KR101128242B1 - Cylinder apparatus - Google Patents

Abstract

An object of the present invention is to provide a novel cylinder device having a pinch prevention function and a damper function.

A cylinder device according to the present invention is a cylinder device, which is a cylindrical cylinder member (1; 31) and a rod supported movably in an axial direction with respect to the cylinder member, and having one end protruding from an end of the cylinder member ( 7 and 40, provided inside the cylinder member, and when the protruding length of the rod from the cylinder member is greater than or equal to a predetermined length, a spring force is applied, and when it is less than a predetermined length, a spring force is not applied to the rod. Spring mechanisms 4, 11, 12, 13, 14, 15; 60, 61, 62, 63, 64, 65.

Description

Cylinder unit {CYLINDER APPARATUS}

The present invention relates to a cylinder device for assisting the opening and closing of a door, in particular to a cylinder device used for a door closer.

By linking a cylinder device such as a spring damper to the swing door to apply spring force and damping force to the opening and closing of the door, the door is automatically closed, the opening and closing speed is adjusted at the closing, or the door is held in the open position. Door closers are known. DESCRIPTION OF RELATED ART Conventionally, as a door closer using cylinder apparatuses, such as this kind of spring damper, there exist some which were described in Unexamined-Japanese-Patent No. 2008-2124, for example.

The door closer described in Japanese Unexamined Patent Application Publication No. 2008-2124 discloses that the door is opened by linking a spring damper that causes the spring force of the compression coil spring to act in the direction of extension of the working rod between the door of the door and the door frame. According to the figure, when the door is near the closed position, a force in the closing direction is applied, and when the door is near the fully open position, the door is held in the open position.

However, there is a problem that the relatively strong spring force is generated when the spring damper is in the intermediate position where the spring damper is shortest.

An object of the present invention is to provide a cylinder device for use in a door closer that solves the above problem.

In order to solve the above problems, the cylinder device according to the present invention,

A cylindrical cylinder member,

A rod supported movably in the axial direction with respect to the cylinder member, one end protruding from an end of the cylinder member,

And a spring mechanism provided inside the cylinder member to impart spring force when the protruding length of the rod from the cylinder member is greater than or equal to a predetermined length, and to impart no spring force to the rod when less than a predetermined length. .

First embodiment

EMBODIMENT OF THE INVENTION Hereinafter, the spring damper as a cylinder device which concerns on 1st Embodiment of this invention is demonstrated with reference to drawings. In addition, this embodiment shows the case where the spring damper of this invention is applied to opening / closing control of a swing door.

In FIG. 1, the code | symbol 1 shows the whole cylinder of a spring damper (cylinder apparatus). The cylinder 1 is formed by successively installing the first cylinder 3 and the second cylinder 5 along the axial direction and with the partition wall 6 interposed therebetween. Hydraulic fluid is filled in the first cylinder 3, and the piston 2 is slidably fitted. The cylindrical clutch ring 4 is slidably fitted to the second cylinder 5.

In the illustrated embodiment, the partition wall 6 has a tubular body having an insertion hole through which the piston rod 7 penetrates, and a partition plug (coded) that is fitted in liquid-tight manner with the piston rod 7. Not attached).

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

The piston rod 7 mounted to the cylinder 1 penetrates through the second cover plug 9 and the partition wall 6. The piston 2 is attached to the inner end of the piston rod 7 facing the first cylinder 3.

Moreover, the clutch ring 4 which consists of a thick cylinder part is fitted in the part in the 2nd cylinder 5 of the piston rod 7.

As shown in Fig. 2, the clutch ring 4 has a plurality of ball receiving holes 11 (four in the illustrated embodiment) formed at equally spaced intervals so that the cylindrical portion penetrates radially. . In each ball receiving hole 11, the clutch ball 12 is accommodated so as to be movable in the radial direction of the clutch ring, respectively.

On the other hand, an annular inner circumference in which part of the clutch ball 12 can be caught at a predetermined position in the axial direction of the inner circumferential surface of the second cylinder 5 and the outer circumferential surface of the piston rod 7 in the second cylinder, respectively. And outer clutch grooves 13 and 14 (see Fig. 4) are formed. In the illustrated embodiment, each clutch groove 13, 14 is trapezoidal in cross section. The inner clutch groove 13 and the outer clutch groove 14 have substantially the same depth, and the diameter of the clutch ball 12 is the sum of the side wall thickness of the clutch ring 4 and the depth of the inner clutch groove 13, and the clutch ring. It is equal to the sum of the sidewall thickness of (4) and the depth of the outer clutch groove 14.

Then, the compression coil spring 15 is elastically mounted between the partition 6 and the clutch ring 4, and the clutch ring 4 moves to the left side in FIG. 1 by the elastic force of the compression coil spring 15. It is deflected in the direction of escape from the 2nd cylinder 5. In addition, in the state shown in FIG. 1, since the clutch ball 12 spans between the inner circumferential clutch groove 13 and the ball receiving hole 11 of the clutch ring, the clutch ring 4 includes the second cylinder 5. Is hung on the inner circumferential surface thereof, so that the elastic force of the compression coil spring 15 is supported by the second cylinder 5.

On the other hand, the piston 2 in the 1st cylinder 3 is provided with the orifice apparatus of the type which buffers at the time of expansion of the piston rod 7.

Since such an orifice device is well known, a detailed description thereof will be omitted. For example, the orifice device may be made of a flexible orifice plate having an orifice hole covering the opening on the left side in FIG. 1 of the communication hole 16 penetrating the piston in the axial direction. In addition, this orifice apparatus may use the structure of the piston part of 3rd Embodiment mentioned later.

In addition, as shown in FIG. 1, when the clutch ball 12 extends through the inner circumferential clutch groove 13 and the ball receiving hole 11, the piston rod 7 is freed from the clutch ring 4. In the position of the piston 2, the inner wall of the 1st cylinder 3 fitted with the piston 2 expands, and the undercut 17 is formed.

1, reference numeral 18 denotes an air chamber formed in the first cylinder 3. The air chamber 18 is partitioned intimately from the first cylinder 3 by the pre-piston 19 to absorb the expansion and contraction of the working oil according to the temperature change, but this air chamber is well known in the art, Since it is not the summary, more detailed description is abbreviate | omitted.

In the spring damper according to the embodiment of the present invention configured as described above, as shown in FIG. 3, for example, the front end 21 of the piston rod 7 is sandwiched between a door 22 or a door frame ( On one side of 23, the base end 24 of the cylinder 1 is sandwiched between brackets and used to link to the door 22 or the other side of the door frame 23 so as to be swingable.

The positional relationship of each member of the spring damper at this time is as shown in FIG. Thus, when the door is opened, the piston rod 7 of the spring damper moves in the right direction as shown in Fig. 6 because the piston rod 7 is pressed into the cylinder 1 as shown in Fig. 5. do.

At this time, the compression coil spring 15 of the piston rod 7 is pressed to move, but the orifice plate (not shown) of the piston 2 elastically deforms, so that the hydraulic fluid communicates with the communication hole 16 (see FIG. 6). The piston rod 7 is lightly pressurized into the cylinder 1 without being buffered because it is moved from right to left through the "

Moreover, when the piston rod 7 is in the position shown in FIG. 6, the inner and outer clutch grooves 13 and 14 are matched in the axial direction, and the outer clutch groove 14 and the ball receiving hole 11 until then. The clutch ball 12 that has been sandwiched between the inner circumferential clutch groove 13 and the ball receiving hole 11 is released so that the piston rod 7 is released from the clutch ring 4 to be freed.

Therefore, the piston rod 7 is lightly pressed 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 pivot shaft 25 of the door hinge, the tip 21 of the piston rod 7 and the base 24 of the cylinder are arranged in a straight line, As shown, the piston rod 7 is most deeply pressed into the cylinder 1 (so-called dead point).

If the door is further opened in the state shown in FIG. 7, this time the piston rod 7 and the piston 2 move to the left in the state shown in FIG. Brake is applied, but since the diameter of the inner circumferential surface of the first cylinder 3 around the piston 2 is expanded at this time, the hydraulic fluid is shown in FIG. 1 between the outer circumferential surface of the piston 2 and the undercut 17. Flowing from left to right, the piston rod 7 moves to the left without a load.

In time, the piston rod 7 extends to the position shown in FIG. 6, but at this time, the door 22 is opened, for example, by about 70 °, as shown in FIG. The piston rod 7 and the clutch ring 4 are integrally connected between the ball receiving hole 11 and 14.

From this time, the piston rod 7 is subjected to the elastic force of the compression coil spring 15, and at the same time, the orifice device is operated, and the piston 2 moves to the small diameter portion of the first cylinder 3, so that the piston rod ( The door 22 connected to 7) is deflected in the opening direction while being buffered.

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

As shown in FIG. 9, the piston rod 7 extends as much as possible, at which time the piston rod 7 becomes a stopper of the door 22.

When the door 22 is closed in this state, the piston rod 7 is pressed into the cylinder 1 while compressing the compression coil spring 15 as shown in FIG. 4, but the orifice device is not operated at this time. Therefore, the door is lightly closed.

When the door 22 is further closed, the spring damper is press-fitted to the state shown in FIGS. 6 and 1, and the door 22 is closed than the state shown in FIG. 7 (the spring damper is shown in FIG. 1). Moving further in the direction, the piston rod 7 of the spring damper starts to stretch and in the state shown in FIG. 6, for example, with the opening angle of the door 22 about 20 °, the door 22 is closed. The piston 2 is braked in the direction.

In other words, the spring damper this time starts to act as a door closer and completely closes the door 22 in the state shown in FIG. 4 and maintains its closure elastically.

2nd embodiment

In the above embodiment, the compression coil spring 15 is elastically mounted between the partition wall 6 and the clutch ring 4, but this is caused by elastically mounting between the second cover plug 9 and the clutch ring 4. When the piston rod 7 contracts, it can be a spring damper which buffers this (not shown).

In this case, however, the forming position in the longitudinal direction of the piston 2 of the inner and outer circumferential clutch grooves 13 and 14 is appropriately set in accordance with the set amount of extension of the piston 2.

Third embodiment

A third embodiment of the present invention will be described with reference to FIGS. 10 to 15.

The longitudinal cross-sectional view of the cylinder apparatus which concerns on this embodiment is shown in FIG. As shown in FIG. 10, the cylinder device 30 has a rod guide 32 having an inner circumferential portion that slides with the piston rod 40 at an opening end of a substantially cylindrical cylinder member 31 with a bottom. Is inserted and fixed by caulking the open end of the cylinder member 31. Inside the rod guide 32, an oil seal 33 is formed of a rubber that seals the inside and the outside of the cylinder member 31, and a metal ring is embedded therein. Moreover, the intermediate rod guide 34 is attached to the inside of the intermediate part of the cylinder member 31, and the inside of the cylinder member 31 is opened by the intermediate rod guide 34, and the cylinder part 35 of the bottom side, and an opening part are shown. It is partitioned by the rod guide part 36 of a side. The intermediate rod guide 34 may be a bearing sliding with the piston rod 40 similarly to the rod guide 32. In this case, the coaxiality between the rod guide 32 and the intermediate rod guide 34 needs to be increased, so that the intermediate rod guide 34 has a larger inner diameter than the rod guide 32. This is good. In addition, the pre-piston 37 is slidably fitted to the cylinder portion 35, and the pre-piston 37 allows the inside of the cylinder portion 35 to be located on the gas chamber 38 and the intermediate rod guide 34 side of the bottom side. It is partitioned by the cylinder chamber 39.

The piston rod 40 is inserted into the cylinder member 31 by slidingly and fluidly penetrating the rod guide 32 and the oil seal 33. The proximal end 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 the damping force generating mechanism is connected to the distal end thereof. The piston 41 is slidably fitted to the cylinder portion 35, and the rod on the intermediate rod guide 34 side in the cylinder chamber 39 by the O-ring 41A (see FIG. 13) as the piston seal member of the outer circumference. The chamber is divided into two chambers, the side chamber 39A and the lower side chamber 39B on the prepiston 37 side. The working liquid is sealed in the cylinder chamber 39 and the rod guide portion 36, and low pressure gas of about atmospheric pressure is sealed in the gas chamber 38. The gas at the atmospheric pressure is introduced into the gas chamber when the piston rod 40 is at its maximum length. Therefore, it may be higher than atmospheric pressure at the time of use depending on temperature conditions.

In addition, although the gas pressure may be somewhat higher depending on the required characteristics of the cylinder device, since a high spring pressure generates some spring force in the free section, which will be described later, preferably, Gas pressures with less force than friction are preferred. Furthermore, the gas chamber 38 may be opened to the air. In this case, it is better to provide a filter in the hole for opening 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 face of the intermediate rod guide 34 side of the piston 41 is shown in FIG. 14. As shown in Figure 13 and 14, the base end of the piston rod 40 is formed with a guide portion 42 of a circular cross section of reduced diameter and an attachment portion 43 further reduced in diameter. And the attachment part 43 of the piston rod 40 penetrates the attachment opening 44 of substantially the same shape as the attachment part 43 in the center of the piston 41, and cocks the front end part, and the piston rod 40 is It is coupled to the piston 41. The attachment portion 43 and the attachment opening 44 have a shape in which the side portions are chamfered, whereby the piston rod 40 and the piston 41 are also fixed in the rotational direction.

The piston 41 penetrates along the axial direction a communication path 45 for communicating the rod side chamber 39A and the lower side chamber 39B. In the present embodiment, the communication paths 45 are arranged at three points at equal intervals along the circumferential direction of the piston 41 in this embodiment. The disc-shaped shutter 46 shown in FIG. 15 is attached to the end part of the piston 41 at the intermediate rod guide 34 side. As for the shutter 46, the guide part 42 of the piston rod 40 is inserted in the circular center opening 47, and is rotatably supported with respect to the piston 41. As shown in FIG. A disc spring 48 is interposed between an end portion formed at the base of the guide portion 42 of the piston rod 40 and the shutter 46, and the shutter 46 is formed of the disc spring 48. It is pressed by the piston 41 by the spring force, and is movable in the axial direction against the spring force.

In the shutter 46, a plurality of orifice passages 49 having different diameters pass through the portion facing the communication passage 45 of the piston, and the shutter 46 is rotated to communicate one of the plurality of orifice passages 49. By selectively communicating with the furnace 45, the flow path area of the communication passage 45 can be adjusted. At this time, the orifice passage 49 may communicate with any of the three communication passages 45, and the remaining communication passages 45 are closed by the shutter 46. In the present embodiment, three orifice passages 49 having different diameters are formed, and the flow path area of the communication passage 45 can be adjusted in three stages according to the rotational position of the shutter 46.

In addition, when the number of the orifice passages 49 is increased, the flow passage cross-sectional area can be obtained as much as the increase. In addition, when the minimum flow path area is required, the orifice passage may be removed and the leak hole from the contact surface of the shutter 46 and the piston 41 or the like may be regarded as the orifice passage. In this case, a groove may be formed in the contact surface between the shutter 46 and the piston 41 to form a flow path. In other words, the orifice passage 49 is not limited to a small hole shape, and a groove may be provided in the outer circumference of the shutter 46.

A plurality of circular detent recesses 50 are formed in the outer peripheral portion of the end face of the intermediate rod guide 34 side of the piston 41 along the circumferential direction, and the detent recesses are formed in the outer peripheral portion of the end surface of the shutter 46. An almost hemispherical detent convex portion 51 protrudes from the portion facing 50. Then, the detent concave portion 50 and the detent convex portion 51 constitute the rotational position indexing means, and the combination of the communication path 45 of the piston 41 and the selected orifice of the shutter 46 are combined. The rotational position of the shutter 46 in which the passage 49 communicates can be indexed and maintained therein. In addition, when the disc spring 48 is bent and the shutter 46 moves in the axial direction, the coupling between the detent concave portion 50 and the detent convex portion 51 is released, so that the shutter 46 can be rotated. In this embodiment, the shutter 46 is provided with three detent convex portions 51 at equal intervals along the circumferential direction, and three orifice passages 49 for each of these three detent convex portions 51. The three detent recesses 50 are required to index (), so that the piston 41 has three detent recesses 50 arranged at three points, so that the total of nine detent recesses 50 Is provided. Moreover, the rectangular notch 52 is formed in the outer peripheral part of the shutter 46 at two points along a radial direction. In addition, the detent convex part 51 may embed a steel ball in the shutter 46, and may comprise the shutter itself by forging shaping | molding, or press molding or cutting. Moreover, also in the shape, if it is a shape which the shutter 46 can rotate smoothly, a cone etc. may be sufficient.

Referring to FIG. 13, in the intermediate rod guide 34, an annular groove 53 is formed on the outer circumference thereof, and a rotation preventing recess 54 is provided in a portion of the bottom of the annular groove 53. Then, the cylinder member 31 is caulked on the outer circumferential side to project the curl portion 55 to the inner circumference, and the curl portion 55 is inserted into the annular groove 53 to fix the intermediate rod guide 34 in the axial direction. have. In addition, a part of the curled portion 55 is caulked from the outside to protrude the anti-rotation convex portion 56 to the inside, and the anti-rotation convex portion 56 is inserted into the anti-rotation concave portion 54, thereby providing an intermediate rod guide ( 34) is fixed in the rotational direction. In the intermediate rod guide 34, two engaging projections 57 protrude from the two notches 52 of the shutter 46 attached to the piston 41. 13, only one of the two engagement convex parts 57 is shown according to the relationship of the break position. 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 functions as a coupling member for fixing the shutter 46 in the rotational direction with respect to the cylinder member 31, and by rotating the cylinder member 31 and the piston rod 40 relative to the piston 41, the shutter ( 46) can be rotated. In addition, the intermediate rod guide 34 has a clearance between the piston rod 40, and the flow path of the working liquid is formed between the inside of the rod guide 36 and the cylinder chamber 39.

The shutter 46 attached to the piston 41 also functions as a valve body of the check valve, in addition to adjusting the flow path area of the communication passage 45 of the piston 41 by the orifice passage 49 described above. That is, the shutter 46 moves in the axial direction against the spring force of the disc spring 48 so that the hydraulic fluid flows from the lower chamber 39B side of the communication path 45 to the rod chamber 39A side, and the piston By being spaced apart from the end face of 41, the flow path between the shutter 46 and the piston 41 becomes a flow path and does not impart flow resistance by the orifice passage 49, thereby allowing flow in this direction.

Referring to FIG. 10, a bypass concave portion 58 is formed on the inner circumferential surface of the cylinder portion 35 of the cylinder member 31 that extends over a predetermined range L along the axial direction. In the present embodiment, the bypass concave portion 58 is provided at three points along the circumferential direction of the cylinder portion 35 at equal intervals. When the piston 41 is in the range L of the bypass concave 58, a gap is created between the bypass concave 58 and the outer circumferential surface of the piston 41. The hydraulic fluid flows between the rod side chamber 39A and the lower side chamber 39B with almost no flow resistance. In addition, the intermediate rod guide 34 side end portion of the bypass concave portion 58 is set so that the cross-sectional area of the gap gradually decreases between the piston 41 and the bypass concave portion 58 when the bypass concave portion 58 is closed. The oil hammer can be made small.

The rod guide part 36 is provided with a spring mechanism B for applying a spring force to the piston rod 40. The structure of the spring mechanism B is demonstrated with reference to FIG. A cylindrical guide sleeve 59 is inserted and fitted into the cylinder member 31, and both ends thereof are fixed in the axial direction in contact with the oil seal 33 and the intermediate rod guide 34. An inner circumferential clutch groove 60 which is an inner circumferential groove is formed in the middle portion of the guide sleeve 59. In the present embodiment, the guide sleeve 59 is divided into two guide sleeves 59A, 59B at the end of the intermediate rod guide 34 side of the inner clutch groove 60 in consideration of the workability of the inner clutch groove 60. You may form these integrally. The piston rod 40 is formed with an outer circumferential clutch groove 61 in the middle portion of the portion facing the guide sleeve 59. Side portions of the inner circumferential clutch groove 60 and the outer circumferential clutch groove 61 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. In addition, the cylinder member 31 and the guide sleeve 59 may be shared by extending only the diameter of the inner circumferential clutch groove 60 of the cylinder member 31 without installing the guide sleeve 59.

Between the guide sleeve 59 and the piston rod 40, a cylindrical clutch ring 62, which is a holding member of a ball 64 (sphere) made of steel balls, is slidably fitted thereto. The clutch ring 62 has the same structure as the clutch ring 4 shown in Fig. 2, and a plurality of ball holes 63 penetrating in the radial direction are radially disposed at equal intervals on the side wall thereof. Each ball hole 63 is slidably inserted with a ball 64 having a diameter substantially the same as the ball hole 63 and larger than the thickness of the clutch ring 62. In addition, the inner clutch groove 60 of the guide sleeve 59 and the outer clutch groove 61 of the piston rod 40 have almost the same depth, and the diameter of the ball 64 is the thickness of the side wall of the clutch ring 62, The sum of the depths of the outer clutch groove 60 and the inner clutch groove 61 is the same. Accordingly, in the state where the clutch ring 62 into which the ball 64 is inserted is inserted between the guide sleeve 59 and the piston rod 40, the ball 64 must be the outer clutch groove 60 and the inner clutch groove. It is in the state inserted in at least one of 61. A compression coil spring 65, which is a spring means, is interposed between the intermediate rod guide 34 and the clutch ring 62 to always bias the clutch ring 62 toward the oil seal 33 side. In addition, the ball 64 does not necessarily need to be a sphere, For example, what divided | segmented the annular ring which is circular in cross section about three points in the circumferential direction may be sufficient.

The arrangement of the bypass concave portion 58 of the cylinder portion 35 and the inner circumferential clutch groove 60 of the guide sleeve 59 of the spring mechanism B and the outer circumferential clutch groove 61 of the piston rod 40 is performed by the cylinder device. It can be set suitably according to the application condition of (30). In the example of this embodiment, as shown in FIG. 10, the outer clutch groove 61 of the piston rod 40 is positioned on the intermediate rod guide 34 side with respect to the inner clutch groove 60 of the guide sleeve 59. When present, the piston 41 is in the range L of the bypass recess 58. On the other hand, as shown in FIG. 11, when the piston rod 40 is extended so that the outer clutch groove 61 is on the oil seal 33 side with respect to the inner clutch groove 60 of the guide sleeve 59. The piston 41 is set so as to deviate from the range L of the bypass concave portion 58 toward the intermediate rod guide 34 side.

An attachment portion 66 for linking the cylinder device 30 is rotatably attached to the bottom of the cylinder member 31 so as to be rotatable about the axis of the cylinder member 31, and to the protruding side tip of the piston rod 40. The attachment portion 67 is fixed. In addition, the shape of these attachment parts 66 and 67 becomes a shape matched with skin-attached members, such as a door.

The effect | action of this embodiment comprised as mentioned above is demonstrated next. The cylinder device 30 links the attaching portion 66 and the attaching portion 67 to the door 22 and the door frame 23 of the swing door similarly to the embodiments shown in FIGS. 3, 5, 7 and 8. Can be used as a door closer in combination.

And, as shown in Fig. 7, when the door 22 is in the intermediate position (dead point), as shown in Fig. 10, the outer peripheral clutch groove 61 of the piston rod 40 is the inner circumference of the guide sleeve It is on the side of the intermediate rod guide 34 with respect to the clutch groove 60. At this time, in the state where the ball 64 inserted into the ball hole 63 of the clutch ring 62 is inserted into the inner circumferential clutch groove 60 of the guide sleeve 59, the diameter is formed by the outer circumferential surface of the piston rod 40. Since movement inwardly in the direction is restricted, the clutch ring 62 is fixed in the axial direction against the spring force of the compression coil spring 65. Accordingly, the spring force of the compression coil spring 65 does not act on the piston rod 40. This section is called a free section.

In this free section, the piston 41 strokes within the range L of the bypass concave portion 58 of the cylinder portion 35 with respect to the expansion and contraction of the piston rod 40. At this time, since the working fluid flows almost without resistance in the gap between the piston 41 and the bypass concave portion 58, the damping force hardly occurs with respect to the expansion and contraction of the piston rod 40. In addition, the gas in the gas chamber 38 is compressed and expanded with respect to the volume change in the cylinder guide 39 and the inside of the rod guide 36 due to expansion and contraction of the piston rod 40. Because of the low pressure, this pressure hardly affects the expansion and contraction of the piston rod 40.

In this free section, since the piston rod 40 hardly generates resistance and can be freely expanded and contracted, when the door 22 is in the intermediate position shown in Fig. 7, it receives little resistance from the cylinder device 30. Can move freely in both opening and closing 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 is extended so that the outer clutch groove 61 has the guide sleeve 59. ) Moves toward the oil seal 33 with respect to the inner circumferential clutch groove 60. 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 59, the ball 64 to the outer peripheral clutch groove 61 of the piston rod 40 Is inserted, the clutch ring 62 is released in the axial direction with respect to the guide sleeve 59, and fixed in the axial direction with respect to the piston rod (40). Accordingly, the piston rod 40 is deflected in the extending direction together with the clutch ring 62 by the spring force of the compression coil spring 65, so that the door 22 automatically moves to the closed position shown in FIG. . This section is called the deflection section.

In this deflection section, as shown in FIG. 11, since the piston 41 deviates from the range L of the bypass concave portion 58, the piston 41 on the rod-side chamber 39A side with respect to the extension of the piston rod 40. The working fluid flows through the orifice passage 49 of the shutter 46 and the communication passage 45 of the piston 41 to the lower chamber 39B side, and a damping force is generated in accordance with the flow path area of the orifice passage 49. Thereby, the moving speed of the door 22 can be reduced, and the impact and noise at the time of the door 22 closing can be reduced.

The damping force can be adjusted by selectively switching the orifice passage 49 which rotates the shutter 46 and communicates with the communication passage 45 of the piston 41, thereby allowing the weight, dimensions, and desired closure of the door 22 to be adjusted. Appropriate damping force can be obtained according to the speed or the like, or the change in characteristics caused by aging change or room temperature change. When switching the damping force, as shown in Fig. 12, the engagement projections 57 of the intermediate rod guide 34 are moved by moving the piston rod 40 to the position of maximum protrusion, that is, the door 22 to the fully open position. ) And the notch 52 of the shutter 46. In this state, the shutter 46 can be rotated by rotating the cylinder member 31. Thereby, the damping force can be adjusted in the state which attached the cylinder apparatus 30 to the sliding door. At this time, the rotational position of the shutter 46 can be easily indexed by the detent action due to the coupling and detachment of the detent concave portion 50 and the detent convex portion 51. In addition, the rotational position of the shutter 46 can be visually confirmed by marking the cylinder member 31 and the piston rod 40. Further, the detent concave portion 50 and the detent convex portion 51 can be confirmed without marking. It can recognize by the touch of a detent effect | action.

In this embodiment, as shown in FIG. 14, three sets of three detent recesses 50 are provided on the end face of the piston 41, and between three detent recesses 50 in the same tank. Since the interval (60 °) between the interval 30 ° and the detent recess 50 of the adjacent jaw is different, after the orifice passage 49 is switched to three stages of "large", "medium" and "small", It can be recognized as a texture by this angle difference that it returned to next "large". In addition, in each tank, it is not necessary to arrange the detent recesses 50 at equal intervals, but may be arranged at different intervals.

When the door 22 is opened in the closed state, the shutter 46 acts as a check valve with respect to the stroke of the piston 41 along the shortening of the piston rod 40, and the disc spring 48 is bent to release the shutter. The 46 is spaced apart from the piston 41 so that the communication path 45 is opened, and the working liquid on the lower side chamber 39B side flows almost without flow resistance to the rod side chamber 39A side. Since the damping force hardly occurs by this, the door 22 can be opened smoothly against the spring force of the compression coil spring 65 only.

When the door 22 is opened to a predetermined position, as shown in FIG. 10, the piston rod 40 is shortened so that the outer clutch groove 61 of the guide sleeve 59 together with the clutch ring 62. When passing through the inner circumferential clutch groove 60, the ball 64 is inserted into the inner circumferential clutch groove 60 of the guide sleeve 59 so that the clutch ring 62 is released in the axial direction with respect to the piston rod 40. And axially fixed with respect to the guide sleeve 59. Accordingly, the piston rod 40 is open from the spring force of the compression coil spring 65 to be free to move and is switched from the deflection section to the free section.

In addition, as shown in FIG. 8, when the door 22 is moved to the vicinity of the fully open position, the deflection section shown in FIG. 11 is again performed, and the piston rod 40 is extended to thereby expand the door 22 described above. As in the case of moving to the close position, 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 piston rod 40 The damping force by the orifice passage 49 acts on the stretching. In this way, the door 22 is automatically moved to the fully open position and maintained. At this time, the moving speed of the door 22 can be reduced, and the shock and noise when the door 22 is fully opened can be reduced.

Next, the first to third modified examples of the third embodiment will be described with reference to FIGS. 16 to 20. In addition, in the following description, the same code | symbol is used for the same part as 3rd Embodiment shown in FIGS. 10-15, and only another part is demonstrated in detail.

The first modification will be described with reference to FIGS. 16 to 18. An enlarged longitudinal cross-sectional view of the vicinity of the piston 41 of the present modification is shown in FIG. 16, and an end surface of the piston rod 41 in the middle rod guide 34 side is shown in FIG. 17, and the piston 41 of the shutter 46 is shown. The side end face is shown in FIG. In the present modification, as shown in Figs. 16 to 18, in contrast to the third embodiment, the shutter 46 is fixed in the axial direction by omitting the disc spring 48, and the shutter 46 Instead of functioning as a check valve, an independent check valve 68 is provided. In addition, the detent concave part 50 and the detent convex part 51 are abbreviate | omitted, and the check valve 68 doubles as a detent mechanism instead.

The structure of the check valve 68 is demonstrated. The piston 41 is provided with a check valve passage 69 for communicating the rod side chamber 39A and the lower side chamber 39B with each other. The opening of the shutter 46 side of the check valve passage 69 is expanded in diameter to form a tapered seat portion 70. On the other hand, in the shutter 46, a valve hole 71 is formed in a portion facing the seat portion 70, and a passage 72 through the rod side chamber 39A passes through the bottom of the valve hole 71. It is. Then, the check ball 73 is inserted into the valve hole 71 and seated on the seat portion 70, and the valve spring 74, which is a compression coil spring, is disposed between the bottom of the valve hole 71 and the check ball 73. Is interposed.

As a result, the check valve 73 is bent from the seat portion 70 with respect to the flow of the working fluid from the lower side chamber 39B side to the rod side chamber 39A side. Thereby allowing flow in this direction. 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. The check valve passage 69 is provided in plural along the circumferential direction on the inner circumferential side of the communication passage 45 as shown in FIG. 17, and the check ball 73 retreats against the spring force of the valve spring 74. The shutter 46 can be rotated by being on the tapered surface of the sheet portion 70. In addition, the check ball 73 is pressed against the tapered seat portion 70 by the spring force of the valve spring 74 to be centered, thereby indexing the rotational position of the shutter 46 and maintaining the position. In order to index the respective positions of the three orifice passages 49 with respect to each of the three communication passages 45, three are arranged at three points in the circumferential direction corresponding to these arrangements. By configuring in this way, the cylinder device which concerns on this modification can exhibit the effect similar to the said 3rd Embodiment.

Next, a second modification of the third embodiment will be described with reference to FIG. 19. 19 is a longitudinal cross-sectional view of the entirety of this modification. As shown in FIG. 19, in this modification, the sleeve 59 divided | segmented in the said 3rd Embodiment is integrated, and is also integrated with the intermediate rod guide 34. As shown in FIG. An oil seal 33 is mounted to the intermediate rod guide 34, and an O-ring 75 is installed between the intermediate rod guide 34 and the cylinder member 31, so that the working fluid is provided at the intermediate rod guide 34. This seal | sticker is not and the working liquid is not enclosed in the rod guide part 36. As shown in FIG. Thereby, the effect similar to the said 3rd Embodiment can be exhibited, and the quantity of working liquid can be reduced, and weight reduction can be aimed at.

Next, a third modification of the third embodiment will be described with reference to FIG. 20. 20 is an enlarged longitudinal sectional view of the vicinity of the cylinder portion 39 of the present modification. As shown in FIG. 20, in this modification, compared with the said 3rd Embodiment, the attachment direction and arrangement | positioning of the piston 41 and the shutter 46 are reversed, and the shutter 46 is lower side chamber 39B side. In addition, the shutter 46 is fixed in the axial direction and an independent check valve 76 is provided instead of the shutter 46 functioning as a valve body of the check valve. In addition, in response to the shutter 46 being arranged on the lower side chamber 39B side, the engagement convex portion 57 of the intermediate rod guide 34 is omitted, and instead of the shutter 46 in the lower side chamber 39B. An engagement member 77 is attached to the notch 52.

The check valve 76 provides a check valve passage 78 for communicating the rod side chamber 39A and the lower side chamber 39B to the piston 41, and an end portion of the piston 41 at the rod side chamber 39A side. The disk valve 79 for opening and closing the check valve passage 78 is attached to allow the flow of the working liquid from the lower side chamber 39B side of the check valve passage 78 to the rod side chamber 39A side. Moreover, the shutter 46 is provided with the some channel | path 80 which always connects the check valve channel | path 78 to the lower side chamber 39B.

The engagement member 77 is an annular member having an outer circumferential groove 81, which is fitted in the cylinder portion 39, and rotates in the axial direction and the circumference around the axis by caulking the sidewall of the cylinder member 31 from the outside to the inside. It is fixed in the direction. Further, the engaging member 82 protrudes from the engaging member 77 to face the notch 52 of the shutter 46 attached to the piston 41, and shortens the piston rod 40 to shorten the piston 41. Is moved to the bottom side of the cylinder member 31, so that the engaging projection 82 can be engaged with the notch 52 of the shutter 46. As shown in FIG.

Thereby, the effect similar to the said 3rd Embodiment can be exhibited. In addition, when adjusting damping force, the piston rod 40 is shortened and the cylinder member 31 is rotated in the state which fitted the engagement convex part 82 of the engagement member 77 to the notch 52 of the shutter 46. As shown in FIG. . Accordingly, the outer circumferential portion of the shutter 46 is slightly bent to rotate the shutter 46 while separating the detent concave portion 50 and the detent convex portion 51, and can be switched to the desired damping force.

In addition, in each said embodiment, although damping force is obtained by narrowing the flow-path area through which fluid flows, a damping force may be obtained by friction between a piston and a cylinder like a friction damper, and a damping force can be generated. It is good to have a structure. However, the most stable damping force can be obtained by using a fluid, especially an emulsion.

In addition, when using the cylinder apparatus of each said embodiment as a door closer, it is better to provide a makeup case around. Particularly, in the case of using an emulsion, since a piston or the like adheres to the piston rod, it is preferable to attach the case.

In addition, in the said 3rd Embodiment, when the piston rod 40 was made into the maximum length or the minimum length, it was set as the structure which rotates the shutter 46. However, the thickness of a shutter is made thick and the engaging convex parts 57 and 82 are made. By lengthening the axial length of, the damping force can be adjusted even if it is slightly less than the maximum length or the minimum length. Thereby, at the time of attachment of this cylinder apparatus, the damping force can be adjusted even if it attaches it so that the person who attaches may not overlap the attachment position to some extent. In addition, the same effect can be obtained even if the engaging convex portions 57 and 82 are allowed to move somewhat in the axial direction.

According to the cylinder device and the door closer according to the present invention, the characteristics required for assisting the opening and closing of the door can be obtained.

In addition, when the spring damper according to the present invention configured as described above starts to close the door and reaches a predetermined angle, the clutch ball spans the outer clutch groove and the ball storage hole so that the clutch ring and the piston rod are integrally connected. The orifice device of the piston is then actuated to close the door while cushioning it. Therefore, since the door is fully buffered and the closing speed is reduced before the door is completely closed, so-called finger pinching is effectively prevented, and when the door is opened, the opener of the door that has not existed at a predetermined opening angle or more ( Automatic opening device). This means that the function of the stopper for maintaining the opening angle of the door can also be imparted. In addition, when the clutch ball is interposed between the inner circumferential clutch groove and the ball receiving hole of the clutch ring, when the piston rod is free from the clutch ring, the elastic force of the compression coil spring of the piston rod does not act, thereby making the opening and closing operation force of the door very small. It can exert several effects.

While only some exemplary embodiments of the invention have been described above, it will be readily apparent to those skilled in the art that various modifications may be made in the exemplary embodiments without departing substantially from the novel teachings and advantages of the invention. Accordingly, all such modifications are intended to be included within the scope of this invention. In addition, all features and all claims of all embodiments may be combined with each other as long as they do not contradict each other.

This application claims priority from Japanese Patent Application No. 2008-124879, filed May 12, 2008, and Japanese Patent Application No. 2008-307570, filed December 2, 2008. The entire disclosures of these Japanese Patent Application Nos. 2008-124879 and 2008-307570, including the specification, claims, drawings and summaries, are hereby incorporated by reference in their entirety.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view of a spring damper as a cylinder device according to a first embodiment of the present invention, showing a state where the piston rod is most retracted.

Figure 2 is an external perspective view showing the clutch ring and the clutch ball deployed.

3 is a diagram showing a state in which the spring damper according to the present invention is mounted on the door, and the door is closed.

4 is a longitudinal sectional view of the spring damper shown in FIG. 3.

FIG. 5 is the same diagram as FIG. 3, showing a slightly open door. FIG.

FIG. 6 is a longitudinal cross-sectional view of the same spring damper as in FIG. 1, showing a state where the piston rod is slightly pressed in. FIG.

FIG. 7 is the same diagram as FIG. 3, showing the state where the tip of the piston rod is at a dead point.

FIG. 8 is the same diagram as FIG. 3, showing a state in which the door is deflected in the opening direction and braked.

FIG. 9 is a longitudinal cross-sectional view of the same spring damper as in FIG. 1, illustrating a state in which the piston rod is fully extended.

It is a longitudinal cross-sectional view of the cylinder apparatus which concerns on 3rd embodiment of this invention.

FIG. 11 is a longitudinal sectional view showing the piston rod in an extended state in the cylinder device shown in FIG. 10.

FIG. 12 is a longitudinal sectional view showing the piston rod extended to the stroke end in the cylinder device shown in FIG.

FIG. 13 is an enlarged longitudinal sectional view of the piston of the cylinder device shown in FIG. 10. FIG.

14 is a cross-sectional view of the piston of the cylinder device shown in FIG. 10.

15 is a cross-sectional view of the shutter of the cylinder device shown in FIG. 10.

It is a longitudinal cross-sectional view which expands and shows the piston part of the cylinder apparatus which concerns on the 1st modified example of 3rd Embodiment of this invention.

17 is a cross-sectional view of the piston of the cylinder device shown in FIG. 16.

18 is a cross-sectional view of the shutter of the cylinder device shown in FIG.

It is a longitudinal cross-sectional view of the cylinder apparatus which concerns on the 2nd modified example of the 3rd Embodiment 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 modified example of 3rd Embodiment of this invention.

<Explanation of symbols for the main parts of the drawings>

1, 31: cylinder member

2, 41: piston

7, 40: load

4, 11, 12, 13, 14, 15: spring mechanism

60, 61, 62, 63, 64, 65: spring mechanism

Claims (10)

As a cylinder device, Cylindrical cylinder members 1 and 31, A rod 7; 40 supported movably in the axial direction with respect to the cylinder member, one end of which protrudes from an end of the cylinder member; Provided inside the cylinder member, the rod being strokeable in a state in which a spring force is applied in a direction in which the rod protrudes when the rod protruding length from the cylinder member is equal to or greater than a predetermined length, and the rod of the rod Spring mechanisms (4, 11, 12, 13, 14, 15; 60, 61, 62 which enable stroke of the rod without applying spring force to the rod when the protruding length from the cylinder member is less than the predetermined length) , 63, 64, 65) Cylinder device comprising a. A working fluid is sealed in at least a portion of the interior of the cylinder member (1; 31), The rods 7 and 40 are connected with pistons 2 and 41 which move in the working fluid inside the cylinder member, The cylinder device further comprises a damping force generating mechanism for generating a damping force by applying a flow resistance to a communication path (45) of the working fluid provided in the piston. The spring mechanism according to claim 1 or 2, An outer circumferential clutch groove 14; 61 provided on an outer circumferential portion of the rods 7; 40, and An inner circumferential clutch groove 13; 60 provided inside the cylinder member 1; 31 to face the outer circumferential clutch groove 61; When the protruding length of the rod from the cylinder member is greater than or equal to a predetermined length, the rod is fixed in the axial direction with respect to the rod and movable in the axial direction with respect to the cylinder member when engaged with the outer circumferential clutch groove. Clutch means (4, 11, 12) engaged with the inner circumferential clutch groove and axially fixed relative to the cylinder member and movable in the axial direction relative to the rod when the protruding length from the cylinder member is less than a predetermined length; 62, 63, 64), Spring means (15; 65) for biasing said clutch means Cylinder device comprising a. 3. A cylinder device according to claim 2, wherein damping force adjusting means (46, 57; 46, 77) for adjusting the damping force of said damping force generating mechanism outside said cylinder member (1; 31) is provided. The shutter 46 according to claim 4, wherein the damping force adjusting means is provided so as to be relatively rotatable with respect to the piston (2; 41), and changes the flow passage area of the communication passage (45) of the working fluid according to the rotational position thereof. Cylinder device). 6. The shutter (46) according to claim 5, wherein the shutter (46) contacts the opening of the communication passage (45) of the working fluid of the piston (2; 41) as a valve body of the check valve to close the valve, and the shutter opens the opening. The cylinder device adapted to open the valve by being spaced apart from the cylinder. 6. The shutter (46) according to claim 5, wherein the piston (2; 41) is rotatably installed about an axis with respect to the rod (7; 40), and when the rod is moved to the stroke end side of the rod, The cylinder device (57; 77) which engages is fixed and installed in the said cylinder member (1; 31) so that it may not rotate about an axis. 3. The cylinder device according to claim 2, wherein the piston (41) is provided with a check valve (46) for allowing the flow of the working fluid only when the rod (40) strokes in the short axis direction. 3. The inner peripheral surface of the cylinder member (1; 31) in which the piston (2; 41) slides, according to claim 2, when the protruding length of the rod (7; 40) is within a predetermined range. The cylinder apparatus in which the bypass recessed part (17; 58) which forms a clearance gap is formed in it. The coil spring (1) according to claim 1, wherein the spring mechanism (1) has a coil spring for applying a force in the protruding direction to the rod when the protruding length of the rod (7; 40) from the cylinder member (1; 31) is equal to or greater than a predetermined length ( 15; 65).

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