TW201344077A - Gas spring - Google Patents
Gas spring Download PDFInfo
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- TW201344077A TW201344077A TW101147448A TW101147448A TW201344077A TW 201344077 A TW201344077 A TW 201344077A TW 101147448 A TW101147448 A TW 101147448A TW 101147448 A TW101147448 A TW 101147448A TW 201344077 A TW201344077 A TW 201344077A
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- gas spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0218—Mono-tubular units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3228—Constructional features of connections between pistons and piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
本發明係關於一種氣體彈簧(gas spring)。 The present invention relates to a gas spring.
有一種氣體彈簧，其係將氣體與油液封入壓力缸內，在分隔成二個缸室之活塞設置使流動於二個缸室的流路，且用具有孔口(orifice)之圓盤(disc)來開閉該流路(例如，參照專利文獻1之第4圖)。 There is a gas spring which seals a gas and an oil into a pressure cylinder, and a piston which is divided into two cylinder chambers is provided to flow a flow path to the two cylinder chambers, and a disc having an orifice is used ( This channel is opened and closed (for example, refer to FIG. 4 of Patent Document 1).
(專利文獻1)日本特開平4-102734號公報 (Patent Document 1) Japanese Patent Laid-Open No. Hei 4-102734
在該氣體彈簧中，較期望使安裝角度變化時之作動特性穩定。 In the gas spring, it is more desirable to stabilize the actuation characteristics when the mounting angle is changed.
因而，本發明之目的係在於提供一種能夠謀求作動特性之穩定化的氣體彈簧。 Accordingly, an object of the present invention is to provide a gas spring capable of stabilizing actuation characteristics.
為了達成上述目的，本發明係構成在活塞或圓盤閥，設置有：透過流路使二個缸室始終連通的切口部；以及限制與桿之相對旋轉的限制部，在使用狀態下，是以相對於水平面成為傾斜或水平之方式，使得桿側托架安裝於一側構件，且使得壓力缸側托架安裝於另一側構件，並且前述 切口部，係配置於前述活塞或前述圓盤閥之-下部預定位置。 In order to achieve the above object, the present invention is configured such that a piston or a disk valve is provided with a notch portion that allows the two cylinder chambers to communicate with each other through a flow path, and a restriction portion that restricts relative rotation with the rod, and in use, Mounting the rod side bracket to one side member in such a manner as to be inclined or horizontal with respect to the horizontal plane, and causing the cylinder side bracket to be mounted to the other side member, and the foregoing The notch portion is disposed at a predetermined position of the piston or the lower portion of the disc valve.
依據本發明，能夠謀求作動特性之穩定化。 According to the present invention, it is possible to stabilize the actuation characteristics.
以下，參照圖式就本發明之各實施形態加以說明。 Hereinafter, each embodiment of the present invention will be described with reference to the drawings.
「第1實施形態」 基於第1圖至第5圖說明本發明之第1實施形態。 "First Embodiment" A first embodiment of the present invention will be described based on Figs. 1 to 5 .
如第1圖所示，第1實施形態之氣體彈簧11，係具有：壓力缸12，其係以能夠混合在一起的方式封入有油液等之液體L與氣體G作為作動流體；及活塞15，其係***壓力缸12內，且將壓力缸12內分隔成缸室13與缸室14；及桿16，其係使得一端連結於活塞15且使得另一端突出於壓力缸12之外部；及二片圓盤17、18，其係附設於活塞15之桿16的延伸出側；及油封19，其係密閉桿16與壓力缸12之間；及桿導件20，其係在比壓力缸12內之油封19還靠近外側位置導引桿16；桿側托架21，其係固定於桿16之成為突出側的另一端；以及壓力缸側托架22，其係固定於壓力缸12之一端。第1實施形態之氣體彈簧11，係成為在壓力缸12內不具自由活塞(free piston)之型式。另外，亦可在缸室13設置螺旋彈簧，以對氣體補充彈簧力，或是調整彈簧特性。 As shown in Fig. 1, the gas spring 11 of the first embodiment includes a pressure cylinder 12 in which a liquid L and a gas G such as oil and the like are sealed as an actuating fluid, and a piston 15 , which is inserted into the pressure cylinder 12, and divides the inside of the pressure cylinder 12 into the cylinder chamber 13 and the cylinder chamber 14; and the rod 16 such that one end is coupled to the piston 15 and the other end protrudes outside the pressure cylinder 12; Two discs 17, 18 attached to the extended side of the rod 16 of the piston 15; and an oil seal 19 between the sealing rod 16 and the pressure cylinder 12; and a rod guide 20 attached to the specific pressure cylinder The oil seal 19 in the 12 is also close to the outer position guiding rod 16; the rod side bracket 21 is fixed to the other end of the rod 16 which is the protruding side; and the cylinder side bracket 22 is fixed to the pressure cylinder 12 One end. The gas spring 11 of the first embodiment is a type in which the free piston is not provided in the cylinder 12. Alternatively, a coil spring may be provided in the cylinder chamber 13 to supplement the spring force with the gas or to adjust the spring characteristics.
壓力缸12，係由圓筒狀之壓力缸本體31；以及閉塞壓力缸本體31之一端側的閉塞構件32所構成。在壓力缸本體31，係在閉塞構件32之相反側的中間位置形成有圓環狀之環狀小徑部33，該環狀小徑部33係從外周面朝向徑向內方下凹並且從內周面朝向徑向內方突出，在最大長度時用以防止活塞15與油封19抵接。又，在壓力缸本體31，係在閉塞構件32之相反側之作為端部的開口部34之位置形成有圓環狀之環狀段差部35，該環狀段差部35係從外周面朝向徑向內方下凹並且從內周面朝向徑向內方突出，且以桿導件(rod guide)20不從壓力缸12脫落的方式保持。環狀小徑部33及環狀段差部35，皆是藉由對壓力缸本體31之鉚接加工所形成。 The cylinder 12 is composed of a cylindrical cylinder body 31 and a closing member 32 that closes one end side of the cylinder body 31. In the cylinder main body 31, an annular annular small-diameter portion 33 is formed at an intermediate position on the opposite side of the closing member 32, and the annular small-diameter portion 33 is recessed from the outer peripheral surface toward the inner side in the radial direction and The inner peripheral surface protrudes inward in the radial direction, and serves to prevent the piston 15 from abutting against the oil seal 19 at the maximum length. Further, in the cylinder main body 31, an annular annular step portion 35 is formed at a position of the opening portion 34 as an end portion on the opposite side of the closing member 32, and the annular step portion 35 is oriented from the outer peripheral surface toward the diameter. The inner side is recessed and protrudes inward from the inner peripheral surface in the radial direction, and is held in such a manner that the rod guide 20 does not fall off from the pressure cylinder 12. Both the annular small diameter portion 33 and the annular step portion 35 are formed by caulking of the cylinder body 31.
閉塞構件32，係構成球面狀，且以在外側構成凸狀之姿態固定於壓力缸本體31之與開口部34呈相反側的端部。閉塞構件32，係及於全周毫無間隙地熔接於壓力缸本體31之端部。在閉塞構件32之中央，係在壓力缸本體31之中心軸上以沿著該軸向延伸之方式形成有貫通孔38。 The closing member 32 is formed in a spherical shape and is fixed to an end portion of the cylinder body 31 opposite to the opening portion 34 in a posture in which the outer side is convex. The occluding member 32 is welded to the end of the cylinder body 31 without any gap throughout the circumference. In the center of the closing member 32, a through hole 38 is formed in the central axis of the cylinder body 31 so as to extend along the axial direction.
壓力缸側托架22，係構成具有基板部41及安裝板部42之L字狀，該安裝板部42係從基板部41之一緣部對基板部41構成垂直而延伸出，且在基板部41之中央形成有朝向安裝板部42之相反方向突出的安裝軸部43。在安裝板部42係形成有朝向板厚方向貫通之安裝孔44。壓力缸側托架22，係以將安裝軸部43***壓力缸12之貫通孔38的狀態使得基板部41及於全周毫無間隙地熔接於閉塞 構件32。壓力缸12，係藉由閉塞構件32及壓力缸本體31熔接，且閉塞構件32及壓力缸側托架22熔接，而密閉軸向之壓力缸側托架22側。安裝板部42係沿著壓力缸12之軸向，安裝孔44係沿著壓力缸12之軸正交方向。 The cylinder side bracket 22 has an L shape including a board portion 41 and a mounting plate portion 42. The mounting board portion 42 extends perpendicularly from the edge portion of the board portion 41 to the board portion 41, and is on the substrate. A mounting shaft portion 43 that protrudes in a direction opposite to the mounting plate portion 42 is formed at the center of the portion 41. The mounting plate portion 42 is formed with a mounting hole 44 that penetrates in the thickness direction. The cylinder side bracket 22 is configured such that the mounting shaft portion 43 is inserted into the through hole 38 of the cylinder 12 so that the substrate portion 41 and the entire circumference are welded to each other without any gap. Member 32. The cylinder 12 is welded by the closing member 32 and the cylinder body 31, and the closing member 32 and the cylinder-side bracket 22 are welded to each other to seal the cylinder-side bracket 22 side in the axial direction. The mounting plate portion 42 is along the axial direction of the cylinder 12, and the mounting holes 44 are oriented in the direction orthogonal to the axis of the cylinder 12.
如第2圖所示，活塞15，係具有：滑接於壓力缸12之壓力缸本體31內的圓環狀之活塞本體48；以及由活塞本體48所保持並密封活塞本體48與壓力缸本體31之間隙的O環49。活塞本體48為表背同形狀者，且在徑向之中央，形成有朝向軸向貫通的貫通孔51。該貫通孔51，係軸向之中央成為小徑孔部52，小徑孔部52之軸向兩側成為直徑比小徑孔部52還大的大徑孔部53。 As shown in FIG. 2, the piston 15 has an annular piston body 48 that is slidably connected to the cylinder body 31 of the cylinder 12; and the piston body 48 holds and seals the piston body 48 and the cylinder body. O-ring 49 with a gap of 31. The piston main body 48 has the same shape as the front and back, and a through hole 51 penetrating in the axial direction is formed in the center of the radial direction. The through hole 51 has a small diameter hole portion 52 at the center in the axial direction, and the large diameter hole portion 53 having a diameter larger than the small diameter hole portion 52 is formed on both sides in the axial direction of the small diameter hole portion 52.
在活塞本體48，係在外周部之軸向的中央形成有朝向徑向內方下凹的圓環狀之密封保持槽55，而在比密封保持槽55還靠近徑向內側且比貫通孔51還靠近徑向外側，於周方向以等間隔形成有複數個順沿軸向的流路孔56。又，在活塞本體48，係在流路孔56之軸向的兩側，以與貫通孔51構成同心狀並朝向軸向下凹的方式形成有圓環狀之流路槽57，俾於連繫所有的流路孔56。複數個流路孔56及兩側之流路槽57，係形成當設置於活塞15且活塞15與桿16一起移動時使得作動流體流通的流路58。活塞15，係如第1圖所示配置於壓力缸12中的環狀小徑部33與閉塞構件32之間。壓力缸12之環狀小徑部33，係限制活塞15之朝向開口部34側的移動。 In the piston body 48, an annular seal holding groove 55 that is recessed toward the radially inner side is formed in the center of the axial direction of the outer peripheral portion, and is closer to the radially inner side than the seal holding groove 55 and is larger than the through hole 51. Further, the radially outer side is formed, and a plurality of flow path holes 56 in the axial direction are formed at equal intervals in the circumferential direction. Further, the piston main body 48 is formed with an annular flow path groove 57 on both sides in the axial direction of the flow path hole 56 so as to be concentric with the through hole 51 and recessed in the axial direction. All flow path holes 56 are provided. The plurality of flow path holes 56 and the flow path grooves 57 on both sides form a flow path 58 for allowing the operating fluid to flow when the piston 15 is provided and the piston 15 moves together with the rod 16. The piston 15 is disposed between the annular small diameter portion 33 of the cylinder 12 and the closing member 32 as shown in Fig. 1 . The annular small diameter portion 33 of the pressure cylinder 12 restricts the movement of the piston 15 toward the opening portion 34 side.
桿16，係具有：固定直徑之主軸部61；及中間軸部 62，其係以鄰接於主軸部61之軸向之一端側的方式所形成，且比主軸部61還小徑；及嵌合軸部63，其係以鄰接於中間軸部62之軸向之與主軸部61呈相反之側的方式所形成，且直徑比中間軸部62還小；以及鉚接部64，其係以鄰接於嵌合軸部63之軸向之與中間軸部62呈相反之側的方式所形成，且比嵌合軸部63還大徑。 The rod 16 has a spindle portion 61 of a fixed diameter; and an intermediate shaft portion 62, which is formed to be adjacent to one end side of the axial direction of the main shaft portion 61 and has a smaller diameter than the main shaft portion 61; and the fitting shaft portion 63 is adjacent to the axial direction of the intermediate shaft portion 62. The side opposite to the main shaft portion 61 is formed to have a smaller diameter than the intermediate shaft portion 62; and the caulking portion 64 is opposite to the intermediate shaft portion 62 in the axial direction adjacent to the fitting shaft portion 63. The side is formed and has a larger diameter than the fitting shaft portion 63.
如第2圖所示，中間軸部62，係成為比活塞15之貫通孔51的小徑孔部52還大徑且比大徑孔部53還小徑。嵌合軸部63，係成為比小徑孔部52還稍微小徑，以便能夠嵌合於活塞15之貫通孔51的小徑孔部52。鉚接部64，係在鉚接前與嵌合軸部63成為同徑，且藉由以嵌合軸部63***小徑孔部52直至中間軸部62抵接於一方之大徑孔部53的小徑孔部52側之底面為止的狀態，使得嵌合軸部63之前端側被鉚接所形成。鉚接部64，係成為比小徑孔部52還大徑且比大徑孔部53還小徑。活塞15係藉由形成有鉚接部64而成為對桿16限制軸向移動的狀態。桿16，係如第1圖所示在主軸部61中通過油封19及桿導件20並從壓力缸12朝向外部突出。 As shown in FIG. 2, the intermediate shaft portion 62 has a larger diameter than the small diameter hole portion 52 of the through hole 51 of the piston 15, and has a smaller diameter than the large diameter hole portion 53. The fitting shaft portion 63 is a small diameter hole portion 52 that is slightly smaller than the small diameter hole portion 52 so as to be fitted into the through hole 51 of the piston 15. The caulking portion 64 has the same diameter as the fitting shaft portion 63 before the caulking, and is inserted into the small diameter hole portion 52 by the fitting shaft portion 63 until the intermediate shaft portion 62 abuts against one of the large diameter hole portions 53. The state of the bottom surface of the radial hole portion 52 side is formed such that the front end side of the fitting shaft portion 63 is swaged. The caulking portion 64 has a larger diameter than the small diameter hole portion 52 and a smaller diameter than the large diameter hole portion 53. The piston 15 is in a state in which the rod 16 is restricted from moving in the axial direction by forming the caulking portion 64. The rod 16 passes through the oil seal 19 and the rod guide 20 in the main shaft portion 61 as shown in Fig. 1 and protrudes outward from the cylinder 12.
如第2圖所示，圓盤17，係能夠抵接於活塞15，且構成在徑向之中央形成有朝向軸向貫通的插通孔67之圓環狀。該插通孔67，係能夠插通桿16之中間軸部62。如第3圖所示，在該圓盤17之徑向外側，係形成有一個部位之從外周部朝向徑向內方下凹之形狀的切口部68。該切口部68，換言之，係構成從圓盤17之外周部沿著圓盤17 之徑向朝向外側帶有缺口的形狀。切口部68，係朝向圓盤17之軸向即厚度方向貫通。 As shown in Fig. 2, the disk 17 is abuttable against the piston 15, and has an annular shape in which an insertion hole 67 penetrating in the axial direction is formed in the center in the radial direction. The insertion hole 67 is capable of being inserted into the intermediate shaft portion 62 of the rod 16. As shown in Fig. 3, a notch portion 68 having a shape in which a portion is recessed from the outer peripheral portion toward the inner side in the radial direction is formed on the outer side in the radial direction of the disk 17. The cutout portion 68, in other words, is formed from the outer circumference of the disk 17 along the disk 17 The shape has a notch in the radial direction toward the outside. The notch portion 68 penetrates in the axial direction of the disk 17, that is, in the thickness direction.
如第2圖所示，圓盤17，係成為其外徑比活塞15之流路槽57的最大徑還大徑，且以抵接於活塞15之狀態覆蓋流路槽57。如第4圖所示，藉由形成有圓盤17之切口部68而成為最小的外徑，係成為比流路槽57之最大徑還小徑。因而，圓盤17，係藉由抵接於活塞15而閉塞除了切口部68以外的流路58，而切口部68係始終開放流路58。 As shown in Fig. 2, the disk 17 has a larger outer diameter than the maximum diameter of the flow path groove 57 of the piston 15, and covers the flow path groove 57 in a state of abutting against the piston 15. As shown in Fig. 4, the smallest outer diameter is formed by the notch portion 68 in which the disk 17 is formed, and is smaller than the maximum diameter of the flow path groove 57. Therefore, the disk 17 closes the flow path 58 other than the notch portion 68 by abutting against the piston 15, and the notch portion 68 always opens the flow path 58.
如第2圖所示，圓盤18，係能夠從活塞15之相反側抵接於圓盤17，且構成在徑向之中央形成有朝向軸向貫通的插通孔69之圓環狀。圓盤18，係能夠將桿16之中間軸部62插通於插通孔69，而圓盤18之外徑，係成為與圓盤17之外徑相同。另外，將圓盤17之軸向長度(厚度)與圓盤18之軸向長度(厚度)合在一起的值，係比桿16之中間軸部62之從活塞15突出的突出量還小，因而，圓盤17、18，係能夠利用桿16之中間軸部62的導引而對活塞15及桿16進行軸向移動。另外，亦可使圓盤17、18不能夠對活塞15及桿16進行軸向移動，而藉由彎曲(bending)來開閉流路58。 As shown in Fig. 2, the disk 18 is abuttable against the disk 17 from the opposite side of the piston 15, and has an annular shape in which an insertion hole 69 penetrating in the axial direction is formed in the center of the radial direction. The disk 18 is capable of inserting the intermediate shaft portion 62 of the rod 16 into the insertion hole 69, and the outer diameter of the disk 18 is the same as the outer diameter of the disk 17. Further, the value of combining the axial length (thickness) of the disk 17 with the axial length (thickness) of the disk 18 is smaller than the amount of protrusion of the intermediate shaft portion 62 of the rod 16 from the piston 15. Therefore, the disks 17, 18 can axially move the piston 15 and the rod 16 by the guidance of the intermediate shaft portion 62 of the rod 16. Further, the disks 17 and 18 may not be axially movable to the piston 15 and the rod 16, and the flow path 58 may be opened and closed by bending.
上述之圓盤17及圓盤18，係構成用以開閉活塞15之流路58的環狀之圓盤閥70。如第4圖所示，該圓盤閥70，係在圓盤17抵接於活塞15之狀態下，成為除了由切口部68與流路槽57之連通口所構成的孔口71以外用以 閉塞活塞15之流路58的狀態，且僅透過該孔口71來容許流體之移動。藉此，流體之流路阻抗增大，衰減力上升。此時，孔口71係成為流路58之一端的開口。另一方面，圓盤閥70，係當圓盤17遠離活塞15而開放流路58時，就容許透過流路58之全體的流體之移動。藉此，流體之流路阻抗減少，衰減力下降。利用如此之衰減力的調整來控制桿16之對壓力缸12的移動速度。形成於圓盤閥70之圓盤17的切口部68，係透過流路58而使缸室13與缸室14之二個缸室始終連通。 The disk 17 and the disk 18 described above constitute an annular disk valve 70 for opening and closing the flow path 58 of the piston 15. As shown in Fig. 4, the disk valve 70 is used in addition to the opening 71 formed by the communication port between the cutout portion 68 and the flow path groove 57 in a state where the disk 17 abuts against the piston 15. The state of the flow path 58 of the piston 15 is blocked, and only the orifice 71 is allowed to allow the movement of the fluid. Thereby, the flow path impedance of the fluid increases, and the damping force increases. At this time, the orifice 71 is an opening that is one end of the flow path 58. On the other hand, the disk valve 70 allows the movement of the fluid passing through the entire flow path 58 when the disk 17 is separated from the piston 15 to open the flow path 58. Thereby, the flow path impedance of the fluid is reduced, and the damping force is lowered. The adjustment of such damping force is utilized to control the speed of movement of the rod 16 against the cylinder 12. The notch portion 68 formed in the disk 17 of the disk valve 70 passes through the flow path 58 so that the cylinder chamber 13 and the two cylinder chambers of the cylinder chamber 14 are always in communication.
如第1圖所示，桿導件20，係在徑向之中央形成有朝向軸向貫通的插通孔74，且在徑向之外側依序形成有大徑部75、及比大徑部75還小徑的中間徑部76、及比中間徑部76還小徑的小徑部77。桿導件20，係以使桿16插通於插通孔74的狀態在大徑部75嵌合於鉚接前的壓力缸12。在此狀態下，當壓力缸12之開口部34側的端部被鉚接並形成有環狀段差部35時，該環狀段差部35就會卡合於中間徑部76並使得桿導件20固定於壓力缸12。 As shown in Fig. 1, the rod guide 20 is formed with an insertion hole 74 penetrating in the axial direction in the center in the radial direction, and a large diameter portion 75 and a larger diameter portion are sequentially formed on the radially outer side. The intermediate diameter portion 76 of the small diameter is 75 and the small diameter portion 77 having a smaller diameter than the intermediate diameter portion 76. The rod guide 20 is fitted to the cylinder 12 before the caulking in a state where the rod 16 is inserted into the insertion hole 74 in the large diameter portion 75. In this state, when the end portion on the opening portion 34 side of the cylinder 12 is riveted and the annular step portion 35 is formed, the annular step portion 35 is engaged with the intermediate diameter portion 76 and the rod guide 20 is caused. It is fixed to the pressure cylinder 12.
油封19，係具有：圓環狀之基部80；及位在徑向內側並從基部80朝向軸向一側延伸出的圓環狀之內側唇部81；以及位在徑向外側並從基部80朝向與軸向之內側唇部81同側延伸出的圓環狀之外側唇部82。油封19，係在基部80中強迫抵接於桿導件20之大徑部75側，且在此狀態下，桿16***通於內側唇部81之內側，而在外側唇部82中嵌合於壓力缸12。藉此，油封19，係密封桿16 與壓力缸12之間。 The oil seal 19 has an annular base portion 80 and an annular inner lip portion 81 which is located radially inward and extends from the base portion 80 toward the axial side; and is located radially outward and from the base portion 80. The annular outer lip portion 82 extends toward the same side as the axial inner lip portion 81. The oil seal 19 is forcibly abutted against the large diameter portion 75 side of the rod guide 20 in the base portion 80, and in this state, the rod 16 is inserted into the inner side of the inner lip portion 81 and embedded in the outer lip portion 82. It is combined with the pressure cylinder 12. Thereby, the oil seal 19 is a sealing rod 16 Between the pressure cylinder 12.
桿側托架21，係構成具有基板部85及安裝板部86之L字狀，該安裝板部86係從基板部85之一緣部對基板部85構成垂直而延伸出，且在安裝板部86形成有朝向板厚方向貫通的安裝孔87。在桿側托架21，係藉由熔接將桿16之軸向之與活塞15呈相反之側的端部固定於基板部85之與安裝板部86呈相反之側。安裝板部86，係沿著桿16之軸向，而安裝孔87係沿著桿16之軸向正交。 The lever-side bracket 21 has an L-shape including a base plate portion 85 and a mounting plate portion 86. The mounting plate portion 86 extends perpendicularly from the edge portion of the base plate portion 85 to the base plate portion 85, and is mounted on the mounting plate. The portion 86 is formed with a mounting hole 87 that penetrates in the thickness direction. The rod side bracket 21 is fixed to the side of the board portion 85 opposite to the mounting plate portion 86 by welding the end portion of the rod 16 opposite to the piston 15 in the axial direction. The mounting plate portion 86 is along the axial direction of the rod 16, and the mounting holes 87 are orthogonal along the axial direction of the rod 16.
然後，在第1實施形態中，如第2圖及第3圖所示，桿16之中間軸部62的外周面，係構成由主面部95與平坦面96所構成的D裁切(cut)形狀，該主面部95係形成將以桿16之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面96係連結主面部95之切除側之平行的兩端緣部，且與桿16之中心軸平行。在此，如第1圖所示，桿16之平坦面96，係以用固定於桿16之桿側托架21安裝於安裝對象時成為向上之方式來決定其與桿側托架21的相位關係。換句話說，以桿16之平坦面96成為向上之方式將桿側托架21安裝於安裝對象。 In the first embodiment, as shown in Figs. 2 and 3, the outer peripheral surface of the intermediate shaft portion 62 of the rod 16 is configured to have a D cut formed by the main surface portion 95 and the flat surface 96. In the shape, the main surface portion 95 has a shape in which a cylinder centered on the central axis of the rod 16 is notched at a portion along the axial direction, and the flat surface 96 is coupled to the parallel ends of the cut side of the main surface portion 95. The rim is parallel to the central axis of the rod 16. Here, as shown in Fig. 1, the flat surface 96 of the rod 16 is determined to be in phase with the rod side bracket 21 so as to be upward when the rod side bracket 21 fixed to the rod 16 is attached to the mounting object. relationship. In other words, the rod side bracket 21 is attached to the mounting object such that the flat surface 96 of the rod 16 is upward.
如第3圖所示，配合上述，使圓盤17之桿16插通的插通孔67之內周面，係構成由主面部98與平坦面99所構成的D字狀，該主面部98係形成將以圓盤17之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面99係連結主面部98之切除側之平行的兩端緣部，且與圓盤17之中心軸平行。插通孔67，係形成其主面部98 比主面部95還稍微大徑，以便能夠插通桿16之中間軸部62的主面部95，且成為比主軸部61還小徑，以免從中間軸部62朝向第2圖所示之主軸部61側拔出。又，如第3圖所示，平坦面99之離圓盤17之中心軸的距離，係形成比從桿16之中心軸至平坦面96的距離還稍微長，以便能夠與桿16之平坦面96相對向並藉由抵接於桿16之平坦面96而限制對桿16之旋轉。 As shown in Fig. 3, the inner peripheral surface of the insertion hole 67 through which the rod 16 of the disk 17 is inserted is formed in a D shape including a main surface portion 98 and a flat surface 99, and the main surface portion 98 is formed. Forming a shape in which a cylinder centered on the central axis of the disk 17 is notched at a portion along the axial direction, and the flat surface 99 is coupled to the parallel both end edges of the cut side of the main surface portion 98, and The central axis of the disk 17 is parallel. The through hole 67 is formed to form a main surface portion 98 thereof. The main surface portion 95 is slightly larger in diameter so as to be able to be inserted into the main surface portion 95 of the intermediate shaft portion 62 of the rod 16 and has a smaller diameter than the main shaft portion 61 so as not to be directed from the intermediate shaft portion 62 toward the main shaft portion shown in FIG. Pull out the side 61. Further, as shown in Fig. 3, the distance of the flat surface 99 from the central axis of the disk 17 is formed to be slightly longer than the distance from the central axis of the rod 16 to the flat surface 96 so as to be able to be flat with the rod 16. The rotation of the lever 16 is restricted relative to and by the abutment of the flat face 96 of the rod 16.
換句話說，圓盤17，係以使平坦面96對向於平坦面99的方式藉由使桿16之中間軸部62插通而完成對桿16之旋轉方向的定位，且限制對桿16之相對旋轉。桿16之平坦面96與圓盤17之平坦面99，係構成一邊進行圓盤17與桿16之旋轉方向的定位以限制相對旋轉，一邊容許圓盤17之對桿16之軸向移動的限制部101。 In other words, the disk 17 is positioned such that the flat surface 96 faces the flat surface 99 by inserting the intermediate shaft portion 62 of the rod 16 to complete the positioning of the rod 16 in the rotational direction, and restricting the rod 16 Relative rotation. The flat surface 96 of the rod 16 and the flat surface 99 of the disk 17 define the restriction of the relative rotation of the disk 17 and the rod 16 while restricting the relative rotation, while allowing the axial movement of the disk 17 to the rod 16 Part 101.
然後，圓盤17之平坦面99，係在圓盤17之圓周方向形成於與上述之切口部68相差180度的位置。因而，如第1圖所示，圓盤17之切口部68，係以用固定於桿16之桿側托架21安裝於安裝對象時成為向下之方式來決定其與桿側托架21的相位關係。 Then, the flat surface 99 of the disk 17 is formed at a position 180 degrees apart from the above-described cutout portion 68 in the circumferential direction of the disk 17. Therefore, as shown in Fig. 1, the notch portion 68 of the disk 17 is determined to be downward with respect to the lever-side bracket 21 when the bracket 21 attached to the lever 16 is attached to the mounting target. Phase relationship.
如第2圖所示與圓盤17抵接的圓盤18之插通孔69，係及於全周而構成圓筒面狀，且形成比其主面部95還稍微大徑，以便能夠插通桿16之中間軸部62，且成為比主軸部61還小徑，以免從中間軸部62朝向主軸部61側拔出。 The insertion hole 69 of the disk 18 that abuts against the disk 17 as shown in Fig. 2 is formed into a cylindrical shape over the entire circumference, and is formed to have a larger diameter than the main surface portion 95 so as to be able to be inserted. The intermediate shaft portion 62 of the rod 16 has a smaller diameter than the main shaft portion 61 so as not to be pulled out from the intermediate shaft portion 62 toward the main shaft portion 61 side.
如第1圖所示，如此的氣體彈簧11，係透過安裝於一 側構件110之能夠旋轉的安裝部111與另一側構件112之能夠旋轉的安裝部113之間來使用。此時，桿側托架21之安裝板部86係例如在其厚度方向的基板部85之延出側的相反側之抵接面強迫抵接於安裝部111之支承面(bearing surface)115，且在此狀態下使得螺帽117螺合於從安裝孔87突出的安裝部111之螺桿軸部116，藉此可由螺帽117與支承面115所夾持。同樣地，壓力缸側托架22之安裝板部42，係例如在其厚度方向的基板部41之延出側的相反側之抵接面強迫抵接於安裝部113之支承面119，且在此狀態下使得螺帽121螺合於從安裝孔44突出的安裝部113之螺桿軸部120，藉此可由螺帽121與支承面119所夾持。氣體彈簧11，係可決定如下：在桿側托架21中如上述地安裝於一側構件110之安裝部111，且在壓力缸側托架22中如上述地安裝在另一側構件112之安裝部113。 As shown in Fig. 1, such a gas spring 11 is mounted through a The rotatably mounted mounting portion 111 of the side member 110 is used between the rotatable mounting portion 113 of the other side member 112. At this time, the attachment plate portion 86 of the lever side bracket 21 is forcibly abutted against the bearing surface 115 of the mounting portion 111, for example, on the abutting surface on the side opposite to the extending side of the substrate portion 85 in the thickness direction. In this state, the nut 117 is screwed to the screw shaft portion 116 of the mounting portion 111 protruding from the mounting hole 87, whereby the nut 117 can be held by the support surface 115. Similarly, the attachment plate portion 42 of the cylinder side bracket 22 is forcibly abutted against the bearing surface 119 of the mounting portion 113, for example, on the abutting surface on the side opposite to the extending side of the substrate portion 41 in the thickness direction thereof, and In this state, the nut 121 is screwed to the screw shaft portion 120 of the mounting portion 113 protruding from the mounting hole 44, whereby the nut 121 can be held by the support surface 119. The gas spring 11 can be determined as follows: the rod side bracket 21 is attached to the mounting portion 111 of the one side member 110 as described above, and is mounted to the other side member 112 in the cylinder side bracket 22 as described above. Mounting portion 113.
然後，氣體彈簧11，係藉由一側構件110之安裝部111與另一側構件112之安裝部113相對移動，使得氣體彈簧11一邊整體擺動一邊進行以下的行程：伸展行程，其係強迫增大桿16之從壓力缸12突出的突出量並整體地伸展；以及收縮行程，其係強迫減少桿16之從壓力缸12突出的突出量並整體地收縮。 Then, the gas spring 11 is moved relative to the mounting portion 113 of the other side member 112 by the mounting portion 111 of the one side member 110, so that the gas spring 11 swings as a whole while performing the following stroke: the stretching stroke is forced to increase. The protruding amount of the large rod 16 protruding from the pressure cylinder 12 is integrally extended; and the contraction stroke forcibly reduces the amount of protrusion of the rod 16 protruding from the pressure cylinder 12 and integrally contracts.
另外，氣體彈簧11，係例如在被設置於上邊設置有鉸鏈的排煙窗等之窗口的情況，當閉合時將成為最小長度且呈垂直的狀態，而在窗口開啟90度之狀態下將成為最大 長度，且成為傾斜45度左右的狀態。如此，氣體彈簧，一般是依安裝方法、安裝場所，從最小長度朝向最大長度，使得安裝角度產生變化。亦少有不使角度變化而利用的情形。如此，當一側構件110之安裝部111及另一側構件112之安裝部113在相對移動之全範圍內移動時，有時會在其中一個之位置相對於水平面成為傾斜、或是平行。另外，在連結安裝部111與安裝部113之線相對於水平面呈傾斜時，係以安裝部111成為下側而安裝部113成為上側之方式所安裝。 Further, the gas spring 11 is, for example, a window provided with a smoke exhaust window or the like provided with a hinge on the upper side, and when closed, will be in a minimum length and in a vertical state, and will become a state in which the window is opened at 90 degrees. maximum The length is about 45 degrees. As such, the gas spring is generally changed from the minimum length to the maximum length depending on the mounting method and the installation location. There are also few cases where the angle is not changed. As described above, when the attachment portion 111 of the one-side member 110 and the attachment portion 113 of the other-side member 112 move over the entire range of relative movement, the position of one of them may be inclined or parallel with respect to the horizontal plane. In addition, when the line connecting the attachment portion 111 and the attachment portion 113 is inclined with respect to the horizontal plane, the attachment portion 111 is placed on the lower side and the attachment portion 113 is placed on the upper side.
換句話說，氣體彈簧11，係當處於以如上述所決定之姿態安裝於一側構件110之安裝部111及另一側構件112之安裝部113的使用狀態時，會如第4圖所示，圓盤17、18相對於活塞15成為下側，而圓盤17之切口部68，係成為被配置於包含圓盤17的圓盤閥70之下部的預定位置、具體而言為圓盤17之下端位置的狀態。又，當處於該使用狀態時，在圓盤17之插通孔67中，係成為構成限制部101之平坦面99被配置於上部之預定位置、具體而言為上端位置的狀態。 In other words, when the gas spring 11 is in the use state of the mounting portion 111 of the one side member 110 and the mounting portion 113 of the other side member 112 in the posture determined as described above, as shown in Fig. 4 The discs 17, 18 are lower than the piston 15, and the notch portion 68 of the disc 17 is disposed at a predetermined position, specifically the disc 17, disposed below the disc valve 70 including the disc 17. The status of the lower end position. Moreover, in the use state, the insertion hole 67 of the disk 17 is in a state in which the flat surface 99 constituting the regulating portion 101 is disposed at a predetermined position on the upper portion, specifically, an upper end position.
在氣體彈簧11，雖然在壓力缸12內封入有液體L與氣體G，但是液體L之量，係當處於上述之使用狀態時，會在該擺動範圍之其中一個的位置，如第4圖及第5圖所示，至少被設定為液體L接觸到切口部68的程度之量。 In the gas spring 11, although the liquid L and the gas G are sealed in the pressure cylinder 12, the amount of the liquid L is at a position of one of the swing ranges when in the above-mentioned use state, as shown in Fig. 4 and As shown in Fig. 5, at least the amount by which the liquid L contacts the notch portion 68 is set.
氣體彈簧11，係當處於上述之使用狀態，並從一側構件110之安裝部111與另一側構件112之安裝部113最接 近的位置離開時，成為桿16從壓力缸12伸展出的伸展行程。在其初期，係使得活塞15與圓盤閥70位於比壓力缸12內之液體L還靠近上側，並處於圓盤17、18相對於活塞15在下側分離的狀態，且當活塞15縮窄下側之缸室14時就將缸室14之氣體G透過流路58而流動至缸室13。 The gas spring 11 is in the above-described use state, and is connected to the mounting portion 113 of the other side member 112 from the mounting portion 111 of the one member 110. When the proximal position is released, it becomes an extension stroke in which the rod 16 extends from the pressure cylinder 12. In the initial stage, the piston 15 and the disc valve 70 are located closer to the upper side than the liquid L in the cylinder 12, and are in a state in which the discs 17, 18 are separated from the piston 15 on the lower side, and when the piston 15 is narrowed down. When the cylinder chamber 14 is on the side, the gas G of the cylinder chamber 14 flows through the flow path 58 to the cylinder chamber 13.
之後，由圓盤17、18所構成的圓盤閥70，係接觸到比氣體G還位於下側的液體L而被往上推並在圓盤17中抵接於活塞15，且在流路58之下端位置形成孔口71。一旦抵接到活塞15之狀態的圓盤閥70，係只要伸展行程持續，由於會處在缸室14之壓力比缸室13之壓力還高的狀態並維持抵接到活塞15之抵接狀態，所以在之後的伸展行程中，係透過孔口71使得液體L從缸室14流動至缸室13且衰減力上升。 Thereafter, the disk valve 70 composed of the disks 17 and 18 is brought into contact with the liquid L located lower than the gas G, and is pushed up and abuts against the piston 15 in the disk 17, and is in the flow path. The lower end position of the 58 forms an orifice 71. Once the disc valve 70 is in contact with the state of the piston 15, as long as the extension stroke continues, the pressure at the cylinder chamber 14 is higher than the pressure of the cylinder chamber 13 and maintains the abutment state of the piston 15. Therefore, in the subsequent stretching stroke, the liquid L flows from the cylinder chamber 14 to the cylinder chamber 13 through the orifice 71 and the damping force rises.
然後，在圓盤閥70接觸到上述之液體L時，由於圓盤17之切口部68位於圓盤17之下端位置，所以形成於切口部68的孔口71亦會利用由接觸到該液體L而引起之對活塞15的抵接而位於流路58之下端位置，且在液體L開始流動於孔口71時，桿16之對壓力缸12的位置係成為固定。 Then, when the disc valve 70 is in contact with the liquid L described above, since the slit portion 68 of the disc 17 is located at the lower end position of the disc 17, the orifice 71 formed in the slit portion 68 is also utilized to contact the liquid L. The contact with the piston 15 is caused to be at the lower end position of the flow path 58, and when the liquid L starts to flow to the orifice 71, the position of the rod 16 to the pressure cylinder 12 is fixed.
另一方面，當一側構件110之安裝部111與另一側構件112之安裝部113從最分離之位置接近時，氣體彈簧11，係成為桿16進入壓力缸12的收縮行程。在該收縮行程中，由於缸室14之壓力下降使得缸室13之壓力上升，所以位於缸室13的液體L會一邊使圓盤17、18從活塞 15分離一邊透過比孔口71還寬之流路58流動至缸室14且使得衰減力下降。 On the other hand, when the mounting portion 111 of the one side member 110 approaches the most separated position from the mounting portion 113 of the other side member 112, the gas spring 11 becomes a contraction stroke of the rod 16 into the cylinder 12. In the contraction stroke, since the pressure of the cylinder chamber 14 is increased due to the pressure drop of the cylinder chamber 14, the liquid L located in the cylinder chamber 13 causes the discs 17, 18 to move from the piston. The separation side 15 flows through the flow path 58 which is wider than the orifice 71 to the cylinder chamber 14 and causes the damping force to decrease.
上述之專利文獻1所記載者，由於切口之位置未定，所以衰減力高之衝程範圍在切口變成上側的情況與變成下側的情況會有所不同，故而當作動特性因製品之個體差而有不同時，將有損製品品質。 In the above-described Patent Document 1, since the position of the slit is not fixed, the stroke range in which the damping force is high is different between the case where the slit becomes the upper side and the case where the slit becomes the lower side, and thus the dynamic characteristic is caused by the individual difference of the product. At the same time, it will damage the quality of the product.
相對於此，第1實施形態之氣體彈簧11，係如上述在伸展行程中，從氣體G透過流路58而從缸室14流動至缸室13之狀態開始，藉由液體L使得圓盤閥70強迫抵接於活塞15，並使得從缸室14將液體L流動至缸室13的孔口71形成於流路58。此時，由於構成孔口71之切口部68始終配置於圓盤17之下端位置，所以孔口71亦配置於固定位置，且在液體L開始流動於孔口71時，桿16之對壓力缸12的位置係成為固定。換句話說，若圓盤17能夠對桿16旋轉並使得切口部68未位於固定位置，則雖然孔口71之位置不固定，且在液體L開始流動於孔口71時，桿16之對壓力缸12的位置(減震(damping)開始位置)不成為固定，使得伸展速度不固定而有所變動，但是在第1實施形態之氣體彈簧11中，並不會發生如此的狀況。如此，依據該氣體彈簧11，可謀求作動特性之穩定化。 On the other hand, the gas spring 11 of the first embodiment starts from the state in which the gas G flows through the flow path 58 from the cylinder chamber 14 to the cylinder chamber 13 during the extension stroke, and the disk valve is caused by the liquid L. The force is forced to abut against the piston 15 and the orifice 71 that flows the liquid L from the cylinder chamber 14 to the cylinder chamber 13 is formed in the flow path 58. At this time, since the slit portion 68 constituting the orifice 71 is always disposed at the lower end position of the disk 17, the orifice 71 is also disposed at the fixed position, and when the liquid L starts to flow to the orifice 71, the pair of pressure cylinders of the rod 16 The position of 12 is fixed. In other words, if the disc 17 is capable of rotating the rod 16 such that the slit portion 68 is not in the fixed position, the position of the orifice 71 is not fixed, and when the liquid L begins to flow in the orifice 71, the opposing pressure of the rod 16 The position of the cylinder 12 (damping start position) is not fixed, and the extension speed is not fixed and varies. However, this is not the case in the gas spring 11 of the first embodiment. As described above, according to the gas spring 11, the actuation characteristics can be stabilized.
又，由於作動流體之中的液體L，係在上述之使用狀態下，以至少接觸到切口部68之程度封入壓力缸12內，所以會發生液體L流動於藉由切口部68所形成之孔口71的狀態，因而，可提高謀求作動特性之穩定化的效果。 Further, since the liquid L in the operating fluid is sealed in the cylinder 12 so as to at least contact the notch portion 68 in the above-described use state, the liquid L flows to the hole formed by the slit portion 68. Since the state of the port 71 is improved, the effect of stabilizing the actuation characteristics can be improved.
又，由於以桿16之平坦面96與圓盤17之平坦面99來構成限制圓盤17對桿16之旋轉的限制部101，且將此等對於伸展行程之初期的液體L液面(下側)設為相反方向(上側)，所以可改善伸展行程中的圓盤17之對桿16的滑動性。此係因在伸展行程中當活塞15對液面呈傾斜地進入液體L內時，圓盤17亦會同樣地傾斜並藉由液體L朝向上方往上推，且使其平坦面99一邊從活塞15之平坦面96分離一邊對桿16滑動所致。換句話說，當平坦面96及平坦面99位於下側時，雖然在圓盤17藉由液體L而朝向上方被往上推的情況成為平坦面96與平坦面99之滑動，且接觸面積會增加使得滑動阻抗變大，而有可能妨礙滑動，但是在第1實施形態之氣體彈簧11中，係可抑制如此的滑動阻抗之增大。 Further, since the flat surface 96 of the rod 16 and the flat surface 99 of the disk 17 constitute a restricting portion 101 that restricts the rotation of the disk 17 with respect to the rod 16, and the liquid L level at the beginning of the stretching stroke is The side is set to the opposite direction (upper side), so that the slidability of the rod 17 of the disc 17 in the stretching stroke can be improved. This is because when the piston 15 enters the liquid L obliquely to the liquid surface during the stretching stroke, the disk 17 is also inclined and pushed upward by the liquid L, and the flat surface 99 is pulled from the piston 15 The flat surface 96 separates and slides on the rod 16. In other words, when the flat surface 96 and the flat surface 99 are located on the lower side, the flat surface 96 and the flat surface 99 are slid upward when the disk 17 is pushed upward by the liquid L, and the contact area is The increase in the sliding resistance increases the sliding resistance, but in the gas spring 11 of the first embodiment, such an increase in the sliding resistance can be suppressed.
「第2實施形態」 其次，主要基於第6圖及第7圖並以與第1實施形態之差異部分為中心來說明第2實施形態。另外，有關與第1實施形態共通之部位，係以同一稱呼、同一符號來表示。 [Second Embodiment] Next, the second embodiment will be described mainly on the basis of the difference from the first embodiment based on the sixth and seventh embodiments. In addition, the parts common to the first embodiment are denoted by the same reference numerals and the same symbols.
在第2實施形態中，藉由與第1實施形態之限制部101不同的限制部131，而一邊進行圓盤17與桿16之定位以限制相對旋轉，一邊容許圓盤17之對桿16的軸向移動。換句話說，該限制部131，係由槽部132及突起部133所構成，該槽部132係以在徑向下凹且在軸向延伸之方式形成於桿16之中間軸部62，該突起部133係從圓盤17之插通孔67之內周面朝向徑向內方突出。 In the second embodiment, the positioning of the disk 17 and the rod 16 is performed by the restricting portion 131 different from the regulating portion 101 of the first embodiment, and the relative rotation of the disk 17 is restricted, and the rod 16 of the disk 17 is allowed. Axial movement. In other words, the restricting portion 131 is formed by the groove portion 132 and the protruding portion 133 which is formed in the intermediate shaft portion 62 of the rod 16 so as to be recessed in the radial direction and extend in the axial direction. The protruding portion 133 protrudes inward in the radial direction from the inner circumferential surface of the insertion hole 67 of the disk 17.
換句話說，第2實施形態之桿16的中間軸部62，係具有主面部135、二個部位之槽壁136及槽底面137，該主面部135係形成將以桿16之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該二個部位之槽壁面136係從主面部135之切除側之平行的兩端緣部之各個緣部朝向桿16之徑向的內方延伸出，該槽底面137係連結二個部位之槽壁面136之位於桿16之徑向的內方之端緣部彼此，且兩側之槽壁面136與槽底面137構成槽部132。在此，該槽部132，係藉由固定於桿16之桿側托架21(參照第1圖)而決定其與桿側托架21之相位關係，以便在安裝於一側構件110時成為向上。 In other words, the intermediate shaft portion 62 of the rod 16 of the second embodiment has a main surface portion 135, two groove walls 136, and a groove bottom surface 137 which is formed to be centered on the central axis of the rod 16. The cylinder has a notched shape in a portion along the axial direction, and the groove wall surface 136 of the two portions is directed from the respective edges of the parallel end edges of the cut surface of the main surface portion 135 toward the radial direction of the rod 16. The inner side of the groove extends from the groove bottom wall surface 136 of the two portions to the inner end edge portion of the rod 16 in the radial direction of the rod 16, and the groove wall surface 136 and the groove bottom surface 137 on both sides constitute the groove portion 132. Here, the groove portion 132 is determined by the rod side bracket 21 (see FIG. 1) fixed to the rod 16, and the phase relationship with the rod side bracket 21 is determined so as to be attached to the one side member 110. up.
又，配合上述，第2實施形態之圓盤17，係將使桿16插通的插通孔67之內周面，由主面部140及二個部位之彎曲面部141所構成，該主面部140係形成將以圓盤17之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該二個部位之彎曲面部141係一邊從主面部140之切除側之平行的兩端緣部朝向徑向內方延伸出一邊在前端側連結，且二個部位之彎曲面部141構成突起部133之外面。 In addition, the disk 17 of the second embodiment is configured such that the inner peripheral surface of the insertion hole 67 through which the rod 16 is inserted is formed by the main surface portion 140 and the curved portion 141 of two portions, and the main surface portion 140 is formed. A shape in which a cylinder centered on the central axis of the disk 17 is notched at a portion along the axial direction is formed, and the curved surface portions 141 of the two portions are parallel from the parallel sides of the cut surface of the main surface portion 140. The edge portion is extended inward in the radial direction and joined to the distal end side, and the curved surface portion 141 at the two portions constitutes the outer surface of the protruding portion 133.
圓盤17之插通孔67，係將其主面部140，形成比主面部135還稍微大徑，以便能夠插通桿16之中間軸部62的主面部135，且成為比主軸部61還小徑，以免從中間軸部62朝向主軸部61側拔出。然後，當一邊將突起部133***槽部132一邊使桿16之中間軸部62的主面部135插 通於圓盤17之插通孔67的主面部140時，圓盤17與桿16之相對旋轉，就可藉由突起部133抵接於槽部132而受到限制，且成為藉由突起部133移動於槽部132內而容許圓盤17之對桿16的軸向移動之狀態。 The insertion hole 67 of the disk 17 is formed such that its main surface portion 140 is slightly larger than the main surface portion 135 so as to be able to be inserted into the main surface portion 135 of the intermediate shaft portion 62 of the rod 16, and is smaller than the main shaft portion 61. The diameter is prevented from being pulled out from the intermediate shaft portion 62 toward the side of the main shaft portion 61. Then, the main surface portion 135 of the intermediate shaft portion 62 of the rod 16 is inserted while the projection portion 133 is inserted into the groove portion 132. When the disk portion 17 is inserted into the main surface portion 140 of the through hole 67, the relative rotation of the disk 17 and the rod 16 can be restricted by the protrusion portion 133 abutting against the groove portion 132, and the protrusion portion 133 is formed by the protrusion portion 133. The movement in the groove portion 132 allows the state of the disk 17 to move in the axial direction of the rod 16.
然後，圓盤17之突起部133，係在圓盤17之圓周方向形成於與切口部68相差180度的位置。因而，與第1圖所示之第1實施形態同樣，當桿側托架21安裝於一側構件110且壓力缸側托架22安裝於另一側構件112時，第7圖所示的圓盤17之突起部133就配置於上側，而切口部68，係與第1實施形態同樣，位於圓盤17之下端位置。 Then, the projection 133 of the disk 17 is formed at a position 180 degrees apart from the notch portion 68 in the circumferential direction of the disk 17. Therefore, similarly to the first embodiment shown in Fig. 1, when the rod side bracket 21 is attached to the one side member 110 and the cylinder side bracket 22 is attached to the other side member 112, the circle shown in Fig. 7 The projection 133 of the disk 17 is disposed on the upper side, and the notch portion 68 is located at the lower end of the disk 17 as in the first embodiment.
依據以上所述之第2實施形態，由於使具有切口部68之圓盤17，一邊對桿16進行旋轉方向之定位以限制相對旋轉一邊進行軸向移動的限制部131，係由槽部132及突起部133所構成，所以即便縮小此等之圓周方向長度亦可優異地限制相對旋轉。因而，由於可確保其他圓筒狀之主面部135、140的圓周方向之長度，所以可使圓盤17對桿16更順利地移動。 According to the second embodiment described above, the restricting portion 131 that moves the rod 16 in the rotational direction while restricting the relative rotation while the disk 17 having the notched portion 68 is positioned is the groove portion 132 and Since the protrusions 133 are formed, the relative rotation can be excellently restricted even if the length in the circumferential direction is reduced. Therefore, since the length of the other cylindrical main surface portions 135, 140 in the circumferential direction can be ensured, the disk 17 can be more smoothly moved to the rod 16.
「第3實施形態」 其次，主要基於第8圖及第9圖並以與第1實施形態之差異部分為中心來說明第3實施形態。另外，有關與第1實施形態共通之部位，係以同一稱呼、同一符號來表示。 "Third Embodiment" Next, the third embodiment will be described mainly on the basis of the differences from the first embodiment based on the eighth and ninth embodiments. In addition, the parts common to the first embodiment are denoted by the same reference numerals and the same symbols.
在第3實施形態中，第1實施形態之切口部68係未形成於構成第8圖所示之圓盤閥70的圓盤17，在插通孔 67之內周面亦未形成有第1實施形態之平坦面99。換句話說，圓盤17，係將外周面之整體構成圓筒面狀，且插通孔67之內周面亦整體構成圓筒面狀。又，第1實施形態之圓盤18並未設置，僅有圓盤17以能夠進行軸向移動之方式設置於桿16之中間軸部62。 In the third embodiment, the notch portion 68 of the first embodiment is not formed in the disk 17 constituting the disk valve 70 shown in Fig. 8, and is inserted through the hole. The flat surface 99 of the first embodiment is also not formed on the inner surface of 67. In other words, the disk 17 has a cylindrical surface shape as a whole of the outer peripheral surface, and the inner peripheral surface of the insertion hole 67 also has a cylindrical surface as a whole. Further, the disk 18 of the first embodiment is not provided, and only the disk 17 is provided on the intermediate shaft portion 62 of the rod 16 so as to be axially movable.
又，在第3實施形態中，如第9圖所示，在活塞15之活塞本體48的流路槽57之位置形成有使流路槽57連通於徑向外側的切口部151。藉由該切口部151、與第8圖所示之圓盤17抵接，而在此等之間，形成有透過流路58使缸室13與缸室14始終連通的孔口152。 Further, in the third embodiment, as shown in Fig. 9, a notch portion 151 that allows the flow path groove 57 to communicate with the radially outer side is formed at the position of the flow path groove 57 of the piston main body 48 of the piston 15. The notch portion 151 is in contact with the disk 17 shown in Fig. 8, and between these, an orifice 152 that allows the cylinder chamber 13 and the cylinder chamber 14 to communicate with each other through the flow path 58 is formed.
又，在第3實施形態中，第1實施形態之平坦面96並未形成於桿16之中間軸部62。換句話說，桿16之中間軸部62的外周面係整體構成圓筒面狀。另一方面，桿16之嵌合軸部63的外周面，係構成具有主面部155及平坦面156所構成的D裁切形狀，該主面部155係形成將以桿16之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面156係連結主面部155之切除側之平行的兩端緣部，且與桿16之中心軸平行。在此，桿16之平坦面156，係在用固定於桿16之桿側托架21(參照第1圖)安裝於一側構件110時成為向上之方式來決定其與桿側托架21之相位關係。換句話說，桿16係以平坦面156安裝時成為向上的方式來安裝。 Further, in the third embodiment, the flat surface 96 of the first embodiment is not formed on the intermediate shaft portion 62 of the rod 16. In other words, the outer peripheral surface of the intermediate shaft portion 62 of the rod 16 is formed into a cylindrical surface as a whole. On the other hand, the outer peripheral surface of the fitting shaft portion 63 of the rod 16 is configured to have a D-cut shape including a main surface portion 155 and a flat surface 156 which is formed to be centered on the central axis of the rod 16. The cylinder has a notched shape in a portion along the axial direction, and the flat surface 156 is coupled to the parallel both end edges of the cut side of the main surface portion 155 and is parallel to the central axis of the rod 16. Here, the flat surface 156 of the rod 16 is determined to be in the upward direction when the rod side bracket 21 (see FIG. 1) fixed to the rod 16 is attached to the one side member 110, and is determined to be in the upward direction. Phase relationship. In other words, the rod 16 is mounted in such a manner that the flat surface 156 is mounted upward.
配合上述，活塞15之貫通孔51的小徑孔部52之內周面，構成由主面部160及平坦面161所構成之D字狀， 該主面部160係形成將以活塞15之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面161係連結主面部160之切除側之平行的兩端緣部，且與活塞15之中心軸平行。小徑孔部52，係形成比主面部155稍微大徑，以便能夠插通桿16之嵌合軸部63的主面部155。又，平坦面161之離活塞15之中心軸的距離，係形成比從桿16之中心軸至平坦面156之距離還稍微長，以便能夠與桿16之平坦面156相對向且藉由抵接於桿16之平坦面156而限制相對旋轉。換句話說，活塞15，係以使平坦面156對向於平坦面161之方式使桿16之嵌合軸部63插通藉此完成對桿16之旋轉方向的定位，且限制對桿16之相對旋轉。桿16之平坦面156與活塞15之平坦面161，係構成進行活塞15與桿16之旋轉方向的定位以限制相對旋轉的限制部163。 In addition, the inner circumferential surface of the small-diameter hole portion 52 of the through hole 51 of the piston 15 is formed in a D shape including the main surface portion 160 and the flat surface 161. The main surface portion 160 has a shape in which a cylinder centered on the central axis of the piston 15 is notched in the axial direction, and the flat surface 161 is coupled to the parallel both end edges of the cut surface side of the main surface portion 160. And parallel to the central axis of the piston 15. The small diameter hole portion 52 is formed to have a slightly larger diameter than the main surface portion 155 so as to be able to be inserted into the main surface portion 155 of the fitting shaft portion 63 of the rod 16. Moreover, the distance of the flat surface 161 from the central axis of the piston 15 is formed to be slightly longer than the distance from the central axis of the rod 16 to the flat surface 156 so as to be able to oppose the flat surface 156 of the rod 16 and abut The relative rotation is limited to the flat face 156 of the rod 16. In other words, the piston 15 is such that the flat surface 156 is opposed to the flat surface 161 such that the fitting shaft portion 63 of the rod 16 is inserted thereby completing the positioning of the rod 16 in the rotational direction and restricting the rod 16 Relative rotation. The flat surface 156 of the rod 16 and the flat surface 161 of the piston 15 constitute a restricting portion 163 that positions the piston 15 and the rod 16 in the rotational direction to restrict relative rotation.
然後，活塞15之平坦面161，係在活塞15之圓周方向形成於與上述之切口部151相差180度的位置。因而，與第1圖所示之第1實施形態同樣，當桿側托架21安裝於一側構件110且壓力缸側托架22安裝於另一側構件112時，桿16之平坦面156就變成向上，因而，活塞15之平坦面161在小徑孔部52內成為上側，活塞15之切口部151，係配置於活塞15之下部預定位置，且從流路58之下端沿著活塞15之徑向朝向下方脫落。結果，由活塞15之切口部151與圓盤17所形成的孔口152係與第1實施形態同樣位於圓盤17之下端位置。 Then, the flat surface 161 of the piston 15 is formed at a position different from the above-described cutout portion 151 by 180 degrees in the circumferential direction of the piston 15. Therefore, similarly to the first embodiment shown in Fig. 1, when the rod side bracket 21 is attached to the one side member 110 and the cylinder side bracket 22 is attached to the other side member 112, the flat surface 156 of the rod 16 is When it is upward, the flat surface 161 of the piston 15 is the upper side in the small diameter hole portion 52, and the notch portion 151 of the piston 15 is disposed at a predetermined position below the piston 15, and is located along the lower end of the flow path 58 along the piston 15. Radially falling downwards. As a result, the slit 152 formed by the notch portion 151 of the piston 15 and the disk 17 is located at the lower end position of the disk 17 as in the first embodiment.
依據以上所述之第3實施形態，由於將構成孔口152之切口部151形成於活塞15，所以就圓盤17而言並沒有必要對活塞15及桿16限制相對旋轉，且可將圓盤17之插通孔67的內周面之整體與桿16之中間軸部62之外周面的整體分別形成圓筒面狀。因而，可使圓盤17對桿16更順利地移動。 According to the third embodiment described above, since the slit portion 151 constituting the orifice 152 is formed in the piston 15, it is not necessary for the disc 17 to restrict relative rotation of the piston 15 and the rod 16, and the disc can be used. The entire inner peripheral surface of the insertion hole 67 of the 17 and the outer peripheral surface of the intermediate shaft portion 62 of the rod 16 are each formed into a cylindrical surface. Thus, the disk 17 can be moved more smoothly to the rod 16.
「第4實施形態」 其次，主要基於第10圖及第11圖並以與第1、第3實施形態之差異部分為中心來說明第4實施形態。另外，有關與第1、第3實施形態共通的部位，係以同一稱呼、同一符號來表示。 [Fourth Embodiment] Next, a fourth embodiment will be described mainly on the basis of differences between the first and third embodiments based on the tenth and eleventh drawings. In addition, the parts common to the first embodiment and the third embodiment are denoted by the same reference numerals and the same reference numerals.
在第4實施形態中，與第3實施形態同樣，桿16之嵌合軸部63的外周面，係構成由主面部155及平坦面156所構成的D裁切形狀，且使活塞15之嵌合軸部63插通的小徑孔部52之內周面，係構成由主面部160及平坦面161所構成的D字狀。然後，用由桿16之平坦面156與活塞15之平坦面161所構成的限制部163，來進行活塞15之對桿16的旋轉方向之定位以限制相對旋轉。 In the fourth embodiment, as in the third embodiment, the outer peripheral surface of the fitting shaft portion 63 of the rod 16 is formed in a D-cut shape including the main surface portion 155 and the flat surface 156, and the piston 15 is embedded. The inner circumferential surface of the small diameter hole portion 52 through which the shaft portion 63 is inserted is formed in a D shape including the main surface portion 160 and the flat surface 161. Then, the positioning of the piston 15 in the rotational direction of the rod 16 is performed by the restricting portion 163 composed of the flat surface 156 of the rod 16 and the flat surface 161 of the piston 15 to restrict relative rotation.
又，與第3實施形態同樣，第1實施形態之平坦面96並未形成於桿16之中間軸部62。配合此，第1實施形態之平坦面99並未形成於圓盤17之插通孔67的內周面。換句話說，桿16之中間軸部62的外周面係整體構成圓筒面狀，且圓盤17之插通孔67的內周面亦整體構成圓筒面狀。另外，在圓盤17之外周部，係形成有與第1實施形態同樣的切口部68。 Further, similarly to the third embodiment, the flat surface 96 of the first embodiment is not formed on the intermediate shaft portion 62 of the rod 16. With this arrangement, the flat surface 99 of the first embodiment is not formed on the inner circumferential surface of the insertion hole 67 of the disk 17. In other words, the outer peripheral surface of the intermediate shaft portion 62 of the rod 16 has a cylindrical surface as a whole, and the inner peripheral surface of the insertion hole 67 of the disk 17 also has a cylindrical surface as a whole. Further, a notch portion 68 similar to that of the first embodiment is formed on the outer peripheral portion of the disk 17.
然後，在第4實施形態中的活塞15之外周部的一部分，係形成有朝向軸向之缸室14側即圓盤閥70側突出的凸狀部171。在該凸狀部171，係在該活塞15之徑向的內側，形成有與活塞15之徑向正交的平坦面172。該平坦面172之位置，係與構成限制部163的平坦面161之位置相差90度。 Then, a part of the outer peripheral portion of the piston 15 in the fourth embodiment is formed with a convex portion 171 that protrudes toward the disk valve 70 side which is the axial direction of the cylinder chamber 14 side. In the convex portion 171, a flat surface 172 orthogonal to the radial direction of the piston 15 is formed inside the piston 15 in the radial direction. The position of the flat surface 172 is different from the position of the flat surface 161 constituting the regulating portion 163 by 90 degrees.
配合上述凸狀部171，圓盤17之外周面，係由主面部174及平坦面175所構成，該主面部174係形成將以圓盤17之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面175係連結主面部174之切除側之平行的兩端緣部，且與圓盤17之中心軸平行，在主面部176之位置係形成有切口部68。又，圓盤18之外周面，亦同樣由主面部176及平坦面177所構成，該主面部176係形成將以圓盤18之中心軸為中心的圓筒在沿著軸向之面一部分帶缺口的形狀，該平坦面177係連結主面部176之切除側之平行的兩端緣部，且與圓盤17之中心軸平行。 The outer peripheral surface of the disk 17 is formed by the main surface portion 174 and the flat surface 175, and the main surface portion 174 forms a cylinder centered on the central axis of the disk 17 in the axial direction. A portion having a notch shape, the flat surface 175 is connected to the parallel both end edges of the cut surface side of the main surface portion 174, and is parallel to the central axis of the disk 17, and a notch portion 68 is formed at the position of the main surface portion 176. . Further, the outer peripheral surface of the disk 18 is also constituted by a main surface portion 176 which forms a portion of the cylinder centered on the central axis of the disk 18, and a flat surface 177. In the shape of the notch, the flat surface 177 is connected to the parallel both end edges of the cut side of the main surface portion 176, and is parallel to the central axis of the disk 17.
圓盤17，係在使桿16之中間軸部62插通於插通孔67的狀態下，使得平坦面175對向於活塞15之凸狀部171的平坦面172，藉此，可對活塞15定位於旋轉方向並限制相對旋轉。圓盤18，亦在使桿16之中間軸部62插通於插通孔69的狀態下，使得平坦面177對向於活塞15之凸狀部171的平坦面172，藉此，可對活塞15定位於旋轉方向並限制相對旋轉。換句話說，活塞15之凸狀部171的平坦面172與圓盤17、18之平坦面175、177，係成為 限制部178，該限制部178係一邊進行活塞15與圓盤17、18即圓盤閥70之旋轉方向的定位以限制相對旋轉，一邊容許圓盤閥70之對活塞15及桿16的軸向移動。 The disk 17 is in a state in which the intermediate shaft portion 62 of the rod 16 is inserted into the insertion hole 67 such that the flat surface 175 faces the flat surface 172 of the convex portion 171 of the piston 15, whereby the piston can be opposed to the piston 15 is positioned in the direction of rotation and limits relative rotation. The disk 18 is also in a state in which the intermediate shaft portion 62 of the rod 16 is inserted into the insertion hole 69 such that the flat surface 177 faces the flat surface 172 of the convex portion 171 of the piston 15, whereby the piston can be opposed to the piston 15 is positioned in the direction of rotation and limits relative rotation. In other words, the flat surface 172 of the convex portion 171 of the piston 15 and the flat surfaces 175, 177 of the disks 17, 18 are The restricting portion 178 allows the positioning of the piston 15 and the discs 17, 18, that is, the rotational direction of the disc valve 70, to restrict the relative rotation, while allowing the axial direction of the piston valve 15 and the rod 16 of the disc valve 70. mobile.
然後，圓盤17之平坦面175，係在圓盤17之圓周方向形成於與上述之切口部68相差90度的位置，當使該平坦面175對向於活塞15之凸狀部171的平坦面172時，切口部68係配置於對活塞15之平坦面161及桿16之平坦面156相差180度的位置。因而，與第1圖所示之第1實施形態同樣，當桿側托架21安裝於一側構件110且壓力缸側托架22安裝於另一側構件112時，切口部68，係位於圓盤17之下端位置。 Then, the flat surface 175 of the disk 17 is formed at a position 90 degrees apart from the above-described cutout portion 68 in the circumferential direction of the disk 17, and the flat surface 175 is made flat against the convex portion 171 of the piston 15. At the time of the surface 172, the notch portion 68 is disposed at a position that is different from the flat surface 161 of the piston 15 and the flat surface 156 of the rod 16 by 180 degrees. Therefore, similarly to the first embodiment shown in Fig. 1, when the rod side bracket 21 is attached to the one side member 110 and the cylinder side bracket 22 is attached to the other side member 112, the notch portion 68 is located in a circle. The lower end of the tray 17 position.
依據以上所述之第4實施形態，由於一邊進行圓盤17之對活塞15的旋轉方向之定位以限制相對旋轉一邊容許軸向移動的限制部178，係藉由活塞15之凸狀部171的平坦面172所形成，所以製造容易。 According to the fourth embodiment described above, the restriction portion 178 that allows the axial movement of the disk 15 while restricting the relative rotation while the disk 17 is positioned in the rotational direction of the piston 15 is formed by the convex portion 171 of the piston 15. Since the flat surface 172 is formed, it is easy to manufacture.
另外，第1至第4實施形態之氣體彈簧11，例如係被用在開閉排煙窗、建設機械之引擎罩(engine hood)、設備維修用之門扉等時。 In addition, the gas springs 11 of the first to fourth embodiments are used, for example, when opening and closing the smoke exhaust window, the engine hood of the construction machine, the threshold for equipment maintenance, and the like.
以上所述之實施形態，係透過安裝於一側構件與另一側構件之間的氣體彈簧，其構成是由以下所構成：壓力缸，其係封入有氣體及液體作為作動流體；及活塞，其係***該壓力缸內，且將該壓力缸內分隔成至少二個缸室；及桿，其係使得一端連結於該活塞且使得另一端突出於前述壓力缸之外部；及流路，其係設置於前述活塞，且當前 述桿移動時使得前述作動流體流通；及環狀之圓盤閥，其係可供前述桿插通，且將前述流路予以開閉；及桿側托架，其係設置於前述桿之另一端，且安裝於前述一側構件；以及壓力缸側托架，其係設置於前述壓力缸之一端，且安裝於前述另一側構件，在前述活塞或前述圓盤閥，係設置有：透過前述流路使前述二個缸室始終連通的切口部；以及限制與前述桿之相對旋轉的限制部，在使用狀態下，是以相對於水平面成為傾斜或水平之方式，使得前述桿側托架安裝於前述一側構件，且使得前述壓力缸側托架安裝於前述另一側構件，並且前述切口部，係配置於前述活塞或前述圓盤閥之下部預定位置。因而，由於透過活塞之流路而使二個缸室始終連通的圓盤閥之切口部，係配置於圓盤之下部預定位置，所以液體透過切口部而開始流動至流路時的桿之對壓力缸的位置係成為固定。因而，可謀求作動特性之穩定化。 The embodiment described above is a gas spring that is attached between the one side member and the other side member, and is configured by a pressure cylinder in which a gas and a liquid are sealed as an operating fluid, and a piston. Inserting into the pressure cylinder and dividing the pressure cylinder into at least two cylinder chambers; and a rod having one end coupled to the piston and causing the other end to protrude outside the pressure cylinder; and a flow path thereof Is set in the aforementioned piston, and is currently The movable fluid is caused to flow when the rod is moved; and the annular disk valve is configured to allow the rod to be inserted and to open and close the flow path; and the rod side bracket is disposed at the other end of the rod And the one side member; and the cylinder side bracket, which is disposed at one end of the pressure cylinder and is attached to the other side member, wherein the piston or the disc valve is provided with: a flow path that allows the two cylinder chambers to always communicate with each other; and a restriction portion that restricts relative rotation with the rod, in a state of use, is inclined or horizontal with respect to a horizontal plane, so that the rod side bracket is mounted The one side member is such that the cylinder side bracket is attached to the other side member, and the cutout portion is disposed at a predetermined position of the piston or the lower portion of the disc valve. Therefore, since the notch portion of the disc valve that constantly communicates between the two cylinder chambers through the flow path of the piston is disposed at a predetermined position below the disc, the pair of rods when the liquid passes through the notch portion and starts to flow to the flow path The position of the pressure cylinder is fixed. Therefore, stabilization of the actuation characteristics can be achieved.
又，前述作動液體，係構成在前述使用狀態下，以至少接觸前述切口部之程度封入前述壓力缸內。因而，由於會發生液體透過切口部而流動於流路的狀態，所以可提高謀求作動特性之穩定化的效果。 Further, the actuating liquid is configured to be enclosed in the pressure cylinder to at least contact the notch portion in the use state. Therefore, since the liquid flows through the slit portion and flows into the flow path, the effect of stabilizing the actuation characteristics can be improved.
11‧‧‧氣體彈簧 11‧‧‧ gas spring
12‧‧‧壓力缸 12‧‧‧pressure cylinder
13、14‧‧‧缸室 13, 14‧‧‧ cylinder room
15‧‧‧活塞 15‧‧‧Piston
16‧‧‧桿 16‧‧‧ rod
17、18‧‧‧圓盤 17, 18‧‧‧ disc
19‧‧‧油封 19‧‧‧ oil seal
20‧‧‧桿導件 20‧‧‧ rod guide
21‧‧‧桿側托架 21‧‧‧ rod side bracket
22‧‧‧壓力缸側托架 22‧‧‧Cylinder side bracket
31‧‧‧壓力缸本體 31‧‧‧pressure cylinder body
32‧‧‧閉塞構件 32‧‧‧ occlusion components
33‧‧‧環狀小徑部 33‧‧‧Ringed Small Trails Department
34‧‧‧開口部 34‧‧‧ openings
35‧‧‧環狀段差部 35‧‧‧Annual section
38、51‧‧‧貫通孔 38, 51‧‧‧through holes
41、85‧‧‧基板部 41, 85‧‧‧Parts Department
42、86‧‧‧安裝板部 42, 86‧‧‧Installation Board
43‧‧‧安裝軸部 43‧‧‧Installation shaft
44、87‧‧‧安裝孔 44, 87‧‧‧ mounting holes
48‧‧‧活塞本體 48‧‧‧Piston body
49‧‧‧O環 49‧‧‧O-ring
52‧‧‧小徑孔部 52‧‧‧Small hole
53‧‧‧大徑孔部 53‧‧‧ Large diameter hole
55‧‧‧密封保持槽 55‧‧‧Sealing groove
56‧‧‧流路孔 56‧‧‧Flow hole
57‧‧‧流路槽 57‧‧‧flow channel
58‧‧‧流路 58‧‧‧flow path
61‧‧‧主軸部 61‧‧‧Spindle Department
62‧‧‧中間軸部 62‧‧‧Intermediate shaft
63‧‧‧嵌合軸部 63‧‧‧Fitting shaft
64‧‧‧鉚接部 64‧‧‧Riveting
67、69‧‧‧插通孔 67, 69‧‧‧ inserted through holes
68、151‧‧‧切口部 68, 151‧‧ cut section
70‧‧‧圓盤閥 70‧‧‧disc valve
71、152‧‧‧孔口 71, 152‧‧ ‧ orifice
74‧‧‧插通孔 74‧‧‧ inserted through hole
75‧‧‧大徑部 75‧‧‧The Great Trails Department
76‧‧‧中間徑部 76‧‧‧Intermediate diameter
77‧‧‧小徑部 77‧‧‧Little Trails Department
80‧‧‧基部 80‧‧‧ base
81‧‧‧內側唇部 81‧‧‧ inside lip
82‧‧‧外側唇部 82‧‧‧Outer lip
95、98、135、140、155、160、174、176‧‧‧主面部 95, 98, 135, 140, 155, 160, 174, 176‧‧‧ main faces
96、99、156、161、172、175、177‧‧‧平坦面 96, 99, 156, 161, 172, 175, 177‧‧ ‧ flat surface
101、131、163、178‧‧‧限制部 101, 131, 163, 178‧ ‧ Restrictions
110‧‧‧一側構件 110‧‧‧one side member
111、113‧‧‧安裝部 111, 113‧‧‧ Installation Department
112‧‧‧另一側構件 112‧‧‧The other side member
115、119‧‧‧支承面 115, 119‧‧‧ bearing surface
116‧‧‧螺桿軸部 116‧‧‧ Screw shaft
117、121‧‧‧螺帽 117, 121‧‧‧ nuts
120‧‧‧螺桿軸部 120‧‧‧screw shaft
132‧‧‧槽部 132‧‧‧ slot
133‧‧‧突起部 133‧‧‧Protruding
136‧‧‧槽壁面 136‧‧‧ slot wall
137‧‧‧槽底面 137‧‧‧Slot bottom
141‧‧‧彎曲面部 141‧‧‧Bending face
171‧‧‧凸狀部 171‧‧‧ convex
G‧‧‧氣體 G‧‧‧ gas
L‧‧‧液體 L‧‧‧Liquid
第1圖係顯示本發明之第1實施形態之處於使用狀態的氣體彈簧之剖視圖。 Fig. 1 is a cross-sectional view showing a gas spring in a use state according to a first embodiment of the present invention.
第2圖係顯示本發明之第1實施形態的氣體彈簧之主 要部分的放大剖視圖。 Fig. 2 is a view showing the main part of the gas spring according to the first embodiment of the present invention. A partial enlarged view of the section.
第3圖係顯示本發明之第1實施形態之桿及圓盤的第2圖之X1-X1剖視圖。 Fig. 3 is a cross-sectional view taken along the line X1-X1 of Fig. 2 of the rod and the disk of the first embodiment of the present invention.
第4圖係顯示本發明之第1實施形態的氣體彈簧之主要部分的放大剖視圖。 Fig. 4 is an enlarged cross-sectional view showing a main part of a gas spring according to a first embodiment of the present invention.
第5圖係顯示本發明之第1實施形態的氣體彈簧之壓力缸、桿及圓盤的第4圖之X2-X2剖視圖。 Fig. 5 is a cross-sectional view taken along the line X2-X2 of Fig. 4 showing a cylinder, a rod and a disk of the gas spring according to the first embodiment of the present invention.
第6圖係顯示本發明之第2實施形態的氣體彈簧之主要部分的放大剖視圖。 Fig. 6 is an enlarged cross-sectional view showing a main part of a gas spring according to a second embodiment of the present invention.
第7圖係顯示本發明之第2實施形態的氣體彈簧之桿及圓盤的第6圖之X3-X3剖視圖。 Fig. 7 is a cross-sectional view taken along the line X3-X3 of Fig. 6 showing a gas spring rod and a disk according to a second embodiment of the present invention.
第8圖係顯示本發明之第3實施形態的氣體彈簧之主要部分的放大剖視圖。 Fig. 8 is an enlarged cross-sectional view showing a main part of a gas spring according to a third embodiment of the present invention.
第9圖係顯示本發明之第3實施形態的氣體彈簧之桿及活塞的第8圖之X4-X4剖視圖。 Fig. 9 is a cross-sectional view taken along line X4-X4 of Fig. 8 showing a gas spring rod and a piston according to a third embodiment of the present invention.
第10圖係顯示本發明之第4實施形態的氣體彈簧之主要部分的放大剖視圖。 Fig. 10 is an enlarged cross-sectional view showing a main part of a gas spring according to a fourth embodiment of the present invention.
第11圖係顯示本發明之第4實施形態的氣體彈簧之桿、活塞及圓盤的第10圖之X5-X5剖視圖。 Fig. 11 is a cross-sectional view, taken along the line X5-X5 of Fig. 10, of a gas spring rod, a piston and a disk according to a fourth embodiment of the present invention.
11‧‧‧氣體彈簧 11‧‧‧ gas spring
12‧‧‧壓力缸 12‧‧‧pressure cylinder
13、14‧‧‧缸室 13, 14‧‧‧ cylinder room
15‧‧‧活塞 15‧‧‧Piston
16‧‧‧桿 16‧‧‧ rod
17、18‧‧‧圓盤 17, 18‧‧‧ disc
19‧‧‧油封 19‧‧‧ oil seal
20‧‧‧桿導件 20‧‧‧ rod guide
21‧‧‧桿側托架 21‧‧‧ rod side bracket
22‧‧‧壓力缸側托架 22‧‧‧Cylinder side bracket
31‧‧‧壓力缸本體 31‧‧‧pressure cylinder body
32‧‧‧閉塞構件 32‧‧‧ occlusion components
33‧‧‧環狀小徑部 33‧‧‧Ringed Small Trails Department
34‧‧‧開口部 34‧‧‧ openings
35‧‧‧環狀段差部 35‧‧‧Annual section
38‧‧‧貫通孔 38‧‧‧through holes
41、85‧‧‧基板部 41, 85‧‧‧Parts Department
42、86‧‧‧安裝板部 42, 86‧‧‧Installation Board
43‧‧‧安裝軸部 43‧‧‧Installation shaft
44‧‧‧安裝孔 44‧‧‧Installation holes
48‧‧‧活塞本體 48‧‧‧Piston body
49‧‧‧O環 49‧‧‧O-ring
58‧‧‧流路 58‧‧‧flow path
61‧‧‧主軸部 61‧‧‧Spindle Department
62‧‧‧中間軸部 62‧‧‧Intermediate shaft
63‧‧‧嵌合軸部 63‧‧‧Fitting shaft
64‧‧‧鉚接部 64‧‧‧Riveting
68‧‧‧切口部 68‧‧‧cut section
70‧‧‧圓盤閥 70‧‧‧disc valve
71‧‧‧孔口 71‧‧‧孔口
74‧‧‧插通孔 74‧‧‧ inserted through hole
75‧‧‧大徑部 75‧‧‧The Great Trails Department
76‧‧‧中間徑部 76‧‧‧Intermediate diameter
77‧‧‧小徑部 77‧‧‧Little Trails Department
80‧‧‧基部 80‧‧‧ base
81‧‧‧內側唇部 81‧‧‧ inside lip
82‧‧‧外側唇部 82‧‧‧Outer lip
87‧‧‧安裝孔 87‧‧‧Installation holes
96‧‧‧平坦面 96‧‧‧flat surface
101‧‧‧限制部 101‧‧‧Restrictions
110‧‧‧一側構件 110‧‧‧one side member
111、113‧‧‧安裝部 111, 113‧‧‧ Installation Department
112‧‧‧另一側構件 112‧‧‧The other side member
115、119‧‧‧支承面 115, 119‧‧‧ bearing surface
116‧‧‧螺桿軸部 116‧‧‧ Screw shaft
117‧‧‧螺帽 117‧‧‧ nuts
120‧‧‧螺桿軸部 120‧‧‧screw shaft
121‧‧‧螺帽 121‧‧‧ nuts
G‧‧‧氣體 G‧‧‧ gas
L‧‧‧液體 L‧‧‧Liquid
Claims (4)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011285143A JP5913967B2 (en) | 2011-12-27 | 2011-12-27 | gas spring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| TW201344077A true TW201344077A (en) | 2013-11-01 |
| TWI521156B TWI521156B (en) | 2016-02-11 |
Family
ID=48575885
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW101147448A TWI521156B (en) | 2011-12-27 | 2012-12-14 | Gas spring |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP5913967B2 (en) |
| KR (1) | KR101474079B1 (en) |
| CN (1) | CN103423357B (en) |
| DE (1) | DE102012224392A1 (en) |
| TW (1) | TWI521156B (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101482456B1 (en) * | 2013-12-06 | 2015-01-13 | 주식회사 니프코코리아 | Mixed-type air damper |
| JP6170425B2 (en) * | 2013-12-18 | 2017-07-26 | ニッタ株式会社 | Friction damper |
| JP6174476B2 (en) * | 2013-12-24 | 2017-08-02 | ニッタ株式会社 | Friction damper |
| JP2015209920A (en) * | 2014-04-25 | 2015-11-24 | 日立オートモティブシステムズ株式会社 | Cylinder device and manufacturing method of the same |
| CN107345549B (en) * | 2016-05-04 | 2019-05-24 | 上海汽车集团股份有限公司 | Suspension system and its damper |
| CN108087480A (en) * | 2018-01-29 | 2018-05-29 | 佛山市南海区然铭力佳利五金制品有限公司 | Minitype damper and its piston |
| CN110056594A (en) * | 2019-05-23 | 2019-07-26 | 儒拉玛特自动化技术(苏州)有限公司 | Buffer gear |
| CN113671619B (en) * | 2020-05-14 | 2023-08-25 | 四川龙华光电薄膜股份有限公司 | Reflection type display device and front light source module thereof |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5743162Y2 (en) * | 1976-05-21 | 1982-09-22 | ||
| JPS5347492U (en) * | 1976-09-27 | 1978-04-21 | ||
| JPS5451261U (en) * | 1977-09-16 | 1979-04-09 | ||
| JPS5451262U (en) * | 1977-09-19 | 1979-04-09 | ||
| JPS54112219U (en) * | 1978-01-26 | 1979-08-07 | ||
| JPH04102734A (en) | 1990-08-20 | 1992-04-03 | Tokico Ltd | Gas spring |
| JPH06264953A (en) * | 1993-03-09 | 1994-09-20 | Tokico Ltd | Hydraulic buffer |
| JPH08145103A (en) * | 1994-11-18 | 1996-06-04 | Tokico Ltd | Gas spring |
| JP4212968B2 (en) * | 2003-06-18 | 2009-01-21 | 株式会社ショーワ | Pressure damping force generator for hydraulic shock absorber |
| CN100427793C (en) * | 2004-05-18 | 2008-10-22 | 仇恒超 | Oil-gas spring |
| JP2010196798A (en) * | 2009-02-25 | 2010-09-09 | Kayaba Ind Co Ltd | Valve structure |
| JP2011179550A (en) * | 2010-02-26 | 2011-09-15 | Hitachi Automotive Systems Ltd | Shock absorber |
| JP5518561B2 (en) * | 2010-04-28 | 2014-06-11 | 日立オートモティブシステムズ株式会社 | Shock absorber |
-
2011
- 2011-12-27 JP JP2011285143A patent/JP5913967B2/en not_active Expired - Fee Related
-
2012
- 2012-12-14 TW TW101147448A patent/TWI521156B/en not_active IP Right Cessation
- 2012-12-24 KR KR1020120152090A patent/KR101474079B1/en active IP Right Grant
- 2012-12-27 CN CN201210599471.XA patent/CN103423357B/en not_active Expired - Fee Related
- 2012-12-27 DE DE102012224392A patent/DE102012224392A1/en not_active Ceased
Also Published As
| Publication number | Publication date |
|---|---|
| CN103423357A (en) | 2013-12-04 |
| KR20130075681A (en) | 2013-07-05 |
| KR101474079B1 (en) | 2014-12-17 |
| JP2013133890A (en) | 2013-07-08 |
| JP5913967B2 (en) | 2016-05-11 |
| CN103423357B (en) | 2015-11-25 |
| DE102012224392A1 (en) | 2013-06-27 |
| TWI521156B (en) | 2016-02-11 |
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| MM4A | Annulment or lapse of patent due to non-payment of fees |