JPS6026935Y2 - striking device - Google Patents
striking deviceInfo
- Publication number
- JPS6026935Y2 JPS6026935Y2 JP1980095758U JP9575880U JPS6026935Y2 JP S6026935 Y2 JPS6026935 Y2 JP S6026935Y2 JP 1980095758 U JP1980095758 U JP 1980095758U JP 9575880 U JP9575880 U JP 9575880U JP S6026935 Y2 JPS6026935 Y2 JP S6026935Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- hammer
- chamber
- low
- receiving surface
- 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
Landscapes
- Percussive Tools And Related Accessories (AREA)
Description
【考案の詳細な説明】
この考案はたがねなどの作用工具に往復運動により衝撃
エネルギを与えるピストン式のハンマをそなえた打撃装
置の改良に関する。[Detailed Description of the Invention] This invention relates to an improvement of a striking device equipped with a piston-type hammer that applies impact energy to a working tool such as a chisel through reciprocating motion.
従来第２図に示すように、下降運動時にたがねなどの作
用工具８０を打撃するようにシリンダ８１内に上下方向
に往復自在に嵌装され上昇用受圧面８２を有する大径部
８３をそなえたハンマ８４を、流体圧および／または弾
撥力により下向きに付勢するとともに、上昇用受圧面８
２に油圧を加える下部室８５を、ハンマ８４の位置に関
連して液圧駆動される切換弁（図示しない）の切換動作
によって高圧管路と低圧管路に交番に連通してハンマ８
４を上下駆動するようにした打撃装置においては、一般
に高圧管路および低圧管路にアキュムレータを設けてい
る。Conventionally, as shown in FIG. 2, a large diameter portion 83 having a rising pressure receiving surface 82 is fitted into a cylinder 81 so as to be able to reciprocate in the vertical direction so as to strike a working tool 80 such as a chisel during downward movement. The provided hammer 84 is urged downward by fluid pressure and/or elastic force, and the lifting pressure receiving surface 8
A lower chamber 85 that applies hydraulic pressure to the hammer 8 is alternately connected to the high pressure line and the low pressure line by switching operation of a hydraulically driven switching valve (not shown) in relation to the position of the hammer 84.
In a striking device in which the pump 4 is driven up and down, an accumulator is generally provided in the high-pressure pipe and the low-pressure pipe.
この高圧管路に設けたアキュムレータはハンマ反転時の
サージ圧吸収および油圧ポンプなどの油圧源の高圧油供
給能力の増加をはかるためのものである。The accumulator provided in this high-pressure pipe is intended to absorb surge pressure when the hammer is reversed and to increase the high-pressure oil supply capacity of a hydraulic source such as a hydraulic pump.
これに対して低圧管路に設けたアキュムレータは、ハン
マ８４の下降時において下部室８５から低圧管路に排出
される油を吸収して低圧管路の圧力上昇を防止するため
のものである。On the other hand, the accumulator provided in the low-pressure pipe is for absorbing oil discharged from the lower chamber 85 into the low-pressure pipe when the hammer 84 is lowered, thereby preventing the pressure in the low-pressure pipe from rising.
しかしながら上記打撃装置においては、ハンマ８４が上
昇から下降に反転する際に高圧の下部室８５が低圧管路
に連通ずるため低圧管路には瞬間的に高油圧がかかるの
で、この作用油圧範囲の過大によるアキュムレータのゴ
ム袋の破損をおこしやすく、またハンマ下降中には下部
室８５から大流量の油が低圧管路に排出されるので余程
大きいアキュムレータを使用しない限りその排出油を吸
収蓄積することができず、いきおい多量の油が低圧管路
内をタンクへ流れるため下部室８５の背圧が上昇してハ
ンマ速度ひいては打撃力の低下を招くとともに、打撃装
置からタンク等に至る低圧管路の圧力脈動が大きくゴム
ホースの振動による寿命低下などの不具合を生じていた
。However, in the above-mentioned impact device, when the hammer 84 reverses from rising to falling, the high-pressure lower chamber 85 communicates with the low-pressure pipe, and high hydraulic pressure is momentarily applied to the low-pressure pipe. The rubber bag of the accumulator is likely to be damaged due to oversize, and a large amount of oil is discharged from the lower chamber 85 into the low pressure pipe while the hammer is descending, so unless a very large accumulator is used, the discharged oil will be absorbed and stored. As a result, a large amount of oil flows through the low-pressure pipe to the tank, which increases the back pressure in the lower chamber 85, resulting in a decrease in hammer speed and impact force. The pressure pulsations were large, causing problems such as a shortened lifespan due to vibration of the rubber hose.
この考案は上記従来の欠点を解消するもので、ハンマ下
降時における低圧管路の油流の吸収能力が大きく下部室
の背圧を低く維時でき、低圧管路の圧力脈動を低くおさ
えることができる打撃装置を提供しようとするものであ
る。This invention solves the above-mentioned drawbacks of the conventional technology.The low-pressure pipe has a large oil flow absorption capacity when the hammer descends, and the back pressure in the lower chamber can be kept low, making it possible to suppress pressure pulsations in the low-pressure pipe. The aim is to provide a striking device that can.
以下第１図によってこの考案の一実施例を説明する。An embodiment of this invention will be explained below with reference to FIG.
図中、１は打撃装置で、２はシリンダであり、このシリ
ンダ内にハンマ３が上下方向に摺動自在に嵌装されてい
る。In the figure, 1 is a striking device, 2 is a cylinder, and a hammer 3 is fitted into this cylinder so as to be slidable in the vertical direction.
４はハンマの上部大径部、５はこれと同直径の下部大径
部、６は最上部小径部、７は上部小径部、８は中部小径
部、９は下部小径部である。4 is an upper large diameter part of the hammer, 5 is a lower large diameter part of the same diameter as this, 6 is an uppermost small diameter part, 7 is an upper small diameter part, 8 is a middle small diameter part, and 9 is a lower small diameter part.
下部小径部９の直径は上部小径部７の直径より小さく、
従って下部大径部５の下側に形成された上昇用受圧面１
０の面積は上部大径部４の上側に形成された下降用受圧
面１１の面積より大きい。The diameter of the lower small diameter portion 9 is smaller than the diameter of the upper small diameter portion 7;
Therefore, the rising pressure receiving surface 1 formed on the lower side of the lower large diameter portion 5
The area of 0 is larger than the area of the descending pressure receiving surface 11 formed on the upper side of the upper large diameter portion 4.
また最上部小径部６と上部小径部７との接続部に形成さ
れた段付部１２の面積は上昇用受圧面１０の面積にほぼ
等しくなるよう、最上部小径部６の直径が定められてい
る。Further, the diameter of the uppermost small diameter portion 6 is determined so that the area of the stepped portion 12 formed at the connection portion between the uppermost small diameter portion 6 and the upper small diameter portion 7 is approximately equal to the area of the rising pressure receiving surface 10. There is.
／’％ンマ３の大径部４．５とこの各大径部が嵌り込む
ピストン穴１３によって、シリンダ２内には、ハンマ３
の移動に伴い容積が増減する上部室１４と下部室１５、
−およびハンマ３と共に移動する容積不変の中部室１６
が形成されている。/'% The large diameter portion 4.5 of the hammer 3 and the piston hole 13 into which each of the large diameter portions fit allows the hammer 3 to be inserted into the cylinder 2.
an upper chamber 14 and a lower chamber 15 whose volumes increase and decrease as the
- and a volume-invariant middle chamber 16 moving with the hammer 3;
is formed.
１７は環状のパイロット室、１８は同じく環状の低圧室
で、いずれもピストン穴１３の壁面に凹溝状に連設され
ている。17 is an annular pilot chamber, and 18 is an annular low pressure chamber, both of which are connected to the wall surface of the piston hole 13 in the form of a groove.
１９は段付部１２が挿入された筒状の緩衝室で低圧管路
（後記）に連通している。Reference numeral 19 denotes a cylindrical buffer chamber into which the stepped portion 12 is inserted, and communicates with a low-pressure pipe (described later).
この緩衝室１９の内径はピストンの上部小径部７の直径
より大きくすることが好ましい。The inner diameter of this buffer chamber 19 is preferably larger than the diameter of the upper small diameter portion 7 of the piston.
またノ＼ンマの最上部小径部６が出入する最上室２０お
よび下部小径部９が出入する最下室２１は大気中に連通
している。Further, the uppermost chamber 20 into which the uppermost small diameter portion 6 of the gauge enters and exits, and the lowermost chamber 21 into which the lower small diameter portion 9 enters and exits communicate with the atmosphere.
一方３０はハンマ３の往復運動制御用の切換弁で、その
スプール３１はハウジング３２内に上下方向に摺動自在
に嵌装されている。On the other hand, 30 is a switching valve for controlling the reciprocating motion of the hammer 3, and its spool 31 is fitted in a housing 32 so as to be slidable in the vertical direction.
スプール３１は下方の大径部３３とそれに連続する中径
部３４とから戊る略二段型を呈し、中径部３４の中間部
にはハンマ駆動回路切換用の環状凹溝部３５が、中径部
３４の上端部には同じ＜ノ）ンマ駆動回路切換用の小径
部３６が形成されている。The spool 31 has a substantially two-stage shape consisting of a lower large-diameter portion 33 and a medium-diameter portion 34 continuous thereto, and an annular groove portion 35 for switching the hammer drive circuit is provided in the middle of the medium-diameter portion 34. A small diameter part 36 for switching the same <nominal drive circuit is formed at the upper end of the diameter part 34.
スプール３１の中心部には穴３７が貫通し、この穴の下
端部に形成された太孔３８には、ノ＼ウジング３２に突
設固着したピン３９が僅少量のすきまをもって嵌入して
いる。A hole 37 passes through the center of the spool 31, and a pin 39, which is fixed and protrudes from the nozzle 32, is fitted into a wide hole 38 formed at the lower end of the hole with a slight clearance.
このピン３９の直径は中径部３４の直径より小さく、従
ってスプール３１の下端部の環状の大受圧面４０の面積
は、この大受圧面に相対して中径部３４と大径部３３の
段付部に形成された小受圧面４１の面積より大きい。The diameter of this pin 39 is smaller than the diameter of the medium diameter portion 34, and therefore the area of the annular large pressure receiving surface 40 at the lower end of the spool 31 is the area of the medium diameter portion 34 and large diameter portion 33 relative to this large pressure receiving surface. The area is larger than the area of the small pressure receiving surface 41 formed in the stepped portion.
４２はハウジング３２に設けられた大径部３３が嵌り込
むバルブ穴で、４３はこのバルブ穴と小受圧面４１とで
形成された第一弁室、４４は同様にバルブ穴４２と大受
圧面４０とで形成された第二弁室である。42 is a valve hole provided in the housing 32 into which the large diameter portion 33 fits, 43 is a first valve chamber formed by this valve hole and the small pressure receiving surface 41, and 44 is the valve hole 42 and the large pressure receiving surface. 40 is a second valve chamber formed by.
一方５０は高圧油供給用の高圧管路で、スプールの中径
部３４が嵌り込むバルブ***５１に設けた環状の入口室
５２、第一弁室４３およびシリンダの上部室１４に連通
しており、その人口５３は外部に設けた油圧ポンプなど
の圧力源５４に接続されている。On the other hand, 50 is a high-pressure pipeline for supplying high-pressure oil, which communicates with an annular inlet chamber 52 provided in a small valve hole 51 into which the medium-diameter portion 34 of the spool fits, the first valve chamber 43, and the upper chamber 14 of the cylinder. , the population 53 is connected to an external pressure source 54 such as a hydraulic pump.
５５は高圧管路５０の途中に設けたアキュムレータであ
る。55 is an accumulator provided in the middle of the high-pressure pipe 50.
また５６は戻り曲用の低圧管路で、シリンダの低圧室１
８および切換弁のバルブ***５１の上端部に連通してお
り、その出口５７はタンク５８に接続されている。Also, 56 is a low pressure pipe line for return bending, which is the low pressure chamber 1 of the cylinder.
8 and the upper end of a small valve hole 51 of the switching valve, and its outlet 57 is connected to a tank 58.
５９および６０は低圧管路５６に接続された枝管で、緩
衝室１９に連通している。Branch pipes 59 and 60 are connected to the low pressure pipe 56 and communicate with the buffer chamber 19.
また６１はパイロット管路で、シリンダのパイロット室
１７と切換弁の第二弁室４４を連通する。Further, 61 is a pilot conduit that communicates the pilot chamber 17 of the cylinder with the second valve chamber 44 of the switching valve.
６２は供給兼排出管路で、シリンダの下部室１５と切換
弁のバルブ***５１に設けた環状の供給兼排出室６３と
を連通ずる。Reference numeral 62 denotes a supply/discharge pipe that communicates the lower chamber 15 of the cylinder with an annular supply/discharge chamber 63 provided in the small valve hole 51 of the switching valve.
７０はシリンダ２に上下動自在に挿入されたたがね、７
１はその抜は止め具である。70 is a chisel inserted into cylinder 2 so as to be able to move up and down, 7
1 is the stopper for removing it.
なお上記構成においてシリンダ２およびハウジング３２
は、ハンマやスプール等を収容可能なように固着自在に
適宜分割しである。Note that in the above configuration, the cylinder 2 and the housing 32
It is divided as appropriate so that it can be fixed freely to accommodate hammers, spools, etc.
次に上記構成になる打撃装置の動作を説明する。Next, the operation of the striking device having the above structure will be explained.
第１図はハンマ３が作用工具打撃位置においてたがね７
０を打撃した直後の状態を示し、高圧管路５０が接続さ
れた上部室１４にパイロット室１７が連通ずることによ
り、圧力源５４が発する高圧油Ｐがパイロット管路６１
を経てスプールの大受圧面４０に作用して、それまで鎖
線７２で示す位置にあったスプール３１が第一弁室４３
側（上方）に移動した状態を示す。Figure 1 shows the hammer 3 in the working tool striking position with the chisel 7.
0, the pilot chamber 17 communicates with the upper chamber 14 to which the high pressure pipe 50 is connected, so that the high pressure oil P generated by the pressure source 54 flows into the pilot pipe 61.
is applied to the large pressure-receiving surface 40 of the spool, and the spool 31, which had been in the position shown by the chain line 72, moves to the first valve chamber 43.
Shows the state moved to the side (upward).
なおスプール３１の小受圧面４１にも高油圧Ｐが作用し
ているが、大受圧面４０の方が面積が大きいためスプー
ル３１は上方へ駆動されて図示の状態に切換えられるの
である。The high oil pressure P is also acting on the small pressure receiving surface 41 of the spool 31, but since the large pressure receiving surface 40 has a larger area, the spool 31 is driven upward and switched to the state shown.
このスプール３１の移動により環状凹溝部３５が供給兼
排出室６３と入口室５２とを連通ずるので、ハンマの上
昇用受圧面１０には供給兼排出管路６２を経て高油圧Ｐ
が作用腰上弁用受圧面１０の面積は下降用受圧面１１の
面積より大であるのでハンマ３は上昇する。Due to this movement of the spool 31, the annular groove 35 communicates the supply/discharge chamber 63 with the inlet chamber 52, so that the high hydraulic pressure P
However, since the area of the pressure receiving surface 10 for the above-the-waist valve is larger than the area of the lowering pressure receiving surface 11, the hammer 3 rises.
ハンマ３の上昇に伴って緩衝室１９内の油の一部が低圧
管路５６へ流出し出口５７を経てタンク５８へ戻るが、
ノ＼ンマ３の上昇速度はその下降速度はど大きくする必
要はないので、油の流出に伴い緩衝室１９内に多少の背
圧が生じても差支えない。As the hammer 3 rises, some of the oil in the buffer chamber 19 flows out into the low pressure pipe 56 and returns to the tank 58 via the outlet 57.
Since it is not necessary to increase the ascending speed of the gauge 3 or its descending speed, there is no problem even if some back pressure is generated in the buffer chamber 19 as the oil flows out.
ノ）ンマ３の上昇によるパイロット室１７！断（鎖線７
３で図示）後、次いで低圧室１８が中部室１６に開口し
、ハンマ３がほぼ上部反転位置に達すると、パイロット
室１７が中部室１６に開口してパイロット管路６１が低
圧室１８、低圧管路５６と連通ずる。(n) Pilot room 17 due to the rise of Nma 3! Cut (dashed line 7
3), then the low pressure chamber 18 opens to the middle chamber 16, and when the hammer 3 reaches almost the upper inversion position, the pilot chamber 17 opens to the middle chamber 16 and the pilot conduit 61 opens to the low pressure chamber 18, the low pressure It communicates with the conduit 56.
これにより第二弁室４４内は急速に低圧となり、スプー
ル３１は第二弁室側（下方）へ駆動され鎖線７２で示す
位置まで移動する。As a result, the pressure inside the second valve chamber 44 becomes low rapidly, and the spool 31 is driven toward the second valve chamber (downward) and moves to the position shown by the chain line 72.
スプール３１の下方への移動により供給兼排出室６３と
入口室５２との連通は断たれ、供給兼排出室６３はスプ
ール上端部の小径部３６とバルブ***５１のすきまを介
して低圧管路５６に連通し、これに伴って供給兼排出管
路６２およびシリンダの下部室１５が低圧となるめ、ハ
ンマ３は下降用受圧面１１に作用する高油圧Ｐにより下
方に駆動される。Due to the downward movement of the spool 31, communication between the supply/discharge chamber 63 and the inlet chamber 52 is cut off, and the supply/discharge chamber 63 is connected to the low pressure pipe 56 through the gap between the small diameter portion 36 at the upper end of the spool and the valve small hole 51. As a result, the pressure in the supply/discharge pipe 62 and the lower chamber 15 of the cylinder becomes low, and the hammer 3 is driven downward by the high hydraulic pressure P acting on the lowering pressure receiving surface 11.
このときハンマ３の下降に伴い下部室１５内から流出す
る油の殆んど全部が低圧管路５６を経てノ＼ンマ３の下
降により容積の増加する緩衝室１９内に流入し、大量の
油がタンク５８へ戻ることはないので、下部室１５の背
圧は低くノ＼ンマ３が低抗少なく高速度で降下する。At this time, almost all of the oil flowing out from the lower chamber 15 as the hammer 3 descends passes through the low pressure pipe 56 and flows into the buffer chamber 19 whose volume increases as the hammer 3 descends, resulting in a large amount of oil flowing out. does not return to the tank 58, so the back pressure in the lower chamber 15 is low and the gauge 3 descends at high speed with low resistance.
ハンマ３がほぼ第１図示の位置に達したがね７０を打撃
すると、パイロット室１７が高圧管路５０と連通して切
換弁のスプール３１を第一弁室側（上方）に駆動し、以
下上記の運動を繰返すのである。When the hammer 3 reaches approximately the position shown in the first diagram and hits the spring 70, the pilot chamber 17 communicates with the high-pressure pipe 50 and drives the spool 31 of the switching valve toward the first valve chamber (upward). Repeat the above exercise.
なお上記の運動において、ハンマ３の上昇中にアキュム
レータ５５に苗圧された高圧油がノ）ツマ３下降時に高
圧管路５０中に放出されるため高圧管路５０の圧力低下
は少なく、前記の下部室１５の背圧が低いこととあいま
ってハンマ３は一層高速度で降下し、たがね７０には大
きな打撃力が与えられるのである。In addition, in the above movement, the high-pressure oil applied to the accumulator 55 while the hammer 3 is rising is released into the high-pressure pipe 50 when the knob 3 is lowering, so the pressure drop in the high-pressure pipe 50 is small, and the pressure drop in the high-pressure pipe 50 is small. Combined with the low back pressure in the lower chamber 15, the hammer 3 descends at a higher speed, and a greater striking force is applied to the chisel 70.
なお以上はハンマの下降運動を油圧力によっておこなう
場合について説明したが、この考案はハンマの下降運動
をばねや圧縮ガスなどの弾撥力によって、あるいはこの
弾撥力と流体圧力を伴用しておこなう形式の打撃装置に
も適用できるものである。The above description has been about the case in which the downward movement of the hammer is performed by hydraulic pressure, but this invention also uses the elastic force of a spring or compressed gas, or the combination of this elastic force and fluid pressure to perform the downward movement of the hammer. It can also be applied to a type of striking device.
また切換弁のスプールは糸巻状など上記の２段型以外の
形状のものであってもよい。Further, the spool of the switching valve may have a shape other than the two-stage type described above, such as a pincushion shape.
以上説明したようにこの考案によれば、ハンマに上昇用
受圧面の面積とほぼ等しい面積を有し上方が小径の段付
部を設け、この段付部をシリンダに設けた緩衝室内に挿
入し、この緩衝室を低圧管路に接続したので、ハンマ下
降時に下部室から低圧管路に流出する油の殆んど全部を
上記緩衝室内に流入させることができ、ハンマ下降中に
おける下部室の背圧が低く、大きなハンマ速度が得られ
るとともに、低圧管路の圧力脈動が小さく、また低圧管
路にアキュムレータを用いる必要がないため保守の手間
が減り長寿命の打撃装置が得られる。As explained above, according to this invention, the hammer is provided with a stepped part that has an area approximately equal to the area of the lifting pressure receiving surface and has a small diameter at the top, and this stepped part is inserted into the buffer chamber provided in the cylinder. Since this buffer chamber is connected to the low-pressure pipe, almost all of the oil that flows out from the lower chamber to the low-pressure pipe when the hammer is lowered can flow into the buffer chamber, and the back of the lower chamber can be Since the pressure is low and a high hammer speed can be obtained, the pressure pulsation in the low-pressure line is small, and there is no need to use an accumulator in the low-pressure line, maintenance efforts are reduced and a striking device with a long life can be obtained.
第１図はこの考案の一実施例を示す打撃装置の縦断面図
、第２図は従来の打撃装置の略示縦断面図である。
１・・・・・・打撃装置、２・・・・・・シリンダ、３
・・・・・・ハンマ、４・・・・・・上部大径部、５・
・・・・・下部大径部、６・・・・・・最上部小径部、
７・・・・・・上部小径部、１０・・・・・・上昇用受
圧面、１２・・・・・・段付部、１５・・・・・・下部
室、１９・・・・・・緩衝室、３０・・・・・・切換弁
、５０・・・・・・高圧管路、５６・・・・・・低圧管
路、５９・・・・・・枝管、６０・・・・・・枝管、７
０・・・・・・たがね。FIG. 1 is a longitudinal sectional view of a striking device showing an embodiment of this invention, and FIG. 2 is a schematic longitudinal sectional view of a conventional striking device. 1...Blow device, 2...Cylinder, 3
... Hammer, 4 ... Upper large diameter section, 5.
...Lower large diameter part, 6...Top small diameter part,
7... Upper small diameter part, 10... Pressure receiving surface for rising, 12... Stepped part, 15... Lower chamber, 19...・Buffer chamber, 30...Switching valve, 50...High pressure pipe line, 56...Low pressure pipe line, 59...Branch pipe, 60... ...branch pipe, 7
0...Tagane.
Claims (1)
リンダ内に上下方向に往復自在に嵌装され上昇用受圧面
を有する大径部をそなえたハンマを、流体圧および／ま
たは弾撥力により下向きに付勢するとともに、上記上昇
用受圧面に油圧を加える下部室を、上記ハンマの位置に
関連して液圧駆動される切換弁の切換動作によって高圧
管路と低圧管路に交番に連通して上記ハンマを上下駆動
するようにした打撃装置において、上記ハンマの上記上
昇用受圧面の面積とほぼ等しい面積を有し上方が小径の
段付部を設け、上記シリンダに設けた緩衝室内に上記段
付部を挿入し、上記緩衝室を上記低圧管路に接続したこ
とを特徴とする打撃装置。A hammer equipped with a large diameter part that is fitted in a cylinder so as to be able to reciprocate vertically in the vertical direction and has a pressure-receiving surface for upward movement so as to strike a working tool such as a chisel during downward movement is driven by fluid pressure and/or elastic force. The lower chamber, which applies hydraulic pressure to the lifting pressure receiving surface, is alternately switched between a high pressure pipe and a low pressure pipe by switching operation of a hydraulically driven switching valve in relation to the position of the hammer. A striking device configured to communicate with each other to drive the hammer up and down, wherein a stepped portion having an area approximately equal to the area of the lifting pressure receiving surface of the hammer and having a small diameter at the top is provided, and a stepped portion provided in the buffer chamber provided in the cylinder. A striking device characterized in that the stepped portion is inserted into the buffer chamber, and the buffer chamber is connected to the low-pressure pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980095758U JPS6026935Y2 (en) | 1980-07-07 | 1980-07-07 | striking device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980095758U JPS6026935Y2 (en) | 1980-07-07 | 1980-07-07 | striking device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5718981U JPS5718981U (en) | 1982-01-30 |
| JPS6026935Y2 true JPS6026935Y2 (en) | 1985-08-14 |
Family
ID=29457620
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980095758U Expired JPS6026935Y2 (en) | 1980-07-07 | 1980-07-07 | striking device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6026935Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6233325U (en) * | 1985-08-13 | 1987-02-27 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5835421Y2 (en) * | 1979-11-08 | 1983-08-09 | 三菱重工業株式会社 | striking device |
-
1980
- 1980-07-07 JP JP1980095758U patent/JPS6026935Y2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5718981U (en) | 1982-01-30 |
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