JPH0478793B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to an autohinge for a door, and more specifically, a door that opens and closes along a rotational trajectory while being supported by a pivot, that is, a hinged door. This relates to a semi-concealed type auto hinge that is installed on.

BACKGROUND TECHNOLOGY In general, automatic door closing devices store the force when opening a door as elastic force in a spring, and when the door is closed, the elastic restoring force of this spring biases the door body in the closing direction. The closing speed of the door body is controlled by a hydraulic shock absorber.

Among the above automatic closing devices, those that are applied to hinged doors include a door checker that has two link arms and compresses an internal spring, and an automatic hinge that has an integral hinge part and uses a torsion spring. is known, and in recent years, concealed type auto hinges built into doors have been used.

The auto hinge mentioned above transmits the door opening operation to the torsion spring through two gears built into the hinge, which accumulates elastic force in the closing direction and moves the piston in the hydraulic shock absorber. Then, the elastic restoring force of the torsion spring biases the door in the closing direction, and the viscosity of the hydraulic oil when the piston returns to its original position provides resistance to the closing speed of the door. The applicant has previously filed an application for this type of door auto hinge. (Japanese Utility Model Publication No. 62-27180) Problems to be Solved by the Invention In general, in auto hinges for doors, the viscosity of the hydraulic oil increases or decreases depending on the temperature, which slows down or accelerates the closing speed of the door. .

However, in the conventional autohinge mentioned above,
The time required for closing can only be adjusted by adjusting the check position of the door, i.e., the boundary position between the range where the door closes quickly from fully open to halfway, and the range where it closes slowly from fully closed. The speed itself could not be adjusted.

Means for Solving the Problems The present invention has been made in view of the above problems, and is an auto hinge for doors that is installed near the center of rotation of a hinged type door, and which is installed at a predetermined eccentric distance from the door body. A pivot shaft that is vertically installed and does not move with respect to the floor surface, a force storage mechanism that is housed in the side edge of the door body and applies a force in the closing direction to the door body, and a force storage mechanism that controls the speed of the door body in the closing direction. It consists of an autohinge main body in which a shock absorbing mechanism is connected by a pivot, and a gear transmission mechanism disposed between the pivot shaft and the pivot of the autohinge main body, and the force storage mechanism is fitted concentrically to the pivot shaft. The other end of the equipped torsion spring is locked to a cylindrical case extending concentrically surrounding the pivot shaft, and the buffer mechanism is integrally fixed to the tip of the pivot shaft and filled with hydraulic oil. a cylinder that is screwed into the cylinder and is movable only in the axial direction; a check valve that is disposed on the piston and connects hydraulic chambers formed on both sides of the piston in the axial direction; This auto hinge for a door is characterized in that it is comprised of a flow rate regulating valve interposed in an oil passage that constantly communicates with a hydraulic chamber.

Function The auto hinge for a door according to the present invention rotates the pivot shaft using a gear transmission mechanism when opening the door body by pivoting the door body around the pivot shaft, accumulates elastic force in the torsion spring, and connects the cylinder with the pivot shaft. When the piston is screwed together to move the piston and allow hydraulic oil to flow from one hydraulic chamber to the other through the check valve and close the door body, the elastic restoring force of the torsion spring is used to close the door body. The door body is biased in the closing direction, and the flow regulating valve installed in the oil passage that communicates both hydraulic chambers resists the hydraulic oil passing through the oil passage as the piston returns to its original position. By giving , the closing speed of the door body itself can be adjusted.

Embodiment FIGS. 1 to 4 show an embodiment of an auto hinge for a door according to the present invention. As shown in FIG. The main body part B is built into the side edge of the door body D and is installed in a state in which it protrudes from the door body D. is supported so that it can be opened and closed.

The hinge portion H has a pivot shaft 1 that is eccentric from the door body D by a predetermined distance.
Similarly, H' has a pivot shaft 1', both pivot shafts 1, 1' are located on the same axis, and the door body D rotates around this pivot shaft 1, 1'.
Open and close.

The pivot shaft 1 of the hinge H is fixed to the floor F, and is integrally fixed to a gear 3 housed in a pivot housing 2 on the side of the door body D. The gear 3 is rotatably attached to a base block 4 in the housing 2 via a bearing 5, and this gear 3 meshes with an intermediate gear 6 rotatably attached to the base block 4. , this intermediate gear 6 is connected to the base block 4
A boss portion 8a of the slide bush 7 is meshed with a rotatably supported gear 8.

Here, the pivot shaft 1 to which the gear 3 is fixed is
is always stationary with respect to the floor F, and when the door body D is opened and closed around this pivot shaft 1, the gear 6 rotates while revolving around the gear 3, and the gear 8 also rotates around the gear 3. Like the gear 6, it rotates while revolving, forming a so-called planetary gear mechanism.

The main body B has a structure in which a force storage mechanism S using a spring and a buffer mechanism A using the viscosity of hydraulic oil are integrated into a cylindrical case 10, and both mechanisms S and A are connected by a pivot 11. It's summery.

The force storage section S is for applying a force in the closing direction to the door body D, and includes a pivot shaft 11 disposed approximately along the axis of the cylindrical case 10, and a pivot shaft 11 and the cylindrical case 10. and a torsion spring 12 disposed coaxially between.

The aforementioned gear 8 is integrally connected to the base end of the pivot shaft 11 using a key 13. The pivot shaft 11 is supported at its proximal end by a bearing 14 disposed between the cylindrical case 10 and the cylindrical case 10 at the distal end position of the boss portion 8a of the gear 8. The upper end side is supported by a stopper mechanism C housed in an intermediate position, so that it is rotatable within the cylindrical case 10.

In this embodiment, the torsion spring 12 is formed by winding a wire having a substantially rectangular cross section into a coil, and both ends of the torsion spring 12 are bent toward the center. Hook part 1
2a and 12b. The hook portion 12a on the upper end side of the torsion spring 12 is
It is locked in the slit groove 20a of the slide collar 20 of the stopper mechanism C, and the hook part 12 on the lower end side
b is the base end side of the pivot 11 and the bearing 14
Slit groove 15 of sleeve 15 fixed above
It is locked at a.

Here, the stopper mechanism C includes a slide collar 20 rotatably fitted to the small diameter portion of the pivot shaft 11, a retainer 21 fixed to the cylindrical case 10, and a retainer 2
1, and a cam surface 23 formed on the outer circumferential surface of the pivot shaft 11 facing the inner circumferential surface of the retainer 21.

As mentioned above, the slide collar 20 is
The hook portion 12a on the upper end side of the torsion spring 12 is locked in the slit groove 20a in the small diameter portion at the lower end, and the outer periphery of the upper end is set to have a size that substantially slides into contact with the inner peripheral surface of the cylindrical case 10, and the upper end A recessed groove 20c into which a part of the roller 22 can fit is formed in a part of the cylindrical cavity 20b.

The retainer 21 has a large-diameter cylindrical portion 21 a that is integrally fixed to the cylindrical case 10 and supports the pivot shaft 11 , and a small-diameter cylindrical portion 21 b that has a cam surface of the pivot shaft 11 . 23 and the cavity 20b of the slide collar 20 in a loosely fitted state. A roller holding hole 21c having a size that allows the rollers 22 to move in the radial direction while keeping their axes parallel to each other is formed through the small diameter cylindrical portion 21b.

The cam surface 23 formed on the pivot shaft 11 has a gentle protrusion 23a formed on a part of the circumferential surface, and the protrusion height of the protrusion 23a from the circumferential surface is as follows:
The recess depth from the circumferential surface of the groove 20c of the slide collar 20 is made to correspond to the depth.

The roller 22 is connected to the circumferential surface of the cam surface 23 and the hollow portion 20b of the slide collar 20.
This is the diameter that can be interposed between the circumferential surface of the

As shown in FIG. 4, the slide collar 20 and the pivot shaft 11 have a phase difference between the groove 20c and the protrusion 23a that corresponds to a desired angular position at which the door body D is desired to be stopped and held midway. are arranged so that

The shock absorber A includes a cylinder 31 fixed to the head 11a of the pivot shaft 11 using fluid viscosity.
and the piston 3 housed within this cylinder 31.
2, and a guide member 33 disposed downwardly from the upper end of the cylindrical case 10.

The shock absorber A includes a cylinder 31 fixed to a large-diameter head portion 11a at the upper end of the pivot shaft 11, a piston 32 housed in the cylinder 31, and a piston 32 extending downward from the upper end of the cylindrical case 10. It is composed of a guide member 33 arranged therein.

The head 11a of the pivot 11 is formed to have a slightly smaller diameter than the inner diameter of the cylindrical case 10, and round holes 34 and 35 are bored along the axial direction in the center and sides of the head 11a. This double round hole 3
4 and 35 communicate with each other at the bottom via a flow rate regulating valve V disposed from the side of the head 11a.

A small-diameter pipe 37 that extends upward and axially is fixed to the central round hole 34, and a filter 38 is arranged on the upper end surface of the head 11a so as to cover the opening of the round hole 35. It is set up.

The cylinder 31 is a cylindrical body having an outer diameter approximately the same as that of the head 11a, and has a base end side of the inner circumferential surface.
A multi-start threaded portion 31a with a large lead is formed, and a slide sleeve 39 having the same outer diameter as the cylinder 31 is integrally fixed to the tip.

The piston 32 has a cylindrical shape with an outer diameter substantially equal to the inner diameter of the cylinder 31, and has a multi-threaded threaded portion 3 of the cylinder 31 on the outer circumferential surface of the lower end.
A multithread threaded portion 32a is formed to be screwed into the piston 1a, and the inner peripheral surface of the piston 32 is formed into a spline hole 32b over substantially the entire length thereof.

A check valve 4 is provided on the inner periphery of the lower end of the piston 32.
0 support member 41 is fixedly provided. The check valve 40 is of a ball and cup type and is attached to the side of the support member 41, and is configured to prevent hydraulic oil from flowing into the piston 32 from the lower part thereof. There is. Further, a through hole 41a is formed in the center of the support member 41, and a pipe 37 extending from the head 11a is inserted into the through hole 41a so as to be relatively slidable. The hole 41a and the outer periphery of the pipe 37 are kept sealed by an O-ring _O1 .

The guide member 33 is connected to the cylindrical case 10.
The large diameter portion 33a and the cylinder 3 are fitted into and fixed to the cylinder 3.
Small diameter portion 3 that can be fitted into the slide sleeve 39 of 1
A through hole 33c is formed along the axial direction, and a sealing plug 42 is screwed onto the upper end of the through hole 33c via an O-ring _O2 .

A slide sleeve 39 of the cylinder 31 is provided on the upper outer periphery of the small diameter portion 33a of the guide member 33.
is fitted so as to be slidable in the circumferential direction, and the small diameter portion 33
The outer periphery of a and the inner periphery of the slide sleeve 39 are kept in a sealed state by an O-ring O ₃ fitted to the slide sleeve 39.

A portion below the center of the guide member 33 is a spline shaft 33d that engages with the spline hole 32b of the piston 32.
It is restricted only in the axial direction along the spline shaft 33d.

A pipe 37 fixed to the head portion 11a of the pivot shaft 11 is loosely fitted into the lower end of the through hole 33c formed in the guide member 33 with a predetermined gap in the axial and circumferential directions. 33c
is communicated with the side surface of the small diameter portion 33b through a through hole 33e formed on the side surface of the small diameter portion 33b.

With the above configuration, a first hydraulic chamber a is formed between the upper surface of the head 11a of the pivot shaft 11 on the inner surface of the cylinder 31 and the lower end surface of the piston 32, and the first hydraulic chamber a is formed between the inner surface of the cylinder 31 and the small diameter portion 33b of the guide member 33. and between the lower end of the slide sleeve 39 and the upper surface of the piston 32.
A hydraulic chamber b is formed, and a third hydraulic chamber c is formed between the inside of the piston 32 and the lower end surface of the guide member 33.

The first hydraulic chamber a and the third hydraulic chamber c communicate with each other via a check valve 40 provided in the piston 32, and the first hydraulic chamber a and the second hydraulic chamber b communicate with each other through a check valve 40 provided in the piston 32.
1a, the flow rate adjustment valve V, the round hole 34, the pipe 37, the through hole 33c of the guide member 33, and the through hole 33e. The hydraulic chamber c in FIG. 3 refers to the gap between the through hole 33c of the guide member 33 and the outer periphery of the pipe 37, and the through hole 33c in FIG.
They are also communicated through the through hole 33e. Therefore, the first hydraulic chamber a and the second hydraulic chamber b communicate with each other through the check valve 40, and also through the through hole 33c from the oil passage that communicates the first hydraulic chamber a with the third hydraulic chamber c. and the outer periphery of the pipe 37 through a gap formed therebetween.

Note that the first to third hydraulic chambers a, b, and c are filled with hydraulic oil through the through hole 33 of the guide member 33.
This is done with the sealing plug 42 removed from c, and after the hydraulic oil is filled, the sealing plug 42 is screwed on to seal.

Below, the functions and operations of the above door auto hinge will be explained.

When the door body D is closed, the initial elastic force given to the torsion spring 12 in advance is transmitted from the pivot shaft 11 to the pivot shaft 1 via the gear 8, the intermediate gear 6, and the gear 3, and this reaction force causes the door to close. The main body D is always biased in the closing direction.

When the door main body D is opened in the direction of the arrow in FIG. 1 from this state, since the gear 3 of the pivot shaft 1 is a stationary gear, the intermediate gear 6 that meshes with this gear 3 will move as shown in FIG. 3. The gear 8 rotates in the direction of the arrow while revolving around the gear 3 in the direction of the arrow, and the gear 8 meshing with the intermediate gear 6 similarly rotates around the pivot shaft 11 in the direction of the arrow while revolving in the direction of the arrow.

When the gear 8 and the pivot 11 begin to rotate, the fourth
As shown in FIGS. a and b, the roller 22, which is held in a predetermined position with respect to the cylindrical case 10 by the retainer 21, is inserted into the groove 20c of the slide sleeve 20.
The slide sleeve 20 is located between the opening edge of the cylindrical case 1 and the cam surface 23 of the pivot shaft 11.
0, the torsion spring 12 is compressed between the pivot shaft 11 and the slide collar 20 and accumulates elastic force.
At the same time, the multithreaded threaded portion 31 on the inner surface of the cylinder 31
The piston 32 that is screwed into the piston 32 moves upward because its rotational movement is restricted by engagement with the spline shaft 33d of the guide member 33.

When moving the piston 32 upward,
The hydraulic oil in the third hydraulic chamber c is compressed within the piston 32 by the lower end of the small diameter portion 33b of the guide member 33, passes through the check valve 40 without resistance, flows into the first hydraulic chamber a, and flows into the first hydraulic chamber a. 2 The hydraulic oil in hydraulic chamber b is
It is compressed between the slide sleeve 39 and the upper end of the piston 32, and flows into the third hydraulic chamber c through the through hole 33e, the through hole 33c, and the gap between the through hole 33c and the pipe 37. It flows into the first hydraulic chamber a together with the hydraulic oil inside, and at the same time, the through hole 33
e, it flows into the first hydraulic chamber a through the through hole 33c, the pipe 37, the round hole 34, the flow rate adjustment valve V, and the round hole 35.

When the pivot shaft 11 further rotates, the protrusion 23a of the cam surface 23 presses the roller 22 diametrically outward as shown in FIG.
, and further press the protrusion 2 as shown in Fig. 5d.
3a rides over the roller 22. If the opening operation of the door body D is canceled in this state, the roller 22
is pressed between the base of the protrusion 23a of the cam surface 23 and the opening edge of the groove 20c of the slide sleeve 20 by the elastic restoring force of the torsion spring 12, so that the pivot shaft 11 is pressed against the cylindrical sleeve 1.
0, and the door body D can be stopped at a preset angle, for example at a 90° open position of the door body D.

In the above opening operation of the door body D, the check valve 40 does not operate and the hydraulic oil flows from the second and third hydraulic chambers b and c to the first hydraulic chamber a without resistance, so that the opening operation described above is performed. This is performed with an operating force that approximately corresponds to the elastic force of the torsion spring 12.

When closing the door body D, if the force for opening the door body D is released before the operating position of the stopper mechanism C, the pivot shaft 11 rotates in the opposite direction due to the elastic restoring force of the torsion spring 12. However, due to this rotation of the pivot shaft 11, the gear 8 and the intermediate gear 6 rotate and revolve in the opposite direction to the above, and the door body D moves in the closing direction.

On the other hand, when the door body D is stopped at a predetermined position by the stopper mechanism C, if the door body D is pressed in the closing direction, the protrusion 23a
presses the roller 22 again toward the groove 20c of the slide sleeve 20, and the torsion spring 1
2 while resisting the elastic force of the slide sleeve 2.
0 to push the roller 22 into the groove 20c and overcome the roller 22 to release the stopped state of the door body D. From then on, the torsion spring 1 is rotated in the same manner as above.
The door body D is urged in the closing direction by the elastic restoring force of No. 2.

At the same time, the piston 32 begins to move downward as the cylinder 31 rotates in the opposite direction together with the pivot 11. Then, the hydraulic oil in the first hydraulic chamber a is compressed by the descent of the piston 32,
Since the check valve 40 operates, the water flows into the round hole 35 after being filtered through the filter 38 . The hydraulic oil that has flowed into the round hole 35 flows through the flow control valve V,
It is returned to the second hydraulic chamber b through the round hole 34, the pipe 37, the through hole 33c, and the through hole 33e. Further, a portion of the hydraulic fluid flowing back from the first hydraulic chamber a to the second hydraulic chamber b is returned to the third hydraulic chamber c through the gap between the through hole 33c and the pipe 37.

During the recirculation process of the hydraulic oil, the flow rate of the hydraulic oil is restricted by the flow rate regulating valve V, so that the piston 32 receives resistance and slowly descends. Therefore, the rotation of the pivot shaft 11 is also gradual, and the door body D moves slowly and smoothly in the closing direction.

In the autohinge having the above structure, the closing speed can be adjusted by tightening or loosening the flow rate regulating valve V, and by the above adjustment, the door body D can be smoothly closed at a desired constant speed until it is fully opened. can.

Effects of the Invention As explained above, according to the auto hinge for a door according to the present invention, even if the closing speed of the door body changes due to a change in the viscosity of the hydraulic oil due to a change in temperature, the flow rate adjustment valve By increasing or decreasing the resistance when the hydraulic oil flows back, the closing speed of the door body itself can be adjusted as desired, and the door body can be smoothly closed at substantially the same speed when fully closed.

[Brief explanation of the drawing]

1 to 4 show an example of the position of an auto hinge for a door according to the present invention, and FIG. 1 is an overall perspective view showing a state in which the device of the present invention is attached to a door;
Fig. 2 is a longitudinal sectional view of the present invention, Fig. 3 is a bottom view for explaining the relative arrangement positions of the pivot shaft and the pivot axis, and Figs. 4 a to d are enlarged sectional views for explaining the stopper mechanism. It is. A...Buffer mechanism, B...Auto hinge, C...
Stopper mechanism, D...door body, G...gear transmission mechanism, H...hinge section, S...force storage mechanism, V...
Flow rate adjustment valve, 1... Pivot shaft, 6... Intermediate gear, 10... Cylindrical case, 11... Pivot, 12
...Torsion spring, 31...Cylinder,
32... Piston, 40... Check valve, a... First
Hydraulic chamber, b...second hydraulic chamber, c...third hydraulic chamber.

Claims (1)

[Scope of Claims] 1. An auto hinge for a door that is installed near the center of rotation of a swing-type door, which comprises a pivot shaft that is vertically installed at a predetermined eccentric distance from the door body and that is immovable with respect to the floor surface; an autohinge body that is housed in the side edge of the door body and has a force storage mechanism that applies a force in the closing direction to the door body and a buffer mechanism that controls the speed of the door body in the closing direction, connected by a pivot; and the pivot shaft; and a gear transmission mechanism disposed between the pivot shaft of the autohinge body, and the force storage mechanism has the other end of a torsion spring fitted concentrically to the pivot shaft so that the other end of the torsion spring concentrically surrounds the pivot shaft. The buffer mechanism includes a cylinder that is integrally fixed to the tip of the pivot shaft and filled with hydraulic oil, and a cylinder that is screwed into the cylinder and that extends only in the axial direction. a movable piston; a check valve disposed on the piston to connect hydraulic chambers formed on both sides of the piston in the axial direction; and a flow rate regulating valve interposed in an oil passage that constantly communicates the two hydraulic chambers. An auto hinge for doors characterized by comprising: