JPS633496Y2 - - Google Patents
Info
- Publication number
- JPS633496Y2 JPS633496Y2 JP1982137667U JP13766782U JPS633496Y2 JP S633496 Y2 JPS633496 Y2 JP S633496Y2 JP 1982137667 U JP1982137667 U JP 1982137667U JP 13766782 U JP13766782 U JP 13766782U JP S633496 Y2 JPS633496 Y2 JP S633496Y2
- Authority
- JP
- Japan
- Prior art keywords
- seal ring
- packing
- ring
- pressure
- tightening
- 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
- 238000012856 packing Methods 0.000 claims description 38
- 239000012530 fluid Substances 0.000 claims description 13
- 230000004323 axial length Effects 0.000 claims description 5
- 239000013013 elastic material Substances 0.000 claims description 4
- 239000011347 resin Substances 0.000 claims description 4
- 229920005989 resin Polymers 0.000 claims description 4
- BFKJFAAPBSQJPD-UHFFFAOYSA-N tetrafluoroethene Chemical group FC(F)=C(F)F BFKJFAAPBSQJPD-UHFFFAOYSA-N 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 description 8
- 230000007246 mechanism Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 5
- 238000009825 accumulation Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
Landscapes
- Sealing Devices (AREA)
Description
【考案の詳細な説明】
本考案はパツキングに関し、とくにピストン機
構のシリンダ部材とピストン部材間のシール部に
組み込まれるパツキングの改良に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to packing, and particularly relates to an improvement in packing incorporated in a seal portion between a cylinder member and a piston member of a piston mechanism.
第１図に示すようなピストン機構において、図
中左側を油圧側、右側を大気圧側とすると、従来
シリンダ部材ａとピストン部材ｂ間の隙間をシー
ルするため、下記のごとくの構造が用いられてい
る。すなわちｃおよびｄは前記シリンダ部材ａの
内周面に形成した環状溝であり、両環状溝ｃ，ｄ
内に各一組のパツキングｅ，ｆが内挿嵌着されて
いる。このうち前記油圧側の環状溝ｃに嵌着され
たパツキングｅは内周面にリツプ部を有して前記
ピストン部材ｂ外周面とシール摺動する四弗化エ
チレン樹脂材製のシールリングe1と、環状溝底面
側に位置し前記シールリングe1に対して適宜密接
圧を付与するゴム様弾性材製の締付けリングe2と
からなり、大気圧側の環状溝ｄに嵌着されたパツ
キングｆは前記油圧側に環状凹部を向けたゴム様
弾性材製のＣリングf1と、該Ｃリングf1の軸方向
背面に配置された四弗化エチレン樹脂材製のバツ
クアツプリングf2との組み合わせとからなつてい
る。 In a piston mechanism as shown in Fig. 1, assuming that the left side in the figure is the hydraulic pressure side and the right side is the atmospheric pressure side, the following structure has been conventionally used to seal the gap between the cylinder member a and the piston member b. ing. That is, c and d are annular grooves formed on the inner peripheral surface of the cylinder member a, and both annular grooves c and d
A pair of packings e and f are inserted and fitted inside. Of these, the packing e fitted in the annular groove c on the hydraulic side has a lip portion on its inner circumferential surface and is a seal ring e 1 made of tetrafluoroethylene resin that seals and slides on the outer circumferential surface of the piston member b. and a tightening ring e2 made of a rubber-like elastic material that is located on the bottom side of the annular groove and applies appropriate tight pressure to the seal ring e1 , and a packing fitted in the annular groove d on the atmospheric pressure side. f is a C-ring f1 made of a rubber-like elastic material with an annular concave portion facing the hydraulic pressure side, and a back-up spring f2 made of a tetrafluoroethylene resin material disposed on the back surface of the C-ring f1 in the axial direction. It consists of a combination of.
上記構成になるシール構造は、前記油圧側に存
する被密封流体に対して、油圧側に位置するパツ
キングｅによつて第１次シール部が形成され、該
第１次シール部を通過した流体に対して大気圧側
のパツキングｆが第２次的にシール作用をなすよ
うに構成されているが、前記油圧側のパツキング
ｅのピストン部材ｂに対する締代が、当該ピスト
ン機構が加圧時にあるとき（第１図）も減圧時に
あるとき（第２図）も常時一定であるために、前
記油圧側のパツキングｅを通過した流体は両パツ
キングｅ，ｆにより密閉されるから、該流体は両
パツキングｅ，ｆ間の環状空間ｉに溜まる一方と
なり、該空間ｉ内が漸次増圧して、ついには前記
各パツキングｅ，ｆに損傷させる結果となつてい
た。また油圧側のパツキングｅはピストン部材ｂ
外周面に対してリツプ部による線接触状態にある
ためきわめて安定性の悪いものであつた。 In the seal structure configured as described above, a primary seal portion is formed by the packing e located on the hydraulic side with respect to the fluid to be sealed that exists on the hydraulic side, and the fluid passing through the primary seal portion is On the other hand, the packing f on the atmospheric pressure side is configured to perform a secondary sealing action, but the tightening margin of the packing e on the hydraulic side with respect to the piston member b is when the piston mechanism is pressurized. (Fig. 1) and when the pressure is reduced (Fig. 2), it is always constant, so the fluid that has passed through the packing e on the hydraulic side is sealed by both packings e and f, so the fluid is The gas continued to accumulate in the annular space i between e and f, and the pressure in the space i gradually increased, eventually causing damage to each of the packings e and f. Also, the packing e on the hydraulic side is the piston member b.
Since the lip portion was in line contact with the outer peripheral surface, the stability was extremely poor.
本考案は以上のような問題点に鑑みなされたも
のであつて、その目的は上記油圧側の環状溝に嵌
着されるパツキングの締代が加圧時と減圧時にお
いて変化するように構成し、前記両パツキング間
の環状空間における蓄圧を防止し、もつて長期耐
久性に優れたパツキングを得ることにある。 The present invention was developed in view of the above-mentioned problems, and its purpose is to configure the packing so that the tightness of the packing fitted into the annular groove on the hydraulic side changes when pressurizing and when depressurizing. The object of the present invention is to prevent pressure from accumulating in the annular space between the two packings, and to obtain a packing with excellent long-term durability.
以下、本考案の実施例を図面にしたがつて説明
すると、第３図は第１の実施例を示すものであ
り、３はピストン部材２を内挿したシリンダ部材
１の内周面に形成した環状溝であつて、第１図に
おける油圧側の環状溝ｃに該当し、該環状溝３内
に本考案に係るパツキング４が内挿嵌着されてい
る。該パツキング４は前記ピストン部材２の外周
面とシール摺動する四弗化エチレン樹脂材製のシ
ールリング５と、該シールリング５に対して密接
圧を付与するゴム様弾性材製の締付けリング６と
が組み合わされており、該締付けリング６は断面
円形状に形成され、前記シールリング５の平面状
に形成された外周面に対し、適宜接触幅ｍをもつ
て圧接してなる。また該シールリング５と締付け
リング６は、その軸方向長さ（幅長）において前
者シールリング５の方が長く形成され、後者締付
けリング６は、器内圧力の変動に応じて、シール
リング５上を移動自在に、すなわち軸方向におけ
る相対的な位置を変動自在になる。一方、前記シ
ールリング５も、環状溝３の軸方向幅よりわずか
に短くなるため、圧力変動によつて軸方向に移動
する（第４図）。該シールリング５は前記油圧側
の一端部（図中、略左半分）内周面にテーパ状の
環状切欠部５ａが形成され、該環状切欠部５ａを
有する分だけ前記油圧側の一端部が同他端部（図
中、略右半分）よりも薄肉状に形成されてなる。
締付けリング６は、第４図に示すように環状溝３
の油圧側側壁に当接した状態においてはシールリ
ング５の薄肉部５ｂに接しており、このとき、締
付けリング６の一端（図中左端）から接触面の他
端までの長さｎは薄肉部５ｂの軸方向長さｌより
も短く形成されている。同様に、締付けリング６
が第３図に示すように環状溝３の大気圧側側壁に
当接した状態においては、前記接触面がシールリ
ング５の厚肉状他端部との間に形成されるよう寸
法設定がなされている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Fig. 3 shows the first embodiment, and 3 is formed on the inner circumferential surface of the cylinder member 1 into which the piston member 2 is inserted. This annular groove corresponds to the annular groove c on the hydraulic side in FIG. 1, and a packing 4 according to the present invention is inserted and fitted into the annular groove 3. The packing 4 includes a seal ring 5 made of tetrafluoroethylene resin that seals and slides on the outer peripheral surface of the piston member 2, and a tightening ring 6 made of a rubber-like elastic material that applies close pressure to the seal ring 5. The tightening ring 6 is formed to have a circular cross section and is pressed against the planar outer peripheral surface of the seal ring 5 with an appropriate contact width m. In addition, the seal ring 5 and the tightening ring 6 are formed so that the former seal ring 5 is longer in the axial length (width length), and the latter tightening ring 6 is formed so that the seal ring 5 It is possible to move freely on the top, that is, to change the relative position in the axial direction. On the other hand, since the seal ring 5 is also slightly shorter than the axial width of the annular groove 3, it moves in the axial direction due to pressure fluctuations (FIG. 4). The seal ring 5 has a tapered annular notch 5a formed on the inner circumferential surface of one end (approximately left half in the figure) on the hydraulic side, and the one end on the hydraulic side has the annular notch 5a. It is formed thinner than the other end (approximately the right half in the figure).
The tightening ring 6 is attached to the annular groove 3 as shown in FIG.
When it is in contact with the hydraulic side wall of the seal ring 5, it is in contact with the thin wall portion 5b of the seal ring 5, and at this time, the length n from one end of the tightening ring 6 (the left end in the figure) to the other end of the contact surface is equal to the thin wall portion. It is formed shorter than the axial length l of 5b. Similarly, tightening ring 6
As shown in FIG. 3, the dimensions are set so that when the contact surface is in contact with the atmospheric pressure side wall of the annular groove 3, the contact surface is formed between it and the other thick end of the seal ring 5. ing.
また、シールリング５の大気圧側他端部内周縁に
は加圧時における端部はみ出し防止用の面取り５
ｃが施こされている。In addition, the inner peripheral edge of the other end on the atmospheric pressure side of the seal ring 5 is chamfered to prevent the end from protruding when pressurized.
c has been applied.
上記構成になるパツキング４は、第１図に示し
たようにシリンダ部材１の内周面に形成した２本
の環状溝のうちの油圧側の環状溝３に内挿嵌着さ
れ、図中左方向から流入する被密封流体に対する
第１次シール部として機能するものであり、今１
つの大気圧側の環状溝には第１図に示したものと
同一の構成になるパツキングが嵌着されてなる。 As shown in Fig. 1, the packing 4 having the above structure is inserted into the annular groove 3 on the hydraulic side of the two annular grooves formed on the inner peripheral surface of the cylinder member 1, and is inserted into the annular groove 3 on the hydraulic side. It functions as a primary seal against the fluid to be sealed flowing in from the direction.
Packing having the same structure as that shown in FIG. 1 is fitted into each of the annular grooves on the atmospheric pressure side.
今ピストン部材２が図中左方向へ移動するため
に器内が加圧されると（第３図）、シリンダ部材
１とピストン部材２の隙間を通つて環状溝３にい
たる高圧の流体によつてパツキング４は環状溝３
の大気圧側側壁に押し付けられるようになり、該
パツキング４中締付けリング６はシールリング５
上を移動するため、シールリング５の厚肉状他端
部外周に位置することになる。該締付けリング６
はシールリング５に対して密接圧を付与すること
を主目的とするものであるが、シールリング５自
体もピストン部材２に対する締代を有し、さらに
該締代は当該シールリング５が一端に薄肉部５ｂ
を有するため軸方向の各部位において異なり、す
なわち該薄肉部５ｂにおいて小さく、厚肉状他端
部において大きく構成されている。したがつて、
該加圧時締付けリング６がシールリング５の厚肉
状他端部外周にあるときは、圧力により径方向に
弾性変形された締付けリング６の比較的大きな値
になる締代によつてシールリング５を締付けるか
らピストン部材２に対して大なる密接圧（締付
力）を得、従来構造と同様なシール効果を奏する
ことになる。 Now, when the inside of the container is pressurized to move the piston member 2 to the left in the figure (Fig. 3), high-pressure fluid passes through the gap between the cylinder member 1 and the piston member 2 and reaches the annular groove 3. The packing 4 is an annular groove 3
The tightening ring 6 in the packing 4 is pressed against the atmospheric pressure side wall of the sealing ring 5.
Since it moves above, it is located on the outer periphery of the thick-walled other end of the seal ring 5. The tightening ring 6
The main purpose of this is to apply close pressure to the seal ring 5, but the seal ring 5 itself also has an interference with the piston member 2, and the interference is such that the seal ring 5 is at one end. Thin wall portion 5b
Therefore, it is different at each location in the axial direction, that is, the thin portion 5b is smaller and the thicker end portion is larger. Therefore,
When the tightening ring 6 is located on the outer periphery of the thick-walled other end of the seal ring 5 during pressurization, the tightening interference of the tightening ring 6, which is elastically deformed in the radial direction due to the pressure and has a relatively large value, causes the seal ring to tighten. 5, a large tight pressure (clamping force) is obtained against the piston member 2, and a sealing effect similar to that of the conventional structure is achieved.
ピストン機構の作動時間が暫時経過して被密封
流体が当該パツキング４による第１次シール部を
漏出すると、該漏出流体は既述のとうり、該パツ
キング４と大気圧側に配された今１つのパツキン
グｆとの間の環状空間７に溜まり、該空間７内に
おいて漸次蓄圧される。該ピストン機構は作動に
よつてシリンダ内が加圧、減圧を繰り返してお
り、前記環状空間７の蓄圧力がシリンダ部材１内
の減圧時（低圧時）の圧力を上まわるようになる
と、該時点において当該パツキング４は、該蓄圧
力に押されて環状溝３内を油圧側に移動するよう
になり、これを詳述するとシールリング５は環状
溝３の軸方向幅との幅差量分移動し、締付けリン
グ６はさらにシールリング５上を移動して、両リ
ング５，６とも環状溝３の油圧側側壁に押し付け
られ、該締付けリング６はシールリング５の薄肉
部５ｂ外周に位置することになる（第４図）。既
述のとうりシールリング５の該薄肉部５ｂの締代
と締付けリング６の締代とによつて得られる密接
圧（締付力）は小さくなり、前記環状空間７に溜
まつた圧力流体は容易に油圧側に逆流し、該空間
７内の圧力を下げることができる。したがつて上
記構成のパツキング４を使用すれば、従来環状空
間３にそのまま溜り続けた漏出流体を間欠的に油
圧側へ返流するようになり、該環状空間７内の蓄
圧により惹起する各パツキンの損傷を未然に防止
することができる。 When the operating time of the piston mechanism has elapsed for a while and the sealed fluid leaks out of the primary seal by the packing 4, the leaked fluid flows through the packing 4 and the gasket 1 located on the atmospheric pressure side. The pressure accumulates in the annular space 7 between the two packings f, and the pressure gradually accumulates within the space 7. The piston mechanism repeatedly pressurizes and depressurizes the inside of the cylinder as it operates, and when the accumulated pressure in the annular space 7 exceeds the pressure in the cylinder member 1 during depressurization (low pressure), at that point In this case, the packing 4 is pushed by the accumulated pressure and moves toward the hydraulic pressure side within the annular groove 3. To explain this in detail, the seal ring 5 moves by the width difference between the axial width of the annular groove 3 and the annular groove 3. However, the tightening ring 6 further moves on the seal ring 5, and both rings 5 and 6 are pressed against the hydraulic side wall of the annular groove 3, and the tightening ring 6 is located on the outer periphery of the thin wall portion 5b of the seal ring 5. (Figure 4). As described above, the close pressure (clamping force) obtained by the tightening margin of the thin wall portion 5b of the seal ring 5 and the clamping margin of the clamping ring 6 becomes smaller, and the pressure fluid accumulated in the annular space 7 is reduced. can easily flow back to the hydraulic side and lower the pressure in the space 7. Therefore, if the packing 4 having the above configuration is used, the leakage fluid that has conventionally continued to accumulate in the annular space 3 will be intermittently returned to the hydraulic pressure side, and each packing caused by the accumulation of pressure in the annular space 7 will be damage can be prevented.
以上述べたように、本考案はパツキングは一端
側（油圧側）と他端側（大気圧側）において密接
圧（締付力）を異ならしめ、一端側の締付力を小
さく構成して蓄圧を放出せしめるものであり、シ
ールリング５と締付けリング６の形状に関しては
種種の変形が可能である。 As mentioned above, the present invention is designed to make the sealing pressure (clamping force) different between one end (hydraulic side) and the other end (atmospheric pressure side), and to reduce the tightening force at one end to accumulate pressure. The shapes of the seal ring 5 and the tightening ring 6 can be modified in various ways.
第５図および第６図はこの変形例として本考案
の第２の実施例を示すものであり、シールリング
５外周面の軸方向略中央にテーパ状の段部５ｄが
形成され、該シールリング５を油圧側（図中左
側）の薄肉（小径）部と大気圧側（図中右側）の
厚肉（大径）部とに区分けしてなる。当該パツキ
ング４は、定常時にあつては、第５図に示すよう
に、油圧側からの圧力によつて環状溝３の大気圧
側側壁に押付けられ、締付けリング６も適宜接触
幅ｍをもつてシールリング５の厚肉他端部外周に
位置してなるが、環状空間７内の蓄圧力が高まる
と環状溝３の油圧側側壁に押付けられ（第６図）、
締付けリング６一端から接触面の他端までの幅ｎ
をもつてシールリング５の薄肉状一端部外周に位
置して密接圧（締付力）を減少せしめて環状空間
７内の蓄圧を解消する。該実施例のパツキング４
は、シールリング５自体の有する締代が軸方向に
各部位において異なるほか、該シールリング５外
周面に段部５ｄが形成されて、該段部５ｄの前後
において外径が異なるため、締付けリング６の半
径方向の伸縮による締付力の変化も密接圧の増減
に寄与することになる。 FIG. 5 and FIG. 6 show a second embodiment of the present invention as a modification example, in which a tapered step portion 5d is formed approximately at the center of the outer peripheral surface of the seal ring 5 in the axial direction. 5 is divided into a thin wall (small diameter) part on the hydraulic pressure side (left side in the figure) and a thick wall (large diameter) part on the atmospheric pressure side (right side in the figure). In steady state, as shown in FIG. 5, the packing 4 is pressed against the atmospheric pressure side wall of the annular groove 3 by pressure from the hydraulic pressure, and the tightening ring 6 is also pressed with an appropriate contact width m. Although it is located on the outer periphery of the thick-walled other end of the seal ring 5, when the accumulated pressure in the annular space 7 increases, it is pressed against the hydraulic side wall of the annular groove 3 (Fig. 6).
Width n from one end of the tightening ring 6 to the other end of the contact surface
is located on the outer periphery of one thin end of the seal ring 5 to reduce close contact pressure (clamping force) and eliminate pressure buildup in the annular space 7. Packing 4 of this example
In addition to the tightening allowance of the seal ring 5 itself being different in each part in the axial direction, a step 5d is formed on the outer peripheral surface of the seal ring 5, and the outer diameter is different before and after the step 5d. Changes in the tightening force due to expansion and contraction in the radial direction of 6 also contribute to an increase or decrease in the contact pressure.
また、第７図および第８図は、本考案の第３の
実施例として、さらに他の変形例を示すものであ
り、シールリング５の外周面を一律的なテーパ面
５ｅに形成し、該テーパ面５ｅ上を締付けリング
６が移動するように構成してなり、上記第２実施
例と同様な作用を奏するようにしたものである。 Further, FIGS. 7 and 8 show still another modification as the third embodiment of the present invention, in which the outer circumferential surface of the seal ring 5 is formed into a uniform tapered surface 5e, and The tightening ring 6 is configured to move on the tapered surface 5e, and has the same effect as the second embodiment.
本考案は以上説明したように、シールリングの
軸方向長さを締付けリングの長さよりも長く形成
して、該締付けリングがシールリング上を移動自
在に構成するとともにシールリングの軸方向一端
部を同他端部に比して薄肉状に形成し、締付けリ
ングがシールリング上のいずれの位置にあるかに
よつて締付け力を増減するようになり、漏出流体
による蓄圧が大きくなつたときに、該締付け力を
小さくしてこれを解消するものである。したがつ
て本考案パツキングを使用すると、漏出流体によ
る過度の蓄圧をなくし、不測の事故等を防止する
ことができる。また本考案のパツキングはシール
面に面接触部を形成し、ピストン機構の作動に対
して安定性の良いものである。 As explained above, in the present invention, the axial length of the seal ring is formed to be longer than the length of the tightening ring, so that the tightening ring is movable on the seal ring, and one end of the seal ring in the axial direction is configured to be movable on the seal ring. It is formed thinner than the other end, and the tightening force is increased or decreased depending on the position of the tightening ring on the seal ring, so that when the pressure buildup due to leakage fluid increases, This problem is solved by reducing the tightening force. Therefore, by using the packing of the present invention, it is possible to eliminate excessive pressure accumulation due to leaked fluid and prevent unexpected accidents. In addition, the packing of the present invention forms a surface contact portion on the sealing surface, and has good stability with respect to the operation of the piston mechanism.
図面は本考案の実施例を示すものであり、第１
図および第２図は従来のパツキングの使用状態を
示すピストン機構の部分断面図、第３図および第
４図は本考案の第１の実施例に係るパツキングの
正断面図、第５図および第６図は同第２の実施例
に係るパツキングの正断面図、第７図および第８
図は同第３の実施例に係るパツキングの正断面図
である。
１……シリンダ部材、２……ピストン部材、３
……環状溝、４……パツキング、５……シールリ
ング、５ａ……環状切欠部、５ｂ……薄肉部、５
ｃ……面取り部、５ｄ……段部、５ｅ……テーパ
面、６……締付けリング、７……環状空間。
The drawings show an embodiment of the present invention.
3 and 4 are front sectional views of the packing according to the first embodiment of the present invention, and FIG. 5 and FIG. Figure 6 is a front sectional view of the packing according to the second embodiment, Figures 7 and 8.
The figure is a front sectional view of the packing according to the third embodiment. 1...Cylinder member, 2...Piston member, 3
... Annular groove, 4 ... Packing, 5 ... Seal ring, 5a ... Annular notch, 5b ... Thin wall part, 5
c... Chamfered portion, 5d... Stepped portion, 5e... Tapered surface, 6... Tightening ring, 7... Annular space.
Claims (1)
いずれか一方の部材の対向周面に形成した環状溝
に嵌挿されるパツキングにおいて、他方の部材と
密接する四弗化エチレン樹脂材製のシールリング
と、該シールリングに嵌合して密接圧を付与する
ゴム様弾性材製の締付けリングとを有し、前記シ
ールリングの軸方向長さを前記締付けリングの軸
方向長さより長く形成して前記シールリングの軸
方向一端部を同他端部に比して薄肉部に形成する
とともに、前記締付けリングが流体圧力の方向に
応じてシールリングの一端薄肉部の周面および他
端厚肉部の周面のうちいずれか一方と接触してな
ることを特徴とするパツキング。 A seal ring made of a tetrafluoroethylene resin material that is in close contact with the other member in a packing that is inserted into an annular groove formed on the opposing circumferential surface of one of the cylinder member and the piston member that are fitted to each other; a tightening ring made of a rubber-like elastic material that fits into the seal ring and applies close pressure; the axial length of the seal ring is formed to be longer than the axial length of the tightening ring; One end in the axial direction of the seal ring is formed to have a thinner wall than the other end, and the tightening ring adjusts the circumferential surface of the thin walled portion at one end of the seal ring and the circumferential surface of the thick walled portion at the other end depending on the direction of fluid pressure. Packing is characterized by contact with either one of these.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13766782U JPS5942365U (en) | 1982-09-13 | 1982-09-13 | Patsuking |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13766782U JPS5942365U (en) | 1982-09-13 | 1982-09-13 | Patsuking |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5942365U JPS5942365U (en) | 1984-03-19 |
| JPS633496Y2 true JPS633496Y2 (en) | 1988-01-28 |
Family
ID=30309145
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13766782U Granted JPS5942365U (en) | 1982-09-13 | 1982-09-13 | Patsuking |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5942365U (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH073087Y2 (en) * | 1990-05-16 | 1995-01-30 | 株式会社電業社機械製作所 | High pressure fluid sealing device |
| JP5169352B2 (en) * | 2008-03-18 | 2013-03-27 | Ｎｏｋ株式会社 | Sealing device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4933641U (en) * | 1972-06-20 | 1974-03-25 | ||
| JPS5533508A (en) * | 1978-08-31 | 1980-03-08 | Yamazaki Denki Kogyo Kk | Electric furnace for highhtemperature heat treatment |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6040937Y2 (en) * | 1980-01-22 | 1985-12-11 | 三菱重工業株式会社 | battle ring |
-
1982
- 1982-09-13 JP JP13766782U patent/JPS5942365U/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4933641U (en) * | 1972-06-20 | 1974-03-25 | ||
| JPS5533508A (en) * | 1978-08-31 | 1980-03-08 | Yamazaki Denki Kogyo Kk | Electric furnace for highhtemperature heat treatment |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5942365U (en) | 1984-03-19 |
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