JP5493184B2 - Cylinder device, spring damper and door closer using the same - Google Patents

Description

  The present invention relates to a cylinder device that assists in opening and closing a door, a spring damper, and a door closer using the same.

A cylinder device such as a spring damper is linked to the hinged door, and the door is automatically closed by adjusting the opening and closing speed by applying spring force and damping force to the opening and closing of the door. There is known a door closer that holds a door in an open position. Conventionally, as a door closer using a cylinder device such as this type of spring damper, there is one described in Patent Document 1, for example.
JP 2008-2124 A

  In the door closer described in Patent Document 1, the opening degree of the door is obtained by linking a spring damper, which allows the spring force of the compression coil spring to act in the extending direction of the operating rod, between the door of the opening door and the door frame. Accordingly, when the door is in the vicinity of the closed position, a force in the closing direction is applied, and when the door is in the vicinity of the fully open position, the door is held in the open position.

  However, the one described in Patent Document 1 has a problem that a relatively strong spring force is generated when the spring damper is at the intermediate position where the spring damper is most shortened.

  It is an object of the present invention to provide a cylinder device, a spring damper, and a door closer using the same, which have solved the above problems.

In order to solve the above problems, a cylinder device according to the invention of claim 1 includes a cylindrical cylinder member,
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, and when the protruding length of the rod from the cylinder member is equal to or longer than a predetermined length, the rod can be stroked with a spring force applied in a direction in which the rod protrudes. A spring mechanism that allows the rod to stroke in a state where no spring force is applied to the rod when less than a predetermined length ;
A damping force generating mechanism that applies a damping force to the movement of the rod in the axial direction;
Working fluid is sealed in at least a part of the inside of the cylinder member,
A piston that moves in the working fluid inside the cylinder member is connected to the rod,
The damping force generating mechanism is provided with damping force adjusting means for generating a damping force by applying a flow resistance to a flow path of a working fluid provided in the piston and adjusting the damping force from the outside of the cylinder member. And
The damping force adjusting means includes a shutter that is provided so as to be relatively rotatable with respect to the piston, and that changes a flow passage area of the working fluid flow passage according to the rotational position .
A cylinder device according to an invention of claim 9 is a cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, and when the protruding length of the rod from the cylinder member is equal to or longer than a predetermined length, the rod can be stroked with a spring force applied in a direction in which the rod protrudes. A spring mechanism that allows the rod to stroke in a state where no spring force is applied to the rod when less than a predetermined length;
A damping force generating mechanism that applies a damping force to the movement of the rod in the axial direction;
Working fluid is sealed in at least a part of the inside of the cylinder member,
A piston that moves in the working fluid inside the cylinder member is connected to the rod,
The damping force generation mechanism generates a damping force by applying a flow resistance to the flow path of the working fluid provided in the piston,
The inner circumferential surface of the cylinder member on which the piston slides is provided with a bypass recess that forms a gap with the piston when the protruding length of the rod is within a predetermined range. And

The door closer according to the invention of claim 11 is in an extended state between the door of the hinged door and the door frame when the door is in the closed position and the open position, and is in a position between the closed position and the open position. A door closer connected to be shortened to assist in opening and closing the door,
A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
When the protruding length of the rod from the cylinder member is not less than a predetermined length provided inside the cylinder member, the rod can be stroked with a spring force applied in the protruding direction of the rod, When the length is less than a predetermined length, a spring mechanism is provided that enables the rod to stroke in a state where no spring force is applied to the rod.

The door closer according to the invention of claim 13 is in an extended state between the door of the hinged door and the door frame when the door is in the closed position and the open position, and is in an intermediate position between the closed position and the open position. A door closer connected to be in a shortened state to assist in opening and closing the door,
A cylinder filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder, and one end protruding from an end of the cylinder;
A piston that is coupled to the rod so as not to rotate around an axis and divides the cylinder into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston, and changes a flow passage area of the communication path according to the rotation position;
An engagement member that is fixed so as not to rotate around the axis inside the cylinder, and engages with the shutter when the rod is moved to the stroke end to fix the shutter in the rotational direction with respect to the cylinder. When,
When the protruding length of the rod from the cylinder is equal to or longer than a predetermined length, the rod can be stroked in a state in which a spring force in the protruding direction is applied to the rod, and when the protruding length is less than the predetermined length, A spring mechanism is provided that enables the rod to stroke in a state where no spring force is applied.

The door closer according to the invention of claim 14 is a door closer connected between the door of the hinged door and the door frame to assist in opening and closing the door,
A cylinder member filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
A piston that is coupled to the end of the rod so as not to rotate about an axis and divides the inside of the cylinder member into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston on the rod side, and changes a flow passage area of the communication path according to the rotation position;
It is fixed to the middle part of the cylinder member so as not to rotate around the axis, the rod is penetrated so as to be movable in the axial direction, a flow path for hydraulic fluid is formed along the axial direction of the rod, and the rod protrudes And an engagement member that engages with the shutter and fixes the shutter in the rotational direction with respect to the cylinder member when moved to the stroke end in the direction.

According to a fifteenth aspect of the present invention, a spring damper includes a first cylinder in which hydraulic oil is filled and a piston is fitted, and a second cylinder in which a cylindrical clutch ring is slidably fitted. And the open ends of the first and second cylinders are closed by the first and second lid plugs, respectively, and a clutch ring is fitted to the outside, and the second lid plug and the above-mentioned A piston rod having the piston attached to the inner end thereof is provided through the partition wall, and the clutch balls are accommodated in at least one ball housing hole penetrating the clutch ring in the radial direction, respectively. An annular inner side in which a part of the clutch ball can be engaged at predetermined positions in the axial direction of the inner peripheral surface of the second cylinder and the outer peripheral surface of the piston rod in the second cylinder, and A side clutch groove is formed, a compression coil spring is elastically mounted between the partition wall and the clutch ring, and an orifice device of a type for buffering when the piston rod is extended is provided in the piston in the first cylinder, When the clutch ball straddles the inner clutch groove and the ball housing hole and the piston rod is free from the clutch ring, the inner wall of the first cylinder fitted with the piston is enlarged to form a relief groove. It is characterized by.

According to a sixteenth aspect of the present invention, there is provided a spring damper comprising: a first cylinder that is filled with hydraulic oil and in which a piston is fitted; and a second cylinder in which a cylindrical clutch ring is slidably fitted. The first and second cylinders are connected to each other along the direction and through the partition wall, and the opening ends of the first and second cylinders are closed by the first and second lid plugs, respectively, and the clutch ring is fitted to the outside, and the second lid plug And a piston rod having the piston mounted on the inner end thereof, penetrating the partition wall, and storing the clutch balls movably in the radial direction in at least one ball storage hole penetrating the clutch ring in the radial direction, On the other hand, each of the inner circumferential surfaces of the second cylinder and the outer circumferential surface of the piston rod in the second cylinder has an annular inner surface in which a part of the clutch ball can be engaged at predetermined positions in the axial direction. And an outer clutch groove, and a compression coil spring is mounted between the second lid plug and the clutch ring, and an orifice device of the type that cushions the piston in the first cylinder when the piston rod contracts. And when the clutch ball straddles the inner clutch groove and the ball housing hole and the piston rod is free from the clutch ring, the inner wall of the first cylinder fitted with the piston is enlarged in diameter and the escape groove Is formed.

  According to the cylinder device and the door closer according to the present invention, it is possible to obtain desired characteristics for assisting the opening and closing of the door.

  In the spring damper according to the present invention configured as described above, when the door starts to close and reaches a predetermined angle, the clutch ball straddles the outer clutch groove and the ball storage hole, The piston rod and the piston rod are integrally connected, and thereafter, the piston orifice device is actuated to close the door while being buffered. Therefore, since the door is buffered before the door is completely closed and the closing speed is reduced, so-called finger padding is effectively prevented, and when the door is opened, there is no conventional opening angle above a certain level. Acts as a door opener. This means that the function of a stopper that holds the opening angle of the door can also be provided. In addition, when the clutch ball straddles between the outer clutch groove and the ball storage hole of the clutch ring and the piston rod is free from the clutch ring, the elastic force of the compression coil spring of the piston rod does not act, so the door opening / closing operation There are various effects such as a very small force.

A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, when a protruding length of the rod from the cylinder member is equal to or longer than a predetermined length, a spring force is applied, and when less than a predetermined length, no spring force is applied to the rod. A cylinder device comprising a spring mechanism.

It is connected between the door of the hinged door and the door frame so that when the door is in the closed position and the open position, it is in an extended state, and when it is in a position between the closed position and the open position, it is in a shortened state. , A door closer for assisting in opening and closing the door,
A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, when a protruding length of the rod from the cylinder member is a predetermined length or more, a spring force is applied in a protruding direction of the rod, and when the rod is less than a predetermined length, the rod A door closer comprising a spring mechanism that does not impart spring force to the door closer.

Between the door of the hinged door and the door frame, when the door is in the closed position and the open position, it is in an extended state, and when it is in an intermediate position between the closed position and the open position, it is connected so as to be in a shortened state, A door closer for assisting in opening and closing the door,
A cylinder filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder, and one end protruding from an end of the cylinder;
A piston that is coupled to the rod so as not to rotate around an axis and divides the cylinder into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston, and changes a flow passage area of the communication path according to the rotation position;
An engagement member that is fixed so as not to rotate around the axis inside the cylinder, and engages with the shutter when the rod is moved to the stroke end to fix the shutter in the rotational direction with respect to the cylinder. When,
A spring mechanism that applies a spring force in a protruding direction to the rod when the protruding length of the rod from the cylinder is equal to or greater than a predetermined length, and does not apply a spring force to the rod when the rod is less than a predetermined length; A door closer.

A door closer connected between the door of the hinged door and the door frame to assist in opening and closing the door,
A cylinder member filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
A piston that is coupled to the end of the rod so as not to rotate about an axis and divides the inside of the cylinder member into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston on the rod side, and changes a flow passage area of the communication path according to the rotation position;
It is fixed to the middle part of the cylinder member so as not to rotate around the axis, the rod is penetrated so as to be movable in the axial direction, a flow path for hydraulic fluid is formed along the axial direction of the rod, and the rod protrudes And an engaging member that engages with the shutter and fixes the shutter in the rotational direction with respect to the cylinder member when moved in the direction to the stroke end.

  In the spring damper according to the present invention, the first cylinder filled with the hydraulic oil and fitted with the piston and the second cylinder fitted with the cylindrical clutch ring so as to be slidable are arranged along the axial direction. And the first and second cylinders are closed by the first and second lid plugs, respectively, and a clutch ring is fitted on the outside, and the second lid plug and the partition wall are connected. A piston rod having the piston mounted on the inner end thereof is provided, and at least one ball storage hole penetrating the clutch ring in the radial direction is accommodated in each of the clutch balls so as to be movable in the radial direction. Annular inner side and outer side where a part of the clutch ball can be engaged at predetermined positions in the axial direction of the inner peripheral surface of the two cylinders and the outer peripheral surface of the piston rod in the second cylinder. Since the clutch groove is formed, the operating force is switched by straddling the clutch ball between the inner clutch groove and the ball storage hole of the clutch ring, or between the ball storage hole and the outer clutch groove. The range of use was expanded by rationalizing the control mechanism of the spring damper.

An embodiment of the present invention will be described below with reference to the drawings.
In addition, this Example shows the case where the spring damper of this invention is applied to the opening / closing control of a swing door.

  In FIG. 1, reference numeral 1 denotes an entire cylinder of a spring damper. This cylinder 1 is filled with hydraulic oil and a piston 2 is slidably fitted therein, and a cylindrical clutch ring 4 is provided. A second cylinder 5 that is slidably fitted is provided along the axial direction and via a partition wall 6.

  In the illustrated embodiment, the partition wall 6 is composed of a cylinder cylinder step and a partition wall plug (not numbered) that fits the piston rod 7 in a fluid-tight manner.

  The open ends of the first and second cylinders 3 and 5 are closed by first and second lid plugs 8 and 9, respectively.

  The piston rod 7 attached to the cylinder 1 passes through the lid plug 9 and the partition wall 6, and the piston 2 is attached to the inner end facing the first cylinder 3.

  In addition, the thick-walled cylindrical clutch ring 4 is fitted into a portion of the piston rod in the second cylinder 5.

  The clutch ring 4 has a plurality of (four in the illustrated embodiment) ball receiving holes 11 and 11 formed at equal angular intervals so as to penetrate the cylindrical portion in the radial direction. Clutch balls 12 are accommodated in the accommodating holes 11 so as to be movable in the radial direction of the clutch ring.

On the other hand, annular inner and outer clutch grooves into which a part of the clutch ball 12 can be engaged respectively at predetermined positions in the axial direction of the inner peripheral surface of the second cylinder 5 and the outer peripheral surface of the piston rod 7 in the second cylinder. 13 (see FIG. 4) and 14 are formed.
In the illustrated embodiment, each clutch groove has a trapezoidal cross section.

  A compression coil spring 15 is elastically mounted between the partition wall 6 and the clutch ring 4, and the clutch ring 4 escapes from the second cylinder 5 to the left in FIG. 1, the clutch ball 12 straddles between the inner clutch groove 13 and the ball storage hole 11 of the clutch ring in the state shown in FIG. Therefore, the elastic force of the compression coil spring is carried by the second cylinder 5.

  On the other hand, the piston 2 in the first cylinder is provided with an orifice device that cushions when the piston rod 7 is extended.

Such an orifice device is well known and will not be described in detail. For example, the orifice device is constituted by a flexible orifice plate with an orifice hole that covers the opening on the left side in FIG. 1 of the communication hole 16 penetrating the piston in the axial direction. be able to.
In addition, you may use the structure of the piston part of Example 3 mentioned later for this orifice apparatus.

  Further, as shown in FIG. 1, when the clutch ball 12 straddles the inner clutch groove 13 and the ball storage hole 11 and the piston rod 7 is free from the clutch ring 4, The inner wall of one cylinder 3 is expanded in diameter, and a relief groove 17 is formed.

  In FIG. 1, reference numeral 18 denotes an air chamber formed in the first cylinder 3, and this air chamber 18 is partitioned liquid-tightly from the first cylinder 3 by an idler plug 19, so that the operating oil is changed due to temperature changes. The air chamber absorbs expansion and contraction, but this air chamber is well known in the art and is not the gist of the present invention, so a more detailed description is omitted.

  As shown in FIG. 3, the spring damper according to one embodiment of the present invention configured as described above has, for example, a piston rod with a tip 21 attached to one of a door 22 or a door frame 23 via a bracket and a base end of a cylinder. 4 is connected to the other of the door 22 or the door frame 23 via a bracket so as to be swingable.

The positional relationship of each member of the spring damper at this time is as shown in FIG. 4, for example.
Therefore, when the door is opened, the piston rod 7 is pushed into the cylinder 1 as shown in FIG. 5, so that the piston rod 7 of the spring damper moves rightward as shown in FIG.

  At this time, the compression coil spring 15 of the piston rod 7 is pushed in the direction to compress, but the orifice plate (not shown) of the piston is elastically deformed, and the hydraulic oil is passed from the right to the left through the communication hole 16 (see FIG. 6). Therefore, the piston rod 7 is lightly pushed into the cylinder 1 without being buffered.

  When the piston rod 7 is in the position shown in FIG. 6, the inner and outer clutch grooves 13, 14 are aligned in the axial direction, and so far spanned between the outer clutch groove 14 and the ball storage hole 11. The clutch ball 12 straddles between the inner clutch groove 13 and the ball storage hole 11, and the piston rod 7 is released from the clutch ring 4 and becomes free.

  Therefore, the piston rod 7 is pushed lightly into the cylinder 1 because it is not necessary to compress the compression coil spring 15.

  When the door is further opened, as shown in FIG. 7, the rotation shaft 25 of the hinge of the door, the tip 21 of the piston rod, and the base end 24 of the cylinder are aligned in a straight line, and as shown in FIG. It is pushed deepest into the cylinder (so-called dead point).

  When the door is further opened from the state shown in FIG. 7, the piston rod 7 and the piston 2 are moved leftward from the state shown in FIG. 1, so that the orifice device is activated and the piston 2 is braked. However, at this time, since the inner peripheral surface of the first cylinder 3 around the piston 2 is enlarged, the hydraulic oil flows between the outer peripheral surface of the piston 2 and the escape groove 17 from the left to the right in FIG. The piston rod 7 moves to the left without load.

  Eventually, the piston rod 7 extends to the position shown in FIG. 6. At this time, the door 22 opens about 70 degrees as shown in FIG. 8, and at the same time, the clutch ball 12 moves between the outer clutch groove 14 and the ball storage hole 11. The piston rod 7 and the clutch ring 4 are integrally connected.

  From this time, the piston rod 7 receives the elastic force of the compression coil spring 15 and simultaneously operates the orifice device, and the piston 2 moves to the small diameter portion of the first cylinder 3, so the door connected to the piston rod 7. 22 is urged in the opening direction while being buffered.

  That is, the spring damper according to the present invention is a novel door opener (door automatic opening device).

  As shown in FIG. 9, the piston rod 7 extends to the maximum extent as shown in FIG. 9. At this time, the piston rod 7 serves as a stopper of the door 22.

  When the door is closed from this state, the piston rod 7 is pushed into the cylinder while compressing and compressing the compression coil spring 15 as shown in FIG. 4. At this time, the orifice device does not operate, so the door is lightly closed. To go.

  When the door is further closed, the spring damper is pushed to the state shown in FIGS. 6 and 1, and when the door moves further in the closing direction than the state shown in FIG. 7 (the spring damper is in the state shown in FIG. 1), this time. The piston rod 7 of the spring damper starts to extend, and from the state shown in FIG. 6, for example, from the state where the door opening angle is about 20 degrees, this time the piston is braked in the door closing direction.

  In other words, the spring damper now operates as a door closer, completely closing the door in the state shown in FIG. 4 and holding the closure elastically.

  In the illustrated embodiment, the compression coil spring 15 is elastically mounted between the partition wall 6 and the clutch ring 4, but this may be elastically mounted between the second lid plug 9 and the clutch ring 4. For example, a spring damper that cushions the piston rod when it contracts can be used (not shown).

  However, at this time, the formation positions of the inner and outer clutch grooves 13 and 14 in the length direction of the piston 2 are appropriately set according to the set extension amount of the piston.

A third embodiment of the present invention will be described with reference to FIGS.
FIG. 10 shows a longitudinal sectional view of the cylinder device according to this embodiment. As shown in FIG. 10, in the cylinder device 30, a rod guide 32 whose inner peripheral portion is a bearing that slides with the piston rod 40 is inserted into the opening end portion of the substantially bottomed cylindrical cylinder member 31. The cylinder member 31 is fixed by caulking the opening end. Inside the rod guide 32, an oil seal 33 made of rubber and having a metal ring embedded therein is attached to seal the inside and outside of the cylinder member. Further, an intermediate rod guide 34 is attached to the inside of the intermediate portion of the cylinder member 31, and the intermediate rod guide 34 causes the inside of the cylinder member 31 to be connected to the cylinder portion 35 on the bottom side and the rod guide portion 36 on the opening side. It is partitioned. The intermediate rod guide 34 may be a bearing that slides with the piston rod 40 in the same manner as the rod guide 32, but in this case, the coaxiality between the rod guide 32 and the intermediate rod guide 34 needs to be increased. The intermediate rod guide 34 is more manufacturable when the inner diameter is larger than that of the rod guide 32. Furthermore, a free piston 37 is slidably fitted into the cylinder portion 35, and the inside of the cylinder portion 35 is partitioned into a gas chamber 38 on the bottom side and a cylinder chamber 39 on the intermediate rod guide 34 side by the free piston 37. ing.

  A piston rod 40 is inserted into the cylinder member 31 through the rod guide 32 and the oil seal 33 slidably and liquid-tightly. The proximal end side of the piston rod 40 extends through the intermediate rod guide 34 to the inside of the cylinder chamber 39, and a piston 41 constituting a damping force generating mechanism is connected to the distal end portion thereof. The piston 41 is slidably fitted to the cylinder portion 35, and an O-ring 41A as a piston seal member on the outer periphery thereof is used to move the inside of the cylinder chamber 39 between the rod side chamber 39A on the intermediate rod guide 34 side and the free piston 37 side. It is divided into two chambers, the bottom side chamber 39B. The cylinder chamber 39 and the rod guide 36 are filled with hydraulic fluid, and the gas chamber 38 is filled with low-pressure gas of about atmospheric pressure. The gas of about atmospheric pressure is a gas introduced into the gas chamber when the piston rod 40 has the maximum length. Therefore, at the time of use, it may be higher than atmospheric pressure depending on temperature conditions and the like.

The gas pressure may be slightly higher depending on the required characteristics of the cylinder device. However, if the gas pressure is high, some spring force is generated in the free section described later. A gas pressure with a smaller force than the friction on the mounting side is desirable.
Furthermore, the gas chamber may be opened to the atmosphere. In this case, it is better to provide a filter in the hole opened to the atmosphere.

  An enlarged view of the vicinity of the intermediate rod guide 34 and the piston 41 of the cylinder device 30 is shown in FIG. 13, and an enlarged view of the end surface of the piston 41 on the intermediate rod guide 34 side is shown in FIG. As shown in FIGS. 13 and 14, the base end portion of the piston rod 40 is formed with a guide portion 42 with a reduced circular section and a mounting portion 43 with a further reduced diameter. The attachment portion 43 of the piston rod 40 passes through the attachment opening 44 having substantially the same shape as the attachment portion 43 at the center of the piston 41, and the piston rod 40 is coupled to the piston 41 by caulking the tip. The attachment portion 43 and the attachment opening 44 have a shape with a chamfered side surface portion, whereby the piston rod 40 and the piston 41 are also fixed in the rotational direction.

  In the piston 41, a communication passage 45 that allows the rod side chamber 39A and the bottom side chamber 39B to communicate with each other is penetrated along the axial direction. In this embodiment, the communication passage 45 is arranged at three locations at equal intervals along the circumferential direction of the piston 41 as shown in FIG. A disc-shaped shutter 46 shown in FIG. 15 is attached to the end of the piston 41 on the intermediate rod guide 34 side. The shutter 46 is rotatably supported with respect to the piston 41 by inserting the guide portion 42 of the piston rod 40 into the circular central opening 47. A disc spring 48 is interposed between a step formed on the base of the guide portion 42 of the piston rod 40 and the shutter 46, and the shutter 46 is pressed against the piston 41 by the spring force of the disc spring 48. It can move in the axial direction against the spring force.

  A plurality of orifice passages 49 having different diameters are penetrated through a portion of the shutter 46 opposite to the piston communication passage 45, and one of the plurality of orifice passages 49 is communicated by rotating the shutter 46. By selectively communicating with 45, the flow passage area of the communication passage 45 can be adjusted. At this time, the orifice passage 49 may be communicated with any of the three communication passages 45, and the remaining communication passage 45 is closed by the shutter 46. In the present embodiment, orifice passages 49 having three different diameters are provided, and the flow passage area of the communication passage 45 can be adjusted in three stages according to the rotational position of the shutter 46.

  Note that if the number of orifice passages 49 is increased, the increased channel cross-sectional area can be obtained. Further, when a very small flow path area is required, the orifice passage may be eliminated, and a leak from the contact surface between the shutter 46 and the piston 41 may be regarded as the orifice passage. In this case, a flow path may be formed by positively providing a groove on the contact surface between the shutter 46 and the piston 41.

A plurality of circular detent recesses 50 are formed along the circumferential direction on the outer peripheral portion of the end surface of the piston 41 on the intermediate rod guide 34 side, and a portion facing the detent recess 50 is formed on the outer peripheral portion of the end surface of the shutter 46. A substantially hemispherical detent convex portion 51 protrudes from the bottom. The detent concave portion 50 and the detent convex portion 51 constitute a rotational position indexing means, and by their engagement, the rotation of the shutter 46 in which the communication passage 45 of the piston 41 and the selected orifice passage 49 of the shutter 46 communicate with each other. The position can be determined and maintained. Further, when the disc spring 48 is bent and the shutter 46 moves in the axial direction, the engagement between the detent concave portion 50 and the detent convex portion 51 is released, and the shutter 46 can be rotated. In the present embodiment, the shutter 46 is provided with three detent convex portions 51 at equal intervals along the circumferential direction, and three orifice passages 49 are indexed to each of the three detent convex portions 51. Therefore, three detent recesses 50 are necessary, and therefore, three detent recesses 50 are arranged at three locations on the piston 41, and a total of nine detent recesses 50 are provided. In addition, rectangular notches 52 are provided at two locations along the diameter direction on the outer periphery of the shutter 46.
In addition, the detent convex part 51 may embed a steel ball in the shutter 46, or may be configured by the shutter itself by forging the shutter 46 or by press molding or cutting. Further, the shape may be a cone or the like as long as the shutter 46 can rotate smoothly.

  Referring to FIG. 13, the intermediate rod guide 34 has an annular groove 53 formed in the outer peripheral portion, and a rotation-preventing recess 54 is provided in a part of the bottom of the annular groove 53. Then, the intermediate rod guide 34 is fixed in the axial direction by crimping the cylinder member 31 from the outer peripheral side to project the curled portion 55 on the inner peripheral portion and inserting the curled portion 55 into the annular groove 53. Further, a part of the curled portion 55 is caulked from the outside to project the anti-rotation convex portion 56 inward, and the anti-rotation convex portion 56 is inserted into the anti-rotation concave portion 54 to fix the intermediate rod guide 34 in the rotation direction. doing. In the intermediate rod guide 34, two engagement convex portions 57 protrude from the two notches 52 of the shutter 46 attached to the piston 41. In FIG. 13, only one of the two engaging convex portions 57 is shown because of the broken position. Then, as shown in FIG. 12, when the piston rod 40 is extended and the engagement convex portion 57 of the intermediate rod guide 34 and the notch 52 of the shutter 46 are engaged, the intermediate rod guide 34 moves the shutter 46 to the cylinder member. The shutter 46 can be rotated with respect to the piston 41 by functioning as an engaging member that is fixed in the rotational direction with respect to 31 and rotating the cylinder member 31 and the piston rod 40 relative to each other. The intermediate rod guide 34 has a gap with the piston rod 40, and a flow path for hydraulic fluid is formed between the inside of the rod guide portion 36 and the cylinder chamber 39. .

  In addition, the shutter 46 attached to the piston 41 adjusts the flow area of the communication passage 45 of the piston 41 by the above-described orifice passage 49, and also functions as a valve body of a check valve. That is, the shutter 46 moves in the axial direction against the spring force of the disc spring 48 with respect to the flow of the hydraulic fluid from the bottom side chamber 39B side to the rod side chamber 39A side of the communication passage 45, and is separated from the end face of the piston 41. By doing so, the flow between the shutter 46 and the piston 41 becomes a flow path, and flow in this direction is allowed without giving flow resistance by the orifice passage 49.

Referring to FIG. 10, a bypass recess 58 extending over a predetermined range L along the axial direction is formed on the inner peripheral surface of the cylinder portion 35 of the cylinder member 31. In the present embodiment, the bypass recesses 58 are provided at three locations at equal intervals along the circumferential direction of the cylinder portion 35. When the piston 41 is in the range L of the bypass recess 58, a gap is generated between the bypass recess 58 and the piston 41, and the hydraulic fluid is transferred between the rod side chamber 39A and the bottom side chamber 39B by this gap. Circulate with almost no distribution resistance.
In addition, the intermediate rod guide 34 side end portion of the bypass recess 58 is set so that the cross-sectional area of the gap between the piston 41 and the piston 41 is gradually reduced, thereby reducing the oil hammer when the bypass recess 58 is closed. can do.

The rod guide portion 36 is provided with a spring mechanism B that applies a spring force to the piston rod 40. The configuration of the spring mechanism B will be described with reference to FIG. A cylindrical guide sleeve 59 is inserted and fitted into the cylinder member 31, and both end portions thereof are in contact with the oil seal 33 and the intermediate rod guide 34 and fixed in the axial direction. An inner circumferential clutch groove 60 that is an inner circumferential groove is formed in an intermediate portion of the guide sleeve 59. In this embodiment, the guide sleeve 58 is divided into two guide sleeves 59A and 59B at the end on the intermediate rod guide 34 side of the inner peripheral clutch groove 60 in consideration of the workability of the inner peripheral clutch groove 60. These may be integrally formed. An outer peripheral clutch groove 61 is formed in the piston rod 40 at an intermediate portion of the portion facing the guide sleeve 58. Side portions of the inner peripheral clutch groove 60 and the outer peripheral clutch groove are formed in a tapered shape.
The guide sleeve 59 is preferably made of metal in terms of strength, but it is better to use reinforced resin for weight reduction. Alternatively, the guide sleeve 59 may not be provided, and the cylinder member 31 and the guide sleeve 59 may be shared by increasing the diameter of only the portion corresponding to the inner circumferential clutch groove 60 of the cylinder member 31.

Between the guide sleeve 59 and the piston rod 40, a cylindrical clutch ring 62 which is a holding member for a ball 64 (spherical body) made of a steel ball is slidably fitted thereto. The clutch ring 62 has the same structure as that shown in FIG. 2, and a plurality of ball holes 63 penetrating in the radial direction are radially arranged on the side wall thereof, and each ball hole 63 has a diameter. A ball 64 that is substantially equal to the ball hole 63 and larger than the thickness of the clutch ring 62 is slidably inserted. The inner clutch groove 60 of the guide sleeve 58 and the outer clutch groove 61 of the piston rod 40 have substantially the same depth, and the diameter of the ball 64 depends on the thickness of the side wall of the clutch ring 62, the outer groove 60, and the inner circumference. It is equal to the sum of the depth of the groove 61. Thus, when the clutch ring 62 into which the ball 64 is inserted is inserted between the guide sleeve 58 and the piston rod 40, the ball 64 is always inserted into at least one of the outer circumferential groove 60 and the inner circumferential groove 61. It becomes. A compression coil spring 65, which is a spring means, is interposed between the intermediate rod guide 34 and the clutch ring 62, and constantly urges the clutch ring 62 toward the oil seal 33 side.
Note that the ball 64 does not necessarily have to be a sphere, and may be, for example, an annular ring having a circular cross section divided at about three circumferential directions.

  The arrangement of the bypass recess 58 of the cylinder part 35 and the inner peripheral clutch groove 60 of the guide sleeve of the spring mechanism B and the inner peripheral groove 61 of the piston rod 40 can be appropriately set according to the application conditions of the cylinder device 30. In the example of the present embodiment, as shown in FIG. 10, when the outer peripheral clutch groove 61 of the piston rod 40 is on the intermediate rod guide 34 side with respect to the inner peripheral clutch groove 60 of the guide sleeve 58, the piston 41 is bypass bypass 58. When the piston rod 40 is extended and its outer peripheral clutch groove 61 is on the oil seal 33 side with respect to the inner peripheral clutch groove 60 of the guide sleeve 58, as shown in FIG. The piston 41 is set so as to be disengaged from the range L of the bypass recess 58 toward the intermediate rod guide 34 side.

  An attachment portion 66 for linking the cylinder device 30 to the link of the cylinder device 30 is attached to the bottom portion of the cylinder member 31 so as to be rotatable around the axis of the cylinder member 31. It is fixed. In addition, the shape of these attaching parts 66 and 67 becomes a shape matched with to-be-attached members, such as a door.

Next, the operation of this embodiment configured as described above will be described.
The cylinder device 30 can be used as a door closer by linking the attachment portion 66 and the attachment portion 67 to the door 22 and the door frame 23 of the hinged door as in the embodiment shown in FIGS. 3, 5, 7 and 8. it can.

  7, when the door 22 is in the intermediate position, as shown in FIG. 10, the outer peripheral clutch groove 61 of the piston rod 40 is closer to the intermediate rod guide 34 side than the inner peripheral clutch groove 60 of the guide sleeve. It is in. At this time, in a state where the ball 64 inserted into the ball hole 63 of the clutch ring 62 is inserted into the inner peripheral clutch groove 60 of the guide sleeve 58, the movement toward the radially inner side is restricted by the outer peripheral surface of the piston rod 40. Therefore, the clutch ring 62 is fixed in the axial direction against the spring force of the compression coil spring 65. Thereby, the spring force of the compression coil spring 65 does not act on the piston rod 40. This section is called a free section.

  Further, in this free section, the piston 41 strokes within the range L of the bypass recess 45 of the cylinder portion 35 with respect to the expansion and contraction of the piston rod 40. At this time, the hydraulic fluid flows through the gap between the piston 41 and the bypass recess 45 with almost no resistance, so that almost no damping force is generated against the expansion and contraction of the piston rod 40. Note that the gas in the gas chamber 38 is compressed and expanded in response to volume changes in the rod guide portion 38 and the cylinder portion 39 due to expansion and contraction of the piston rod 40, but the gas chamber 38 has a low pressure of about atmospheric pressure. For this reason, this pressure hardly affects the expansion and contraction of the piston rod 40.

  In this free section, the piston rod 40 can be freely expanded and contracted with little resistance, so that the door 22 receives almost no resistance from the cylinder device 30 when in the intermediate position shown in FIG. It can be moved freely in both open and close directions.

  Next, as shown in FIG. 5, when the door 22 is moved to the vicinity of the closed position, as shown in FIG. 11, the piston rod 40 extends, and the outer peripheral clutch groove 61 becomes the inner peripheral clutch groove of the guide sleeve 58. 60 moves to the oil seal 33 side. At this time, when the outer peripheral clutch groove 61 of the piston rod 40 passes through the inner peripheral clutch groove 60 of the guide sleeve 58, the ball 64 is inserted into the outer peripheral groove 64 of the piston rod 40, and the clutch ring 62 is connected to the guide sleeve 58. Is fixed to the piston rod 40 in the axial direction. Thus, the piston rod 40 is urged in the extending direction together with the clutch ring 62 by the spring force of the compression coil spring 65, and the door 22 automatically moves to the closed position shown in FIG. This section is called an energizing section.

  In this energizing section, as shown in FIG. 11, the piston 41 is out of the range L of the bypass recess 58, so that the hydraulic fluid on the rod side chamber 39 </ b> A side becomes the orifice of the shutter 46 when the piston rod 40 extends. The fluid flows through the passage 49 and the communication passage 45 of the piston 41 to the bottom side chamber 39 </ b> B, and a damping force is generated by the flow passage area of the orifice passage 49. Thereby, the moving speed of the door 22 can be decelerated, and the impact and noise when the door 22 is closed can be reduced.

The damping force can be adjusted by selectively switching the orifice passage 49 that rotates the shutter 46 and communicates with the communication passage 45 of the piston 45, so that the weight, size, desired closing speed, etc. of the door 22 can be adjusted. Accordingly, an appropriate damping force can be obtained with respect to changes in characteristics due to changes over time or changes in room temperature. When switching the damping force, as shown in FIG. 12, the piston rod 40 is moved to the maximum protruding state, that is, the door 22 is moved to the fully open position, and the engaging convex portion 57 of the intermediate rod guide 34 and the shutter 46 are moved. The notch 52 is engaged. In this state, the shutter 46 can be rotated by rotating the cylinder member 31. Thereby, the damping force can be adjusted in a state where the cylinder device 30 is mounted on the hinged door. At this time, the rotational position of the shutter 46 can be easily determined by the detent action caused by the engagement and disengagement between the detent recess 50 and the detent protrusion 51. The rotational position of the shutter 46 can be visually checked by marking the cylinder member 31 and the piston rod 40, and even if there is no marking, the detent action between the detent concave portion 50 and the detent convex portion 51 can be sensed. Can be recognized. In this embodiment, as shown in FIG. 14, the set of three detent recesses 50 includes three sets, the interval between three detent recesses 50 (30 degrees), and the interval between adjacent detent recesses 50 (60 degrees). Therefore, after switching between large, medium, and small, it is possible to recognize that it has returned to the next large size as a touch due to this difference in angle.
In addition, you may change each space | interval of this set of three detent recessed parts 50. FIG.

  When the door 22 is opened from the closed state, the shutter 45 acts as a check valve against the stroke of the piston 41 due to the shortening of the piston rod 40, the disc spring 48 is bent, and the shutter 46 is separated from the piston 41. Thus, the communication passage 45 is opened, and the hydraulic fluid on the bottom side chamber 39B side flows to the rod side chamber 39A side with almost no flow resistance. As a result, almost no damping force is generated, so that the door 22 can be smoothly opened against only the spring force of the compression coil spring 65.

  When the door 22 is opened to a predetermined position, as shown in FIG. 10, the piston rod 40 is shortened, and the outer peripheral clutch groove 61 passes through the inner peripheral clutch groove 60 of the guide sleeve 58 together with the clutch ring 62. At this time, the ball 64 is inserted into the outer peripheral groove 60 of the guide sleeve 58, and the clutch ring 62 is released from the axial fixing with respect to the piston rod 40 and is fixed to the guide sleeve 58 in the axial direction. Thus, the piston rod 40 is released from the spring force of the compression coil spring 65 and can move freely, and is switched from the biasing section to the free section.

  Further, as shown in FIG. 8, when the door 22 is moved to the vicinity of the fully open position, the urging section shown in FIG. 11 is obtained again, and the piston rod 40 extends to move the door to the vicinity of the closed position. Similarly to the case, the clutch ring 62 is fixed to the piston rod 40 side, the piston rod 40 is extended by the spring force of the compression coil spring 65, and the damping force by the orifice passage 49 acts on the extension of the piston rod 40. Thereby, the door 22 is automatically moved to the fully open position and held. At this time, the moving speed of the door 22 can be reduced, and the impact and noise when the door 22 is fully opened can be reduced.

  Next, first to third modifications of the third embodiment will be described with reference to FIGS. 16 to 20. In the following description, the same reference numerals are used for the same parts in the third embodiment shown in FIGS. 10 to 15, and only different parts will be described in detail.

A first modification will be described with reference to FIGS. 16 to 18. FIG. 16 shows an enlarged longitudinal sectional view of the vicinity of the piston 41 of this modification, FIG. 17 shows an end surface of the piston 41 on the intermediate rod guide 34 side, and FIG. 18 shows an end surface of the shutter 46 on the piston 41 side.
In this modification, as shown in FIGS. 16 to 18, the shutter 46 is fixed in the axial direction by omitting the disc spring 48 from the third embodiment, and the shutter 46 functions as a check valve. An independent check valve 68 is provided instead. Further, the detent concave portion 50 and the detent convex portion 51 are omitted, and instead, the check valve 68 also serves as a detent mechanism.

  The structure of the check valve 68 will be described. The piston 41 is provided with a check valve passage 69 for communicating the rod side chamber 39A and the bottom side chamber 39B. The opening of the check valve passage 69 on the shutter 46 side is enlarged in diameter to form a tapered seat portion 70. On the other hand, a valve hole 71 is formed in the shutter 46 at a portion facing the seat portion 70, and a passage 72 that opens to the rod side chamber 39 </ b> A is passed through the bottom of the valve hole 71. A chuck ball 73 is inserted into the valve hole 71 and is seated on the seat portion 70, and a valve spring 74, which is a compression coil spring, is interposed between the bottom of the valve hole 71 and the check ball 73.

  Thereby, the check valve 68 is moved in this direction by the valve spring 74 being bent and the check ball 73 being separated from the seat portion 70 with respect to the flow of the hydraulic fluid from the bottom side chamber 39B side to the rod side chamber 39A side. Allow flow. On the other hand, the flow in the opposite direction is blocked by the check ball 73 being pressed against the seat portion 70.

Next, the detent function of the check valve 68 will be described. As shown in FIG. 17, a plurality of check valve passages 69 are provided along the circumferential direction on the inner peripheral side of the communication passage 45, and the check ball 73 moves backward against the spring force of the valve spring 74. However, the shutter 46 can be rotated by going up the taper surface of the sheet portion 70. Further, when the check ball 73 is pressed against the tapered seat portion 70 by the spring force of the valve spring 74 and is centered, the rotational position of the shutter 46 can be determined and the position can be maintained. Then, in order to determine the position of each of the three orifice passages 49 with respect to each of the three communication passages 45, three are arranged in three locations in the circumferential direction corresponding to these arrangements. .
With this configuration, the cylinder device according to the present modification can achieve the same effects as those of the third embodiment.

Next, a second modification of the third embodiment will be described with reference to FIG. FIG. 19 shows an overall longitudinal sectional view of this modification.
As shown in FIG. 19, in the present modification, the sleeve 58 divided into two is integrated with the intermediate rod guide 34 in addition to the third embodiment. An oil seal 33 is attached to the intermediate rod guide 34, and an O-ring 75 is provided between the intermediate rod guide 34 and the cylinder member 31 so that the hydraulic fluid is sealed by the intermediate rod guide 34. No hydraulic fluid is sealed inside 36. Thereby, while having the same effect as the said Example 3, the quantity of hydraulic fluid can be decreased and weight reduction can be achieved.

Next, a third modification of the third embodiment will be described with reference to FIG. FIG. 20 shows an enlarged longitudinal sectional view in the vicinity of the cylinder portion 39 of this modification.
As shown in FIG. 20, in this modification, the mounting direction and arrangement of the piston 41 and the shutter 46 are reversed with respect to the third embodiment, and the shutter 46 is arranged on the bottom side chamber 39B side. Instead of making the shutter 46 function as a valve body of the check valve, an independent check valve 76 is provided. Further, in response to the shutter 46 being disposed on the bottom side chamber 39B side, the engagement convex portion 57 of the intermediate rod guide 34 is omitted, and instead, the bottom side chamber 39 can be engaged with the notch 52 of the shutter 46. An engaging member 77 is attached.

  The check valve 76 is provided with a check valve passage 78 that communicates the rod side chamber 39A and the bottom side chamber 39B with the piston 41, and a disc valve 79 that opens and closes the check valve passage 78 at the end of the piston 41 on the rod side chamber 39 side. To allow only the flow of hydraulic fluid from the bottom side chamber 39B side to the rod side chamber 39A side of the check valve passage 78. The shutter 46 is provided with a plurality of passages 80 that allow the check valve passage 78 to always communicate with the bottom chamber 39B.

  The engagement member 77 is an annular member having an outer peripheral groove 81 and is fitted in the cylinder portion 39 and fixed in the axial direction and the rotational direction around the axis by caulking the side wall of the cylinder member 31 from the outside to the inside. Has been. Further, the engaging protrusion 77 protrudes from the engaging member 77 so as to oppose the notch 52 of the shutter 46 attached to the piston 41, and the piston rod 40 is shortened so that the piston 41 is attached to the cylinder member 31. By moving to the bottom side, the engaging convex portion 82 can be engaged with the notch 52 of the shutter 46.

  Thereby, there can exist an effect similar to the said Example 3. FIG. Further, when adjusting the damping force, the piston rod 40 is shortened, and the cylinder member 31 is rotated in a state where the engagement convex portion 82 of the engagement member 77 is fitted in the notch 52 of the shutter 46. Thereby, the outer peripheral part of the shutter 46 is slightly bent, and the shutter 46 can be rotated while engaging and disengaging the detent concave part 50 and the detent convex part 51, and a desired damping force can be switched.

  In each of the above embodiments, the damping force is obtained by reducing the flow passage area through which the oil liquid flows. However, the damping force may be obtained by friction between the piston and the cylinder, as in a so-called friction damper. Any structure that can generate a damping force may be used. However, the most stable damping force can be obtained by using a fluid, particularly an oil liquid.

  Moreover, when using the cylinder apparatus of each said Example as a door closer, it is better to provide a decorative case around. In particular, when an oil solution is used, it is desirable to attach a case because dust or the like gets on the piston rod.

In the third embodiment, the shutter 46 is rotated when the piston rod 40 has the maximum length or the minimum length. However, the thickness of the shutter is increased and the axial lengths of the engagement convex portions 57 and 82 are increased. By increasing the length, the damping force can be adjusted even slightly before the maximum or minimum length. As a result, when the cylinder device is attached, the damping force can be adjusted even if the person who attaches the cylinder device is slightly displaced from the attachment position.
Further, the same effect can be obtained by making the engagement convex portions 57 and 82 somewhat movable in the axial direction.

1 is a longitudinal sectional view of a spring damper according to an embodiment of the present invention, showing a state where a piston rod is most contracted. FIG. The external appearance perspective view which expands and shows a clutch ring and a clutch ball. It is a diagram which shows the state which mounted | wore the spring damper by this invention with the door, and shows the state which the door closed. It is the same longitudinal cross-sectional view as FIG. 1, and shows the state where the piston rod was pushed in a little. The longitudinal cross-sectional view of the spring damper shown in FIG. It is the same diagram as FIG. 3, and shows a state where the door is slightly opened. It is the longitudinal cross-sectional view of the spring damper similar to FIG. 1, The state which the piston rod was pushed in a little is shown. FIG. 6 is a diagram similar to FIG. 3 and shows a state where the tip of the piston rod is at a dead point. FIG. 6 is a diagram similar to FIG. 3 showing a state where the door is urged in the opening direction and braking is applied. FIG. 2 is a longitudinal sectional view of a spring damper similar to that in FIG. 1, showing a state where the piston rod is extended to the maximum extent. It is a longitudinal cross-sectional view of the cylinder apparatus which concerns on Example 3 of this invention. In the cylinder apparatus shown in FIG. 10, it is a longitudinal cross-sectional view which shows the state which the piston rod extended | stretched. In the cylinder apparatus shown in FIG. 10, it is a longitudinal cross-sectional view which shows the state which the piston rod extended to the stroke end. It is a longitudinal cross-sectional view which expands and shows the piston part of the cylinder apparatus shown in FIG. It is an end view of the piston of the cylinder apparatus shown in FIG. It is an end elevation of the shutter of the cylinder device shown in FIG. It is a longitudinal cross-sectional view which expands and shows the piston part of the cylinder apparatus which concerns on the 1st modification of Example 3 of this invention. It is an end view of the piston of the cylinder apparatus shown in FIG. FIG. 17 is an end view of a shutter of the cylinder device shown in FIG. 16. It is a longitudinal cross-sectional view of the cylinder apparatus which concerns on the 2nd modification of Example 3 of this invention. It is a longitudinal cross-sectional view which expands and shows the cylinder part of the cylinder apparatus which concerns on the 3rd modification of Example 3 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Cylinder, 2 Piston, 3 1st cylinder, 4 Clutch ring, 5 2nd cylinder, 6 Bulkhead, 7 Piston rod, 8 1st lid plug, 9 2nd lid plug, 11 Ball storage hole, 12 Clutch ball, 13 Inside Clutch groove, 14 outer clutch groove, 15 compression coil spring, 16 communication hole, 17 relief groove, 18 air chamber, 19 idle plug, 21 tip, 22 door, 23 door frame, 24 base end, 25 rotating shaft, 30 cylinder Device, 31 Cylinder member, 40 Piston rod, B Spring mechanism

Claims (16)

A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, and when the protruding length of the rod from the cylinder member is equal to or longer than a predetermined length, the rod can be stroked with a spring force applied in a direction in which the rod protrudes. A spring mechanism that allows the rod to stroke in a state where no spring force is applied to the rod when less than a predetermined length ;
A damping force generating mechanism that applies a damping force to the movement of the rod in the axial direction;
Working fluid is sealed in at least a part of the inside of the cylinder member,
A piston that moves in the working fluid inside the cylinder member is connected to the rod,
The damping force generating mechanism is provided with damping force adjusting means for generating a damping force by applying a flow resistance to a flow path of a working fluid provided in the piston and adjusting the damping force from the outside of the cylinder member. And
The damping force adjusting means is provided with a shutter that is provided so as to be rotatable relative to the piston, and that changes a flow area of the flow path of the working fluid in accordance with the rotational position thereof. . The spring mechanism includes an outer peripheral clutch groove provided on an outer peripheral portion of the rod, an inner peripheral clutch groove provided on the inner side of the cylinder member so as to face the outer peripheral clutch groove, and a rod from the cylinder member. When the protruding length is equal to or longer than a predetermined length, the rod is engaged with the outer peripheral clutch groove and fixed in the axial direction with respect to the rod, and is movable in the axial direction with respect to the cylinder member. A clutch that engages with the inner circumferential clutch groove and is fixed in the axial direction with respect to the cylinder member and movable in the axial direction with respect to the rod when a protruding length from the member is less than a predetermined length. cylinder device according to claim 1, characterized in that it comprises means, and a spring means for biasing said clutch means. The clutch means is engaged with at least one of the outer peripheral clutch groove and the inner peripheral clutch groove between an inner peripheral surface on the cylinder member side provided with the inner peripheral clutch groove and an outer peripheral surface of the rod. The cylinder device according to claim 2 , comprising a plurality of spheres inserted therebetween and a holding member that holds the spheres. The cylinder device according to any one of claims 1 to 3 , wherein the piston is provided with a check valve that allows a working fluid to flow only when the rod strokes in a shortening direction. The check valve is closed by contacting the opening of the flow path of the working fluid of the piston with the shutter as a valve body, and is opened when the shutter is separated from the opening. The cylinder device according to claim 4 , wherein the cylinder device is provided. The cylinder device according to any one of claims 1 to 5 , wherein the shutter is provided with a rotation position indexing unit that holds the rotation position for each predetermined rotation position. The shutter, the predetermined rotational position is arranged at different intervals, cage, claim 6, characterized in that is adapted to be able to recognize the rotational position of the shutter based on the difference in the interval The cylinder device described in 1. The piston is provided so as not to rotate around the axis with respect to the rod, and when the rod is moved to the stroke end side, the engaging member that engages with the shutter does not rotate around the axis inside the cylinder member. The cylinder device according to claim 1 , wherein the cylinder device is fixed to the cylinder device. A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
Provided inside the cylinder member, and when the protruding length of the rod from the cylinder member is equal to or longer than a predetermined length, the rod can be stroked with a spring force applied in a direction in which the rod protrudes. A spring mechanism that allows the rod to stroke in a state where no spring force is applied to the rod when less than a predetermined length ;
A damping force generating mechanism that applies a damping force to the movement of the rod in the axial direction;
Working fluid is sealed in at least a part of the inside of the cylinder member,
A piston that moves in the working fluid inside the cylinder member is connected to the rod,
The damping force generation mechanism generates a damping force by applying a flow resistance to the flow path of the working fluid provided in the piston,
The inner circumferential surface of the cylinder member on which the piston slides is provided with a bypass recess that forms a gap with the piston when the protruding length of the rod is within a predetermined range. Cylinder device. The spring mechanism is, when the protruding length of the rod from the cylinder member is equal to or larger than a predetermined length, in any one of claims 1 to 9, characterized in that it comprises a coil spring which gives a force in the projecting direction to the rod The cylinder device described. It is connected between the door of the hinged door and the door frame so that when the door is in the closed position and the open position, it is in an extended state, and when it is in a position between the closed position and the open position, it is in a shortened state. , A door closer for assisting in opening and closing the door,
A cylindrical cylinder member;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
When the protruding length of the rod from the cylinder member is not less than a predetermined length provided inside the cylinder member, the rod can be stroked with a spring force applied in the protruding direction of the rod, A door closer comprising a spring mechanism that enables the rod to make a stroke when a spring force is not applied to the rod when the length is less than a predetermined length. The door closer according to claim 11 , further comprising a damping force generation mechanism that applies a damping force to the movement of the rod in the axial direction. Between the door of the hinged door and the door frame, when the door is in the closed position and the open position, it is in an extended state, and when it is in an intermediate position between the closed position and the open position, it is connected so as to be in a shortened state, A door closer for assisting in opening and closing the door,
A cylinder filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder, and one end protruding from an end of the cylinder;
A piston that is coupled to the rod so as not to rotate around an axis and divides the cylinder into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston, and changes a flow passage area of the communication path according to the rotation position;
An engagement member that is fixed so as not to rotate around the axis inside the cylinder, and engages with the shutter when the rod is moved to the stroke end to fix the shutter in the rotational direction with respect to the cylinder. When,
When the protruding length of the rod from the cylinder is equal to or longer than a predetermined length, the rod can be stroked in a state in which a spring force in the protruding direction is applied to the rod, and when the protruding length is less than the predetermined length, A door closer comprising a spring mechanism that enables the rod to stroke in a state where no spring force is applied. A door closer connected between the door of the hinged door and the door frame to assist in opening and closing the door,
A cylinder member filled with hydraulic fluid;
A rod supported so as to be movable in the axial direction with respect to the cylinder member, and one end protruding from an end of the cylinder member;
A piston that is coupled to the end of the rod so as not to rotate about an axis and divides the inside of the cylinder member into two chambers;
A communication path provided in the piston and communicating with each other two chambers defined by the piston;
A shutter that is rotatably attached to an end of the piston on the rod side, and changes a flow passage area of the communication path according to the rotation position;
It is fixed to the middle part of the cylinder member so as not to rotate around the axis, the rod is penetrated so as to be movable in the axial direction, a flow path for hydraulic fluid is formed along the axial direction of the rod, and the rod protrudes And an engaging member that engages with the shutter and fixes the shutter in the rotational direction with respect to the cylinder member when moved in the direction to the stroke end.   A first cylinder filled with hydraulic oil and fitted with a piston and a second cylinder fitted with a cylindrical clutch ring so as to be slidable are connected along the axial direction and through a partition wall; The open ends of the first and second cylinders are closed by first and second lid plugs, respectively, and a clutch ring is fitted on the outside, penetrating the second lid plug and the partition wall, and the piston at the inner end And a clutch ball is accommodated in at least one ball housing hole that penetrates the clutch ring in the radial direction so as to be movable in the radial direction, while the inner circumferential surface of the second cylinder, and the second In the cylinder, annular inner and outer clutch grooves into which a part of the clutch ball can be engaged are formed at predetermined positions in the axial direction of the outer peripheral surface of the piston rod in the cylinder. A compression coil spring is mounted between the ring and the piston in the first cylinder is provided with an orifice device for buffering when the piston rod is extended, and the clutch ball has an inner clutch groove and a ball storage hole. A spring damper having a relief groove formed by expanding the inner wall of the first cylinder fitted to the piston when the piston rod is free from the clutch ring.   A first cylinder filled with hydraulic oil and fitted with a piston and a second cylinder fitted with a cylindrical clutch ring so as to be slidable are connected along the axial direction and through a partition wall; The open ends of the first and second cylinders are closed by first and second lid plugs, respectively, and a clutch ring is fitted on the outside, penetrating the second lid plug and the partition wall, and the piston at the inner end And a clutch ball is accommodated in at least one ball housing hole that penetrates the clutch ring in the radial direction so as to be movable in the radial direction, while the inner circumferential surface of the second cylinder, and the second An annular inner and outer clutch groove into which a part of the clutch ball can be engaged is formed at a predetermined position in the axial direction of the outer peripheral surface of the piston rod in the cylinder, and the second lid plug A compression coil spring is mounted between the clutch ring and the piston in the first cylinder is provided with an orifice device for buffering when the piston rod is contracted. A spring damper characterized in that when the piston rod is free from the clutch ring across the hole, the inner wall of the first cylinder fitted with the piston is enlarged to form a relief groove.

Images