JPS62276289A - Scroll hydraulic machinery - Google Patents
Scroll hydraulic machineryInfo
- Publication number
- JPS62276289A JPS62276289A JP61117599A JP11759986A JPS62276289A JP S62276289 A JPS62276289 A JP S62276289A JP 61117599 A JP61117599 A JP 61117599A JP 11759986 A JP11759986 A JP 11759986A JP S62276289 A JPS62276289 A JP S62276289A
- Authority
- JP
- Japan
- Prior art keywords
- spiral body
- scroll
- discharge port
- spiral
- central part
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 4
- 230000004323 axial length Effects 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0284—Details of the wrap tips
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/102—Geometry of the inlet or outlet of the outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/50—Inlet or outlet
- F05B2250/502—Outlet
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
３、発明の詳細な説明
〔産業上の利用分野〕
本発明は、スクロール流体機械のスクロールに適用され
る渦巻き形状に関する。Detailed Description of the Invention 3. Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a spiral shape applied to a scroll of a scroll fluid machine.
スクロール流体機械の一種であるスクロール圧縮機につ
いて説明する。A scroll compressor, which is a type of scroll fluid machine, will be explained.
従来のスクロール型圧縮機は第８図作動原理図に示すよ
うに、同一形状の２つのうずまき体の一方２を略中夫に
吐出口４を有するシール端板に固定し、両者を第８図に
示すように、相対的に１８０゜回転させ、かつこの両者
のうずまき体が５１，５２および５１’、 ５２’の４
点で互いに接触するよ５に、距離２ρ（＝うずまきのピ
ッチ−２×うずまきの板厚）だけ相対的にずらして、互
いに重ね合せ、一方のうずまき体２を静止し、他方のう
ずまき体ｌをクランク半径ρを有するクランク機構にて
、一方のうずまき体２の中心Ｏの周りに自転を行なうこ
となく半径ρ＝ｏｏ’ で公転運動をなすように構成
される。In a conventional scroll type compressor, as shown in the diagram of the operating principle in Fig. 8, one of two spiral bodies 2 of the same shape is fixed to a seal end plate having a discharge port 4 approximately in the middle, and both are fixed as shown in Fig. 8. As shown in the figure, the two spiral bodies are rotated 180 degrees relative to each other, and the spiral bodies of the two are rotated 51, 52 and 51', 52'.
5, so that they touch each other at points 5, and overlap each other by a distance of 2ρ (= pitch of the spiral - 2 × thickness of the spiral), one spiral body 2 is stationary, and the other spiral body l is A crank mechanism having a crank radius ρ is configured to revolve around the center O of one spiral body 2 with a radius ρ=oo' without rotating on its own axis.
そうすると、２つのうずまき体１，２間には、両うずま
き体が当接する点５１．５２及び点５１′。Then, between the two spiral bodies 1 and 2, there are points 51, 52 and 51' where both the spiral bodies abut.
５２′間に密閉された小室３，３が形成され、密閉小室
３，３の容積がうずまき体１の公転に伴い徐々に変化す
る。A closed small chamber 3, 3 is formed between 52', and the volume of the closed small chamber 3, 3 gradually changes as the spiral body 1 revolves.
すなわち、同図（１１の状態からうずまき体ｌをまず９
０°公転させろと、同図（２）となり、１８０゜公転さ
せると同図（３）に、２７００公転させると同図（４）
となり、この間、小室３の容積は徐々に減少し、同図（
４）では２つの小室３，３は連通して小室５３となり、
同図（４）の状態から更に９０°公転すると、同図（１
）となり、小室５３の容積は同図（２）より同図（３）
へとその容積を減少し、同図（３）と同図（４）の間で
最小の容積となり、この間、同図（２）で開きはじめた
外側空間が同図（３）、同図（４）から同図（１）に移
り、新たな気体を取りこんで密閉小室を形成し、以後こ
れを（つかえし、うずまき体外側空間より取りこまれた
気体が圧縮され吐出口４より吐出される。In other words, in the same figure (from the state of 11, the spiral body l is first changed to 9
If it revolves 0 degrees, it will become (2) in the same figure, if it revolves 180 degrees, it will get (3) in the same figure, and if it revolves 2700 degrees, it will get (4) in the same figure.
During this period, the volume of small chamber 3 gradually decreases, as shown in the figure (
In 4), the two chambers 3 and 3 are connected to form a chamber 53,
If the state of the figure (4) is further revolved by 90 degrees, the figure (1)
), and the volume of the small chamber 53 is calculated from figure (2) to figure (3).
The volume decreases to the minimum volume between (3) and (4) in the same figure, and during this time, the outer space that started to open in (2) in the same figure becomes (3) and (4) in the same figure. Moving from 4) to (1) in the same figure, a new gas is taken in to form a closed chamber, and the gas taken in from the whirlpool outside the body is compressed and discharged from the discharge port 4. .
上記は、スクロール型圧縮機の作動原理であるが、スク
ロール型圧縮機は具体的には、第９図の縦断面図に示す
ように、ハウジング１０はフロントエンドフレー）１１
． リヤエンドフレート１２゜シリンダプレート１３
よりなり、リヤエンドプレート１２に吸入口１４．吐出
口１５を突設するとともに、うずまき体２５２および円
板２５１よりなる静止スクロール部材２５を固定し、フ
ロントエンドプレート１１にクランクピン２３を有する
主軸１７を枢着し、クランクピン２３に、第１０図（第
９図のＥ−に断面図）Ｋ示すように、ラジアルニードル
軸受２６．公転スクロール部材２４のボス２４３．角筒
部材２７１．摺動体２９１゜リング部材２９２２回り止
め２９３等よりなる公転機構を介して、５ずまぎ体２４
２および円板２４１よりなる公転スクロール部材２４が
付設されている。The above is the operating principle of a scroll type compressor. Specifically, as shown in the vertical cross-sectional view of FIG.
．． Rear end plate 12° cylinder plate 13
There is an intake port 14 in the rear end plate 12. A discharge port 15 is provided protrudingly, a stationary scroll member 25 consisting of a spiral body 252 and a disk 251 is fixed, a main shaft 17 having a crank pin 23 is pivotally mounted to the front end plate 11, and a tenth As shown in FIG. Boss 243 of the revolving scroll member 24. Square tube member 271. Through a revolution mechanism consisting of a sliding body 291, a ring member 2922, a rotation stopper 293, etc.
A revolving scroll member 24 including a disk 241 and a disk 241 is attached.
第５図乃至第７図を参照して説明する。 This will be explained with reference to FIGS. 5 to 7.
圧縮された気体が、これを閉じ込めている密閉小室に隣
接する低圧側の密閉小室へガス漏れが生じないように、
公転スクロールのうずまき体２４２と静止スクロールの
円板２５１との接する部分のうずまき体２４２側にチッ
プシール４４２を装着し、また静止スクロールのうずま
き体２５２と公転スクロールの円板２４１との接する部
分のうずまき体２５２側にチップシール４５２を装着す
る。To prevent compressed gas from leaking into the low-pressure side closed chamber adjacent to the closed chamber that confines it,
A chip seal 442 is attached to the spiral body 242 side of the part where the spiral body 242 of the revolving scroll and the disc 251 of the stationary scroll touch, and a chip seal 442 is attached to the spiral body 242 side of the part where the spiral body 252 of the stationary scroll and the disc 241 of the revolving scroll touch. A chip seal 452 is attached to the body 252 side.
公転スクロールのうずまき体に設けられるチップシール
４４２は破損を防止するため、円板２５１に設げである
吐出口１４と干渉しないように静止スクロールのうずま
き体に設けられるチップシール４５２よりもかなり短か
くしている。また図のようにうずまき体２４２及び２５
２の吐出口１４に近い中心部は、他のうずまき体部分に
比べ幅が若干大きいものの、吐出口に比べれば、はぼ同
程度か幾分小さいのが普通である。以上のような構造の
ために１従来のものは、次のような欠点があった。In order to prevent damage, the chip seal 442 provided on the spiral body of the revolving scroll is made considerably shorter than the chip seal 452 provided on the spiral body of the stationary scroll so as not to interfere with the discharge port 14 provided on the disk 251. There is. Also, as shown in the figure, the spiral bodies 242 and 25
Although the width of the central portion near the outlet 14 of No. 2 is slightly larger than the other portions of the spiral body, the width is usually about the same or somewhat smaller than the outlet. Due to the above structure, the conventional one had the following drawbacks.
（１）吐出口１４近くの中心部でチップシール４４２の
存在しないうずまき体２４２の先端部分よりガス漏れが
生じ、性能を低下させていた。(1) Gas leakage occurred from the tip of the spiral body 242 where the tip seal 442 was not present at the center near the discharge port 14, reducing performance.
（２） うずまき体の中心部に直接クランプピンを挿
入するスペースがないため、クランクピンは公転スクロ
ール２４の外側にボスを設けて軸支持せざやを得す、従
って、軸方向の長さが長くなるため、クランクピンは強
度及び振動の点から太くせざるを得なかった。(2) Since there is no space to insert a clamp pin directly into the center of the spiral body, the crank pin is provided with a boss on the outside of the revolving scroll 24 to provide axial support. Therefore, the length in the axial direction is long. Therefore, the crank pin had to be made thicker in terms of strength and vibration.
うずまき体中６部における一方のうずまき体の厚さを極
端に大きくする。他方のうずまき体の中心部厚さは相手
方と完全に噛み合うように作られるため必然的に小さく
なる。従来の問題点（１）を解決するのが第１図、第２
図であり、静止スクロールのうずまき体厚さの大きくな
った中心部分に吐出口を内蔵させて、公転スクロールの
テップシールが従来のように吐出口と接触しない様にす
る。The thickness of one of the 6th part of the spiral body is made extremely large. The thickness of the center of the other spiral body is necessarily smaller because it is made to completely mesh with the other spiral body. Figures 1 and 2 solve the conventional problem (1).
In this figure, a discharge port is built into the central portion of the stationary scroll where the spiral body thickness is increased, so that the tip seal of the revolving scroll does not come into contact with the discharge port as in the conventional case.
従来の問題点（２）を解決するのが棺３図、第４図であ
り、この場合は公転スクロール側のうずまき体中６部厚
さを大きくして、クランクシ／でＩｉ接細軸支持出来様
にする。The solution to the conventional problem (2) is shown in Figures 3 and 4. In this case, the thickness of the 6th part of the spiral body on the side of the revolving scroll is increased, and the crankshaft is able to support the Ii fine shaft. I'll do it like that.
（１） 静止スクロールのうずまき体中６部のプロフ
ァイル厚さを大ぎくし、この内部に吐出口を設ける場合
は、公転スクロールのチップシールと吐出口との接触が
なくなり、チップシールを中心部にまで取付けることが
でき、シール効果が向上する。(1) If the profile thickness of the 6th part of the spiral body of the stationary scroll is increased and the discharge port is provided inside this part, the contact between the tip seal of the revolving scroll and the discharge port will be eliminated, and the tip seal will be placed in the center. The sealing effect can be improved by attaching up to
（２）公転スクロールのうずまき体中６部のプロファイ
ル厚さを大きクシ、この内部にクランクピンな挿入する
時は、クランクピンの軸方向長さ従って装置全体の軸方
向長さが減少する。(2) When the profile thickness of the 6th part of the spiral body of the revolving scroll is increased and a crank pin is inserted into this comb, the axial length of the crank pin and therefore the axial length of the entire device is reduced.
クランクピンに働くモーメントが減少し、振動が減少す
る。The moment acting on the crank pin is reduced, reducing vibration.
（１）第１図、第２図において、２５１′は静止スクロ
ールの円板、２５２’は静止スクロールのうずまき体、
４５２’はチップシール、２４２′は公転スクロールの
うずまき体、４４２’はチップシール、１４′は吐出口
、９４′は吐出ガス通路である。(1) In Figures 1 and 2, 251' is a disk of a stationary scroll, 252' is a spiral body of a stationary scroll,
452' is a tip seal, 242' is a spiral body of a revolving scroll, 442' is a tip seal, 14' is a discharge port, and 94' is a discharge gas passage.
静止スクロールのうずまき体２５２′の厚くなった中心
部に吐出口１４′が内蔵されていて、うず巻体２５２′
の側面には吐出口へ通ずる通路９４′がある。これによ
り従来静止スクロールの円板に設けられていた吐出口１
４がなくなるため、公転スクロールのうず巻体に設けら
れているチップシール４４２′はうず巻体２４２′の中
心部まで十分な長さをとることができる。A discharge port 14' is built in the thick center of the spiral body 252' of the stationary scroll, and the spiral body 252'
On the side thereof there is a passage 94' leading to the discharge port. As a result, the discharge port 1 which was conventionally provided on the disk of the stationary scroll
4 is eliminated, the tip seal 442' provided on the spiral body of the revolving scroll can have a sufficient length to reach the center of the spiral body 242'.
（２）第３図、第４図において、２４１“は公転スクロ
ールの円板、２４２“は公転スクロールのうずまき体、
２７１“は公転機栴の角筒部材、２３“はクランクピン
、２５２“は静止スクロールのうずまき体である。(2) In Figures 3 and 4, 241" is the disk of the revolving scroll, 242" is the spiral body of the revolving scroll,
271" is a rectangular tube member of the revolution machine, 23" is a crank pin, and 252" is a spiral body of a stationary scroll.
公転スクロールの５ずまき体２４２“の厚（すった中心
部に軸受を設け、クランクピン２３″を挿入している。A bearing is provided in the center of the five-wheel body 242'' of the revolving scroll, and a crank pin 23'' is inserted.
これにより従来公転スクロール部材の外側に設けられて
いたクランクピンの挿入部（第９図の２４３）がなくな
り、この分だけ軸方向が短かくなる。As a result, the crank pin insertion portion (243 in FIG. 9), which was conventionally provided on the outside of the revolving scroll member, is eliminated, and the axial direction is shortened by this amount.
（１）静止スクロールのうずまき体の中心部のプロファ
イル厚さを極端に太きくし、この部分に吐出口を内置す
ることにより、公転スクロールのチップシールと吐出口
との接触がな（なり、テップシールをうず巻体の中心部
にまで取付けることができ、従来のものに比べ、２この
部分からのガス漏れがなくなる。(1) By making the profile thickness of the central part of the spiral body of the stationary scroll extremely thick and locating the discharge port in this part, there is no contact between the tip seal of the revolving scroll and the discharge port. can be installed up to the center of the spiral body, which eliminates gas leakage from this area compared to conventional products.
（２）公転スクロールのうずまき体の中心部のプロファ
イル厚さを極端に太き（してこの部分にクランクピンを
挿入することにより、軸方向構造が短か（なり、駆動機
構に対するモーメントが小さくなって、強度及び振動の
点で有利となる。(2) By making the profile thickness of the central part of the spiral body of the revolving scroll extremely thick (and inserting a crank pin into this part, the axial structure becomes short (and the moment for the drive mechanism becomes small). This is advantageous in terms of strength and vibration.
第１図は本発明スクロール流体機械の実施例におけるう
ずまき体中６部の構成を示す概略図、第２図は第１図の
Ａ−Ａ断面図、第３図は本発明の他の実施例におけるう
ずまき体中６部の構成を示す概略図、第４図は第３図の
Ｂ−Ｂ断面図、第５図は従来装置におけるうずまき体中
６部の構成を示す概略図、第６図は第５図のＣ−Ｃ断面
図、第７図は第５図のＤ−Ｄ断面図、第８図（１）、
−（２＞、 （３）。
（４）はスクロール圧縮機の作動原理図、第９図は従来
のスクロール圧Ｈｉ機の縦断面図、第１０図は第９図の
Ｅ −ＥｖＪＴ面図である。
２４２’、２５２’・・・うずまき体、４４２’、４５
２’・・・チップシール、１４′・・・吐出口
復代理人 弁理士開本重文
外２名
第４図
第５図FIG. 1 is a schematic diagram showing the structure of the six parts in the spiral body in an embodiment of the scroll fluid machine of the present invention, FIG. 2 is a sectional view taken along the line A-A in FIG. 1, and FIG. 3 is another embodiment of the present invention. 4 is a sectional view taken along the line BB in FIG. 3. FIG. 5 is a schematic diagram showing the structure of the 6th part of the spiral body in a conventional device. 5 is a CC sectional view, FIG. 7 is a DD sectional view in FIG. 5, FIG. 8 (1),
-(2>, (3). (4) is a diagram of the operating principle of a scroll compressor, Figure 9 is a vertical cross-sectional view of a conventional scroll pressure Hi machine, and Figure 10 is an E-EvJT plane view of Figure 9. Yes. 242', 252'... spiral body, 442', 45
2'...Tip seal, 14'...Discharge port Sub-agent: 2 patent attorneys and non-Kaimoto important documents Figure 4 Figure 5
Claims (1)
体の中心部のプロフアイル厚さを大きくし、相手側のう
ずまき体の中心部プロフアイルは、これに噛み合うもの
とし、プロフアイル厚さの大きい中心部のうずまき体の
内部に吐出口又はクランクピン挿入用の空間を形成した
ことを特徴とするスクロール流体機械。The profile thickness at the center of one of the spiral bodies of the stationary or revolving scroll member is made large, and the center profile of the other spiral body is meshed with this, and the profile thickness of the center part with the large profile thickness is increased. A scroll fluid machine characterized by forming a discharge port or a space for inserting a crank pin inside the spiral body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61117599A JP2538877B2 (en) | 1986-05-23 | 1986-05-23 | Scroll fluid machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61117599A JP2538877B2 (en) | 1986-05-23 | 1986-05-23 | Scroll fluid machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62276289A true JPS62276289A (en) | 1987-12-01 |
| JP2538877B2 JP2538877B2 (en) | 1996-10-02 |
Family
ID=14715790
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61117599A Expired - Fee Related JP2538877B2 (en) | 1986-05-23 | 1986-05-23 | Scroll fluid machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2538877B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5364247A (en) * | 1992-05-21 | 1994-11-15 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Sealing structure for scroll type compressor |
| US5427513A (en) * | 1992-12-03 | 1995-06-27 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor having a displaced discharge port |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5958187A (en) * | 1982-09-26 | 1984-04-03 | Sanden Corp | Scroll type compressor |
| JPS6023284U (en) * | 1983-07-25 | 1985-02-18 | 株式会社日立製作所 | compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6023284B2 (en) * | 1979-04-24 | 1985-06-06 | 沖電気工業株式会社 | position detection device |
-
1986
- 1986-05-23 JP JP61117599A patent/JP2538877B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5958187A (en) * | 1982-09-26 | 1984-04-03 | Sanden Corp | Scroll type compressor |
| JPS6023284U (en) * | 1983-07-25 | 1985-02-18 | 株式会社日立製作所 | compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5364247A (en) * | 1992-05-21 | 1994-11-15 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Sealing structure for scroll type compressor |
| US5427513A (en) * | 1992-12-03 | 1995-06-27 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor having a displaced discharge port |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2538877B2 (en) | 1996-10-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |