holes 34a and 34b of the first camshaft 30 are the third and fourth lifting guide holes 64a and 64b of the second camshaft 60 as shown in FIG. 2A. Compared with a short section, one end is formed to open to the end of the circular body 33, and the third and fourth lifting guide holes 64a and 64b of the second cam shaft 60 are both ends. It is formed in the circular body 63 to be closed.

delete

Accordingly, at the end of the automatic door return, the pair of pistons 53 and 83 to be described below are simultaneously raised and lowered to increase the damping force, thereby increasing the closing force of the door.

Also, between the inner circumference of the central body 11 and the shafts 31 and 61, the repulsive force of the return springs 111 and 113 for elastically supporting the pair of pistons 53 and 83, which will be described below, is applied. First and second thrust bearings 71a and 71b are inserted respectively to reduce rotational friction and noise when the shafts 30 and 60 rotate.

In addition, between the upper end of the circular body 33 of the first cam shaft 30 and the first sealing cap 93 and between the upper end of the circular body 63 of the second cam shaft 60 and the second sealing cap 97, respectively. The first and second radial bearings 75a and 75b are coupled to reduce rotational friction and noise as the first and second camshafts 30 and 60 rotate, similar to the thrust bearings 71a and 71b. .

In this case, first and second spring washers 73a and 73b are disposed between the first thrust bearing 71a and the first sealing cap 93 and between the second thrust bearing 71b and the second sealing cap 97. Are respectively disposed, and the first and second spring washers (73a, 73b) to remove the frictional resistance of the side of the central body 11 and the first and second guide cylinders (21, 23) abut each other, The fall of the rotational force of a 1st and 2nd guide cylinder can be prevented beforehand.

Meanwhile, both ends of the first and second guide pins 41 and 43 respectively have the first and second elevating guide holes 34a and 34b and the third and fourth elevating guide holes 64a and 64b. The first and second vertical guide grooves 22a and 22b and the third and fourth vertical guide grooves 24a and 24b are coupled to each other.

In addition, the first and second piston rods 51 and 81 through which the central portions of the first and second guide pins 41 and 43 are coupled to one side thereof, respectively, are rotated by the first and second cam shafts 30 and 60. The first and second camshafts 30 and 60 in a sliding manner along the first and second vertical guide grooves 22a and 22b and the third and fourth vertical guide grooves 24a and 24b respectively. Ascending and descending along the inner circumferences of the circular barrels 33 and 63, through holes 51a and 81a are bent at one end and bent perpendicularly to the outer circumference.

Furthermore, one end of the first and second piston rods 51 and 81 having the through holes 51a and 81a is formed in the coupling holes 53b and 83b formed at the centers of the first and second pistons 53 and 83. Removably coupled.

Accordingly, the first and second pistons 53 and 83 are interlocked with the first and second piston rods 51 and 81 so that an outer circumference thereof is along the inner circumference of the first and second guide barrels 21 and 23. The inner spaces of the first and second guide cylinders 21 and 23 are partitioned into the first upper and lower chambers 21a and 21b and the second upper and lower chambers 23a and 23b, respectively. Doing.

In addition, the first and second pistons 53 and 83 are formed smaller than the diameters of the coupling holes 53b and 83b and at the same time communicate with the coupling holes 53b and 83b, respectively. , 83a) is formed.

Accordingly, the hinge device includes a first flow path communicating with the first upper / lower chambers 21a and 21b, that is, a through hole 51a and a first central through hole 53a and a first center through hole of the first piston rod 51. It has a 2nd flow path which communicates two upper / lower chambers 24a and 24b, ie, the through-hole 81a of the 2nd piston rod 81, and the 2nd center through-hole 83a.

Meanwhile, the first and second flow paths may be opened and closed inside the first and second pistons 53 and 83 by raising and lowering the first and second pistons 53 and 83, respectively. The first and second valve actuators for controlling the rising / lowering speed of the first and second pistons 53 and 83 by increasing or decreasing the flow rate of the oil moving through the lower chambers 21a, 21b; 23a, 23b. 54, 84 are arranged to be flowable.

The first and second valve actuators 54 and 84 have a larger diameter than the first and second through holes 53b and 83b, but are somewhat larger than the diameters of the first and second central through holes 53a and 83a. It is formed small, and small through holes 54a and 84a are formed in the center to allow oil to pass therethrough.

In addition, when the through hole 51a of the first piston rod is closed by the first valve mover 54 as shown in FIG. 3A, the first oil flow amount continues from the upper chamber 21a to the lower chamber 21b. A plurality of flow path grooves 52 are formed in the through-hole 51a of the first piston rod along its inner circumferential surface so as to flow therethrough.

Similarly, when the through hole 81a of the second piston rod is closed by the second valve mover 84 as shown in FIG. 3B, the oil is continuously transferred from the lower chamber 23b to the upper chamber 23a. A plurality of flow path grooves 82 are formed along the inner circumferential surface of the through hole 81a of the second piston rod so as to flow in the flow amount.

On the other hand, look at the action of the check valve operating in accordance with the opening and closing of the door of the hinge device as follows.

First, when the door is opened, the first valve actuator 54 sequentially passes through the first flow paths 53a, 54a, and 51a in the first upper chamber 21a as the first piston 53 rises. It is lowered in the coupling hole 53b, and at the same time, the second valve mover 84 moves from the second lower chamber 23b to the second flow paths 83a, 84a, as the second piston 83 descends. The oil passes sequentially through 81a) and rises in the coupling hole 83b.

In this process, the oil filled in the first upper chamber 21a passes through the first central through hole 53a between the outer circumference of the first valve mover 54 and the inner circumferential surface of the coupling hole 53b and the small through hole 54a. When the first valve actuator 54 closes the bent through hole 51a through the bent through hole 51a, it continues through the plurality of flow path grooves 52 and the small through holes 54a. The first oil flow amount flows into the first lower chamber 21b.

At the same time, the oil filled in the second lower chamber 23b passes through the second central through hole 83a between the outer circumference of the second valve mover 84 and the inner circumferential surface of the coupling hole 83b and the small through hole 84a. When the second valve movable body 84 closes the bent through hole 81a through the bent through hole 81a, the second valve movable body 84 closes the bent through hole 81a. It flows into the 2nd upper chamber 23a by 1 oil flow amount.

 On the contrary, when the door is closed, the first valve actuator 54 sequentially passes through the first flow paths 51a, 54a, and 53a in the first lower chamber 21b as the first piston 53 descends. The bottom surface of the first valve mover 54 closes the first central through hole 53a of the first piston 53 while being raised in the coupling hole 53b by oil, and then the first upper chamber ( As the outflow passage of the oil moving to 21a) is limited to the small through hole 54a, the oil flows in the second oil flow amount, which is less than the first oil flow amount. Therefore, the flow amount of the oil flowing as compared with the opening of the door is greatly reduced, the rising speed of the first piston 53 is reduced, and eventually serves to slow down the rotation speed of the door.

At the same time, the second valve movable body 84 is lowered in the coupling hole 83b by oil passing sequentially through the second flow paths 83a, 84a, and 81a in the second upper chamber 23a. The bottom surface of the movable body 84 closes the second central through hole 83a of the second piston 83, and then the outflow passage of the oil moving to the second lower chamber 23b is a small through hole 84a. In this case, the second oil flow amount is smaller than the first oil flow amount. Therefore, as in the first valve movable body 54, the amount of oil flowing in the door is greatly reduced as compared with the opening of the door, so that the descending speed of the second piston 83 is reduced, thereby lowering the rotation speed of the door.

On the other hand, the first and second return springs 111 and 111 to elastically support the first and second pistons 53 and 83 on the upper side of the first upper chamber 21a and the lower side of the second lower chamber 23b. 113) are installed respectively.

The first and second return springs 111 and 113 are compressed when the door is opened and provide a restoring force for returning the first and second pistons 53 and 83 to their original positions when the door is returned.

Reference numerals 131, 132, 133, 134, 135, and 136 shown in the drawings all represent O-rings for preventing leakage of oil, respectively.

4A and 4B are enlarged views showing another example of the check valve shown in FIGS. 3A and 3B, that is, a ball type valve movable member.

In the present embodiment, the first and second valve actuators 54 and 84 have a disc shape, but it is also possible to form such a valve actuator in a ball type. That is, as illustrated in FIG. 4A, the first valve body 154 has a spherical first valve movable body 154 having a diameter larger than the diameter of the first central through hole 53a of the first piston and the bent through hole 51a of the first piston rod. And when the first central through hole 53a of the first piston is closed by the first valve mover 154 as the first piston 53 descends, oil is discharged from the lower chamber of the first chamber. As the flow path groove 55 is formed at the inner circumferential end of the first central through hole 53a of the first piston, the flow rate of oil can be increased or decreased as in the case of a disk-shaped valve moving body.

Similarly, as shown in FIG. 4B, the second valve moving body 184 has a diameter larger than the diameter of the second central through hole 83a of the second piston and the bending through hole 81a of the second piston rod. When the second piston 83 is raised, the second central through hole 83a of the second piston is closed by the second valve mover 184, and oil is transferred from the upper chamber to the lower chamber of the second chamber. As the flow path groove 85 is formed at the inner circumferential end of the second central through hole 83a of the second piston, the flow amount of oil can be increased or decreased as in the case of the disc-shaped valve moving body.

Hereinafter, the lifting and lowering guide structure of the piston according to the present invention will be described in detail with reference to FIGS. 2A and 2B.

First, the first and second lifting guide holes 34a and 34b of the first camshaft 30 each have one section a linked to the door opening angle, that is, the door opening angle is 0, as shown in FIG. 2B. The first section a between ˜15 ° and the second section b to d with the first piston 53 stopped when the door is opened between 15 and 160 °.

Here, the patterns corresponding to the second sections b to d are omitted in the first and second lifting guide holes 34a and 34b. That is, it consists only of the length corresponding to the first section (a).

In addition, the third and fourth lifting and lowering guide holes 64a and 64b of the second camshaft 60 have four sections ad interlocked with the door opening angle, that is, the door opening angle is zero, as shown in FIG. 2B. A first section (a) between -15 °, a second section (b) between 15-90 ° door opening angle, a third section (c) between 90-130 ° door opening angle, and door The opening angle is divided into a fourth section d between 130-160 °.

The first section a, in which the first and second pistons 53 and 83 operate simultaneously, has a closing force such that a latch installed in the door can be coupled to a locking device installed in the door frame when the door automatically returns. This is a hydraulic circuit state (see FIG. 5E).

In this case, the cam diagram angle α of the elevating guide holes 34a, 34b; 64a, 64b is increased by the resistance of the hydraulic circuit and the closing force loss due to the proportional decrease in the restoring force of the return springs 111, 113. The closing force loss is compensated for by increasing the efficiency when the piston is raised by setting it in the 45 to 65 ° range, which is larger than the angle β of (b).

As a result, even when the compression spring is used without using the torsion spring as the return spring in the automatic return of the door, it can be completely returned (locked) to the initial position of the door.

In addition, the second section b in which only the second piston 83 is operated while the first piston 53 is stopped is the hydraulic circuit state of FIG. 5C which will be described later when the door is automatically returned. In this case, when the door is opened, only the second piston 83 supported by the second return spring 113 is operated while the first piston 53 is stopped.

Accordingly, the opening force is increased in direct proportion to the opening angle as the door is opened from 0 ° to 160 ° when the door of the prior art is fully opened, and since the second section requires a lot of force to open the door. In the case of the first section (a) in order to preserve the closing force of the door similar to the conventional opening force is required, but from the second section (b) compared to the first section (a) the opening force is greatly reduced and heavy large The door can be opened easily.

On the other hand, in the second section b, the cam line angle beta of the third and fourth elevating guide holes 64a and 64b is 10-45, which is relatively smaller than the angle α of the first section a. By setting the range, the rotational efficiency of the camshafts 30 and 60 is increased proportionally when the door is opened to compensate for the opening force rising portion that increases in proportion to the opening of the door.

In addition, the third section (c) in which both the first and second pistons (53, 83) are stopped is a section in which the automatic return by the return spring 113 is blocked by setting the cam diagram angle to zero (0). As a result, the angle of the door is kept open, and the restoring force of the return spring 113 is greatest. The fourth section d is a stopping force reinforcement section which is formed to be inclined upward in the third section c and is stopped so that the second guide pin 43 cannot move by being caught. In this case, the fourth section d may be formed to extend so that the door opening angle is between 130 and 180 degrees.

On the other hand, when the guide pin 43 rises due to the repulsive force of the compressed return spring 113, the hydraulic pressure of the upper side of the piston 83 is near the limit point at which the second piston 83 can rise. By acting larger than the elastic force of, the piston 83 can be sharply lowered in the reverse direction.

In addition, the guide pin 43 may cause internal noise and breakage of internal components due to irregular movement in the initial stage of entering the second section b from the third section c. In order to prevent this, it is preferable that the boundary between the first cam line diagram holding unit 644 and the second cam line diagram holding unit 645 is formed in a curved surface in the third and fourth lifting guide holes 64a and 64b. .

In addition, the first cam line diagram holding unit 644 and the second cam line diagram holding unit 645 are set to face opposite curved surfaces with the third elevating guide hole 64a.

Hereinafter, the overall operation of the hinge apparatus for a large door of the present invention will be described with reference to FIGS. 5A to 5F.

Figure 5a is a cross-sectional view of the piston and the return speed control showing the initial position where the first and second pistons are located at the bottom dead center and the top dead center, respectively, Figure 5b is a door opening angle of 0 ° to 15 ° according to the opening of the door When the pistons of the first and the second piston unit in the process of lifting and lowering, respectively, Figure 5c shows the second piston in a state in which the first piston is stopped in the process of the door opening angle reaches 15 ° to 90 ° according to the opening of the door 5D is a hydraulic flow chart when the piston descends, FIG. 5D is a hydraulic flow chart when the second piston ascends while the first piston is stopped until the door opening angle reaches 90 ° to 15 ° according to the closing of the door, 5E is a hydraulic flow chart when the first and second pistons are simultaneously lowered / ascended during the process of reaching the door opening angle from 15 ° to 0 ° according to the closing of the door, and FIG. 5F is the door opening angle according to the closing of the door. Reaching zero degrees A cross-sectional view of the piston and the return speed control unit showing the state where the first and second pistons are returned to their initial positions located at the bottom dead center and the top dead center, respectively.

In the hinge apparatus for a large door according to the first embodiment of the present invention, the hydraulic circuit is set as shown in FIG. 5B by opening the door in the closed state as shown in FIG. 5A.

That is, in the hinge apparatus 100 for a large door according to the first embodiment of the present invention, an external rotational force is transmitted to the shafts 31 and 61 of the first and second cam shafts 30 and 60 when the door is opened. The components inside it operate as follows.

When the user opens the door in the initial state of FIG. 5A in which the door is closed, since the rotational force in the right-hand direction is transmitted to the first guide cylinder 21, the first and second lifting guide holes 34a and 34b and the first The guide pin 41 having both ends inserted into the pair of vertical guide grooves 22a and 22b formed in the guide cylinder 21 rotates together with the rotation of the first guide cylinder 21 while the first camshaft 30 is rotated. The first and second elevating guide holes (34a, 34b) of the upper direction is moved.

At the same time, since the rotational force in the right-hand direction is transmitted to the second guide cylinder 23 similarly to the first cam shaft, a pair formed in the third and fourth lifting guide holes 64a and 64b and the second guide cylinder 23. The guide pins 43 having both ends inserted into the vertical guide grooves 24a and 24b thereof are moved downward along the third and fourth lifting guide holes 64a and 64b by the rotation of the cam shaft 60. do.

In this case, as illustrated in FIG. 5B, the pair of guide pins 41 and 43 moving in a direction away from each other and the first and second pistons interlocking with each other through the first and second piston rods 51 and 81 ( 53 and 83, the force to move in the upper and lower direction, respectively.

Accordingly, the oil located above the first piston 53, that is, the first upper chamber 21a, opens the first valve mover 54 so that the first flow paths 53a, 54a and 51a and the first valve mover are opened. (54) Passes between the outer circumference and the inner circumference of the recess 53b, and easily moves to the lower side of the first piston 53, that is, the first lower chamber 21b.

At the same time, the oil located under the second piston 83, that is, the second lower chamber 23b, opens the second valve mover 84 so that the second flow paths 83a, 84a, 81a and the second valve mover ( 84) It passes between the outer circumference and the inner circumference of the recess 83b, and moves to the upper side of the second piston 83, that is, the second upper chamber 23a.

Then, the first guide pin 41 moves in the first section (a) as in the operating state in the first and second lifting guide holes (34a, 34b) shown in Figure 2b, the first piston 53 Is compressed while the return spring 111 is compressed, and at the same time, the second guide pin 113 is moved in the first and second sections as in the operating states in the third and fourth lifting guide holes 64a and 64b. While moving in a, b), the second piston 83 descends while compressing the return spring 113.

In addition, as shown in FIG. 5C, the second guide pin 43 reaches the third section c when the second cam shaft 60 continuously rotates while the first guide pin 41 is stopped. As the movement is restricted by the first stop portion 642 of the third section c of the third and fourth elevating guide holes 64a and 64b, the second piston 83 moves to the bottom dead center. It stays stationary in its positioned position.

On the other hand, when the door is closed, the hinge device of the present invention, as shown in FIG. 5D, when the user closes the door so that the opening angle of the door is within 90 °, or opens the door and releases the door within 90 °, the door automatically opens. Perform the return operation.

When the opening angle of the door is 90 °, that is, when the user rotates the door and a slight external force is transmitted to the second cam shaft 60 in the left direction, the second guide pin 43 stops the first stop. The part 642 passes through the third section c.

Then, the second piston 83 starts to move upward by the repulsive force of the compressed return spring 113, and the guide pin 43 connected to the second piston 83 also moves the third and fourth lifting guide holes. It rises along the 2nd section b of 64a, 64b, ie the raising and lowering guide part 641 of the gentle inclination angle of 10-45 degrees. As a result, the second guide cylinder 23 attempts to return the door to the initial position by rotating in the left screw direction.

At this time, the oil of the second upper chamber 23a is separated from the second upper chamber 23a through the second flow paths 81a, 84a, and 83a by the second piston 83 rising as shown in FIG. 5D. It moves to the central through-hole 83a.

As a result, the second valve mover 84 closes the second center through hole 83a of the second piston 83 by oil introduced through the second flow paths 81a, 84a, and 83a. The second center through hole 83a is blocked while being seated in the recess 83b of the 83.

Thereafter, when the opening angle of the door reaches 30 °, since the second flow path is blocked by the second valve mover 84, the oil on the upper side of the second piston 83 is the second valve mover 84. Since only the through-hole 84a of the (2) flows into the second lower chamber 23b, the flow rate of the oil decreases to 1/2 and rises slowly at a second speed slower than the first speed at the door opening.

In this case, the guide pin 43 connected to the second piston 83 ascends along the second section b of the elevating guide holes 34a and 34b, that is, the elevating guide portion 641 having a gentle angle.

The second piston 83 at a slow second speed is maintained until the door opening angle reaches 15 ° so that the user can prevent a safety accident due to the rapid return of the door.

Then, as the door opening angle passes 15 degrees as shown in FIG. 5E, the 1st piston 53 which was stopped with the 2nd piston 83 which continues to raise toward top dead center will begin to descend. That is, the guide pins 41 and 43 respectively connected to the first and second pistons 53 and 83 are the first sections a of the elevating guide holes 34a, 34b and 64a and 64b, that is, 45 °- It begins to descend and ascend along the elevation guide 641 set at a steep inclination angle between 65 °.

At this time, the oil of the first lower chamber 21b is discharged from the first upper chamber 21a through the first flow paths 51a, 54a, 53a by the first piston 53 descending as shown in FIG. 5E. The first valve moving body 54 is moved to the central through hole 53a so that the first central through hole of the first piston 53 is caused by oil introduced through the first flow paths 51a, 54a, and 53a. The first central through hole 53a is blocked while being seated in the recess 53b of the piston 53 in a state of closing 53a.

Accordingly, since the oil on the lower side of the first piston 53 flows to the first upper chamber 21a only through the through-hole 54a of the first valve mover 54, the flow amount of oil is greatly reduced and the second piston It rises slowly at the 2nd speed slower than the 1st speed of 83.

delete

Therefore, when the door opening angle is between 15 ° and 0 °, the hydraulic circuit is set in the same manner as when the door opening angle is between 90 ° and 15 °, but the inclination angle of the elevating guide part 641 is set to the second section b. It is set relatively larger than the inclination angle. As a result, the restoring force of the first and second return springs 111 and 113 is reduced, but the frictional resistance of the elevating guide portion 641 is reduced, so that the first and second pistons 53 and 83 are lowered and raised. The speed is accelerated to the third speed. Thus, the door is returned to the initial position and locked by the latch of the door.

At this time, the first and second pistons 53 and 83 return to the initial position as shown in FIG. 5F.

As described above, in the present invention, when the cam spring angle of the elevating guide portion 641 of the elevating guide holes 34a, 34b; 64a, 64b is appropriately set, the compression spring is used as the return spring. When the door is close to the initial position, the spring's restoring force is reduced to solve the problem of the door not closing completely.

As described above, the hinge device of the present invention preserves the closing force of the door when the door is closed, as well as the opening force of about 15 ° or more from opening the door at least 15 ° when the door is opened. It can be reduced by 1/2 to easily open large doors with less force.

In addition, the present invention can control the automatic return speed and the return force of the door by changing the frictional resistance by the restoring force of the return spring at the automatic return of the door, the control of the flow path of the hydraulic circuit and the angle of the cam diagram of the elevating guide hole. have.

6 is a partial cross-sectional view showing an elastic force setting unit for adjusting the elastic force of the return spring to the sealing cap shown in FIG.

On the other hand, in the first embodiment according to the present invention it is also possible to have a structure that can adjust the opening and closing force of the door according to the user arbitrarily set the elastic force of the spring as shown in FIG.

That is, a separate elastic force setting unit may be installed in the first or second sealing caps 91 and 95 illustrated in FIG. 1, and FIG. 6 illustrates an example installed in the second sealing cap 95.

First, the screw coupling groove 95b and the sliding hole 95c penetrating the second sealing cap 95 in the center of the second sealing cap 95 are formed stepped on the same axis, and the push bolt 950 The head portion 951 is screwed into the screw coupling groove 95b, and the body portion 952 formed at one end of the head portion 951 is slidably inserted into the sliding hole 95c.

In addition, the push bolt 950 is formed with a wrench groove (not shown) on one surface of the head portion 951 so as to rotate using a tool such as a wrench.

In addition, the pressing plate for pressing the second return spring 113 while rising along the inner circumferential surface of the second guide cylinder 23 by the push bolt 950 between the second sealing cap 95 and the second return spring 113 ( 960 is disposed. In addition, the pressure plate 960 is preferably made of a diameter larger than the diameter of the second return spring (113).

Therefore, when the closing force of the door is increased by increasing the elastic force of the second return spring 113, the head portion 951 is rotated inside the hinge device along the screw coupling groove 95b by rotating the push bolt 951. When moved to the body portion 952 to push the one surface of the pressure plate 960 to contract the return spring 113.

Accordingly, the return spring 113 increases the elastic force by the contracted distance, thereby increasing the closing force of the door. On the contrary, when the push bolt 950 is rotated outward of the hinge device, the return spring 113 is rotated. Since the elastic force of the door is reduced, the closing force of the door can be reduced, and the strength of the closing force of the door can be easily controlled by adjusting the push bolt 950.

7 is a longitudinal sectional view of a hinge device for a large door according to a second embodiment of the present invention.

On the other hand, the second embodiment of the present invention is a premise configuration and its operation is made somewhat similar to the first embodiment, except that the hinge device of the first embodiment according to the present invention is opposed to the central body 11 Hydraulic closing circuits are formed in the first and second guide barrels 21 and 23, respectively, but in the case of the hinge device 200 according to the second embodiment of the present invention, as shown in FIG. It is formed relatively longer than the first and second upper and lower bodies 221 and 223, and forms a partition 211 at the inner center and simultaneously combines the first and second sealing caps 293 and 297 at both ends. The difference between the two hydraulic closed circuits in one central body 210 is different.

In addition, the shafts 231 and 261 of the first and second cam shafts 230 and 260 are respectively inserted into and fixed through the keys 299a and 299b inside the first and second upper and lower bodies 221 and 223, respectively. Although it is formed in the key fixing method, in addition to the first and second upper and lower body portion of the shaft (231, 261) to be inserted into the first and second upper and lower body (221, 223) to form a polygon and It is also possible to fix the inner circumference of the 221, 223 to the corresponding shape, and of course, it is also possible to adopt a fixing method by a spring pin penetrating at a right angle to the shaft as in the first embodiment.

In the hinge device 200 according to the second embodiment of the present invention, the cam line lengths of the first and second cam shafts 230 and 260 are set differently from each other, as in the first embodiment. Between 0 and 15 °, a pair of pistons are raised and lowered simultaneously to preserve the closing force of the door when the door is closed, and to release the opening force from opening the door at least 15 ° when the door is opened. Compared to 1/2, it is possible to easily open a heavy large door with little force.

Reference numerals 233 and 263 denote circular bodies of the camshaft, respectively.

8 is a longitudinal sectional view of a hinge device for a large door according to a third embodiment of the present invention.

The hinge device 300 according to the third embodiment of the present invention employs a pair of camshafts as in the first and second embodiments, and at the same time, the overall configuration is similarly formed and its operation is similar.

However, while the first and second embodiments have two hydraulic closed circuits, the third embodiment has a configuration having a hydraulic closed circuit partitioned into upper and lower chambers 323a and 323b by the second piston 383. There is one flow path 383a, 384a, 381a for oil to move the upper and lower chambers 323a, 323b.

That is, in the case of the first piston 353, a separate flow path and a valve moving body for controlling the same do not exist, and are simply configured to serve as pistons in a state supported by the return spring 311.

Meanwhile, in the case of the first and second embodiments, any one of a pair of pistons is omitted in a separate flow path and a valve moving body for controlling the same as in the third embodiment, and is simply formed in a state supported by a return spring. It is also possible, in this case, to remove the oil from the chamber where the simplified piston is present.

In the second and third embodiments according to the present invention as well as the first embodiment, it is also possible to form and apply the valve mover to a disc type as well as a ball type.

As described in detail above, the automatic return hinge device for a large door according to the present invention installs a pair of camshafts having different cam lead lengths and a pair of pistons coupled thereto in a hinge type hinge device used for a large door. At the beginning and the end of door opening, a pair of pistons can be raised and lowered simultaneously to preserve the closing force of the door and at the same time reduce the opening force of the door, making it easier to open heavy doors with less force. By implementing this there is an advantage to improve the reliability of the product.

Although the technical idea of the hinge apparatus for a large door of the present invention has been described above with the accompanying drawings, this is illustrative of the best embodiment of the present invention and is not intended to limit the present invention. In addition, it is obvious that any person skilled in the art can make various modifications and imitations without departing from the scope of the technical idea of the present invention.

Claims (9)

In the self-returning hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, which automatically returns when the door is closed, A central body having one circumferential surface fixedly coupled to the center of the first hinge; One or more circumferential surfaces are fixedly coupled to upper and lower ends of the second hinge so as to maintain a distance corresponding to the height of the central body, respectively, and the first and second vertical guide grooves and the third vertical guide grooves are respectively positioned at positions opposite to each other. A fourth vertical guide groove formed therein, the first and second guide passages having first and second chambers into which oil is charged, respectively; A pair of shafts are fixedly inserted into the central body so as to face each other, and a circular body extending in the pair of shafts is rotatably installed on the inner circumferences of the first and second guide barrels, respectively, along the outer circumferential surface of the cylindrical body. First and second elevating guide holes and third and fourth elevating guide holes each having a cam diagram formed in a spiral shape having a symmetrical moving structure in the through hole, and the first and second guide barrels when the door is rotated. First and second camshafts that are rotated by a relative external force generated in the; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; The central portions of the first and second guide pins are respectively penetrated through one end thereof so that the first and second vertical guide grooves and the third and fourth vertical guide grooves are linked to the rotation of the first and second cam shafts. First and second piston rods which are moved up and down along the circular body inner circumferential surfaces of the first and second cam shafts, respectively, in a sliding manner, and bent through-holes communicating with the outer circumferential portion at the other ends thereof, respectively; First and second coupling holes are formed at the center of one side and the other ends of the first and second piston rods are coupled, respectively, and the first and second central through holes communicating with the first and second coupling holes are formed at the other side. First and second pistons formed on the outer circumferential portion to be slidable along the inner circumference of the first and second guide barrels, and partitioning the first and second chambers up and down, respectively; The first and second pistons are formed in the first and second pistons to increase or decrease the flow amount of oil moving in the first and second upper / lower chambers according to the rise / fall of the first and second pistons. First and second check valves for controlling the piston's rising / falling speed; First and second sealing cap portions coupled to the upper and lower ends of the first and second guide cylinders in a sealing state, respectively, such that the insides of the first and second guide barrels form independent hydraulic closed circuits; First and second lower chambers respectively installed to elastically support the first and second pistons, the first and second pistons providing a restoring force for returning the first and second pistons to their original positions upon return of the door; Automatic return hinge device for a large door, characterized in that composed of a second elastic member. In the self-returning hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, which automatically returns when the door is closed, One circumferential surface is fixedly coupled to the center of the first hinge, the inner side is divided into the first and second chambers by the partition wall, and the first and second in the vertical direction at positions facing each other inside the first and second chambers, respectively. A central body having two vertical guide grooves and third and fourth vertical guide grooves formed therein; First and second fixed bodies each having one side coupled to upper and lower side ends of the second hinge, respectively, while maintaining a distance from which the central body can be inserted; Shafts are fixedly inserted into the first and second fixing bodies, respectively, and first and second circular bodies respectively detachably coupled to the shafts are rotatably inserted into the first and second chamber inner circumferences of the central body, respectively. When the first and second elevating guide holes and the third and fourth elevating guide holes each having a cam diagram consisting of spirally symmetrical moving structures along the outer circumferential surface of the circular body are formed through each other, and the door is rotated. First and second camshafts that are rotated by relative external forces generated in the first and second fixed bodies; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; An upper end portion is penetrated by the first and second guide pins, respectively, and along the first and second vertical guide grooves and the third and fourth vertical guide grooves in association with rotation of the first and second camshafts. First and second piston rods which are moved up and down along the inner circumferential surfaces of the first and second camshafts in a sliding manner, respectively, and have bent through holes at one end thereof, the bending through-holes communicating vertically with the outer circumference; First and second coupling holes are formed at the center of one side and the other ends of the first and second piston rods are coupled, respectively, and the first and second central through holes communicating with the first and second coupling holes are formed at the other side. First and second pistons formed on the outer circumference thereof so as to be slidable along the inner circumference of the central body, and simultaneously partitioning the first and second chambers up and down; The first and second pistons are formed in the first and second pistons to increase or decrease the flow amount of oil moving in the first and second upper / lower chambers according to the rise / fall of the first and second pistons. First and second check valves for controlling the piston's rising / falling speed; A pair of sealing caps coupled to the upper and lower ends of the central body in a sealing state, respectively, so that the first and second spaces of the central body form independent hydraulic closed circuits; An elastic member installed in each of the first lower chamber and the second upper chamber to elastically support the first and second pistons, and providing a restoring force for returning the first and second pistons to their original positions upon return of the door; An automatic return hinge device for a large door, characterized in that the configuration. The first check valve of claim 1 or 2, wherein the first check valve is arranged to be movable in the coupling hole of the first piston, and the diameter of the first bent through hole of the first central through hole and the first piston rod. The larger disk-shaped first valve mover and the oil moving from the upper chamber to the lower chamber of the first chamber when the first bent through hole is closed by the first valve mover as the first piston rises are removed. A plurality of flow path grooves formed along the inner circumferential end of the first groove and the first central through hole of the first piston is closed by the first valve mover as the first piston descends so as to flow in one oil flow amount. A small through hole formed in the first valve mover to move the oil moving from the lower chamber of the first chamber to the upper chamber to a second oil flow amount which is less than the first oil flow amount; The second check valve is arranged to be movable in the coupling hole of the second piston, the disk-shaped second valve movable body is formed larger than the diameter of the groove of the second central through hole and the second piston rod, 2 As the piston descends, when the groove of the second piston rod is closed by the second valve mover, the oil moving from the lower chamber of the second chamber to the upper chamber flows in the first oil flow rate. A plurality of flow path grooves formed along the inner circumferential end of the groove, and the lower chamber from the upper chamber of the second chamber when the second central through hole of the second piston is closed by the second valve mover as the second piston is raised. And a small through hole formed in the second valve mover for flowing the oil moving to the second oil flow amount which is less than the first oil flow amount. Automatic return hinge device for mold door. The first check valve of claim 1 or 2, wherein the first check valve is disposed to be movable in the coupling hole of the first piston, and the diameter of the first central through-hole of the first piston and the groove of the first piston rod. A spherical first valve mover formed larger than the diameter, and oil moving from the upper chamber to the lower chamber of the first chamber when the first groove is closed by the first valve mover as the first piston rises, A plurality of flow path grooves formed along the inner circumferential end of the first groove for flowing the oil flow amount, and when the first central through hole of the first piston is closed by the first valve mover as the first piston descends; One flow path groove formed in the inner circumferential end of the first central through hole of the first piston to move the oil moving from the lower chamber of the first chamber to the upper chamber to the second oil flow amount which is less than the first oil flow amount Done; The second check valve is arranged to be movable in the coupling hole of the second piston, the second valve movable body of the spherical shape is formed larger than the diameter of the groove of the second central through hole and the second piston rod, 2 As the piston descends, when the groove of the second piston rod is closed by the second valve mover, the oil moving from the lower chamber of the second chamber to the upper chamber flows in the first oil flow rate. A plurality of flow path grooves formed along the inner circumferential end of the groove, and the lower chamber from the upper chamber of the second chamber when the second central through hole of the second piston is closed by the second valve mover as the second piston is raised. In order to flow the oil moving to the second oil flow amount which is a flow amount less than the first oil flow amount is composed of one flow path groove formed in the inner circumferential end of the second central through hole of the second piston Automatic return hinge device for large doors characterized in that the falling. In the self-returning hinge device for a large door having a pair of first and second hinges fixed to the door frame and the door, which automatically returns when the door is closed, One circumferential surface is fixedly coupled to the center of the first hinge, and the first and second vertical guide grooves and the third and fourth vertical guide grooves are respectively formed in the up and down directions at positions opposing each other on the upper and lower inner peripheral parts. A central body having a chamber therein; First and second fixed bodies each having one side coupled to upper and lower side ends of the second hinge, respectively, while maintaining a distance from which the central body can be inserted; Circular bodies fixedly inserted into the first and second fixed bodies respectively and detachably coupled to the shafts are rotatably installed on the inner circumference of the chamber of the central body, respectively, and are symmetrically moved along the outer circumferential surface of the cylindrical body. The first and second elevating guide holes and the third and fourth elevating guide holes each having a cam diagram made of a spiral shape of the structure are formed therethrough, and are formed in the first and second guide barrels when the door is rotated. First and second camshafts rotating by relative external force; First and second ends of the first and second lifting guide holes and the third and fourth lifting guide holes respectively coupled to the first and second vertical guide grooves and the third and fourth vertical guide grooves, respectively. A second guide pin; As the central portion of the first guide pin penetrates through one end and cooperates with the rotation of the first camshaft, the first guide pin moves up and down along the cylindrical body inner circumferential surface of the first camshaft in a sliding manner along the first and second vertical guide grooves. The drop has a first piston rod; A first piston integrally formed at the other end of the first piston rod and having an outer circumference portion slidably coupled to an inner circumference portion of the central body; The central portion of the second guide pin is coupled to one end portion and is moved up and down along the cylindrical body inner circumferential surface of the second cam shaft in a sliding manner along the third and fourth vertical guide grooves in association with rotation of the second cam shaft. A second piston rod having a bent through hole at one end formed in communication with the outer circumference; Coupling holes are formed at the other end of the second piston rod is coupled to each other, the center through-hole is formed in communication with the coupling hole on the other side, the outer circumference is arranged so as to slide along the inner circumference of the chamber of the central body, respectively And a second piston for partitioning the chambers up and down at the same time; A check for controlling the rising / falling speed of the first and second pistons by increasing or decreasing the flow amount of oil which is formed in the second piston and moves mutually in the upper / lower chamber according to the rising / falling of the second piston. A valve; A pair of sealing caps coupled to the upper and lower ends of the central body in a sealing state; A large view, comprising: an elastic member installed in the upper chamber to elastically support the first and second pistons to provide a restoring force for returning the first and second pistons to their original positions upon return of the door; Automatic return hinge device for fish. The disk-shaped valve of claim 5, wherein the check valve is disposed to be movable in the coupling hole of the second piston and has a diameter larger than the diameter of the central through hole of the second piston and the groove of the second piston rod. Of the groove of the second piston to flow the first oil flow amount into the moving body and the oil moving from the upper chamber to the lower chamber of the chamber when the groove of the second piston is closed by the valve actuator as the second piston is raised. A plurality of flow path grooves formed along the inner circumferential end and oil moving from the lower chamber of the chamber to the upper chamber when the central passage hole of the second piston is closed by the valve mover as the second piston descends. A large door comprising a small through hole formed in the valve moving body for moving to a second oil flow amount that is less than the oil flow amount Automatic return hinge apparatus. The spherical first valve of claim 5, wherein the check valve is disposed in a coupling hole of the second piston and has a diameter greater than a diameter of a central through hole of the second piston and a groove of the second piston rod. The second piston for flowing the valve mover and the oil moving from the upper chamber to the lower chamber of the chamber at the first oil flow rate when the groove of the second piston is closed by the valve mover as the second piston is raised. A plurality of flow path grooves formed along the inner circumferential end of the groove of the rod, and the central piston hole of the second piston moves from the lower chamber to the upper chamber when the second piston is closed by the valve mover. It consists of one flow path groove formed in the inner circumferential end of the central through hole of the second piston to move the oil to the second oil flow amount which is less than the first oil flow amount Automatic return hinge device for large doors characterized in that the falling. 6. The cam line according to any one of claims 1, 2 and 5, wherein the hinge device is a cam diagram of any one of the first and second lifting guide holes and the third and fourth lifting guide holes of the pair of camshafts. The length is formed longer than the other pair, so that a pair of pistons are simultaneously raised and lowered by a pair of cam shafts at the door opening angle of 0 to 15 °, and a pair of cam shafts are opened at the door angle of 15 to 90 degrees. As the cam diagram is raised and lowered only to the piston that is connected to the long camshaft, the door can be preserved and the door can be opened with less opening force than necessary at the door opening angle from 0 to 15 ° when the door is opened. Automatic return hinge device for a large door, characterized in that opening the. According to any one of claims 1, 2 and 5, wherein the first and second elevating guide hole comprises a first elevating section having a door opening angle of 0-15 °, The 3 and 4 elevating guide holes are the first elevating section with the same length and angle of cam diagram of the first and second elevating guide holes when the door opening angle is between 0-15 ° and the second elevating section between 15-90 °. Automatic return hinge device characterized in that it comprises a falling section.

Images