KR100835730B1 - Ball type clutch device and automatic return hinge device using the same - Google Patents

Abstract

The present invention is provided with a clutch device to install a torsion spring on the hinge upper side to minimize the closing force to reinforce the door closing force, and at the bottom side is provided with at least one hydraulic circuit for sufficiently controlling the damping force by the return spring Accordingly, the present invention relates to an automatic return hinge device capable of minimizing the diameter of the device.

The hinge device includes a first hydraulic circuit having a notch for providing a uniform damping force at the time of closing the door to the check valve to compensate for the reduction of the damping force due to the reduction of the diameter of the chamber, and the flow amount of oil according to the rising position of the piston. It is possible to increase the damping force by providing a second hydraulic circuit in which a hydraulic control rod is inserted into a flow path formed in the piston rod so as to variably control (that is, the rising speed of the piston). In addition, the hinge device has a hydraulic circuit having a notch for providing a uniform damping force when closing the door to the check valve, the door closing speed can be set at a constant speed, remove the return spring and associated with the torsion spring Only the clutch device can provide restoring force to the movable body.

The hinge device of the present invention is applicable to the clutch device associated with the torsion spring and the hydraulic circuit unit to be separated and embedded in both sides of the door to form a hinge shaft.

Hinge device, automatic return, opening force, closing force, torsion spring, clutch device

Description

Ball type clutch device and automatic return hinge device using the same {Ball Type Clutch Apparatus and Hinge Apparatus Having Automatic Return Function Using the Same}

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

2 is a perspective view showing a cam shaft of the automatic return hinge device shown in FIG.

3 is a schematic view showing the position of the guide pin according to the door opening angle and the compression state of the return spring in the elevating guide hole of the camshaft shown in FIG.

4 is a perspective view showing an external clutch of the automatic return hinge device shown in FIG.

5 is a partially enlarged cross-sectional view showing the hydraulic flow in the operation of the overpressure check valve shown in FIG.

6a to 6d are sectional views sequentially showing the operating state of the clutch device according to the opening of the door;

7A to 7C are partially enlarged cross-sectional views sequentially showing hydraulic flow when the movable body descends in accordance with the opening of the door in the first embodiment;

7D and 7E are partially enlarged cross-sectional views sequentially showing hydraulic flows when the movable body is raised in accordance with the closing of the door in the first embodiment;

8 is a partially enlarged cross-sectional view showing a feature of an automatic return hinge device having a structure in which a check valve is embedded in a piston according to a second embodiment of the present invention;

9A is a sectional view of an automatic returning hinge device showing a modification of the first embodiment;

FIG. 9B is a cross-sectional view showing a check valve having a notch portion applied to a modification of the first embodiment shown in FIG. 9A;

10 is a longitudinal sectional view showing a slim type automatic return hinge device having a double hydraulic circuit according to a third embodiment of the present invention;

11A to 11C are partially enlarged sectional views sequentially showing hydraulic flows when the movable body descends when the door is opened in the third embodiment;

11D and 11E are some enlarged cross-sectional views sequentially showing hydraulic flows when the movable body rises according to the closing of the door;

12 is a longitudinal sectional view showing a slim type automatic return hinge device having a ball type clutch device and a double hydraulic circuit according to a fourth embodiment of the present invention;

13 is a perspective view showing a ball type clutch device;

14A to 14C are sectional views sequentially showing an operating state of the ball type clutch device when the door is opened;

15 is a cross-sectional view showing a separation structure of a slim automatic return hinge device according to a fourth embodiment;

FIG. 16 is an explanatory diagram for explaining a state in which the detachable automatic return hinge device shown in FIG. 15 is applied to a door; FIG.

17 is an explanatory diagram for explaining a state in which the integrated self-returning hinge device shown in FIG. 12 is applied to a door.

* Description of Signs for Main Parts in Drawings *

11: upper torso 13: lower torso

15: center torso 21: first hinge

23: second hinge 31,131: upper cap

32, 72, 132: fixing piece 33: lower cap

41: adjusting bolt 43: support

45,145: Hydraulic control rod 47: sealing cap

45a, 145a, 145c: high speed section setting section 45b, 145b, 145d: low speed section setting section

48: ball bearing 50,150: camshaft

51,151: shaft 52a, 71a: tightening groove

53,153: round body 54a: first elevation guide hole

54b: second lifting guide hole 60, 160: movable body

61,161,610: piston rod 62,62a, 162a, 162b, 620: piston part

63: overpressure protection 63a: opening and closing ball

64: counter spring 65: snap ring

66: support nut 66a, 74b: through hole

67,167: return springs 68a to 68f: first to sixth euros

69: notch 78: guide hole forming portion

70: guide pin 71: external clutch

73: internal clutch 74a: first insertion groove

74c: second insertion groove 75: roller pin

76,176,276: torsion spring 77a: first fixing hole

77b: second fixing hole 78a: first guide hole

78b: 2nd guide hole 81, 82, 83, 87, 88: O-ring

84: packing 85: bushing

86: bearing 91: upper chamber

93: lower chamber 100: connector

115: trunk 121: first fixing member

123: second fixing member 162a: first piston portion

162b: second piston portion 163a: first overpressure protector

163b: second overpressure preventing member 164a: first dish spring

164b: second dish spring 165a: first snap ring

165b: second snap ring 168a: first flow path

168b: second euro 168c: third euro

168d: Euro 4 170,171,631-633: check valve

191a: first upper chamber 191b: second upper chamber

193a: second lower chamber 193b: second lower chamber

200: isolation tool 270: rotation axis

271: clutch body 271a, 271b: upper insertion hole

271c and 274c: through hole 272: shaft disk

272a, 272b: through hole 273a, 273b: ball

274: body holder 274a, 274b: lower insertion hole

271d: square projection 275: retaining pin

277: shaft holders 278a, 278b: fixing holes

300,311: hinge device 310: door

320: door frame 321: bearing part

542: first stop part 544,545: cam leading holding part

630,630a, 630b: Overpressure check valve 700,710,720: Clutch device

A, B: hinge device

The present invention relates to a ball-type hinge device and an automatic return hinge device using the same, in particular provided with a clutch device provided with a torsion spring on the upper side of the hinge to reinforce the door closing force, the lower side is provided with a hydraulic circuit provided with a return spring Accordingly, the damping force can be maximized while minimizing the diameter of the device, and the hydraulic circuit is added by extending the length of the hinge and adding a piston part with a check valve to compensate for the reduction of the door closing force due to the reduction of the chamber diameter. The present invention relates to a slim automatic return hinge device capable of increasing damping force.

The hinge device is a device that connects two members so that they can be opened or contacted with each other about one axis as needed. As a representative example, a hinge device (including a movable part in a horizontal direction) used for a door and a door frame, a refrigerator, a mobile phone, etc. And a hinge device for opening and closing (including a movable part in a vertical direction) used for a laptop and the like.

A hinge hinge device having a conventional automatic return function is described in Korean Laid-Open Patent Publication No. 2001-0027832.

In the hinge hinge device of the prior art, when the door is opened, the change head is raised by the rotation of the movable hinge plate, and when the door is closed, the change head is lowered by the elastic restoring force of the compression spring. The hinge device for hinges adjusts the speed at which the door is closed by controlling the amount of foreclosure flowing through the reducing flow passage and the first and second speed adjusting flow passages, thereby changing the raising and lowering speed of the switching head.

However, in the hinge hinge device as described above, the switching head that is lifted / lowered by the rotation of the door is guided by a pair of guide pins, the guide pins are fixed to the hinge knuckles, and the cylinders are formed inside the four hinge knuckles. Since the moving head hinge knuckle has to be rotated for a long period of time due to the internal structure of the switching head, durability is inferior and its configuration is complicated, resulting in poor assembly productivity.

In addition, the compression spring for performing the automatic return of the door is disposed on the upper side of the switching head, the hydraulic circuit for adjusting the return speed of the door is disposed on the lower side, so that the overall length of the hinge device is difficult to reduce, and furthermore, the compression spring Since the length of the layout space is limited only to the upper side, it is difficult to apply to a large door because it cannot provide a large restoring force upon automatic return of the door.

In addition, the connection structure of the inside of the hinge device, the fixed part and the movable part is suitable only as a hinge device for the hinge, and has a structure that is not applicable to the structure where the center of the door and the center of the hinge device are different.

In addition, the hinge hinge device of the prior art does not have a means for temporarily fixing the door so that it does not rotate in an open state at a predetermined angle has a disadvantage that its use is inconvenient.

On the other hand, Korean Utility Model Registration No. 0511646 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.

Conventionally, an optimized structure has not been proposed for a hinge device of a left / right or up / down rotary door applied to a kimchi refrigerator, a refrigerator, a trunk of a vehicle, and the like.

In addition, there is disclosed a hinge device using a single camshaft having a spiral cam diagram that stabilizes a multi-step automatic return speed setting structure as in Korean Patent No. 435188, but such a conventional hinge device has an outer cylinder to the outside. In addition, as the overall diameter is larger than the thickness of the door it was impossible to buy into the door. If the conventional hinge device is manufactured by reducing the diameter of the camshaft and the chamber so that it can be used in the door, the hinge device cannot obtain the damping force required when the door is closed from the hinge device. There is a problem that automatic return is not safe.

Furthermore, in the case of the hinge device using the double camshaft proposed by the inventor in the prior patent application 2004-66832 (August 24, 2004), in the case of the upper camshaft installed to compensate for the reduction of the closing force, Like the lower camshaft, it has a pair of helical elevating holes, which, when the piston rod and valve are actuated by the rotating camshaft, convert about 30% of the force in the direction of rotation in the vertical direction. Since the degree of loss, the role of the upper camshaft in the end did not have a great help in improving the closing force of the door.

Therefore, the present invention has been made to solve the above problems, the object of which is to provide a clutch device associated with the torsion spring on the upper side of the hinge to reinforce the door closing force, the lower side is provided with a hydraulic circuit provided with a return spring Accordingly, to minimize the diameter of the device to maximize the closing force of the door and to provide an automatic return hinge device for a large door that can minimize the opening force over a certain angle.

Another object of the present invention is a slim type that can be embedded in the door automatic return for a slim large door that can increase the damping force by adding at least one hydraulic circuit in the longitudinal direction to compensate for the reduction of the damping force due to the reduction of the chamber diameter It is to provide a hinge device.

It is still another object of the present invention to provide a first hydraulic circuit having a notch for providing a uniform damping force at the time of closing the door to the check valve to compensate for the reduction of the damping force due to the reduction of the chamber diameter as a slim type that can be embedded in the door; Slim type large size to increase the damping force with a second hydraulic circuit with a hydraulic control rod inserted in the flow path formed in the piston rod to variably control the flow rate of the oil (that is, the rising speed of the piston) according to the rising position of the piston An automatic return hinge device for a door is provided.

Another object of the present invention is to provide an automatic return hinge device for a large door having a hydraulic circuit including a notch for providing a uniform damping force to the check valve when closing the door.

Still another object of the present invention is to provide a slim automatic return hinge device for a small door that removes the return spring, provides a restoring force for the movable body only by the clutch device associated with the torsion spring, and provides an efficient door closing force.

Another object of the present invention is to separate the production of the clutch device and the hydraulic circuit unit that can control the flow rate of the oil (that is, the rising speed of the piston) according to the ascending position of the piston and the clutch device associated with the torsion spring It is to provide a slim automatic return hinge device for a small door that can be applied to the structure to form a hinge shaft is embedded on both sides of the.

Still another object of the present invention is to provide an overpressure check valve that can prevent damage to various O-rings for maintaining the body and the piston part by the overpressure generated in the upper chamber when the door is rapidly closed by an external force such as a strong wind. An automatic return hinge device is provided.

Still another object of the present invention is to provide an automatic return hinge device that can maintain an open state of a door in a predetermined angle section by appropriately setting a cam diagram for first and second lifting guide holes of a camshaft.

Another object of the present invention is to control the closing speed of the door in multiple stages by the combination of the shape of the hydraulic control rod, the cam diagram for the first and second lifting guide holes of the camshaft and the clutch device associated with the torsion spring. An automatic return hinge device is provided.
Still another object of the present invention is a ball type clutch for stopping the increase of the elastic force of the torsion spring when the opening angle exceeds the preset opening angle in connection with the torsion spring, and restoring the elastic force of the torsion spring when it falls within the opening angle. To provide a device.

In order to achieve the above object, the present invention is a door hinge device having a first hinge and a second hinge fixed to the door frame and the door, respectively, the upper / lower one of the first hinge is fixed to the upper / lower Lower torso; A central body fixed to one side of the second hinge and pivotally disposed between the upper and lower bodies; A guide hole forming portion disposed at an intermediate portion of the central body and having first and second guide holes formed to face each other in a vertical direction; A shaft having an upper end fixed to the upper body, and a circular body extending from the shaft and having first and second lifting guide holes formed in a spiral shape having a symmetrical moving structure along the outer circumferential surface thereof; A camshaft pivoted by a relative external force applied to the upper body when it is rotated; Guide pins having both ends coupled to the first and second guide holes through the first and second lifting guide holes, respectively; A piston rod slidably coupled to the inside of the circular shaft of the camshaft by a guide pin through which the tip penetrates, and a piston part connected to the central portion and partitioning the inside of the central body into an upper / lower chamber, and a cam A movable body provided with a piston rod and a piston part, each having a first flow path and at least one second flow path through which oil can flow between the upper and lower chambers while the shaft moves up and down; At least one check valve installed in at least one second flow path of the piston to open a flow path of oil flowing from the lower chamber to the upper chamber only when the door is opened; An upper cap coupled to an upper upper end of the upper body and a lower cap coupled to a lower end of the lower body so as to surround the shaft of the camshaft; A return spring is provided between the movable body and the lower cap inside the central body to elastically support the movable body, and provides a restoring force that is compressed when the door is opened and returns the movable body to its original position upon return of the door. and; One end is supported by the lower cap and the front end is inserted into the first flow path of the piston rod to control the lifting speed of the movable body which is moved up and down by the restoring force of the return spring when the door is closed. A hydraulic control rod for controlling the flow amount of oil moving through the lower chamber; A torsion spring disposed at the upper region of the central body and having one end fixed to the upper cap to compensate for the closing force of the door together with the return spring when the door is closed; It is connected to the other end of the torsion spring to block the increase of the elastic force of the torsion spring when the clutch stop start time is reached when the door is opened, and restore the restoring force of the torsion spring when the clutch stop start time is reached when the door is closed. It provides an automatic return hinge device, characterized in that configured as a clutch means for.

In addition, according to another feature of the invention, the invention is a single circular body; A guide hole forming portion disposed at an intermediate portion of the body and having first and second guide holes formed to face each other in a vertical direction; A shaft having an upper end fixed to the body, and a circular body extending from the shaft and having first and second lifting guide holes formed in a spiral shape having a symmetrical structure symmetrically moved along an outer circumferential surface thereof; A camshaft pivoted by a relative external force applied to the body when it is rotated; Guide pins having both ends coupled to the first and second guide holes through the first and second lifting guide holes, respectively; A piston rod slidably coupled to the inside of the circular shaft of the cam shaft by a guide pin through which the tip penetrates, and a piston portion connected to the central portion and partitioning the inside of the body into an upper / lower chamber, and a cam shaft A movable body having a piston rod and a piston part, respectively, having a first flow path and at least one second flow path through which oil can flow between the upper and lower chambers while being lowered according to the rotation of the upper and lower chambers; At least one check valve installed in at least one second flow path of the piston to open a flow path of oil flowing from the lower chamber to the upper chamber only when the door is opened; An upper cap coupled to the top of the body and a lower cap coupled to the bottom of the body to surround the camshaft shaft; A return spring which is installed between the movable body and the lower cap inside the body to elastically support the movable body, and provides a restoring force that is compressed when the door is opened and returns the movable body to its original position upon return of the door; ; One end is supported by the lower cap and the front end is inserted into the first flow path of the piston rod to control the lifting speed of the movable body which is moved up and down by the restoring force of the return spring when the door is closed. A hydraulic control rod for controlling the flow amount of oil moving through the lower chamber; A torsion spring disposed at the upper region of the body and having one end fixed to the upper cap to complement the closing force of the door together with the return spring when the door is closed; It is connected to the other end of the torsion spring to block the increase of the elastic force of the torsion spring when the clutch stop start time is reached when the door is opened, and restore the restoring force of the torsion spring when the clutch stop start time is reached when the door is closed. It provides a self-returning hinge device characterized in that the clutch means for making.

Therefore, in the present invention described above, the return spring and the torsion spring are installed together in the hinge device to compensate for the loss of the closing force of the door occurring at the end of the open return, and at the same time, the opening force of the door is reduced by the clutch device and the heavy large door It can be easily opened with little force.

In addition, the hinge device of the present invention is formed in a slim shape so that it can be embedded inside the various doors that require a very small diameter, it is possible to maintain the overall appearance simply when installed in the door, and also to reduce the damping force due to the reduction in diameter By extending the at least one hydraulic circuit there is an advantage that can be applied to large and small doors.

(Example)

Hereinafter, the automatic return hinge apparatus according to the present invention will be described in detail with reference to the accompanying drawings.

1 is a cross-sectional view showing an automatic return hinge device according to a first embodiment of the present invention, Figure 2 is a perspective view showing a cam shaft of the automatic return hinge device according to a first embodiment of the present invention, Figure 3 Figure 2 is a schematic diagram showing the position of the guide pin according to the door opening angle and the compression state of the return spring in the lifting guide hole of the cam shaft shown in Figure 2, Figure 4 is a self-returning hinge device according to a first embodiment of the present invention 5 is a perspective view showing an external clutch, and FIG. 5 is a partially enlarged cross-sectional view illustrating a hydraulic flow of the overpressure preventing valve when overpressure is generated in the hinge as the closing of the door proceeds at a high speed.

1. First embodiment

1-1. Hinge Unit Overall Structure

First, in the automatic return hinge device according to the first embodiment of the present invention, the upper body 11, the central body 15 and the lower body 13 are disposed along the longitudinal direction in the same axial direction, and the upper and lower body 11 and 13 are respectively coupled to the upper and lower sides of the first hinge 21 fixed to the door, the central body 15 is respectively coupled to one side of the second hinge 23 fixed to the door frame.

Although the first and second hinges 21 and 23 are fixed to the doors and the door frames in the first embodiment, the present invention is not limited thereto, but any one of the first and second hinges is coupled to the door frame. When the other one can be used fixedly coupled to the door.

In addition, the upper cap 31 and the lower cap 33 for closing the inside of the hinge device is coupled to the upper side and the lower body 13 of the upper body 11, respectively, the upper body 11 And the cam shaft 50 is inserted into the inner side of the central body 15, as shown in FIG.

In addition, the cam shaft 50 receives the rotational force of the door when the door is opened and closed so that the upper side of the shaft 51 is rotated in the same direction as the rotation direction of the door upper body 11 and the upper cap 31 It is fixed by a pair of fixing pieces 32 passing through the. That is, the front end of the pair of fixing pieces 32 is inserted to the fastening groove 52a formed on the shaft 51, the cam shaft 50 is fixed to rotate with the rotation of the upper body (11).

Moreover, the circular body 53 extending at the lower end of the shaft 51 has a space portion in which the upper end of the piston rod 61 of the movable body 60 described below is slidably inserted therein, and further along the outer circumferential surface thereof. The first and second lifting guide holes 54a and 54b each having a spiral shape having a moving symmetrical structure are provided. The first and second elevating guide holes 54a and 54b have a cam diagram angle as shown in FIG. 3, which will be described in detail with the operation of the hinge device.

Meanwhile, in the movable body 60 shown in FIG. 1, the upper end of the piston rod 61 is penetrated by the guide pin 70, and both ends of the guide pin 70 are first and first of the circular body 53. 2 It penetrates so that it may be guided by the elevating guide holes 54a and 54b.

Furthermore, a piston portion 62 having a diameter in contact with the outer circumferential surface of the central barrel 15 at the center lower portion of the piston rod 61 and at the same time dividing the oil chamber in the central barrel 15 into upper and lower chambers 91 and 93. ) Is integrally formed, and an overpressure preventing device 63 forming an overpressure preventing valve 630 is disposed under the piston part 62 in a state in which a center is penetrated and coupled to a lower portion of the piston rod 61.

In this case, the piston rod 61 has a first flow path 68a formed from the lower end thereof to the upper part thereof, and the second flow path 68b communicating the upper end of the first flow path 68a with the outer circumference of the piston rod 61. Is formed. In addition, the piston portion 62 includes a plurality of third flow passages 68c penetrating in the vertical direction.

On the other hand, the overpressure valve 630 is provided with an overpressure preventing device 63 formed smaller than the inner diameter of the central body 15, as shown in Figure 5, as a result of the outer passage and the central body ( A sixth flow path 68f through which the oil in the upper chamber 91 flows into the lower chamber 93 is formed between 15.

In addition, the plate spring 64 and the snap ring 65 for fixing the plate spring 64 are sequentially penetrated through the lower end of the piston rod 61 at the lower side of the overpressure preventing device 63.

The overpressure preventing valve 630 of the above structure does not operate when the user closes the door at a normal speed as described below, and only when the door is rapidly closed due to an external force having a large force such as a strong wind. It works. That is, when the door is opened and closed at a normal speed as described below, at least one pair of check valves 631 formed in accordance with the action of the opening and closing ball 63a embedded in the overpressure preventing device 63 may act to block the flow path. (See FIG. 7D).

The disc spring 64 elastically supports the overpressure preventing device 63 at a lower end of the piston 62 at a predetermined pressure, and the overpressure generated in the upper chamber 91 is greater than the elastic force of the disc spring 64. In this case, the overpressure preventing device 63 moves downward by the oil pressure. When the overpressure protector 63 moves downward, a fifth flow path 68e is formed between the lower surface of the piston portion 62 and the upper surface of the overpressure protector 63, and oil in the upper chamber 91 A large amount flows into the lower chamber 93 through the fifth and sixth flow paths 68e and 68f to release the overpressure state. As a result, one of the various O-rings 81-83, 87, 88 disposed for airtightness around the central body 15 and the piston part 62 by the overpressure of the upper chamber 91 is destroyed or the body This breakage prevents oil leakage problems.

However, when the pressure generated in the upper chamber 91 becomes smaller than the elastic force of the disc spring 64 according to the normal closing of the door, the overpressure preventing device 63 is not moved downward by the oil pressure. As such, when the overpressure preventing member 63 does not move downward and is elastically maintained in contact with the lower surface of the piston part 62, between the lower surface of the piston part 62 and the upper surface of the overpressure preventing device 63. The fifth flow path 68e is not formed.
In addition, when the door is opened, the oil moves from the lower chamber 93 to the upper chamber 91 via the fourth flow passage 68d and the check valve 631.

In this case, it is preferable that the dish spring 64 is designed to have an elastic modulus that can move the overpressure preventing device 63 when the overpressure occurs.

On the other hand, the support nut 66 is screwed to the end of the piston rod 61, the role of the support nut 66 is the elastic force of the return spring 67 for elastically supporting the movable body 60 By not directly affecting the elastic force of the dish spring 64 is to be able to smoothly perform the overpressure prevention function in the chamber.

In the first embodiment illustrated in FIG. 1, the check valve 631 is separated from the piston 62 to be incorporated into the overpressure preventing device 63 to employ the overpressure preventing valve 630. However, the adoption of the overpressure check valve 630 is not essential, and when the overpressure check valve 630 is not employed, the check valve 631 is built in place of the third flow passage 68c formed in the piston 62. It may have a structure. An example in which a check valve is integrally formed with the piston part is shown in FIG. 8 as a second embodiment.

Whether or not to employ the overpressure check valve and the installation location of the check valve can be equally applied to other embodiments described later.

In addition, the lower end of the return spring 67 is disposed at the lower end of the central body 15, the sealing cap 47 for sealing the lower chamber 93 is coupled. In addition, a ball bearing 48 is installed between the lower cap 33 and the sealing cap 47 to enable smooth rotation between the central body 15 and the lower body 13.

In addition, a hydraulic control rod 45 having a tip inserted therein is installed in the first flow passage 68a of the piston rod 61, and the hydraulic control rod 45 is provided on the lower cap 33. The lower end is fixed by 43. The specific structure of the hydraulic control rod 45 will be described later.

In addition, the support 43 is coupled to the adjustment bolt 41 vertically coupled to the center of the lower cap 33 to the inside, the hydraulic control rod 45 in accordance with the forward / reverse rotation of the adjustment bolt 41 The amount of oil passing through the first flow path 68a can be freely set by setting the level of). As a result, the automatic return speed of the door is determined.

1-2. Clutch device

On the other hand, in order to improve the closing force when the door is closed, the torsion spring 76 is arranged in the state surrounding the shaft 51 on the inner side of the central body 15 and is generated in the torsion spring 76 according to the rotation of the door. The clutch device 700 is disposed in connection with the lower end of the torsion spring 76 to control the elastic force.

The clutch device 700 has an outer clutch 71 fixed to the inner center of the central body 15 by a fixing piece 72, and a lower end is rotatably inserted in the upper end of the outer clutch 71 and is disposed in the inner space. The opening angle of the shaft (that is, the door) is disposed between the inner clutch 73 for supporting the shaft 51 of the cam shaft 50 in a rotatable contact state and the outer / inner clutches 71 and 73. In accordance with the inner clutch 73 is composed of a pair of roller pins (roller pin) (75) that serves to couple or separate from the shaft (51).

In addition, the torsion spring 76 has an upper end fixed by the first fixing hole 77a formed at the lower end of the upper cap 31, and the lower end thereof has a second fixing hole 77b formed at the upper end of the inner clutch 73. Are fixed by each. Therefore, when the camshaft 50 rotates when the door is opened, the torsion spring 76 is torsionally deformed while the internal clutch 73 also rotates together, for example, in the range of 0 to 90 °. Then, when reaching the clutch stop start time of 90 ° of the clutch device 700, the clutch is operated so that the torsional deformation of the torsion spring 76 is stopped and only the camshaft 50 is rotated.

6A to 6D illustrate the case where the clutch stop start time is 90 °, which is a slim type automatic return suitable for a small door using only a torsion spring without using a return spring. This is an example applied to the hinge device.

Therefore, in the automatic return hinge device for the large door which requires both the return spring 67 and the torsion spring 76, it is possible to set the clutching stop start time of the clutch device 700 to the desired angle, for example. , 30 ° can be set.

When the clutch stop start time is set to 30 ° in this manner, the position of the second insertion groove 74c formed at the upper end of the outer clutch 71 on the basis of when the cam shaft 50 is in the initial state is determined by the shaft. It is arrange | positioned in the position rotated 30 degrees from the 1st insertion groove 74a formed in the outer periphery of the 51, and the through hole 74b formed in the inner clutch 73. As shown in FIG.

On the other hand, the pair of roller pins 75 is a pin shape having a circular cross section, and formed in a pair of first insertion grooves 74a and inner clutch 73 which are formed corresponding to the outer circumference of the shaft 51 and have a hemispherical cross section. The through hole 74b is formed and is formed at the upper end of the outer clutch 71 as shown in FIG. 4 and is inserted to be movable between the second insertion grooves 74c having a hemispherical cross section. The process of clutching through the pair of roller pins 75 will be described in detail along with the operation of the hinge device to be described later.

On the other hand, the outer clutch 71 is the first and second guide holes (78a, 78b) is formed with a cylindrical portion extending downward as shown in Figure 4 and both ends of the guide pin 70 is vertically slidably mounted on both sides. The guide hole forming part provided with) is integrally formed. In this case, the guide pin 70 passes through the piston rod 61, the first and second lifting guide holes 54a and 54b and the first and second guide holes 78a and 78b simultaneously. When the door hinge rotates with the first hinge 21 and the camshaft 50 rotates, the guide pin 70 moves vertically downward along the first and second guide holes 78a and 78b. At the same time, the movable body 60 descends a predetermined distance downward while rotating along the first and second elevating guide holes 54a and 54b while being elastically supported by the return spring 67.
Accordingly, the guide hole forming unit, the cam shaft 50 and the guide pin 70 move the rotational motion of the shaft 51 when the rotational force of the door is applied to the shaft 51 according to the rotation of the door. It forms a rotation / linear motion converting means for converting the axial linear motion of the piston 62 forming a.

In Fig. 1, reference numerals 81, 82, 83, 87, and 88 are O-rings for hermeticity, 84 is a packing, 85 is a bushing, and 86 is a thrust bearing, respectively.

The thrust bearing 86 has a lower surface of the inward protrusion of the outer clutch 71 that is fixed to the central body 15 when the cam shaft 50 rotates, and an upper portion of the circular body 53 of the cam shaft 50. It serves to reduce the rolling friction and noise generated between the surfaces.

1-3. Lifting guide structure of movable body

Hereinafter, the lifting and lowering guide structure of the movable body 60 will be described in detail, and the clutching process of the clutch device for controlling the elastic force of the torsion spring 76 for reinforcing the closing force of the door will be described together. .

6A to 6D are flat sectional views sequentially showing the operating state of the clutch device according to the opening of the door, and FIGS. 7A to 7C are partially enlarged sectional views sequentially showing the hydraulic flow when the movable body descends according to the opening of the door. 7D and 7E are partial enlarged cross-sectional views sequentially showing hydraulic flows when the movable body moves up and down in accordance with the closing of the door.

First, the first and second elevating guide holes (54a, 54b) formed in the circular body 53 of the camshaft 50, the four sections for guiding the piston unit ascending and descending in conjunction with the door opening angle as shown in FIG. (ad), i.e., a first section (a) with a door opening angle of 0-15 °, a second section (b) with a door opening angle of 15-90 °, and a door opening angle of 90-130 ° The third section (c) therebetween and the door opening angle are divided into a fourth section (d) between 130-160 °.

The first section (a) of the four sections (ad) is a section in which the opening angle of the piston 62 of the movable body 60 is raised and lowered between 0-15 ° to guide the first and second lifts. The cam diagram angle α of the holes 54a and 54b is set to a range of 45 to 65 ° which is relatively larger than the angle β of the second section b to increase the efficiency at the time of raising the piston 62. The closing force loss due to the decrease in the proportional restoring force of the resistance and the return spring 67 of the hydraulic circuit is compensated for, and the hydraulic circuit state at this time corresponds to FIG. 7B. However, the oil flow direction of FIG. 7B shows the case when the door is opened.

In the first section a, that is, the section having an opening angle of 0-15 °, the return speed of the door is limited to a predetermined speed by the check valve 631 in a section of 90-15 ° in advance for the user's safety. And the elastic restoring force of the return spring 67 is almost exhausted. However, in order to complete the automatic return of the door, the latch installed in the door must have a closing force that can be engaged with the locking device installed in the door frame.

To this end, the present invention stops reverse twisting of the torsion spring 76 when the door, particularly the large door, is clutched at an opening angle of 30 ° as described below, and stops reverse twisting when the door exceeds 30 °. A clutch device 700 is provided to release the clutching operation when the angle is less than 30 degrees, and actuate the restoring force of the reverse twisted torsion spring 76 to the camshaft 50.

Therefore, in the first section a, the check valve 631 does not operate when the door is opened, and the torsion spring 76 is reverse twisted in proportion to the opening angle, and the return spring 67 is also proportional to the opening angle. Is compressed. However, at the time of automatic return of the door, the clutching operation of the clutch device 700 is released from the opening angle of less than 30 °, and the restoring force from the torsion spring 76 in the reverse twisting state is restored to the inner clutch 73 and the camshaft 50. ) To the right direction. As a result, the elastic force of the torsion spring 76 is added to the elastic force of the return spring 67 that raises the piston 62, thereby completely returning (locking) the door to the initial position.

In this case, as compared with the hinge device having the double camshaft structure of the related art, almost all of the elastic force generated when the door is opened can be reduced to the door closing force, thereby increasing the efficiency at the time of raising the piston portion 62, thereby reducing the closing force. To complement.

In addition, in the second section (b), that is, the section between the opening angle 15-90 °, the check valve 631 does not operate when the door is opened, and the torsion spring 76 has an operating angle of the clutch device 700, for example. , When it is set to 30 °, the reverse twisting is made in proportion to the opening angle in the section between the opening angle 15-30 °, and the return spring 67 is also compressed in proportion to the opening angle. In addition, in the section between the opening angle 30-90 ° according to the opening of the door, the torsion spring 76 is in a state where reverse twisting is stopped by the operation of the clutch device 700, and only the return spring 67 is the piston part. Compression follows the descending of 62.

In the conventional hinge device, the opening force required for the door opening increases from 0 ° to 160 ° when the door is fully opened, which is directly proportional to the opening angle, thereby opening the door from the second section (b), that is, 15 °. In the case of the present invention, although the opening force similar to the conventional one is required in order to preserve the closing force of the door in the first section (a), the clutch starts from the opening angle of 30 ° in the second section (b). According to the operation of the apparatus 700, the torsion spring 76 can stop the reverse twisting, the opening force is greatly reduced compared to the section within an opening angle of 30 ° to easily open the heavy large door.

On the other hand, in the second section b, the cam line angle beta of the first and second elevating guide holes 54a and 54b is 10-45, which is relatively smaller than the angle α of the first section a. By setting the temperature range, the rotational efficiency of the camshaft 50 is increased proportionally when the door is opened to compensate for the increase in the opening force, which increases in proportion to the opening of the door.

In addition, in the third section (c) in which the piston section 62 is in a stopped state, that is, in the opening angle range of 90-130 °, the cam line angle is set to zero to block automatic return by the return spring 67. As a section to be maintained, the angle of the door is kept open, and the restoring force of the return spring 67 is the largest. The fourth section (d) is a stopping force reinforcing section is formed to be inclined in the upper direction in the third section (c) is stopped so that the guide pin 70 is not moved by the locking. 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 70 is raised by the repulsive force of the compressed return spring 67, the hydraulic pressure of the upper chamber 91 is the elastic force of the return spring 67 near the threshold point where the piston 62 can rise. By acting more largely, the piston part 62 can fall rapidly in a reverse direction.

In addition, the guide pin 70 may cause internal noise and damage to internal components due to an 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 544 and the second cam line diagram holding unit 545 of the first and second elevating guide holes 54a and 54b is curved. .

Further, the first cam line diagram holding unit 544 and the second cam line diagram holding unit 545 were set at opposing curved surfaces at regular intervals from the elevating guide hole 54a.

1-4. Hydraulic control rod structure

The hydraulic control rod 45 of the first embodiment has a high flow rate setting part 45a having a large flow amount of oil and a small flow amount of oil as shown in FIGS. 7A to 7E so as to be suitable for control of a single hydraulic circuit. The slow section setting part 45b is arrange | positioned up and down.

The high speed section setting section 45a enables a relatively large amount of oil flow in comparison with the flow rate of oil when the check valve 631 is not operated (OFF state), that is, when the door is opened (piston descending). It is set to the same diameter so that the oil flow of about / 2 can be made, and the low-speed section setting section 45b is the piston portion 62 rises compared to the flow amount of the oil when the check valve 631 is OFF The taper is then tapered to increase in diameter from the top to the bottom to vary the flow rate of about 1/2 to 1/80.

In this case, when a portion of the high speed section setting section 45a does not enter the inside of the first flow path 68a when the piston portion 62 ascends, the upper chamber 91 goes from the lower chamber 93 to the lower chamber 93. The moving amount of the moving oil is increased, so that a high speed door return can be achieved.

In addition, the oil moving from the upper chamber 91 to the lower chamber 93 in a section in which a part of the low speed section setting section 45b enters the first flow path 68a when the piston 62 rises. The amount of movement is gradually increased in accordance with the rising position of the piston 62 to compensate for the reduction of the restoring force of the return spring.

The high speed section setting section 45a and the low speed section setting section 45b vary the length of each section according to the object to which the automatic return hinge device is applied, and the taper amount of the low speed section setting section 45b is determined.

For example, in the case of building materials doors (fire doors, etc.), the high-speed section setting unit 45a starts at 30 °, for example, because the doors must be closed at the time of fire. In the case of indoor visits, for example, the door opening angle starts at 5 °, and in the case of up and down doors such as kimchi refrigerators, the high speed section is not required. It consists only of the section setting part 45b.

1-5. Operation of the hinge device

Hereinafter, the overall operation of the hinge device of the present invention will be described with reference to FIGS. 6A to 6D and 7A to 7E. In this case, the clutch device 700 illustrated in FIGS. 6A to 6D has a clutch stop start time set to 90 °. However, in the present description, the hinge device of the large door employing both the torsion spring and the return spring is described. The hinge device operation will be described, for example, when the clutch stop start angle is set to 30 °.

1-5-1. When opening the door

First, in the hinge apparatus according to the first embodiment of the present invention, when the door is opened in a closed (ie, stopped) state as shown in FIGS. 6A and 7A, the hydraulic circuit is set as shown in FIG. 7B. That is, the external rotational force is transmitted to the shaft 51 of the camshaft 50 through the first hinge 21 when the door is opened, so that the components therein operate as follows.

When the user opens the door in the initial state of FIGS. 6A and 7A with the door closed, the shaft 51 and the inner clutch 73 of the camshaft 50 include a pair of roller pins 75 as shown in FIG. 6B. As the torsion spring 76 is also reverse twisted while rotating in the left-hand direction, the elastic force is generated. At the same time, since the rotational force in the left screw direction is transmitted to the cam shaft 50, the pair of first and second guide holes 78a formed in the first and second lifting guide holes 54a and 54b and the external clutch 71 are provided. The guide pin 70 having both ends inserted into the 78b) moves downward along the first and second lifting guide holes 54a and 54b as the camshaft 50 rotates.

In this case, as illustrated in FIG. 7B, a force to move downward is applied to the guide part 70 moving downward and the piston 62 interlocking through the piston rod 61.

Accordingly, the oil located under the piston 62, that is, the lower chamber 93, moves to the upper chamber 91 through the first flow passage 68a and the second flow passage 68b, and at the same time, the overpressure preventing opening 63 A plurality of opening and closing balls (63a) of the) moves upward to the upper chamber 91 through the fourth flow path (68d) and the third flow path (68c) as the fourth flow path (68d) is opened. That is, when the door is opened, the check valve 631 is turned off so that a large amount of oil quickly moves from the lower chamber 93 to the upper chamber 91.

Then, the guide pin 70 supports the movable body 60 while moving in the first and second sections a and b as in the operating states in the first and second lifting guide holes 54a and 54b. The nut 66 is lowered by compressing the return spring 67.

In addition, when the piston rod 61 moves downward and the opening angle of the door exceeds 30 ° as shown in FIG. 7C, the low speed section setting part 45b of the hydraulic control rod 45 tapered into the first flow path 68a is While entering, the amount of oil passing through the first flow path 68a is reduced, Most of the large amount of oil is quickly moved from the lower chamber 93 to the upper chamber 9 through the check valve 631 in the OFF state, so the piston portion 62 is lowered quickly.

Furthermore, when the rotation angle of the door is 30 °, as shown in FIG. 6C, the pair of roller pins 75 are separated from the first insertion grooves 74a of the inner clutch 73 and the second insertion grooves of the outer clutch 71 ( 74c), when the rotation angle of the door is 30 ° or more, as shown in FIG. 6d, the rotation of the inner clutch 73 is stopped and only the shaft 51 of the camshaft 50 rotates the torsion spring 76. ), The elastic force increase is stopped based on the rotation angle of the door 30 °.

In this case, the roller pin 75 which catches on the 1st insertion groove | channel 74a is inserted below the center point. Therefore, in FIG. 6C, when the roller pin 75 receives the torsional force by the torsion spring 76, when the roller pin 75 reaches the second insertion groove 74c, an outward force is applied to the second insertion groove 74c. Get out.

In addition, when the increase in the elastic force of the torsion spring 76 is stopped, the guide pin 70 reaches the third section c at which the door rotation angle is 90 ° when the cam shaft 50 continuously rotates. As the movement is restricted by the first stop portion 542 of the third section c of the first and second lifting guide holes 54a and 54b, the piston 62 is located at the bottom dead center. It remains stationary at.

Therefore, in the present invention, the opening force is greatly reduced compared to a section within the opening angle of 30 ° when the door is opened between the opening angle of 30-90 °, which is commonly used by the user, so that a large heavy door can be easily opened.

Meanwhile, in the above embodiment, the third section c having the door rotation angle of 90-130 ° is set as the stop section. However, the stop section may include the first and second lifting guide holes 54a and 54b as necessary. By moving the position of the first stop portion 542 or reducing or increasing the width thereof, it is possible to correct, for example, to 60-100 ° or 90-100 °.

1-5-2. When closing the door

On the other hand, when the door is closed, as shown in FIG. 7D, when the user closes the door to open the door within 90 °, or opens the door and releases the door within 90 °, the door automatically returns to the initial position. To perform.

When the opening angle of the door is 90 °, that is, when the user rotates the door so that a slight external force is transmitted to the camshaft 50 in the direction of the right screw, the guide pin 70 first stops 542. After passing through), it leaves the third section (c). In this case, the elastic force of the return spring 67 in a compressed state should be set higher than the pressure of the oil of the upper chamber 91 applied to the upper surface of the piston 62.

Then, the piston portion 62 starts to move upward with the strong repulsive force of the compressed return spring 67, and the guide pin 70 connected to the piston portion 62 also has the first and second lifting guide holes ( It rises vertically along the 2nd section b of 54a, 54b, ie, the elevation guide part 541 of the gentle inclination angle of 10-45 degrees, and the 1st and 2nd guide holes 78a and 78b. As a result, the camshaft 50 attempts to return the door to the initial position by rotating in the right direction.

At this time, when the oil in the upper chamber 91 is pressured by the piston portion 62 rising as shown in FIG. 7D, the oil of the upper chamber 91 tries to move to the lower chamber 93 through the third and fourth flow paths 68c and 68d, respectively. Pressure is generated. In this case, as the plurality of opening and closing balls 63a respectively close the plurality of fourth flow passages 68d, the check valves 631 are turned on, and the cylindrical body 53 cannot flow through the fourth flow passage 68d. ) Through the space between the piston rod 61 and the second and first flow paths (68b, 68a) to the lower chamber 93 to rise at a relatively low first speed in the 90-30 ° section do.

In this case, as the piston 62 rises, the repulsive force of the return spring 67 gradually decreases, but the low speed section setting portion 45b inserted into the first flow path 68a gradually becomes a portion having a smaller diameter. As it moves, the flow amount of oil passing through the first flow path 68a gradually increases. Thus, the first speed can be kept constant.

Thereafter, when the piston 62 is raised to enter the opening angle 30-0 °, the low speed section setting section 45b exits from the first flow passage 68a to the lower chamber 93 as shown in FIG. 7E. Since only the high-speed section setting unit 45a is inserted into the first flow path 68a, the oil in the upper chamber 91 passes through the space between the cylindrical body 53 and the piston rod 61 and the second and first flow paths ( 68b, 68a flows into the lower chamber 93 at a higher flow rate than the above 90-30 ° section, thereby increasing at a second speed faster than the first speed.

When judging based on the hydraulic circuit only as described above, the opening of the door as the piston portion 62 rises at a relatively low first speed in the opening angle 90-30 ° section, and ascends at a second speed in the 30-0 ° section. The door is closed at a low oil movement amount, i. Therefore, the door is closed at a low speed of the first speed in the 90-30 ° section affecting the user's entry and exit, it is possible to prevent a safety accident or inconvenience caused by the rapid return of the door. The 30-0 ° section, which does not affect the user's entry and exit, is relatively fast to reinforce the closing force of the door.

Thereafter, when the shaft 51 rotates in the right-hand direction as the piston part 62 rises, and the opening angle of the door is 30 ° or less, the roller pin 75 has a second insertion groove of the outer clutch 71 ( It is separated from 74c and inserted into the first insertion groove 74a of the shaft 51. In this case, the roller pin 75 caught by the second insertion groove 74c is inserted below the center point. Therefore, when the inner clutch 73 receiving the rotational force in the initial setting direction, that is, the right-screw direction by the elastic restoring force of the torsion spring 76, applies the rotational force to the roller pin 75, the roller pin 75 is removed. 2 is separated from the insertion groove (74c) to rotate in the direction of the right screw together with the inner clutch (73).

Accordingly, the inner clutch 73 which is stopped is applied with the rotational force in the initial setting direction, that is, the right-hand screw direction by the elastic restoring force of the torsion spring 76, which is raised to the shaft 51 through the roller pin 75. The closing force of the door by the return spring 67 is further raised while applying the rotational force in the screw direction.

Thereafter, when the door opening angle is 15 ° and 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 30 ° and 15 °. The inclination angle (45 to 65 degrees) of the first section (a) is set relatively larger than the inclination angle (10 to 45 degrees) of the second section (b). As a result, the restoring force of the return spring 67 is reduced, but the frictional resistance of the elevating guide portion 541 is reduced, so that the elevating speed of the piston 62 is accelerated at the third speed. Thus, the door is returned to the initial position and locked by the latch of the door. At this time, the piston 62 is returned to the initial position as shown in Figure 7a.

As described above, in the hinge device of the present invention, when the door is closed, the return spring 67 and the torsion spring 76 are used together to prevent loss of the closing force of the door, as well as clutching the clutch device when the door is opened. From the door opening angle of 30 ° or more, the compression repulsion force of the torsion spring 76 can be removed, so that the large door can be easily opened with a relatively small force as compared with the case without the clutch.

In the description of the first embodiment, it is assumed that the high-speed section setting portion 45a of the hydraulic control rod has a door opening angle of 30 °, but this is suitable for a fire door, and in the case of a small door for home use or an indoor visit, etc. When the opening angle is set to 5 degrees, and in the case of vertically rotating doors such as kimchi refrigerators, it can be constituted only by the tapered low speed section setting section 45b without the high speed section setting section 45a.

2. Second Embodiment

8 is a partially enlarged cross-sectional view showing a feature of an automatic return hinge device having a structure in which a check valve is embedded in a piston portion according to the second embodiment of the present invention.

In the first embodiment described above, when the door is rapidly closed by an external force such as a strong wind, an overpressure preventing valve is provided separately from the piston part to prevent damage to various O-rings for maintaining the body and the piston part. In the second embodiment, there is a difference in that the overpressure preventing valve is removed and the check valve 633 is embedded in the piston portion 62a. The structure and operation of the check valve 633 of the second embodiment are made substantially the same as the check valve 631 of the first embodiment.

Therefore, since the operation of opening and closing the remaining components and the door except for the structure of the check valve 633 and the piston portion 62a is performed in the same manner as in the first embodiment, the same components are assigned the same member numbers and the description thereof will be described. Omit.

3. Modification of the first embodiment

FIG. 9A is a cross-sectional view showing a self-returning hinge device according to a modification of the first embodiment, and FIG. 9B is a cross-sectional view showing a check valve having a notch applied to the modification of the first embodiment shown in FIG. 9A.

9A has a notch 69 which provides a uniform damping force at the time of door closing to the check valve 632 as shown in FIG. 9B when compared with the first embodiment, and the piston The flow path penetrating the inside of the rod 610 and the hydraulic control rod 45 into which the tip is inserted are removed.

In the automatic return hinge device of the above-described modified structure, the operation at the time of door opening is made substantially the same as in the first embodiment, and only a difference occurs at the closing of the door.

That is, when the piston portion 620 rises according to the closing of the door, the oil in the upper chamber 91 is pressurized by the rising piston portion 620, through the third and fourth flow paths 68c and 68d, respectively. It moves to the lower chamber 93. In this case, as the plurality of opening and closing balls 63a of the respective check valves 632 close the plurality of fourth flow paths 68d, the oil amount is lower in the lower chamber 93 through the narrow single notch 69. As it exits by as many as 90-30 ° in the interval ascending at the first low speed.

Thereafter, when the piston 620 rises and reaches an opening angle of 30 °, the clutch device 700 starts operation as in the first embodiment, and the initial setting direction, i.e., the right, is increased by the elastic restoring force of the torsion spring 76 as in the first embodiment. The rotational force in the screw direction is applied, which further raises the closing force of the door by the return spring while applying the rotational force in the right screw direction to the shaft 51 through the roller pin 75.

Further, when the door opening angle passes through 15 ° and the door opening angle enters between 15 ° and 0 °, the second angle is set by setting the inclination angle (45 to 65 °) of the first section a of the elevating guide 541. Since the frictional resistance of the elevating guide portion 541 is reduced from the section (b), the elevating speed of the piston 62 is accelerated at the second speed. Thus, the door is returned to the initial position and locked by the latch of the door. At this time, the piston 62 is returned to the initial position as shown in Figure 7a.

As described above, in the self-returning hinge structure of the modification, the check valve 632 is operated when the door is closed between an opening angle of 90-30 ° so that the oil in the upper chamber 91 passes through the narrow notch 69 only in the lower chamber. As it flows into the (93), the flow rate of the oil greatly decreases and slowly rises at a constant speed.

This constant door closing speed setting is a hydraulic circuit suitable for a product which does not require fine speed control such as a refrigerator, for example, and door closing is required within a certain time (for example, about 4 seconds).

4. Third embodiment

10 is a longitudinal cross-sectional view showing a slim automatic return hinge device having a double hydraulic circuit according to a third embodiment of the present invention, Figures 11a to 11c is the movable body is lowered when the door is opened in the third embodiment 11D and 11E are some enlarged cross-sectional views sequentially showing the hydraulic flow when the movable body rises in accordance with the closing of the door.

The first and second embodiments relate to a hinge device applied to, for example, a large building door, such as a fire door, or a door for a large household appliance, such as a large-capacity refrigerator, and the hinge device of the third embodiment is The present invention relates to a slim type automatic return hinge device having a small diameter of a body to be embedded in a door and used in a door, particularly a door for a large home appliance.

The structure of the hinge apparatus according to the third embodiment of the present invention employs the return spring 167 and the torsion spring 176 together with the first embodiment, and the overall configuration is similar.

Hereinafter, a description of the overlapping configuration with the first embodiment will be omitted, and a structure that can compensate for the damping force that is reduced as the hinge device is reduced by forming two different hydraulic circuits, that is, two independent hydraulic circuits, from the first embodiment. It demonstrates.

First, the hinge device according to the third embodiment of the present invention includes a first fixing member 121 fixed to one end of a door frame of a refrigerator and a second fixing member 123 fixed to a door.

In this case, the first fixing member 121 is fixed to the upper end of the shaft 151 of the camshaft 150 through the connecting hole 100, and the second fixing member 123 according to the rotation of the door when the door is opened. As the body 113 is rotated to lower the movable body 160, the upper cap 131 fixed to the body 113 by the plurality of fixing pieces 132 to operate the hydraulic circuit in the oil chamber. One end is fixed.

In addition, the movable body 160 has a predetermined distance at the center and the lower side of the piston rod 161, the first and second piston parts 162a, 162b are coupled, respectively, the first and second piston parts Between 162a and 162b, the piston rod 161 is movably supported in the axial direction, and an isolator 200 fixed to the body 113 is disposed.

The isolator 200 defines a first lower chamber 193a to partition the first and second upper and lower chambers 191a, 193a; 191b, and 193b by the first and second piston parts 162a and 162b, respectively. ) And the second upper chamber 191b.

In addition, the piston rod 161 of the movable body 160 may move oil charged in the first lower chamber 193a to the first upper chamber 191a according to the lowering (door opening) of the first piston part 162a. The first flow path 168a, the second flow path 168b for communicating the first flow path 168a and the first upper chamber 191a with each other, and the first flow path 168a and the first lower chamber 193a. ) And a third flow path (168c) to communicate with each other, and the oil charged in the second lower chamber (193b) to the second upper chamber (191b) in accordance with the lowering of the second piston portion (162b). A fourth flow path 168d for communicating the first flow path 168a and the second upper chamber 191b with each other is provided.

In this case, one end of the hydraulic control rod 145 for controlling the flow path is inserted into the first flow path 168a and the other end is fixed to a support supported by the lower cap 133.

The hydraulic control rod 145 of the third embodiment includes a pair of fast section setting parts 145a and 145c having a large flow amount of oil as shown in FIGS. 11A and 11B so as to be suitable for the control of the double hydraulic circuit. A pair of low-speed section setting sections 145b and 145d having a small flow rate of the flow rate are alternately arranged.

The pair of high-speed section setting units 145a and 145c has a relatively large amount of oil flow compared to the flow rate of oil when the check valves 170 and 171 are not operated (OFF state), that is, when the door is opened (the piston is lowered). This is set to the same diameter so that the oil flow of about 1/2 is possible, and the pair of low-speed section setting section (145b, 145d) compared with the flow rate of the oil when the check valve (170,171) is OFF As the piston parts 162a and 162b are raised, the diameter is tapered so as to increase the diameter from the top to the bottom so that the flow amount of about 1/2 to 1/80 is varied.

In this case, when the piston sections 162a and 162b are raised, in the section where the pair of high speed section setting sections 145a and 145c correspond to the third and fourth flow paths 168c and 168d, the low speed section setting section 145b Compared to the case of 145d, the amount of oil moving from the first and second upper chambers 191a and 191b to the first and second lower chambers 193a and 193b, respectively, is significantly increased, resulting in a high speed door return. It can be done.

Further, in the section where the pair of low speed section setting sections 145b and 145d correspond to the third and fourth flow paths 168c and 168d, the first and second upper chambers 191a and 191b are respectively used. The amount of oil moving to the lower chambers 193a and 193b is gradually increased in accordance with the rising positions of the piston parts 162a and 162b to compensate for the reduction of the restoring force of the return spring.

The pair of high speed section setting units 145a and 145c and the pair of low speed section setting units 145b and 145d vary the length of each section according to the object to which the automatic return hinge device is applied, and the low speed section setting unit ( The taper amounts of 145b and 145d are determined.

For example, in the case of a building material door (eg, a fire door), the start of the high-speed section setting unit 145a, 145c starts at, for example, the door opening angle of 30 °. In the case of a small door or indoor visit, the door opening angle starts at 5 °, for example, and in the up-and-down rotation type door such as a kimchi refrigerator, the high speed section setting unit 145a, 145c is unnecessary. It is made of only the low-speed section setting section (145b, 145d) without placing.

On the other hand, first and second overpressure prevention ports 163a and 163b are installed under the first and second piston parts 162a and 162b respectively by the first and second dish springs 164a and 164b. Valves 630a and 630b are provided. In this case, the first and second dish springs 164a and 164b are supported by the first and second snap rings 165a and 165b, respectively, and when the overpressure occurs, the first and second dish springs 164a and 164b are supported. 164b is prevented from being pushed downward along the piston rod 161 so that the operation of the overpressure preventing valves 630a and 630b is smoothly performed.

In addition, the third embodiment includes a plurality of check valves 170 and 171 which are the same as the first embodiment in the first and second overpressure preventing devices 163a and 163b, and the return spring is provided under the movable body 160. 167 is disposed. A clutch device 710 is disposed above the circular body 153 of the camshaft 150, and a torsion spring 176 is disposed between the clutch device 710 and the upper cap 131.

Furthermore, the basic mechanism for raising and lowering the movable body 160, in this case, adjusting the raising / lowering speed (door opening / closing speed) is also made in the same manner as in the first embodiment.

In the third embodiment, two closed circuit chambers are formed to complement the damping force that decreases as the hinge device becomes slim as described above, and two independent hydraulic circuits (ie, damping devices) are formed in the longitudinal direction. That is, substantially the same as in the first embodiment except that one independent hydraulic circuit is added.

In addition, in view of the operation surface of the hinge device, in the third embodiment, when the door opening angle is 0 ° when the door is opened, the first and second piston parts 162a and 162b have the top dead center of each chamber as shown in FIG. 11A. Located in When the door opening angle is in the range of 0-30 °, the first and second check valves 170 and 171 are in the OFF state when the first and second piston parts 162a and 162b descend as shown in FIG. 11B. The oil in the lower chambers 193a and 193b is formed by the first and second upper chambers 168a and 168d through the first and second check valves 170 and 171 and the piston rod 161. 191a, 191b).

Also, when the door opening angle is 30 to 90 °, the oil in the first and second lower chambers 193a and 193b may be in the first and second check valves 170 and 171 and the piston rod 161 as shown in FIG. 11C. Rapidly moves to the first and second upper chambers 191a and 191b through the first to fourth flow paths 168a to 168d.

However, when the door opening angle is 0-30 °, the oil moving through the first to fourth flow paths 168a to 168d corresponds to the high speed section setting units 145a and 145c, so that the low speed section setting unit 145b, Although the amount of oil flow increases slightly compared to the case where the door opening angle 145d) corresponds to a 30-90 ° section, most oil moves through the first and second check valves 170 and 171.

Since the operation of the clutch device 700 at the door opening is performed in the same manner as in the first embodiment, the elastic force of the torsion spring 176 when the door opening exceeds the clutch starting angle (for example, 30 °). The increase is stopped. Therefore, after the clutching start angle, the opening force is greatly reduced when the door is opened, so that the heavy large door can be easily opened.

Meanwhile, when the door is closed, as shown in FIG. 11D, when the door opening angle is in the range of 90-30 °, the oil of the first and second upper chambers 191a and 191b is turned on in the first and second check valves 170 and 171. In this state, the first and fourth lower passages 193a and 193b are moved at a low speed through the first to fourth flow paths 168a to 168d in the piston rod 161.

In this case, the oil moving through the first to fourth flow paths 168a to 168d is determined to correspond to the tapered low speed section setting units 145b and 145d, and the amount of oil movement is gradually increased to compensate for the reduction of the restoring force of the return spring. To increase.

Thereafter, when the door opening angle is 30-0 °, as shown in FIG. 11E, the oil in the first and second upper chambers 191a and 191b is turned on so that the first and second check valves 170 and 171 are turned on. 161 moves to the first and second lower chambers 193a and 193b at low speed through the first to fourth flow paths 168a to 168d therein.

In this case, the oil moving through the first to fourth flow paths 168a-168d is determined to correspond to the high speed section setting units 145a and 145c and compensates for the reduction of the restoring force of the return spring and at the same time reinforces the closing force of the door. To do so.

As described above, when the opening angle of the door becomes the clutching start angle, that is, 30 ° or less, the clutching of the clutch device 700 is released and the elastic restoring force of the torsion spring 76 is applied, thereby causing the return spring 167. Further increase the closing force of the door. In addition, when the door opening angle is between 15 ° and 0 °, the lifting speeds of the piston parts 162a and 162b can be accelerated to the third speed according to the large inclination angle setting of the lifting guide 541. Thus, the door is returned to the initial position and locked by the latch of the door.

In the hinge device of the third embodiment as described above, instead of reducing the diameter of the body serving as the housing to a slim shape, it is possible to control the rising speed of the piston parts 162a and 162b by adding one or more hydraulic circuits to the damping force. It was possible to provide sufficient damping force.

In addition, in the third embodiment, the return spring and the torsion spring are employed together to prevent the loss of the closing force of the door and to remove the compression repulsion force of the torsion spring from a certain angle by the operation of the clutch device when the door is opened. The large door can be easily opened with little force.

As described above, in the first embodiment, the door (moving body) is connected to the camshaft 50, and the central body 15 is connected to the door frame (fixing body) in the first embodiment. Cam shaft 50 is rotated in accordance with the rotation of the door, but in the third embodiment the cam shaft 150 is fixed to the door frame through the first fixing member 121, the single body 113 is The door is fixed to the door through the second fixing member 123. Therefore, the body 113 is rotated as the movable body and the camshaft 150 is fixed as the stationary body, but there is a difference in driving the movable body 160 up and down is made the same.

In addition, the hinge device according to the third embodiment of the present invention comprises two independent oil closed circuits in the longitudinal direction, and a pair of check valves 170 and 171 are simultaneously provided as the movable body 160 moves up and down inside the closed circuit. Because of its operation, despite the slim construction, the door is delayed at the set speed while providing sufficient damping force to automatically return to the delayed speed.

In the third embodiment, the oil pressure is controlled by the check valve and the hydraulic control rod, respectively, in the double hydraulic circuit. However, the upper hydraulic circuit has a notch for providing a uniform damping force to the check valve when the door is closed. A second hydraulic circuit is formed, the lower hydraulic circuit is a second hydraulic control rod is inserted into the flow path formed in the piston rod to control the flow rate of the oil (that is, the rising speed of the piston) according to the rising position of the piston It is also possible to form and combine the hydraulic circuit.

5. Fourth embodiment

12 is a longitudinal cross-sectional view showing a slim type automatic return hinge device having a ball type clutch device and a double hydraulic circuit according to a fourth embodiment of the present invention, and FIG. 13 is a perspective view showing the ball type clutch device, FIGS. 14C is a plan sectional view sequentially showing the operating state of the ball type clutch device when the door is opened.

The automatic return hinge device of the fourth embodiment is similar to the third embodiment in that a dual hydraulic circuit is adopted for reinforcing damping force in order to pursue a slim type, and the roller pins employed in the first and third embodiments. There is a difference in that a ball type clutch device having a relatively short length is employed instead of the clutch device of the type.

Therefore, the same components as those in the first to third embodiments are assigned the same member numbers, and description thereof will be omitted.

12 and 13, the ball type clutch device has a clutch body 271 having a through hole 271c at its center portion, and a rotating shaft 270 coupled to the through hole 271c and perpendicular to the rotating shaft. A shaft disk 272 is disposed to face the clutch body 271, and a shaft disk 272 is disposed to face the lower portion of the shaft disk 272, the rotating shaft 270 is rotatably inserted and fixed to the through-hole 274c in the center portion. A body holder 274 secured to the door by pins 275 and a movement between the clutch body 271 and the axial disk 272 and the body holder 274 when the body holder is rotated in one direction and vice versa. And selectively coupled to the first and second balls (273a, 273b) to selectively remove the compression repulsive force of the torsion spring 276 is coupled to the body holder by transmitting a rotational force.

The first and second balls 273a and 273b are selectively coupled while moving between the clutch body 271 and the shaft disk 272 and the body holder 274 to transmit or block the rotational force of the body holder 274. Hemispherical first and second upper insertion holes 271a and 271b are formed in the lower surface of the clutch body 271, and the first and second balls 273a and 273b can pass through the shaft disk 272. First and second through holes 272a and 272b are formed, and hemispherical first and second lower insertion holes 274a and 274b are formed on an upper surface of the body holder 274.

On the upper side of the clutch body 271, a quadrilateral protrusion 271d coupled to the bearing portion of the door frame protrudes outward when the hinge device is installed on the door, and a through hole 271c on the upper side of the protrusion 271d. The E-ring for suppressing the detachment of the clutch body 271 to the rotary shaft 270 extending through the coupling is coupled to the front end of the rotary shaft 270.

In addition, an upper end of the torsion spring 276 is fixed to the lower portion of the body holder 274 by the first fixing hole 278a, and a second fixed end formed of the lower end of the torsion spring 276 on the upper end of the shaft holder 277. The hexagonal lower end of the rotation shaft 270 is coupled to the hexagonal through groove formed at the center of the shaft holder 277 and fixed by the hole 278b. The hexagonal lower end of the rotating shaft 270 may be coupled to the cam shaft 150 of the hydraulic circuit in a simple shaft connection structure.

The operation of the ball type clutch device configured as described above will be described with reference to FIGS. 14A to 14C. In FIG. 14A to FIG. 14C, the hatched portions indicate the positions where the first and second balls 273a and 273b are currently located.

The first and second upper insertion holes 271a and 271b of the clutch body 271 and the first and second through holes 272a of the shaft disk 272 when the door is closed, that is, in the initial state. The first and second balls 273a and 273b located between 272b are blocked by the top surface of the body holder 274.

When the door is opened in this state, when the body holder 274 fixed to the door rotates in the left screw direction, the torsion spring 276 is reverse twisted in conjunction with this. In this state, as shown in FIG. 14B, when the body holder 274 continues to rotate so that the opening angle of the door reaches the clutch stop start time, for example, 30 °, the first and second bodies of the body holder 274 are reached. When the lower insertion holes 274a and 274b face the first and second balls 273a and 273b, the first and second balls 273a and 273b have a torsional force due to the torsional force applied to the body holder 274. The first and second lower insertion holes 274a and 274b are moved.

Thereafter, when the body holder 274 is rotated in accordance with the opening of the door, the body holder 274 and the shaft disk 272 are rotated together with the left screw as shown in FIG. 14C, and the clutch body 271 stops. Will remain intact. That is, when the clutching state is maintained, since the elastic force increase of the torsion spring 276 stops at the time of rotation after the clutch stop start time, the opening force is greatly reduced, and the user can easily open the heavy large door.

In addition, when the door is closed, the clutch is released when the door opening angle reaches the clutch stop start time, and the closing force of the door is increased because the elastic force of the torsion spring 276 is added to the restoring force of the return spring.

6. Application of the hinge device

Since the structure and the effect of the remaining components of the slim automatic return hinge device according to the fourth embodiment having the ball type clutch device and the double hydraulic circuit are made the same as in the above-described third embodiment, a description thereof is omitted. do.

As shown in FIG. 17, the hinge device 300 of the fourth embodiment includes a quadrilateral protrusion 271d of the clutch body 271 that is embedded at one side of the door 310 and protrudes from the hinge device 300. It may be applied to the structure that is coupled to / fixed to the receiving portion 321 of the frame 320, the simple hinge device 311 is rotatably supported by the door frame 320 in the lower portion of the door. In the application example, the body 113 of the hinge device 300 pivots the rotary shaft 270 and the simple hinge device 311 along with the door 310.

On the other hand, the automatic return hinge device according to the third and fourth embodiments described above is to separate the first hinge device A consisting of the torsion spring and the clutch device from the main body of the automatic return hinge device without any functional problem. It is possible. The reason is that the first hinge device A and the second hinge device B from which the first hinge device A is separated from the main body of the automatic return hinge device are coupled to each other in a simple shaft connection structure.

FIG. 15 is a cross-sectional view illustrating a detachment structure of the slim type automatic return hinge device according to the fourth embodiment, and FIG. 16 is an explanatory view for explaining a state in which the detachable type automatic return hinge device shown in FIG. 15 is applied to a door. to be.

The slim automatic return hinge device according to the fourth embodiment includes a torsion spring 276 and a clutch device 720 by separating the shaft holder 277 and the guide hole forming part 78 as shown in FIG. 15. It may be divided into a second hinge device (B) having a first hinge device (A), a return spring 167, a hydraulic circuit portion and the like and having an automatic return function.
In FIG. 15, reference numeral 113a designates a first body and 113b designates a second body.
In addition, as shown in FIG. 10, the automatic return hinge device according to the third embodiment separates the first hinge device A from the main body of the automatic return hinge device and the first hinge device A including the torsion spring and the clutch device. When divided into the second hinge device (B), the body 113 is divided into the first and second body, the outer clutch 71 is the first lower cap and the second hinge of the first hinge device (A) It is divided into a second upper cap of the device, and the shaft 151 is also divided into a first shaft belonging to the first hinge device A and a second shaft belonging to the second hinge device B. In this case, the upper cap 131 is defined as the first upper cap of the first hinge device (A), and the lower cap 133 is defined as the second lower cap of the second hinge device (B).

In this case, as illustrated in FIG. 16, the first hinge device A is embedded in the lower side of one side of the door 310 and the quadrangular protrusion 271d of the clutch body 271 protruding from the first hinge device A is provided. Is coupled to the shaft receiving portion 321 of the door frame 320, the second hinge device (B) is embedded in the upper portion of the door and the protruding shaft 151 of the second hinge device (B) is the door frame It can be applied to the fixed structure of (320).

In this application, the door 310 has a rotation shaft 270 and a second of the first hinge device A together with the first and second bodies 113a and 113b of the first and second hinge devices A and B. The shaft 151 of the hinge device B is pivoted about its axis.

In addition, the automatic return hinge device of the first embodiment has been illustrated to be installed in the door and the frame using a hinge, the present invention is not limited to this, it is also possible to be applied in a known manner. For example, it is also possible to form the body in a single body and to install the body and the shaft using a fixing member having one end fixed to the door frame and the door of the refrigerator as in the third embodiment.

7. Modifications

Meanwhile, in the description of the first embodiment, the torsion spring 76 and the return spring 67 are used in combination, and the hydraulic control structure in which the clutching operation is performed when the clutch device 700 exceeds the opening angle of 30 ° is illustrated. In the case of a slim hinge device, the present invention may remove the return spring and provide a restoring force for the movable body 60 only by the torsion spring 76. The same may also be applied to the hinge devices of the second to fourth embodiments.

That is, in the case of a slim self-returning hinge device used for opening and closing of a small door for home appliances and construction, except for the case where a large resilience force is required for the movable body such as a large door, the torsion spring 76 alone is used for the movable body 60. It is possible to provide a restoring force, in which case the stop start time at which the clutch device 700 is clutched is preferably set to 90 °, for example.

The ball type clutch device illustrated in the fourth embodiment can also be applied to other embodiments or modifications. In addition, although the ball type is illustrated as a check valve in the said embodiment, it can also be formed in plate shape.

As described above, in the present invention, the return spring and the torsion spring are installed together in the hinge device to compensate for the loss of the closing force of the door occurring at the end of the open return, and at the same time, the opening force of the door is reduced by the clutch device so that the heavy and large The door can be easily opened with little force.

In addition, the hinge device of the present invention is formed in a slim shape so that it can be embedded inside the various doors that require a very small diameter, it is possible to maintain the overall appearance simply when installed in the door, and also to reduce the damping force due to the reduction in diameter By extending the at least one hydraulic circuit there is an advantage that can be applied to large and small doors.

In the above, the present invention has been illustrated and described with reference to specific preferred embodiments, but the present invention is not limited to the above-described embodiments, and the present invention is not limited to the spirit of the present invention. Various changes and modifications will be possible by those who have the same.

Claims (41)

In the automatic return hinge device for a door having a first hinge and a second hinge fixed to the door and the door frame, An upper body of which the upper side of the first hinge is integrally formed on one circumferential surface and the upper end of which is blocked by an upper cap in which a groove is formed on an inner surface of the first hinge; A lower body closed with a lower cap having a lower side of the first hinge integrally formed on one circumferential surface and sealing a lower end thereof; A central body having one side of the second hinge integrally formed on one circumferential surface and pivotally disposed between the upper and lower bodies; A shaft having a lower end rotatably installed at a middle portion of the central body and having an upper end inserted into a recess of the upper cap and fixed to the upper body; A piston that is slidably installed along an inner circumferential surface of the central body and divides the inside of the central body into an upper / lower chamber; Rotational / linear motion converting means for converting the rotational motion of the shaft into the axial linear motion of the piston when the rotational force of the door is applied to the shaft according to the rotation of the door; Damping means for lowering and raising the piston according to opening and closing of the door and selectively providing a damping function when the piston is raised; And a returning means for providing a restoring force to the rotational / linear motion converting means to return the door to the initial position when the door is closed. An upper body of which an upper side of the first hinge fixed to the door is integrally formed on one circumferential surface and whose upper end is blocked by an upper cap; A lower body closed with a lower cap having a lower side of the first hinge integrally formed on one circumferential surface and sealing a lower end thereof; A central body having one side of the second hinge fixed to the door frame integrally formed on one circumferential surface and pivotally disposed between the upper and lower bodies; A shaft having one end fixed to the upper cap and the other end extending to the central body; A piston that is slidably installed along an inner circumferential surface of the central body and divides the inside of the central body into an upper / lower chamber; Rotational / linear motion converting means for converting the rotational motion of the shaft into the axial linear motion of the piston when the rotational force of the door is applied to the shaft according to the opening and closing of the door; Damping means installed on the piston to control the flow of the fluid moving between the upper and lower chambers in conjunction with the opening and closing of the door to control the descending and rising speed of the piston, and provides a damping function selectively when the piston is raised and; A torsion spring embedded in an upper portion of a central body so that one end is fixed to an upper end of the shaft and providing a restoring force for rotating the shaft in a direction of closing the door; And a clutch means for stopping the increase in the elastic force of the torsion spring when exceeding a preset opening angle when the door is opened and closed in connection with the torsion spring, and restoring the elastic force of the torsion spring when it falls within the opening angle. Auto return hinge device. An upper body of which an upper side of the first hinge fixed to the door is integrally formed on one circumferential surface and whose upper end is blocked by an upper cap; A lower body closed with a lower cap having a lower side of the first hinge integrally formed on one circumferential surface and sealing a lower end thereof; A central body having one side of the second hinge fixed to the door frame integrally formed on one circumferential surface and pivotally disposed between the upper and lower bodies; A shaft having one end fixed to the upper cap and the other end extending to the central body; A piston that is slidably installed along an inner circumferential surface of the central body and divides the inside of the central body into an upper / lower chamber; Rotational / linear motion converting means for converting the rotational motion of the shaft into the axial linear motion of the piston when the rotational force of the door is applied to the shaft according to the opening and closing of the door; Damping means installed in the piston to control the lowering and raising speed of the piston in conjunction with opening and closing of the door, and selectively providing a damping function when the piston is raised; A return spring installed in the lower chamber, the return spring being compressed at the opening of the door and providing a restoring force for raising the piston at the closing of the door; A torsion spring embedded in an upper portion of a central body so that one end is fixed to an upper end of the shaft and providing a restoring force for rotating the shaft in a direction of closing the door; And a clutch means for stopping the increase in the elastic force of the torsion spring when exceeding a preset opening angle when the door is opened and closed in connection with the torsion spring, and restoring the elastic force of the torsion spring when it falls within the opening angle. Auto return hinge device. According to any one of claims 1 to 3, wherein the rotation / linear motion converting means A guide hole forming part installed on an inner circumferential surface of the central body and having first and second vertical guide holes formed to face each other in a vertical direction; A circular portion extending from the shaft and having first and second lifting guide holes formed in a spiral shape having a symmetrical structure helically moved along an outer circumferential surface thereof, and having a relative external force applied to the upper body when the door is rotated. A cam shaft pivoting by; Automatic return, characterized in that the both ends are coupled to the first and second vertical guide hole through the first and second lifting guide hole, and the other end is composed of a guide pin coupled to the upper end of the piston rod connected to the piston Hinge device. The method of claim 4, wherein the first and second lifting guide holes each include a first lifting section formed with a first cam drawing angle and a second cam drawing angle that is relatively smaller than the first cam drawing angle. 2. A self-returning hinge device comprising a stopping section in which the elevating section and the cam diagram angle are zero. The damping means according to any one of claims 1 to 3, wherein the damping means A piston rod having a first flow path connected to the guide pin so as to be slidably coupled to the inside of the cylindrical portion of the camshaft, the lower end connected to the center of the piston, and the oil flowing between the upper and lower chambers; At least one check valve installed in a second flow path capable of flowing the upper / lower chamber provided in the piston to open the second flow path when the door is opened, and close the second flow path when the door is closed; And an elevating speed control means for controlling an elevating speed of the elevating piston by controlling the oil flow amount of the first flow path when the door is closed. The method of claim 6, wherein the lifting speed control means And a hydraulic control rod for distal end portion inserted into the first flow path of the piston rod to control the flow rate of the oil moving from the upper chamber to the lower chamber through the first flow path. 8. The automatic return hinge device as set forth in claim 7, wherein the hydraulic control rod includes a high speed section setting section and a low speed section setting section to vary the flow rate of oil moving through the first flow path according to the opening angle of the door. 9. The automatic return hinge device according to claim 8, wherein the high speed section setting section of the hydraulic control rod has the same diameter, and the low speed section setting section is tapered so as to gradually decrease in diameter toward the tip section. 8. The automatic return hinge device as set forth in claim 7, wherein the hydraulic control rod is composed of a low speed section setting portion tapered to gradually reduce the diameter toward the tip portion. 4. The damping means according to any one of claims 1 to 3, wherein the damping means is installed in at least one third flow path of the piston to open a third flow path of oil moving from the lower chamber to the upper chamber when the door is opened. And at least one check valve configured to restrict the third flow path of oil moving from the upper chamber to the lower chamber in a relatively small amount so as to provide a uniform damping force at the closing of the door. . The method of claim 1, wherein the return means A torsion spring embedded in the upper body such that one end is fixed to the upper end of the shaft to provide a restoring force for rotating the shaft in a direction of returning the door when the door is closed; It is connected to the other end of the torsion spring and stops the increase of elastic force due to reverse twisting of the torsion spring when the clutch stop start time is reached when the door is opened, and the torsion when the clutch stop start time is reached when the door is closed Composed of clutch means for restoring the restoring force of the spring, The clutching stop start time is set in the range of 30 to 90 ㅀ automatic return hinge device. 13. A clutch according to any one of claims 2, 3 and 12, wherein the clutch means An outer clutch of which an outer circumference is fixed to the inner circumference of the central body by a forced press structure; An inner clutch having a lower end rotatably inserted at an upper end of the outer clutch and supporting the shaft in a rotatably contacting state with an inner space, and having a lower end of the torsion spring fixed at an upper end thereof; And a pair of roller balls disposed between the outer / inner clutch and configured to couple or separate the inner clutch from the shaft according to the opening angle of the door. 13. The rotating / linear motion converting means according to any one of claims 2, 3, and 12, wherein A guide hole forming part installed on an inner circumferential surface of the central body and having first and second vertical guide holes formed to face each other in a vertical direction; A circular portion extending from the shaft and having first and second lifting guide holes formed in a spiral shape having a symmetrical structure helically moved along an outer circumferential surface thereof, and having a relative external force applied to the upper body when the door is rotated. A cam shaft pivoting by; It is composed of a guide pin coupled to the upper end of the piston rod connected to the first and second vertical guide holes, respectively, and the other end through the first and the second lifting guide hole, the other end, The clutch means An outer clutch of which an outer circumference is fixed to the inner circumference of the central body by a forced press structure; An inner clutch having a lower end rotatably inserted at an upper end of the outer clutch and supporting the shaft in a rotatable contact state with an inner space, and having a lower end of the torsion spring fixed at an upper end thereof; It is composed of a pair of roller balls disposed between the outer / inner clutch and serves to couple or separate the inner clutch from the shaft according to the opening angle of the door, And the outer clutch and the guide hole forming unit are integrally formed. In the automatic return hinge device for a door having a first hinge and a second hinge fixed to the door and the door frame, An upper body of which the upper side of the first hinge is integrally formed on one circumferential surface and the upper end of which is blocked by an upper cap in which a groove is formed on an inner surface of the first hinge; A lower body closed with a lower cap having a lower side of the first hinge integrally formed on one circumferential surface and sealing a lower end thereof; A central body having one side of the second hinge integrally formed on one circumferential surface and pivotally disposed between the upper and lower bodies; A shaft having a lower end rotatably installed at a middle portion of the central body and having an upper end inserted into a recess of the upper cap and fixed to the upper body; An isolation tool for dividing the oil-filled chamber of the central body into first and second chambers; First and second pistons whose outer circumferential surfaces are slidably installed along the inner circumferential surfaces of the first and second chambers of the central body and which divide the interior of the first and second chambers into upper and lower chambers, respectively; Rotational / linear motion converting means for converting the rotational motion of the shaft into axial linear motion of the first and second pistons when the rotational force of the door is applied to the shaft according to the rotation of the door; First and second damping means for providing a damping function to delay the rising speed of the first and second pistons when the first and second pistons are raised in accordance with the closing of the door; And a returning means for providing a restoring force to the rotational / linear motion converting means to return the door to the initial position when the door is closed. The method of claim 15, wherein the damping means The lower end is connected to the center of the first and second pistons so that the first and second pistons move up and down in association with the operation of the rotational / linear motion converting means, and oil is respectively upper and lower parts of the first and second chambers. A piston rod having a first flow path that can flow between the chambers; At least installed in each of the first and second pistons to open a flow path of oil moving from the lower chamber to the upper chamber when the door is opened, and at least to shut off a flow path of oil moving from the upper chamber to the lower chamber when the door is closed. One first and second check valve; And an elevating speed control means for controlling an elevating speed of the first and second pistons which are elevated when the door is closed. 17. The method of claim 16, wherein the lifting speed control means includes a hydraulic control rod formed by repeating the high speed section setting section and the low speed section setting section to vary the flow rate of the oil moving through the first flow path in accordance with the opening angle of the door. An automatic return hinge device. 17. The method of claim 16, wherein the first and second check valves are respectively configured to release the overpressure when the first and second pistons are required to rise at high speed by an external force so that the upper chamber increases above a predetermined pressure. Automatic return hinge device further comprises a first and second overpressure preventing means. The method of claim 15, wherein the return means A torsion spring embedded in the upper body such that one end is fixed to the upper end of the shaft to provide a restoring force for rotating the shaft in a direction of returning the door when the door is closed; It is connected to the other end of the torsion spring to block the increase of elastic force due to reverse twisting of the torsion spring when the clutch stop start time is reached when the door is opened, and torsion when the clutch stop start time is reached when the door is closed An automatic return hinge device, characterized in that the clutch means for restoring the restoring force of the spring. 20. The system of claim 19, further comprising a return spring installed in the lower chamber of the second chamber, the return spring being compressed upon opening the door and providing a restoring force for raising the piston upon closing the door. Return hinge device. 16. The method of claim 15, wherein the first damping means is installed in the first piston to open the flow path of the oil moving from the lower chamber of the first chamber to the upper chamber when the door is opened, and uniform damping at the closing of the door At least one first check valve for restricting the flow passage of oil moving from the upper chamber of the first chamber to the lower chamber in a relatively small amount to provide a force; The second damping means is installed in the second piston to open a flow path of oil moving from the lower chamber of the second chamber to the upper chamber when the door is opened, and the lower chamber from the upper chamber of the second chamber at the closing of the door. At least one second check valve for blocking the flow path of the oil moving to the automatic return hinge device. A body formed of a single tubular body, the upper portion of which is blocked by an upper cap, and the lower body of which a lower cap is sealed by a sealing portion; A shaft having one end extending outwardly through the upper cap and the other end extending into the body; A piston that is slidably installed along an inner circumferential surface of the body and divides the inside of the body into an upper / lower chamber; Rotational / linear motion conversion means for converting the rotational motion of the shaft into the axial linear motion of the piston when the rotational force of the door is applied to the shaft according to the opening and closing of the door; Damping means mounted to the piston for controlling the rising speed of the piston when the door is closed; A return spring installed in the lower chamber, the return spring being compressed at the opening of the door and providing a restoring force for raising the piston at the closing of the door; A torsion spring embedded in an upper portion of the body so that one end is fixed to the upper cap and providing a restoring force for rotating the shaft in a direction of closing the door; And a clutch means for stopping the increase in the elastic force of the torsion spring when exceeding a preset opening angle when the door is opened and closed in connection with the torsion spring, and restoring the elastic force of the torsion spring when it falls within the opening angle. Auto return hinge device. 23. The method of claim 22, wherein the first fixing member having one end coupled to the upper cap and the other end coupled to the door, And a second fixing member having one end coupled to the shaft extending outward through the upper cap and the other end coupled to the door frame. 23. The automatic return hinge device of claim 22, wherein the body is embedded in the door. The body of claim 22, wherein the body is A first body including the torsion spring and clutch means inside the body, A second body including a piston, a rotation / linear motion conversion means, a damping means, and a return spring, separated from the first body, The shaft is A first shaft disposed in the first body and coupled to the torsion spring and the clutch means; Automatic return hinge device, characterized in that consisting of a second shaft disposed in the second body coupled to the rotation / linear motion converting means. 27. The method of claim 25, wherein the first body and the second body is embedded in the lower and the upper portion of the door, respectively, the first and second shafts extending from the first and second body, respectively, the lower and upper portion of the door frame An automatic return hinge device, characterized in that fixed to. It is composed of first and second hinge devices which are installed in the lower and upper portions of the door, respectively, The first hinge device A first body having an upper end and a lower end closed by a first upper cap and a first lower cap, respectively; A first shaft having one end extending outwardly through the first upper cap and the other end extending into the first body; A torsion spring embedded in an upper portion of the body so that one end is fixed to the first upper cap and providing a restoring force for rotating the first shaft in a direction of closing the door; It is composed of a clutch means for stopping the increase of the elastic force of the torsion spring when the opening angle exceeds a preset opening angle when the door is opened and closed in connection with the torsion spring, and restores the elastic force of the torsion spring when it is within the opening angle, The second hinge device A second body blocked by a second lower cap, the upper end of which is blocked by a second upper cap, and the lower end of which is sealed; A second shaft having one end extending outwardly through the second upper cap and the other end extending into the second body; An isolation tool for dividing the chamber of the second body into first and second chambers; First and second pistons whose outer circumferential surfaces are slidably installed along the inner circumferential surfaces of the first and second chambers of the second body and which divide the interior of the first and second chambers into upper and lower chambers, respectively; Rotational / linear motion converting means for converting the rotational motion of the second shaft into the axial linear motion of the first and second pistons when the rotational force of the door is applied to the second shaft according to the rotation of the door; And the first and second damping means configured to provide a damping function to delay the ascending speed of the first and second pistons when the first and second pistons are raised according to the closing of the door. Hinge device. It is composed of first and second hinge devices which are installed embedded in the lower and upper portions of the door, respectively The first hinge device A first body having an upper end and a lower end blocked by the clutch body and the shaft holder, respectively; A rotating shaft having one end extending outwardly through the clutch body and the other end extending into the first body; A torsion spring having one end fixed to the shaft holder and providing a restoring force for rotating the rotating shaft in a direction of closing the door; It is composed of a ball-type clutch means for restoring the increase of the elastic force of the torsion spring when the opening angle exceeds the preset opening angle when the door is opened and closed in connection with the torsion spring, and restores the elastic force of the torsion spring when the door is within the opening angle The second hinge device A second body having an upper end blocked by a guide hole forming part and closed by a lower cap to which the lower end is sealed; A shaft having one end extending outwardly through the guide hole forming portion and the other end extending into the second body; An isolation tool for dividing the chamber of the second body into first and second chambers; First and second pistons whose outer circumferential surfaces are slidably installed along the inner circumferential surfaces of the first and second chambers of the second body and which divide the interior of the first and second chambers into upper and lower chambers, respectively; Rotational / linear motion converting means for converting the rotational motion of the second shaft into the axial linear motion of the first and second pistons when the rotational force of the door is applied to the shaft according to the rotation of the door; And the first and second damping means configured to provide a damping function to delay the ascending speed of the first and second pistons when the first and second pistons are raised according to the closing of the door. Hinge device. 28. The clutch of claim 27 wherein the clutch means An outer clutch having an outer circumference portion fixed to the inner circumference portion of the first body by a forced press structure; An inner clutch in which a lower end is rotatably inserted in an upper end of the outer clutch and supports the first shaft in a rotatably contacted state in an inner space, and a lower end of the torsion spring is fixed at an upper end thereof; And a pair of roller balls disposed between the outer / inner clutch and configured to couple or separate the inner clutch from the first shaft according to the opening angle of the door. 29. The apparatus of claim 27 or 28, further comprising a return spring installed in a lower chamber of said second chamber that provides a restoring force for compressing upon opening said door and raising said second piston upon closing of said door. Automatic return hinge device characterized in that. The method of claim 28, wherein the clutch means The clutch body having a first through hole at a central portion thereof; A shaft disk coupled to the first through hole and disposed to face the clutch body at a right angle to the rotation shaft; A body holder which is disposed to face the lower portion of the shaft disk, the rotation shaft is rotatably inserted into the second through hole in the center and fixed to the door; When the body holder is rotated in one direction and vice versa, the compression repulsive force of the torsion spring, one end of which is coupled to the body holder, is selectively removed by moving between the upper cap, the axial disk and the body holder, and being selectively coupled. Automatic return hinge device, characterized in that consisting of the first and second balls. delete 29. The automatic return hinge device according to claim 27 or 28, wherein the door is a door of a refrigerator. A body formed of a single tubular body, the upper portion of which is blocked by an upper cap, and the lower body of which a lower cap is sealed by a sealing portion; A shaft having one end extending outwardly through the upper cap and the other end extending into the body; A piston that is slidably installed along an inner circumferential surface of the body and divides the inside of the body into an upper / lower chamber; Rotational / linear motion conversion means for converting the rotational motion of the shaft into the axial linear motion of the piston when the rotational force of the door is applied to the shaft according to the opening and closing of the door; Damping means mounted to the piston for controlling the rising speed of the piston when the door is closed; A return spring installed in the lower chamber, the return spring being compressed at the opening of the door and providing a restoring force for raising the piston at the closing of the door; A first fixing member having one end coupled to the upper cap and the other end coupled to the door; An automatic return hinge device, characterized in that the first end is coupled to the shaft extending to the outside through the upper cap and the other end is coupled to the door frame. The upper part is blocked by the upper cap and the lower body is blocked by the lower cap coupled to the sealing; A shaft having one end extending outwardly through the upper cap and the other end extending into the body; An isolation tool for dividing the chamber of the body into first and second chambers; First and second pistons having an outer circumferential surface slidably installed along the inner circumferential surfaces of the first and second chambers of the body, and partitioning the interior of the first and second chambers into upper and lower chambers, respectively; Rotational / linear motion converting means for converting the rotational motion of the shaft into axial linear motion of the first and second pistons when the rotational force of the door is applied to the shaft according to the rotation of the door; First and second damping means for providing a damping function to delay the rising speed of the first and second pistons when the first and second pistons are raised in accordance with the closing of the door; And a return spring installed in the lower chamber of the second chamber, the return spring being compressed at the opening of the door and providing a restoring force for raising the second piston at the closing of the door. The method of claim 34, wherein the damping means Oil installed in at least one flow path of the piston to open a flow path of oil moving from the lower chamber to the upper chamber when the door is opened, and move the oil from the upper chamber to the lower chamber to provide a uniform damping force when the door is closed An automatic return hinge device, characterized in that composed of at least one check valve for restricting the flow path to a relatively small amount. The method of claim 34, wherein the damping means A piston rod having a first flow path connected to the guide pin so as to be slidably coupled to the inside of the cylindrical portion of the camshaft, the lower end connected to the center of the piston, and the oil flowing between the upper and lower chambers; At least one check valve installed in a second flow path capable of flowing the upper / lower chamber provided in the piston to open the second flow path when the door is opened, and close the second flow path when the door is closed; And an elevating speed control means for controlling an elevating speed of the elevating piston by controlling the oil flow amount of the first flow path when the door is closed. 38. The method of claim 37, wherein the lifting speed control means The front end portion is inserted into the first flow path of the piston rod to control the flow rate of the oil moving from the upper chamber to the lower chamber through the first flow path, the variable flow amount of the oil moving through the first flow path according to the opening angle of the door An automatic return hinge device comprising a hydraulic control rod including a high speed section setting section and a low speed section setting section. 36. The automatic return hinge device according to claim 34 or 35, wherein the body is embedded in a refrigerator door. A first body having an upper end and a lower end closed by a first upper cap and a first lower cap, respectively; A first shaft having one end extending outwardly through the first upper cap and the other end extending into the first body; A torsion spring embedded in an upper portion of the body so that one end is fixed to the first upper cap and providing a restoring force for rotating the first shaft in a direction of closing the door; And a clutch means for stopping the increase in the elastic force of the torsion spring when exceeding a preset opening angle when the door is opened and closed in connection with the torsion spring, and restoring the elastic force of the torsion spring when it falls within the opening angle. Auto return hinge device. A body fixed to the circular body and having a first through hole at the center thereof, and having a hemispherical first and second upper insertion holes formed at the lower surface thereof; A shaft disc coupled to the first through hole and disposed to face the body at a right angle to the shaft and having first and second through holes through which balls can pass; A body holder disposed opposite the lower portion of the shaft disk and fixed to the door, the shaft being rotatably inserted into the second through hole of the center portion, and having a hemispherical first and second lower insertion holes formed in the upper surface thereof; A torsion spring having one end fixed to the lower side of the body holder and providing a restoring force for rotating the shaft in a direction of closing the door; A shaft holder fixed to the circular body at a distance from the body holder, and having a lower end of the torsion spring fixed at the upper end thereof, the shaft being rotatably coupled to a third through hole formed at the center portion; When the body holder is rotated in one direction and vice versa, the compression reaction force of the torsion spring coupled between the body holder and the shaft holder selectively transfers between the body and the shaft disk and the body holder and is selectively coupled to transmit rotational force. Consisting of first and second balls to remove, Automatic return hinge device for stopping the increase of the elastic force of the torsion spring when the opening angle exceeds the preset opening angle in opening and closing the door in conjunction with the torsion spring, restoring the elastic force of the torsion spring when within the opening angle Ball type clutch device.

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