JPS6153566B2 - - Google Patents
Info
- Publication number
- JPS6153566B2 JPS6153566B2 JP57177384A JP17738482A JPS6153566B2 JP S6153566 B2 JPS6153566 B2 JP S6153566B2 JP 57177384 A JP57177384 A JP 57177384A JP 17738482 A JP17738482 A JP 17738482A JP S6153566 B2 JPS6153566 B2 JP S6153566B2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- rod
- valve
- orifice
- valve body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000006096 absorbing agent Substances 0.000 claims description 7
- 230000035939 shock Effects 0.000 claims description 7
- 230000006835 compression Effects 0.000 description 12
- 238000007906 compression Methods 0.000 description 12
- 238000013016 damping Methods 0.000 description 6
- 239000007789 gas Substances 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 229910001873 dinitrogen Inorganic materials 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
Classifications
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明はピストンのオリフイス孔を環状の弁体
で開閉するようにした油圧緩衝器に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic shock absorber in which an orifice hole of a piston is opened and closed by an annular valve body.
この種の緩衝器は、シリンダ内に嵌挿したピス
トンにロツドを同軸的に連結するとともに、この
ロツドの外側に位置して複数のオリフイス孔を同
一周上に間隔を存し、かつロツドに対して同軸的
に並設し、これらオリフイス孔が開口されるピス
トンのバルブ座面に環状の弁体を同軸的に設けた
構造となつており、この弁体の外周部がオイル圧
を受けて撓み変形することによつて、オリフイス
孔を開閉するようになつている。 In this type of shock absorber, a rod is coaxially connected to a piston inserted into a cylinder, and a plurality of orifice holes are located on the outside of the rod at intervals on the same circumference, and are connected to the rod. The structure is such that an annular valve body is coaxially provided on the valve seat surface of the piston where these orifice holes are opened, and the outer periphery of this valve body is bent when receiving oil pressure. By deforming, the orifice hole is opened and closed.
ところで、このような緩衝器においては、製造
誤差等によつてピストンに対するロツドの取付位
置がずれたりすると、弁体の内周固定部から各オ
リフイス孔の開口までの距離にばらつきが生じ
る。したがつて、各オリフイス孔に流入するオイ
ル圧が同一であつても、弁体の変形が周方向に均
等になされなくなり、減衰性能にばらつきが生じ
る不具合がある。 By the way, in such a shock absorber, if the mounting position of the rod with respect to the piston deviates due to manufacturing errors or the like, the distance from the inner peripheral fixed part of the valve body to the opening of each orifice hole will vary. Therefore, even if the oil pressure flowing into each orifice hole is the same, the valve body is not deformed evenly in the circumferential direction, resulting in a problem that the damping performance varies.
本発明はこのような事情にもとづいてなされた
もので、環状弁体の弾性変形が周方向に均等にな
され、製造誤差等に基づく減衰性能のばらつきを
確実に防止できる油圧緩衝器の提供を目的とす
る。 The present invention was made based on the above circumstances, and an object of the present invention is to provide a hydraulic shock absorber in which the elastic deformation of the annular valve body is uniform in the circumferential direction, thereby reliably preventing variations in damping performance due to manufacturing errors, etc. shall be.
すなわち本発明は、ピストンのバルブ座面にオ
リフイス孔の開口相互を連通させる環状凹部を形
成するとともに、この環状凹部の底面に、弁体に
おける環状凹部との対向面に当接する支持突部を
突設することにより、上記目的を達成しようとす
るものである。 That is, in the present invention, an annular recess is formed on the valve seat surface of the piston to communicate the openings of the orifice holes, and a support protrusion is protruded on the bottom surface of the annular recess, which abuts the surface of the valve body facing the annular recess. The aim is to achieve the above objectives by establishing the following.
以下、本発明を図面に示す一実施例にもとづい
て説明する。 The present invention will be described below based on an embodiment shown in the drawings.
図中１はシリンダであり、内部にオイルが充填
されている。シリンダ１内はピストン２によつて
第１油圧室３と第２油圧室４とに区画され、この
ピストン２の中心部に嵌入固定した連結体５には
ロツド６が同軸的に連結されている。そしてこの
ロツド６はキヤツプ７を液密に貫通して外方に導
出されている。なお、符号８はロツド６を伸張方
向に付勢するスプリング、９は底付防止用のバン
プストツプを示す。 In the figure, 1 is a cylinder, and the inside is filled with oil. The inside of the cylinder 1 is divided into a first hydraulic chamber 3 and a second hydraulic chamber 4 by a piston 2, and a rod 6 is coaxially connected to a connecting body 5 fitted and fixed in the center of the piston 2. . The rod 6 passes through the cap 7 in a liquid-tight manner and is led out. The reference numeral 8 indicates a spring that urges the rod 6 in the direction of extension, and the reference numeral 9 indicates a bump stop for preventing the rod from bottoming out.
上記ピストン２には連結体５の外側に位置して
第１油圧室３と第２油圧室４相互を連通させる複
数の圧縮用オリフイス孔１０……………と伸張用
オリフイイス孔１１……………とが開設されてい
る。これら両オリフイス孔１０……………および
１１……………は第３図に示したように夫々周方
向に間隔を存し、かつ上記連結体５に対して同軸
的に並設されている。そして圧縮用オリフイス孔
１０……………はピストン２の径方向内側から外
側に向つて傾斜して設けられ、また伸張用オリフ
イス孔１１……………は逆に径方向側から内側に
向つて傾斜して設けられている。このような両オ
リフイス孔１０……………および１１……………
は夫々プレートバルブ１２，１３によつて独立し
て開閉される。プレートバルブ１２，１３は複数
枚の薄肉な円環状弾性板１４……………および１
５……………を重合したもので、圧縮用オリフイ
ス孔１０……………を開閉するプレートバルブ１
２はピストン２の第２油圧室４側の面に設けられ
ているとともに、伸張用オリフイス孔１１………
……を開閉するプレートバルブ１３は第１油圧室
３側の面に設けられている。そして、プレートバ
ルブ１２……………および１３……………は連結
体５の外周部に同軸的に嵌挿されており、その内
周部が連結体５に取着したサポート１６やワツシ
ヤ１７とピストン２の両面との間で挾み込まれて
いる。ピストン２の両面は各オリフイス孔１０…
…………，１１……………が開口されるととも
に、プレートバルブ１２，１３が当接されるバル
ブ座面１８，１９をなしており、このバルブ座面
１８，１９には周方向に連続する環状凹部２０，
２１が凹設されている。環状凹部２０，２１の底
面には上記圧縮用オリフイス孔１０……………お
よび伸張用オリフイス孔１１……………が周方向
に間隔を存して開口されており、各オリフイス孔
１０……………，１１……………の開口相互は環
状凹部２０，２１によつて連通されている。そし
てプレートバルブ１２，１３の表面外周部は、油
圧が加わらない状態において環状凹部２０，２１
の径方向外側の片部２２および内側の片部２３上
に当接されており、この当接により各オリフイス
孔１０……………，１１……………を閉塞してい
る。そして本実施例では、環状凹部２０，２１の
底面に周方向に沿つて支持突部２４，２５が突設
されている。支持突部２４，２５は上記片部２
２，２３間に位置されているとともに、各オリフ
イス孔１０……………および１１……………の開
口間に位置されており、プレートバルブ１２，１
３の環状凹部との対向面となる裏面に当接される
ようになつている。 The piston 2 has a plurality of compression orifice holes 10 and expansion orifice holes 11 which are located outside the connecting body 5 and communicate the first hydraulic chamber 3 and the second hydraulic chamber 4 with each other. ... has been established. As shown in FIG. 3, these orifice holes 10 and 11 are spaced apart from each other in the circumferential direction, and are coaxially arranged in parallel with the connecting body 5. There is. The compression orifice hole 10 is inclined from the inside in the radial direction to the outside of the piston 2, and the expansion orifice hole 11 is provided slanting from the inside in the radial direction to the inside. It is installed at an angle. Both such orifice holes 10...... and 11......
are independently opened and closed by plate valves 12 and 13, respectively. The plate valves 12 and 13 include a plurality of thin annular elastic plates 14 and 1
Plate valve 1 for opening and closing compression orifice hole 10
2 is provided on the surface of the piston 2 on the second hydraulic chamber 4 side, and an extension orifice hole 11...
... A plate valve 13 for opening and closing is provided on the surface on the first hydraulic chamber 3 side. The plate valves 12 and 13 are fitted coaxially into the outer circumferential portion of the connecting body 5, and the inner circumferential portion thereof is attached to the support 16 and washer attached to the connecting body 5. 17 and both sides of the piston 2. Both sides of the piston 2 have respective orifice holes 10...
........., 11...... are opened and form valve seating surfaces 18, 19 against which the plate valves 12, 13 come into contact, and these valve seating surfaces 18, 19 have grooves in the circumferential direction. continuous annular recess 20,
21 is recessed. The compression orifice hole 10 and the expansion orifice hole 11 are opened at the bottoms of the annular recesses 20 and 21 at intervals in the circumferential direction, and each orifice hole 10... The openings of . . . , 11 . . . are communicated with each other by annular recesses 20 and 21. The outer periphery of the surface of the plate valves 12 and 13 has annular recesses 20 and 21 in a state where no hydraulic pressure is applied.
The radially outer piece 22 and the inner piece 23 are brought into contact with each other, and each orifice hole 10..., 11...... is closed by this contact. In this embodiment, support protrusions 24 and 25 are provided to protrude from the bottom surfaces of the annular recesses 20 and 21 along the circumferential direction. The supporting protrusions 24 and 25 are attached to the piece 2
2 and 23, and between the openings of each orifice hole 10 and 11.
It is adapted to be brought into contact with the back surface which is the surface facing the annular recess of No. 3.
また第１油圧室３はキヤツプ２６内の通路２７
およびホース２８を通じてタンク２９に連通され
ており、タンク２９内はフリーピストン３０によ
つて上記第１油圧室３に連なるオイル室３１と例
えば窒素ガスが封入されたガス室３２とに区画さ
れている。 Also, the first hydraulic chamber 3 is connected to a passage 27 in the cap 26.
The inside of the tank 29 is divided by a free piston 30 into an oil chamber 31 connected to the first hydraulic chamber 3 and a gas chamber 32 filled with nitrogen gas, for example. .
なお、上記第１油圧室３の一端部には、圧縮用
オリフイス孔３３……………および伸張用オリフ
イス孔３４……………を備えたベースバルブ３５
が取着されており、これら両オリフイス孔３３…
…………，３４……………も夫々プレートバルブ
３６，３７によつて開閉されるようになつてい
る。 In addition, at one end of the first hydraulic chamber 3, a base valve 35 is provided with a compression orifice hole 33 and an expansion orifice hole 34.
are attached, and these two orifice holes 33...
. . . , 34 . . . are also opened and closed by plate valves 36 and 37, respectively.
次に、上記構成の作用について第５図および第
６図を加えて説明する。 Next, the operation of the above configuration will be explained with reference to FIGS. 5 and 6.
いまロツド６が押し込まれてピストン２に圧縮
方向の力が作用したとすると、第１油圧室３内の
油圧が上昇する。このため第５図中矢印で示した
ように第１油圧室３内のオイルが圧縮用オリフイ
ス孔１０……………内に流入するので、プレート
バルブ１２の表面に油圧が作用する。この油圧に
よりプレートバルブ１２の外周部が弾性変形して
表面外周部がバルブ座面１８の肩部２２から離
れ、上記オリフイス孔１０……………が開かれ
る。この場合、バルブ座面１８にはオリフイス孔
１０……………の開口相互を連通させる環状凹部
２０を設けてあるので、油圧はプレートバルブ１
２の裏面全面に加わることになる。したがつて、
製造誤差等の影響により、プレートバルブ１２に
対するオリフイス孔１０……………の開口位置が
ばらついたとしてもプレートバルブ１２は周方向
に沿つて均等に弾性変形し、夫々のオリフイス孔
１０……………の開口面積が均しくなるので、減
衰性能のばらつきが少なくなる。 If the rod 6 is now pushed in and a compression force is applied to the piston 2, the oil pressure in the first hydraulic chamber 3 will rise. Therefore, as shown by the arrow in FIG. 5, the oil in the first hydraulic chamber 3 flows into the compression orifice hole 10, so that oil pressure acts on the surface of the plate valve 12. This oil pressure elastically deforms the outer circumferential portion of the plate valve 12 so that the outer circumferential surface of the plate valve 12 separates from the shoulder portion 22 of the valve seat surface 18, and the orifice hole 10 is opened. In this case, since the valve seat surface 18 is provided with an annular recess 20 that communicates the openings of the orifice holes 10 with each other, the hydraulic pressure is applied to the plate valve 1.
It will be added to the entire back side of 2. Therefore,
Even if the opening positions of the orifice holes 10 with respect to the plate valve 12 vary due to manufacturing errors, the plate valve 12 is elastically deformed uniformly along the circumferential direction, and each orifice hole 10... Since the opening area of . . . becomes uniform, variations in damping performance are reduced.
一方、ロツド６が引き出されてピストン２に伸
張方向の力が作用すると、第２油圧室４の油圧が
上昇するから、第６図中矢印で示したように第２
油圧室４内のオイルが伸張用オリフイス孔１１…
…………に流入し、この油圧はプレートバルブ１
３に加わる。この場合、プレートバルブ１３が密
接するバルブ座面１９にも上記オリフイス孔１１
……………の開口相互を連通させる環状凹部２１
を設けてあるので、プレートバルブ１３が弾性変
形する状態は上述した圧縮時と同様であり、よつ
て伸張時にあつても減衰性能のばらつきが少なく
なる。 On the other hand, when the rod 6 is pulled out and a force in the direction of extension is applied to the piston 2, the hydraulic pressure in the second hydraulic chamber 4 increases, so that the second hydraulic pressure increases as shown by the arrow in FIG.
The oil in the hydraulic chamber 4 flows into the expansion orifice hole 11...
…………, this hydraulic pressure flows into plate valve 1
Join 3. In this case, the orifice hole 11 is also attached to the valve seat surface 19 that the plate valve 13 is in close contact with.
An annular recess 21 that communicates the openings of
is provided, the state in which the plate valve 13 is elastically deformed is similar to that during compression, as described above, and therefore, variations in damping performance are reduced even during expansion.
またこの構造によると圧縮時には伸張用のプレ
ートバルブ１３が、逆に伸張時には圧縮用のプレ
ートバルブ１２が油圧によつてバルブ座面１８，
１９に押圧される。この際、バルブ座面１８，１
９に環状凹部２０，２１を設けたことから、プレ
ートバルブ１２，１３がこの環状凹部２０，２１
内に入り込むように撓むことが考えられ、本来閉
止されていなければならない状態にあるオリフイ
ス孔１０……………又は１１……………が開かれ
る虞れがある。 Further, according to this structure, the expansion plate valve 13 is activated during compression, and conversely, the compression plate valve 12 is activated by the valve seat 18 and the compression plate valve 12 during expansion.
Pressed by 19. At this time, the valve seat surface 18, 1
Since the annular recesses 20 and 21 are provided in the annular recesses 20 and 21, the plate valves 12 and 13 are connected to the annular recesses 20 and 21.
It is conceivable that the orifice hole 10... or 11......, which should originally be in a closed state, may be opened.
しかるに、この実施例のように、環状凹部２
０，２１に支持突部２４，２５を設ければ、各プ
レートバルブ１２，１３がバルブ座面１８，１９
に押圧されても上記支持突部２４，２５がプレー
トバルブ１２，１３の裏面に当接して支持するの
で、上述の如きプレートバルブ１２，１３の撓み
を防止することができ、減衰性能の向上に寄与す
る。 However, as in this embodiment, the annular recess 2
0 and 21, each plate valve 12 and 13 can be attached to the valve seat surface 18 and 19.
Since the support protrusions 24 and 25 contact and support the back surfaces of the plate valves 12 and 13 even when the plate valves 12 and 13 are pressed, it is possible to prevent the plate valves 12 and 13 from being bent as described above, and to improve damping performance. Contribute.
なお、上述した実施例はガス室をタンク内に形
成したが、シリンダ内をフリーピストンで区画す
ることにより、このシリンダ内にガス室を設けて
も良い。 In addition, although the gas chamber was formed in the tank in the above-mentioned embodiment, the gas chamber may be provided in the cylinder by partitioning the inside of the cylinder with a free piston.
また本発明に係る油圧緩衝器は、ガス加圧式に
特定されないことはもちろんである。 Furthermore, it goes without saying that the hydraulic shock absorber according to the present invention is not limited to a gas pressurized type.
以上詳述したように本発明によれば、弁体が油
圧を受けて弾性変形する際には、この弁体の受圧
面全面に油圧が作用することになり、製造誤差等
により弁体に対するオリフイス孔の開口位置がば
らついたとしても、この弁体の変形が周方向に亘
つて均等になされ、夫々のオリフイス孔の開口面
積が等しくなる。 As detailed above, according to the present invention, when the valve body is elastically deformed in response to hydraulic pressure, the hydraulic pressure acts on the entire pressure-receiving surface of the valve body, and due to manufacturing errors etc., the orifice for the valve body is Even if the opening positions of the holes vary, the deformation of the valve body is uniform over the circumferential direction, and the opening areas of the respective orifice holes become equal.
それとともに、弁体が油圧を受けてバルブ座面
に押し付けられた際にも、この弁体の環状凹部と
の対向面は支持突部によつて支えられるから、弁
体の不所望な撓み変形が防止される。 At the same time, even when the valve body is pressed against the valve seat surface under hydraulic pressure, the face of the valve body facing the annular recess is supported by the supporting protrusion, resulting in undesirable bending and deformation of the valve body. is prevented.
したがつて、減衰性能のばらつきが格段に少な
くなる利点がある。 Therefore, there is an advantage that variations in damping performance are significantly reduced.
図面は本発明の一実施例を示し、第１図は全体
の断面図、第２図はピストン部分の拡大断面図、
第３図は第２図中−線に沿う断面図、第４図
は第２図中部の拡大断面図、第５図および第６
図は作用説明図である。
１……シリンダ、２……ピストン、１０，１１
……オリフイス孔（圧縮用、伸張用オリフイス
孔）、１２，１３……弁体（プレートバルブ）、１
８，１９……バルブ座面、２０，２１……環状凹
部、２４，２５……支持突部。
The drawings show an embodiment of the present invention, with FIG. 1 being an overall sectional view, and FIG. 2 being an enlarged sectional view of a piston portion.
Figure 3 is a sectional view along the line - in Figure 2, Figure 4 is an enlarged sectional view of the middle part of Figure 2, Figures 5 and 6.
The figure is an explanatory diagram of the action. 1...Cylinder, 2...Piston, 10, 11
... Orifice hole (orifice hole for compression, expansion), 12, 13 ... Valve body (plate valve), 1
8, 19... Valve seat surface, 20, 21... Annular recess, 24, 25... Support protrusion.
Claims (1)
動可能に嵌挿し、このピストンにロツドを同軸的
に連結するとともに、このロツドの外側に位置し
て複数のオリフイス孔を同一周上に間隔を存し、
かつロツドに対して同軸的に並設し、これらオリ
フイス孔が開口されるピストンのバルブ座面に、
環状で、しかも薄板状をなした弁体を上記ロツド
に対して同軸的に設け、上記ピストン作動時のオ
イル圧に基づく弁体外周部の変形によりオリフイ
ス孔を開閉するようにした油圧緩衝器において、 上記ピストンのバルブ座面にオリフイス孔の開
口相互を連通させる環状凹部を形成するととも
に、この環状凹部の底面に、上記弁体における環
状凹部との対向面に当接する支持突部を突設した
ことを特徴とする油圧緩衝器。[Claims] 1. A piston is slidably inserted into a cylinder filled with oil, a rod is coaxially connected to this piston, and a plurality of orifice holes are located outside of this rod and arranged around the same circumference. with an interval above,
and on the valve seat surface of the piston, which is arranged coaxially in parallel with the rod, and where these orifice holes are opened.
In a hydraulic shock absorber, an annular and thin plate-shaped valve body is provided coaxially with the rod, and the orifice hole is opened and closed by deformation of the outer periphery of the valve body based on oil pressure when the piston is operated. , an annular recess is formed on the valve seating surface of the piston to communicate the openings of the orifice holes, and a support protrusion is provided protruding from the bottom surface of the annular recess to abut against a surface of the valve body facing the annular recess. A hydraulic shock absorber characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17738482A JPS5969544A (en) | 1982-10-08 | 1982-10-08 | Hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17738482A JPS5969544A (en) | 1982-10-08 | 1982-10-08 | Hydraulic damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5969544A JPS5969544A (en) | 1984-04-19 |
| JPS6153566B2 true JPS6153566B2 (en) | 1986-11-18 |
Family
ID=16029994
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17738482A Granted JPS5969544A (en) | 1982-10-08 | 1982-10-08 | Hydraulic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5969544A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6345459A (en) * | 1986-08-09 | 1988-02-26 | Nippon Denso Co Ltd | Fuel injection valve |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2519364Y2 (en) * | 1989-06-13 | 1996-12-04 | 株式会社ユニシアジェックス | Hydraulic shock absorber |
| JP2578901Y2 (en) * | 1989-09-20 | 1998-08-20 | 株式会社ユニシアジェックス | Variable damping force type hydraulic shock absorber |
| DE69506148T2 (en) * | 1994-03-07 | 1999-05-06 | Delphi Automotive Systems Espana S.A., Cadiz | Suspension leg |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS499431U (en) * | 1972-04-26 | 1974-01-26 |
-
1982
- 1982-10-08 JP JP17738482A patent/JPS5969544A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS499431U (en) * | 1972-04-26 | 1974-01-26 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6345459A (en) * | 1986-08-09 | 1988-02-26 | Nippon Denso Co Ltd | Fuel injection valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5969544A (en) | 1984-04-19 |
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