JP7109342B2 - floor hinge - Google Patents

Description

The present invention relates to floor hinges.

2. Description of the Related Art Conventionally, there has been known a floor hinge that rotatably supports a door installed in an opening of a building from the floor while being biased in the closing direction of the opening. This type of floor hinge is used by being embedded in the floor surface of an opening of a building. and a hinge case rotatably supported in a state of being biased. In the hinge case, oil is stored inside, and by adjusting the flow rate of the oil, the rotational biasing force to the rotating shaft due to the rotational energy based on the elastic force stored in the compression coil spring when the door is opened is adjusted. A mechanism is provided.

For example, Patent Document 1 below discloses a conventionally known general floor hinge. In the configuration of the floor hinge described in Patent Document 1 below, the inner chamber of a hinge case (casing) is divided into two pressure medium chambers separated by a piston member (piston). With passages for different throttling discharge of the pressure medium from the pressure chamber to be reduced on closing of the door, and arranged in a piston member (piston) to effect the closing movement of the door They are of the type that are connectable to each other by means of safety valves that open at overpressure inside.

JP-A-56-003777

However, in conventionally known general floor hinges represented by the above-mentioned Patent Document 1, a piston member (piston) having a check valve and a forced closing valve and a rod member (rod) are connected by a piston pin. configuration was adopted. In such prior art configurations, there has been a persistent demand in the industry to reduce the number of parts to reduce manufacturing costs.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to reduce manufacturing costs by proposing a configuration that reduces the number of parts of members that constitute a floor hinge. To provide a new floor hinge.

The present invention will be described below. In order to facilitate understanding of the present invention, the reference numbers of the attached drawings are added in parentheses, but the present invention is not limited to the illustrated forms.

A floor hinge (10) according to the present invention includes a hinge case (11) having an oil chamber (12) filled with hydraulic oil, and a hinge case (11) arranged at one end side of the hinge case (11) and connected to a door. A rotating shaft (14) that rotates with the opening and closing operation of the door, a non-circular cam member (15) fixedly installed on the rotating shaft (14), and an outer peripheral surface of the cam member (15). a slide plate (17) which reciprocates in the hinge case (11) in accordance with the rotational movement of the cam member (15) by providing a cam follower (16) arranged to be slidable; ) and a rod member (18) connected to the slide plate (17) at the end of the rod member (18) opposite to the connection side of the slide plate (17). A piston member (19) which is divided into a second oil chamber (12b) and which is reciprocally movable within the oil chamber (12); and the hinge case (11) which forms the oil chamber (12). A compression coil spring that is arranged between the stopper-shaped portion (11a) formed on the inner wall surface of the and the piston member (19) to always exert a biasing force in a fixed direction on the piston member (19) (31) and by adjusting the amount of hydraulic oil transferred between the first oil chamber (12a) and the second oil chamber (12b) accompanying the reciprocating movement of the piston member (19). A floor hinge (10) comprising a control mechanism (11b, 11c, 11d, 20) for controlling the moving speed of a piston member (19), thereby controlling the opening speed or closing speed of the door, A valve member (20) forming part of the control mechanism (11b, 11c, 11d, 20) also serves as connection fixing means between the rod member (18) and the piston member (19). It is characterized by

According to the present invention, it is possible to reduce the number of parts of the members constituting the floor hinge, so it is possible to provide a new floor hinge with reduced manufacturing costs.

It is a figure which shows the external appearance shape of the floor hinge which concerns on this embodiment, the part figure (a) in the figure shows the top view of a floor hinge, and the part figure (b) has shown the side view. FIG. 2 is a diagram for explaining a specific configuration of the floor hinge according to the present embodiment, in which the partial view (a) in the figure shows the AA cross section in FIG. 1, and the partial view (b) shows the B in FIG. -B section is shown. It is a diagram showing a part of the members constituting the floor hinge 10 according to the present embodiment. (b) corresponds to part (b) of FIG. FIG. 4 is a cross-sectional view showing the valve member according to the present embodiment, in which part view (a) in the figure shows a closed state of the valve member having the function of a check valve in the door closing operation, and part view (b) shows an open state. It shows a state in which a valve member having a function of a check valve is opened when the door is operated. It is a figure for performing operation|movement description of the floor hinge which concerns on this embodiment, and especially shows the floor hinge when a door is a fully open state. FIG. 4 is a diagram for explaining the operation of the floor hinge according to the present embodiment, and particularly shows the floor hinge in a state in which the door (not shown) is in the process of closing to a door opening angle of 95 degrees. FIG. 4 is a diagram for explaining the operation of the floor hinge according to the present embodiment, and particularly shows the floor hinge in a state in which the door (not shown) is in the middle of closing operation to the opening angle of 90 degrees. FIG. 4 is a diagram for explaining the operation of the floor hinge according to the present embodiment, and in particular, the door (not shown) closes to an opening angle of 74 degrees, the DA mode ends, and the 1st speed mode starts. Fig. 2 shows the floor hinge in the condition; FIG. 4 is a diagram for explaining the operation of the floor hinge according to the present embodiment, and in particular, when the door (not shown) closes to an opening angle of 15 degrees, the 1st speed mode ends and the 2nd speed mode starts. The floor hinge is shown in the FIG. 10 is a diagram for explaining the operation of the floor hinge according to the present embodiment, and particularly shows the floor hinge when the door (not shown) performs the closing operation up to the fully closed door angle.

Preferred embodiments for carrying out the present invention will be described below with reference to the drawings. In addition, the following embodiments do not limit the invention according to each claim, and not all combinations of features described in the embodiments are essential for the solution of the invention. .

First, a specific configuration of the floor hinge 10 according to the present embodiment will be described with reference to FIGS. 1 to 3. FIG. Here, FIG. 1 is a view showing the external shape of the floor hinge according to the present embodiment, in which part view (a) shows a top view of the floor hinge and part view (b) shows a side view. ing. In addition, FIG. 2 is a diagram for explaining the specific configuration of the floor hinge according to the present embodiment, in which the part (a) in the figure shows the AA cross section in FIG. 1 and the part (b) ) shows the BB section in FIG. FIG. 2 is a diagram showing the state of the floor hinge 10 when the door is fully closed. Furthermore, FIG. 3 is a diagram showing a part of the members constituting the floor hinge 10 according to this embodiment, and the part (a) in the figure corresponds to the part (a) in FIG. , and the subdivision (b) in the figure corresponds to the subdivision (b) of FIG.

A floor hinge 10 according to this embodiment includes a hinge case 11 having an oil chamber 12 filled with hydraulic oil. The hinge case 11 is a member having an external shape of a substantially rectangular parallelepiped. The interior of the hinge case 11 is hollow as an oil chamber 12 filled with hydraulic oil, and an opening that opens the hollow is formed on the right side of the paper surface of FIG. This opening is closed by a plugging member 13, and an oil chamber 12 is formed by closing the cavity.

At one end of the hinge case 11 (on the left side of the paper surface in FIGS. 1 and 2), a rotating shaft 14 is rotatably arranged, which is connected to a door (not shown) and rotates as the door opens and closes. . A substantially heart-shaped non-circular cam member 15 is fixedly installed at substantially the center of the rotating shaft 14 (see FIG. 2).

A cam follower 16 is arranged on the left side of the cam member 15 in FIG. Since the cam follower 16 is arranged so as to be able to slide on the outer peripheral surface of the cam member 15, when the door (not shown) opens and closes, the substantially heart-shaped cam member 15 rotates together with the rotating shaft 14, and the cam member 15 rotates. The outer ring of the cam follower 16 rotates along the outer peripheral surface of the cam member 15 while always maintaining a state of sliding contact with the outer peripheral surface of the cam member 15 . In other words, the cam follower 16 and the slide plate 17 to which the cam follower 16 is fixed are reciprocated in the hinge case 11 in the left-right direction of the plane of FIG. is configured to

A rod member 18 is connected to the slide plate 17 . The rod member 18 is arranged on the slide plate 17 on the opposite side of the side on which the cam follower 16 is installed. and the rod member 18.

A piston member 19 is installed at the end of the rod member 18 opposite to the slide plate 17 connection side. The piston member 19 has the function of dividing the oil chamber 12 formed inside the hinge case 11 into an operating oil chamber 12a as a first oil chamber and a pressure oil chamber 12b as a second oil chamber. It is a member. As described above, when the door (not shown) opens and closes, the slide plate 17 reciprocates in the hinge case 11 in the lateral direction of the paper surface of FIG. The piston member 19 also reciprocates in the oil chamber 12 in the horizontal direction of the paper surface of FIG. When the door is fully closed as shown in FIG. 2, the piston member 19 is arranged at a position where the pressure oil chamber 12b, which is the second oil chamber, is the narrowest, and the first oil chamber, which is the operating pressure chamber 12b. The oil chamber 12a is arranged at the widest position. Further, as the door (not shown) opens from the fully closed state and the door opening angle increases, the piston member 19 moves in the direction to widen the pressure oil chamber 12b, which is the second oil chamber, and It moves in the direction to narrow the working oil chamber 12a, which is the first oil chamber.

Further, the piston member 19 according to this embodiment is provided with a valve member 20 having two functions of a check valve and a forced closing valve as a single member. The valve member 20 allows hydraulic fluid to flow from the hydraulic fluid chamber 12a, which is the first fluid chamber, into the pressure fluid chamber 12b, which is the second fluid chamber, while preventing hydraulic fluid from flowing in the opposite direction. It is a valve element that has the function of a non-return valve that stops. Therefore, when the door (not shown) opens from the fully closed state shown in FIG. 2 and the piston member 19 moves in the oil chamber 12 from the right side to the left side in FIG. The piston member 19 moves within the oil chamber 12 by allowing the hydraulic oil to flow from the hydraulic oil chamber 12a, which is the first oil chamber, into the pressure oil chamber 12b, which is the second oil chamber. It is configured so as not to hinder On the other hand, when the door (not shown) closes from the open state to the fully closed state shown in FIG. 2, the piston member 19 moves in the oil chamber 12 from left to right in FIG. At times, the valve member 20 does not allow hydraulic fluid to flow.

The function of the valve member 20 as a forced closing valve is a function that operates when an abnormal hydraulic pressure is generated in the hydraulic oil in the oil chamber 12, such as when a control mechanism section described later does not function. The floor hinge 10 according to this embodiment can also function as a safety device.

Here, a specific configuration of the valve member 20 according to the present embodiment will be described with reference to FIG. 4 . FIG. 4 is a cross-sectional view showing the valve member according to the present embodiment, and the split view (a) in the figure shows the state in which the valve member having the function of a check valve is closed in the door closing operation, and the split view ( b) shows a state in which the valve member having the function of a check valve is opened during the door opening operation.

The valve member 20 according to this embodiment has a valve seat 23 having a substantially T-shaped cross section. The valve seat 23 has a through hole 23a passing through the center of a substantially T-shaped vertical rod, and a valve body 22 having a substantially T-shaped cross section is inserted into the through hole 23a. ing. An O-ring 24 is installed in the valve body 22, and when the valve body 22 is installed so as to block the through-hole 23a, the O-ring 24 is positioned between the valve seat 23 and the valve body 22 so as to close the through-hole 23a. is closed to block the flow of hydraulic oil between the valve seat 23 and the valve body 22 .

An inner passage 27 is also formed in the valve body 22 so as to pass through the center of the substantially T-shaped vertical rod. This inner passage 27 is formed to pass through the valve body 22 . Further, a side hole 25 is formed in the valve body 22 in a direction perpendicular to the penetrating direction of the inner passage 27, so that hydraulic oil can flow not only through the inner passage 27 but also through this side hole 25. ing. The internal shape of the inner passage 27 is composed of a wide inner diameter portion and a narrow inner diameter portion, and a safety valve 29 and a coil spring 28 are arranged in the wide inner diameter portion. The coil spring 28 is installed with one end fixed by a stopper pin 26 installed on the valve body 22 and the other end sandwiched by the head of the safety valve 29 . Therefore, the coil spring 28 always exerts spring elastic force on the safety valve 29 inside the inner passage 27 , the safety valve 29 is always pressed by the coil spring 28 and the head of the safety valve 29 is in the inner passage 27 . It is configured to close the inner passage 27 by pushing the portion where the inner diameter is narrowed. In addition, the stopper pin 26 installed on the valve body 22 is also used as a member that regulates the movable range of the valve body 22, and prevents the valve body 22 from falling off when it moves within the through hole 23a of the valve seat 23. has the function of

Since the valve member 20 according to the present embodiment has the configuration described above, when the piston member 19 moves in the direction of narrowing the pressure oil chamber 12b, which is the second oil chamber, during the door closing operation, As shown in (a), the valve body 22 receives the hydraulic pressure of the pressure oil chamber 12b side, which is the second oil chamber, and moves toward the working oil chamber 12a side, which is the first oil chamber, relative to the valve seat 23. In this state, the O-ring 24 comes into contact with the end face of the valve seat 23 and the side hole 25 is closed. During the door opening operation in which the piston member 19 moves toward the working oil chamber 12a, which is the first oil chamber, the valve body 22 moves toward the working oil chamber 12a, which is the first oil chamber, as shown in FIG. 4(b). The stopper pin 26 of the valve body 22 comes into contact with the end surface of the valve seat 23 and moves toward the pressure oil chamber 12b, which is the second oil chamber, relative to the valve seat 23 by receiving the hydraulic pressure on the side 12a. As a result, the O-ring 24 moves away from the end face of the valve seat 23 toward the pressure oil chamber 12b, which is the second oil chamber, and the side hole 25 opens. The hydraulic oil in the hydraulic oil chamber 12a, which is the first oil chamber, can flow to the pressure oil chamber 12b, which is the second oil chamber. That is, the inner passage 27 and the side hole 25 of the valve body 22 form a communication hole that communicates the working oil chamber 12a, which is the first oil chamber, and the pressure oil chamber 12b, which is the second oil chamber. . The inner passage 27 of the valve body 22 opens not only to the end face of the valve body 22 on the hydraulic oil chamber 12a side, which is the first oil chamber, but also to the end face of the valve body 22 on the pressure oil chamber 12b side, which is the second oil chamber. However, the opening on the side of the pressure oil chamber 12b is always closed by a safety valve 29 that is pressed and biased toward the pressure oil chamber 12b by a coil spring 28, and the door is forcibly closed by an external force. When the hydraulic pressure on the side of the pressure oil chamber 12b, which is the oil chamber 2, suddenly increases, the increased hydraulic pressure in the pressure oil chamber 12b causes the safety valve 29 to push the coil spring 28 against the urging force of the coil spring 28. While being compressed, it moves toward the working oil chamber 12a to open the opening of the inner passage 27 on the side of the pressure oil chamber 12b.

Now, although the valve member 20 has the configuration and operation as described above, the valve member 20 according to the present embodiment is also characterized by its mounting method. That is, in the valve member 20 according to the present embodiment, a screw groove 23b is formed on the outer peripheral surface of a substantially T-shaped vertical rod of a valve seat 23 having a substantially T-shaped cross section. As shown in FIG. 3, the screw groove 23b is configured to be screwed into a screw hole 18a formed in the axial end portion of the rod member 18 on the side where the piston member 19 is installed. When the valve member 20 is threadedly joined to the rod member 18, the piston member 19 is sandwiched between the shaft end of the rod member 18 and the valve member 20, thereby fixing the piston member 19 to the rod member 18. be able to. In other words, the valve member 20 according to the present embodiment not only has two functions of a check valve and a forced closing valve as a single member, but also functions as connecting and fixing means between the rod member 18 and the piston member 19. It is a component that can be Such a configuration leads to a reduction in the number of parts constituting the floor hinge 10 compared to the conventional technology, and achieves the effect of reducing the manufacturing cost and improving the assembling efficiency.

As shown in FIG. 2, the hinge case 11 includes a pressure oil chamber 12b as a second oil chamber and a hydraulic oil chamber 12a as a first oil chamber in addition to the mechanical members such as the valve member 20. 1st-speed flow path 11b and 2nd-speed flow path 11c, which are connected, and 1st-speed flow path 11b which connects pressure oil chamber 12b, which is the second oil chamber, and working oil chamber 12a, which is the first oil chamber, are separated from each other. A DA channel 11d and the like, which are unique channels, are formed. These mechanism members and flow passages form a control mechanism portion according to the present embodiment, which is a working oil chamber 12a, which is a first oil chamber accompanying the reciprocating movement of the piston member 19, and a second oil chamber. The moving speed of the piston member 19 can be controlled by adjusting the amount of hydraulic oil transferred between the pressure oil chambers 12b, thereby controlling the opening speed or closing speed of the door.

Here, a stopper-shaped portion 11a is formed on the inner wall surface of the hinge case 11 forming the oil chamber 12 (see the partial view (b) in FIG. 2). The stopper-shaped portion 11a is formed at a position slightly away from the connection position between the slide plate 17 and the rod member 18 toward the piston member 19 side. A compression coil spring 31 is arranged between the stopper-shaped portion 11a and the piston member 19 to exert a biasing force on the piston member 19 in a constant direction. That is, in the compression coil spring 31 according to the present embodiment, when the door is fully closed, the coil end portion on the left side of FIG. Since the end portion is in contact with the piston member 19, the piston member 19 is always pressed rightward on the paper surface of FIG. The direction of the urging force exerted by the compression coil spring 31 is a direction in which a load is applied to the opening operation of the door (not shown) when the door is opened from a fully closed state. It is a mechanism that always exerts a constant force against it.

Here, in this embodiment, as a configuration for installing the compression coil spring 31, the cross-sectional shape of the member that contacts the end portion of the compression coil spring 31 is inclined with respect to the direction of the biasing force exerted by the compression coil spring 31. It is characterized by having a slope shape or curved surface shape. The features will be specifically described with reference to FIG.

First, in this embodiment, the member that contacts the end of the compression coil spring 31 on the piston member 19 installation side of the rod member 18 is configured as a stopper member 40 having a truncated conical portion 40a. The stopper member 40 is fixed to the shaft end of the rod member 18 via a connecting pin 41 , and a portion of the truncated cone-shaped portion 40 a of the stopper member 40 is inserted into the inner peripheral portion of the compression coil spring 31 . As a result, the inclined slope of the surface of the truncated cone portion 40a exerts an alignment action on the coil-shaped compression coil spring 31, so that the axial center of the rod member 18 and the biasing direction of the compression coil spring 31 are aligned. It is realized to roughly align and position the compression coil spring 31 .

On the other hand, in the present embodiment, the member that contacts the end of the compression coil spring 31 on the anti-piston member installation side of the rod member 18 has the R-shaped portion 18b. The R-shaped portion 18b is provided on the axial end side of the rod member 18 on the installation side with the slide plate 17, and part of the R-shaped portion 18b is inserted into the inner peripheral portion of the compression coil spring 31. By doing so, the compression coil spring 31 is positioned. It should be noted that this R-shaped portion 18b does not come into contact with the compression coil spring 31 when the floor hinge 10 according to the present embodiment is completed and is in operation. is useful in that it can exhibit the function of aligning with respect to the axis of the rod member 18 .

The configuration of the present embodiment described above includes an end portion of the compression coil spring 31 and a member that contacts the end portion of the compression coil spring 31 (the truncated conical portion 40a of the stopper member 40 and the R-shaped portion 18b of the rod member 18). can be said to be configured to be in line contact with each other. By providing such a configuration, it is possible to realize a configuration in which the compression coil spring 31 is not displaced from the axis of the piston member 19, so that the compression coil spring 31 can stably generate an elastic force. It is possible to provide a floor hinge 10 that allows Further, since the floor hinge 10 according to the present embodiment has the above configuration, it is possible to provide the floor hinge 10 with excellent assembling properties.

In particular, in the prior art, the piston member is directly connected to the rod member by means of a connecting pin, and receives elastic force from the compression coil spring in a swingable state with respect to the rod member. The piston member is displaced at the time of assembling, and there is a problem that it cannot be easily assembled. However, in this embodiment, the member with which the compression coil spring 31 contacts is the stopper member 40 separate from the piston member 19, and the piston member 19 is attached to the rod member 18 by the valve member 20. Therefore, the floor hinge 10 can be easily assembled without causing the piston member 19 to be displaced during assembly.

The specific configuration of the floor hinge 10 according to this embodiment has been described above. Next, the operation of the floor hinge 10 according to the present embodiment will be described with reference to FIGS. 5 to 10. FIG. 5 to 10 are diagrams for explaining the operation of the floor hinge according to this embodiment. In particular, FIG. 5 shows the floor hinge when the door is fully open, and FIG. The floor hinge is shown when the door (not shown) is in the process of closing up to a 95-degree opening angle, and FIG. 7 shows the door (not shown) closing up to a 90-degree opening angle. FIG. 8 shows the floor hinge in an intermediate state, and FIG. 8 shows a state in which the door (not shown) closes to an opening angle of 74 degrees, the DA mode ends, and the 1st speed mode starts. 9 shows the floor hinge, and FIG. 9 shows the floor hinge when the door (not shown) closes to an open door angle of 15 degrees, ends the first speed mode, and starts the second speed mode. FIG. 10 shows the floor hinge when the door (not shown) has closed to the full door closing angle.

First, when the door (not shown) is fully open, in the floor hinge 10 according to the present embodiment, the piston member 19 is arranged at the position where the pressure oil chamber 12b, which is the second oil chamber, becomes the widest. The hydraulic oil chamber 12a, which is the first oil chamber, is arranged at the narrowest position. At this time, the compression coil spring 31 is in the most compressed state, but one end side of the compression coil spring 31 (the right side of the paper surface in FIG. 5) is held by the truncated conical portion 40a of the stopper member 40 in line contact. Therefore, the compression coil spring 31 does not shift or buckle due to the positioning effect of the alignment action.

When the closing operation of the door (not shown) is continued from the state of FIG. 5, as shown in FIGS. Move to the right side of the page in FIGS. 6 to 8 . At this time, the valve member 20 does not allow hydraulic fluid to flow from the pressure oil chamber 12b, which is the second oil chamber, into the hydraulic oil chamber 12a, which is the first oil chamber. This is performed by the DA flow path 11d. Therefore, from FIG. 5, in which the door (not shown) is fully open, to FIG. 8, in which the door (not shown) closes to an opening angle of 74 degrees, the DA mode ends and the 1st speed mode starts. During this period, a DA (delayed action) mode is executed in which a door (not shown) is slowly closed.

Thereafter, until the state shown in FIGS. 8 to 9, the first-speed flow path 11b circulates hydraulic oil to quickly operate the door (not shown), and furthermore, the fully closed state shown in FIGS. 9 to 10 Until then, the door closing operation is performed using the second-speed flow path 11c for slowly and surely operating the door (not shown) to realize the closed state of the door. 5 to 10, in the floor hinge 10 according to the present embodiment, the end of the compression coil spring 31 and the stopper member 40 contacting the end of the compression coil spring 31 Since the truncated conical portion 40a is in line contact with the piston member 19, the compression coil spring 31 does not shift from the axial center of the piston member 19, and stable operation can be performed. It has become.

Although the preferred embodiments of the present invention have been described above, the technical scope of the present invention is not limited to the scope described in the above embodiments. Various changes or improvements can be added to the above embodiments. It is clear from the description of the scope of the claims that forms with such modifications or improvements can also be included in the technical scope of the present invention.

10 floor hinge, 11 hinge case, 11a stopper shape portion, 11b 1st speed channel (part of control mechanism portion), 11c 2nd speed channel (part of control mechanism portion), 11d DA channel (of control mechanism portion part), 12 oil chamber, 12a working oil chamber (first oil chamber), 12b pressure oil chamber (second oil chamber), 13 plug member, 14 rotating shaft, 15 cam member, 16 cam follower, 17 slide plate, 18 rod member (member in contact with the end of the compression coil spring), 18a screw hole, 18b R-shaped portion (curved surface shape), 19 piston member, 20 valve member (part of control mechanism portion), 22 valve body , 23 valve seat, 23a through hole, 23b thread groove, 24 O-ring, 25 side hole, 26 stopper pin, 27 inner passage, 28 coil spring, 29 safety valve, 31 compression coil spring, 40 stopper member (end of compression coil spring 40a truncated conical portion (slope shape), 41 connection pin.

Claims (1)

a hinge case having an oil chamber filled with hydraulic oil;
a rotary shaft arranged at one end of the hinge case and connected to the door so as to rotate with the opening and closing operation of the door;
a non-circular cam member fixedly installed on the rotating shaft;
a slide plate that reciprocates within the hinge case according to the rotational movement of the cam member by having a cam follower that is disposed so as to be slidably contactable with the outer peripheral surface of the cam member;
a rod member connected to the slide plate;
It is installed at the end of the rod member opposite to the slide plate connection side, divides the oil chamber into a first oil chamber and a second oil chamber, and is installed so as to be reciprocally movable within the oil chamber. a piston member that
A compression coil spring that is disposed between a stopper-shaped portion formed on an inner wall surface of the hinge case that forms the oil chamber and the piston member, thereby always exerting an urging force in a fixed direction on the piston member. When,
The moving speed of the piston member is controlled by adjusting the amount of hydraulic oil transferred between the first oil chamber and the second oil chamber accompanying the reciprocating movement of the piston member, thereby opening the door. a control mechanism that controls the door speed or the door closing speed;
A floor hinge comprising
a valve member forming a part of the control mechanism unit also serves as connection fixing means between the rod member and the piston member ;
A screw groove is formed in the outer peripheral surface of the valve member, and a screw hole into which the screw groove can be screwed is formed in the shaft end of the rod member,
When the screw groove of the valve member is screwed into the screw hole of the rod member, the piston member is sandwiched between the valve member and the axial end portion of the rod member, so that the rod member and the piston A floor hinge characterized by being connected and fixed to a member .

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