JPH0417793A - scroll type fluid machine - Google Patents
scroll type fluid machineInfo
- Publication number
- JPH0417793A JPH0417793A JP11636190A JP11636190A JPH0417793A JP H0417793 A JPH0417793 A JP H0417793A JP 11636190 A JP11636190 A JP 11636190A JP 11636190 A JP11636190 A JP 11636190A JP H0417793 A JPH0417793 A JP H0417793A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- scroll
- fluid machine
- type fluid
- oil supply
- 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 title claims description 10
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 239000003507 refrigerant Substances 0.000 description 7
- 238000005461 lubrication Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、冷媒の圧縮機等として利用されるスクロール
形流体機械に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a scroll-type fluid machine used as a refrigerant compressor or the like.
（従来の技術）
従来、特開昭５５−１０７０９３号公報に開示され且つ
第４図に示すように、可動スクロール（０）の鏡板に、
圧縮途中の中間圧力室（Ｍ）に開口する貫通穴（Ｈ）を
設けて、密閉ケーシング（Ｋ）の内部を中間圧力に保持
すると共に、モータ（Ｅ）の下部に位置する底部油溜（
Ｗ）と各スクロール（０）（Ｆ）に至る吸入通路（Ｌ）
との間に、キャピラリーチューブで構成する減圧機構（
Ｖ）をもつ油供給管（Ｔ）を接続し、ケーシング（Ｋ）
側の中間圧力と吸入通路（Ｌ）側の低圧圧力との差圧に
より圧縮室（Ｃ）に油インジェクシロンヲ行い、スクロ
ール摺動面でのシールや潤滑又は冷却等を行うようにし
ている。(Prior Art) Conventionally, as disclosed in Japanese Unexamined Patent Publication No. 55-107093 and shown in FIG. 4, an end plate of a movable scroll (0) has a
A through hole (H) that opens into the intermediate pressure chamber (M) during compression is provided to maintain the inside of the sealed casing (K) at an intermediate pressure, and also to maintain the inside of the sealed casing (K) at an intermediate pressure.
W) and the suction passage (L) leading to each scroll (0) (F)
A decompression mechanism consisting of a capillary tube (
Connect the oil supply pipe (T) with the casing (K)
Oil is injected into the compression chamber (C) by the differential pressure between the intermediate pressure on the side and the low pressure on the suction passage (L) side to perform sealing, lubrication, cooling, etc. on the sliding surface of the scroll.
（発明が解決しようとする課Ｈ）
ところで、以上のものでは、密閉ケーシング（Ｋ）の内
部つまり油供給管（Ｔ）における油の押出し側が中間圧
力とされるため、油の注入側の低圧圧力との間の差圧は
、密閉ケーシング（Ｋ）内に高圧の吐出ガスを開放する
高圧ドーム形のものに比べて比較的小さくでき、このた
め、油供給管（Ｔ）を介した圧縮室（Ｃ）への過剰な給
油をある程度防止することができる。(Problem H to be solved by the invention) By the way, in the above, since the inside of the closed casing (K), that is, the oil extrusion side of the oil supply pipe (T) is set to an intermediate pressure, the low pressure on the oil injection side The pressure difference between the compression chamber ( Excessive oil supply to C) can be prevented to some extent.
しかし、前記ケーシング（Ｋ）の内部を中間圧力に保持
するため、可動スクロール（０） ノミｌ板に貫通穴（
Ｈ）を開口しなければならず構造が複雑になるし、又、
油供給管（Ｔ）の出入口の差圧は高圧ドーム形に比べて
は過大にならないが、該供給管（Ｔ）は単に減圧機構（
Ｖ）を備えるだけで、その油の流通面積は常時一定とな
るため、モータ（Ｅ）をインバータ等により低速運転す
る場合には、単位時間あたりに圧縮室（Ｃ）に吸われる
冷媒流量が減少して、相対的に給油量が不足し、逆に高
速運転する場合には、冷媒流量の増大により給油量が過
剰気味となり、運転条件に適合した適正な給油が行えな
い問題がある。However, in order to maintain the inside of the casing (K) at an intermediate pressure, a through hole (
H) must be opened, which makes the structure complicated, and
The differential pressure at the inlet and outlet of the oil supply pipe (T) is not excessive compared to the high-pressure dome type, but the supply pipe (T) is simply a pressure reducing mechanism (
By simply providing V), the oil circulation area is always constant, so when the motor (E) is operated at low speed with an inverter, etc., the flow rate of refrigerant sucked into the compression chamber (C) per unit time decreases. Therefore, when the amount of oil supplied is relatively insufficient and, conversely, the engine is operated at high speed, the amount of oil supplied tends to be excessive due to the increase in the flow rate of refrigerant, and there is a problem that proper oil supply matching the operating conditions cannot be performed.
本発明の目的は、構造部品な高圧ドーム形のものにおい
て、低速及び高速の各運転条件に適合した適正な給油が
行えるスクロール形流体機械を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll-type fluid machine that is capable of appropriately lubricating a high-pressure dome-shaped structural component suitable for both low-speed and high-speed operating conditions.
帽１を解決するための手段）
そこで、本発明では、上記目的を達成するため、底部に
油溜（１０）をもつ高圧ドーム形の密閉ケーシング（１
）に、一対のスクロール（２）（３）と可変速モータ（
４）を内装したスクロール形流体機械を前提構成とし、
該構成において、前記油溜（１０）と前記スクロール（
２，３）における吸入通路（５）との間に、減圧機構（
６）と、低速時に大開度に又高速時に小開度に制御され
る流量制御弁（７）とをもつ油供給管（８）を接続した
。In order to achieve the above object, the present invention provides a high-pressure dome-shaped hermetic casing (10) having an oil reservoir (10) at the bottom.
), a pair of scrolls (2) (3) and a variable speed motor (
The prerequisite configuration is a scroll-type fluid machine equipped with 4),
In this configuration, the oil sump (10) and the scroll (
A pressure reducing mechanism (
6) and an oil supply pipe (8) having a flow control valve (7) which is controlled to a large opening at low speeds and a small opening at high speeds.
又、上記前提構成において、油溜（１０）とスクロール
（２，３）における中間圧力室（９）との間に、減圧機
構（６）と、低速時に大開度に又高速時に小開度に制御
される流量制御弁（７）とをもつ油供給管（８）を接続
した。In addition, in the above-mentioned configuration, a pressure reducing mechanism (6) is provided between the oil sump (10) and the intermediate pressure chamber (9) in the scroll (2, 3), and a pressure reducing mechanism (6) is provided that has a large opening at low speeds and a small opening at high speeds. An oil supply pipe (8) with a controlled flow control valve (7) was connected.
（作用）
低速時、流量制御弁（７）が大開度に制御されることに
より、油供給管（８）から比較的多量の油をスクロール
（２）（３）に供給でき、摺動面での給油補償が行える
と共に、高速時には前記流量制御弁（７）が小開度に制
御されることにより、その過剰な給油を抑制して適正量
の給油が行えるのである。(Function) At low speed, by controlling the flow rate control valve (7) to a large opening, a relatively large amount of oil can be supplied from the oil supply pipe (8) to the scrolls (2) and (3), and the sliding surface In addition, by controlling the flow rate control valve (7) to a small opening at high speeds, excessive oil supply can be suppressed and an appropriate amount of oil can be supplied.
又、油供給管（８）を中間圧力室（９）に接続する場合
には、同様に低速及び高速の各運転条件に適合した適正
な給油が行えると共に、吸入通路（５）に油を供給する
ものに比べて、油による吸入ガスの加熱を防止でき、入
力の増加を抑制できる利点も得られる。In addition, when connecting the oil supply pipe (8) to the intermediate pressure chamber (9), it is possible to supply oil appropriately to suit both low-speed and high-speed operating conditions, and also to supply oil to the suction passage (5). This has the advantage that heating of the intake gas due to oil can be prevented, and an increase in input power can be suppressed.
（実施例）
第１図に示すものは圧縮機としたスクロール形流体機械
であって、底部に油溜（１ｏ）をもつ高圧ドーム形の密
閉ケーシング（１）の上部に、ハウジング（ｌｌａ）（
ｌｌｂ）を介して、鏡板（Ａ、Ｂ）に渦巻体（ａ、ｂ）
を各々突設した固定スクロール（２）と可動スクロール
（３）とを内装すると共に、その下部に、ステータ（４
１）とロータ（４２）とをもち、ターミナル（４３）を
介してインバータ制御回路（４０）に接続される可変速
モータ（４）を内装している。(Example) The one shown in Fig. 1 is a scroll-type fluid machine using a compressor, and a housing (lla) (
The spiral body (a, b) is attached to the end plate (A, B) through the
A fixed scroll (2) and a movable scroll (3) each protruding from each other are installed inside, and a stator (4) is installed at the bottom of the fixed scroll (2) and a movable scroll (3).
1) and a rotor (42), and is equipped with a variable speed motor (4) connected to an inverter control circuit (40) via a terminal (43).
そして、吸入管（１２）から渦巻外周部の吸入ポート（
１３）に取込む低圧の吸入ガスを、各渦巻（ａ、ｂ）間
に画成する圧縮室（１４）で圧縮し、圧縮後の高圧ガス
を、渦巻中心部の吐出穴（１５）から前記ケーシング（
１）内に開放し、トップに設ける吐出管（１６）から外
部に取出すようにしている。Then, from the suction pipe (12) to the suction port (
13) is compressed in the compression chamber (14) defined between each volute (a, b), and the compressed high pressure gas is discharged from the discharge hole (15) in the center of the volute. casing(
1) It is opened inward and taken out to the outside through a discharge pipe (16) provided at the top.
尚、駆動軸（１７）内には給油通路（１８）を備え、オ
イルピックアップ（１９）を介して主軸受（２ｏ）や偏
心ビン軸受（２工）等に給油するようにしている。Note that an oil supply passage (18) is provided in the drive shaft (17), and oil is supplied to the main bearing (2o), eccentric bottle bearing (2 parts), etc. via an oil pickup (19).
以上の構成で、前記油溜（１０）Ａ、前記スクロール（
２，３）における吸入通路（５）を構成する前記吸入管
（１２）内との間に、キャピラリーチューブから成る減
圧機構（６）と、低速時に大開度に又高速時に小開度に
制御する流量制御弁（７）とをもつ油供給管（８）を接
続する。With the above configuration, the oil sump (10) A, the scroll (
2, 3) and the inside of the suction pipe (12) constituting the suction passage (5), there is a pressure reducing mechanism (6) made of a capillary tube, which controls the opening to a large opening at low speeds and to a small opening at high speeds. Connect an oil supply pipe (8) with a flow control valve (7).
前記流量制御弁（７）は、電動式比例制御弁用い
等を←でいるものであり、前記インバータ制御回路（４
０）の周波数出力信号に応じた電気信号を弁開度制御手
段（７０）に入力し、第２図に示すように、モータ（４
）の低速時には大きな開度により油量を増大させ、高速
時には小さな開度で油量を比例的に減少させるように制
御するものである。The flow rate control valve (7) uses an electric proportional control valve, etc., and is connected to the inverter control circuit (4).
An electrical signal corresponding to the frequency output signal of the motor (4) is inputted to the valve opening control means (70), as shown in FIG.
) At low speeds, the oil amount is increased by a large opening, and at high speeds, the oil amount is proportionally reduced by a small opening.
以上の構成によれば、冷媒流量が少なく給油が不足する
低速時には、油供給管（８）から比較的多量の油が供給
されて、低速時の給油補償が行えると共に、給油が過剰
となる高速時には、その過剰な給油を抑制でき、運転条
件に適合した適正な給油が行えるのである。According to the above configuration, at low speeds when the refrigerant flow rate is low and lubrication is insufficient, a relatively large amount of oil is supplied from the oil supply pipe (8) to compensate for lubrication at low speeds, and at high speeds when lubrication is excessive. In some cases, excessive refueling can be suppressed and appropriate refueling can be performed in accordance with the operating conditions.
ところで、以上のもので、流量制御弁（７）の開度を、
インバータ制御回路（４０）からの信号で制御するよう
にしたが、冷媒流量を直接検出して、その検出冷媒流量
が小さい低速時には大開度に、又、検出冷媒流量が大き
くなる高速時には小開度にそれぞれ制御するようにして
もよい。By the way, with the above, the opening degree of the flow control valve (7) is
Although it was designed to be controlled by a signal from the inverter control circuit (40), the refrigerant flow rate is directly detected, and at low speeds where the detected refrigerant flow rate is small, the opening is large, and at high speeds, when the detected refrigerant flow rate is large, the opening is small. It may be possible to control each of them separately.
又、以上のものでは、油供給管（８）を圧縮室（１４）
の前段部に位置する吸入通路（５）に接続したが、第３
図に示すように、前記スクロール（２，・３）における
中間圧力室（９）、つまり吸入行程が完了して圧縮行程
がやや進み、中間的な圧力値とされる前記圧縮室（」４
）に、連通穴（９工）を開口すると共に、この連通穴（
９工）に継手管（９２）を介して前記油供給管（８）の
端部を接続するようにしてもよい。In addition, in the above, the oil supply pipe (8) is connected to the compression chamber (14).
It was connected to the suction passage (5) located at the front stage of the
As shown in the figure, the intermediate pressure chamber (9) in the scroll (2, 3), that is, the compression chamber (9) where the suction stroke has been completed and the compression stroke has progressed slightly, has an intermediate pressure value.
), a communicating hole (9 holes) is opened, and this communicating hole (
The end of the oil supply pipe (8) may be connected to the oil supply pipe (8) via a joint pipe (92).
この場合にも、低速時に大開度に又高速時に小開度に制
御する流量制御弁（７）により、上記同様運転条件に適
合した適正な給油が行えると共に、吸入通路（５）に油
を供給するものに比べて、油による吸入ガスの加熱を防
止でき、入力の増加を抑制できて、能力を改善できる利
点も得られる。In this case as well, the flow rate control valve (7), which controls the opening to a large opening at low speeds and to a small opening at high speeds, allows for proper oil supply matching the operating conditions as described above, and also supplies oil to the suction passage (5). Compared to those that do, it has the advantage of preventing oil from heating the intake gas, suppressing an increase in input, and improving performance.
（発明の効果）
以上、本発明では、構造簡易な高圧ドーム形でありなが
ら、低速時には油供給管（８）から比較的多量の油をス
クロール（２）（３）に供給できて給油補償が行えると
共に、高速時には過剰な給油を抑制でき、運転条件に適
合した適正量の給油が行えるのである。(Effects of the Invention) As described above, although the present invention has a high-pressure dome shape with a simple structure, a relatively large amount of oil can be supplied from the oil supply pipe (8) to the scrolls (2) and (3) at low speeds, and oil supply compensation is achieved. At the same time, excessive refueling can be suppressed at high speeds, and the appropriate amount of refueling can be performed in accordance with the operating conditions.
又、油供給管（８）を中間圧力室（９）に接続する場合
には、同様に低速及び高速の各運転条件に適合した適正
な給油が行えると共に、吸入通路（５）に油を供給する
ものに比べて、油による吸入ガスの加熱を防止でき、入
力の増加を抑制できて能力を改善できる利点も得られる
。In addition, when connecting the oil supply pipe (8) to the intermediate pressure chamber (9), it is possible to supply oil appropriately to suit both low-speed and high-speed operating conditions, and also to supply oil to the suction passage (5). Compared to those that do, it has the advantage of preventing oil from heating the intake gas, suppressing an increase in input, and improving performance.
第１図は本発明にかかるスクロール形流体機械の第１実
施例を示す断面図、第２図は圧縮機回転数と給油量との
関係を示す図、第３図は同第２実施例を示す要部断面図
、第４図は従来例の断面図である。
（１）・・・・密閉ケーシング
（２）・・・・スクロール
（３）・・・・スクロール
（４）・・・・可変速モータ
（５）・・・・吸入通路
（６）・・・・減圧機構
（７）・・・・流量制御弁
（８）・・・・油供給管
（９）・・・・中間圧力室
（１０）・・・・油溜
第２図
圧線ｊｆ＆回転数−
第
８図FIG. 1 is a sectional view showing a first embodiment of a scroll-type fluid machine according to the present invention, FIG. 2 is a diagram showing the relationship between compressor rotation speed and oil supply amount, and FIG. 3 is a cross-sectional view showing the second embodiment of the same. FIG. 4 is a sectional view of a conventional example. (1)... Sealed casing (2)... Scroll (3)... Scroll (4)... Variable speed motor (5)... Suction passage (6)...・Pressure reduction mechanism (7)・・・Flow rate control valve (8)・・Oil supply pipe (9)・・Intermediate pressure chamber (10)・・・Oil reservoir 2nd figure Pressure line jf & rotation speed - Figure 8
Claims (2)
ーシング（１）に、一対のスクロール（２）（３）と可
変速モータ（４）を内装したスクロール形流体機械にお
いて、前記油溜（１０）と前記スクロール（２，３）に
おける吸入通路（５）との間に、減圧機構（６）と、低
速時に大開度に又高速時に小開度に制御される流量制御
弁（７）とをもつ油供給管（８）を接続したことを特徴
とするスクロール形流体機械。(1) A scroll-type fluid machine in which a pair of scrolls (2), (3) and a variable speed motor (4) are installed in a high-pressure dome-shaped sealed casing (1) with an oil reservoir (10) at the bottom. Between the reservoir (10) and the suction passage (5) in the scrolls (2, 3), there is a pressure reducing mechanism (6) and a flow control valve (7) that is controlled to a large opening at low speeds and a small opening at high speeds. ) A scroll-type fluid machine characterized in that an oil supply pipe (8) having an oil supply pipe (8) is connected thereto.
ーシング（１）に、一対のスクロール（２）（３）と可
変速モータ（４）を内装したスクロール形流体機械にお
いて、前記油溜（１０）と前記スクロール（２，３）に
おける中間圧力室（９）との間に、減圧機構（６）と、
低速時に大開度に又高速時に小開度に制御される流量制
御弁（７）とをもつ油供給管（８）を接続したことを特
徴とするスクロール形流体機械。(2) A scroll-type fluid machine in which a pair of scrolls (2), (3) and a variable speed motor (4) are installed in a high-pressure dome-shaped sealed casing (1) with an oil reservoir (10) at the bottom. a pressure reducing mechanism (6) between the reservoir (10) and the intermediate pressure chamber (9) in the scroll (2, 3);
A scroll-type fluid machine characterized in that an oil supply pipe (8) is connected to a flow control valve (7) that is controlled to a large opening at low speeds and to a small opening at high speeds.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2116361A JP2621574B2 (en) | 1990-05-02 | 1990-05-02 | Scroll type fluid machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2116361A JP2621574B2 (en) | 1990-05-02 | 1990-05-02 | Scroll type fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0417793A true JPH0417793A (en) | 1992-01-22 |
| JP2621574B2 JP2621574B2 (en) | 1997-06-18 |
Family
ID=14685063
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2116361A Expired - Fee Related JP2621574B2 (en) | 1990-05-02 | 1990-05-02 | Scroll type fluid machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2621574B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100452596B1 (en) * | 2001-10-18 | 2004-10-12 | 엘지전자 주식회사 | Refrigerating cycle |
| JP2008082309A (en) * | 2006-09-29 | 2008-04-10 | Denso Corp | Compressor |
| FR2916813A1 (en) * | 2007-05-29 | 2008-12-05 | Danfoss Commercial Compressors | SPIRAL REFRIGERATOR COMPRESSOR WITH VARIABLE SPEED |
| WO2012147145A1 (en) * | 2011-04-25 | 2012-11-01 | 株式会社日立製作所 | Refrigerant compressor and refrigeration cycle apparatus using same |
| CN108591064A (en) * | 2018-04-23 | 2018-09-28 | 珠海格力电器股份有限公司 | Compressor, air conditioner and control method of compressor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03271583A (en) * | 1990-03-20 | 1991-12-03 | Hitachi Ltd | Scroll compressor |
-
1990
- 1990-05-02 JP JP2116361A patent/JP2621574B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03271583A (en) * | 1990-03-20 | 1991-12-03 | Hitachi Ltd | Scroll compressor |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100452596B1 (en) * | 2001-10-18 | 2004-10-12 | 엘지전자 주식회사 | Refrigerating cycle |
| JP2008082309A (en) * | 2006-09-29 | 2008-04-10 | Denso Corp | Compressor |
| US8449276B2 (en) | 2007-05-29 | 2013-05-28 | Danfoss Commercial Compressors | Variable-speed scroll-type refrigeration compressor |
| WO2008152280A2 (en) * | 2007-05-29 | 2008-12-18 | Danfoss Commercial Compressors | Variable speed cooling compressor with spirals |
| WO2008152280A3 (en) * | 2007-05-29 | 2009-09-24 | Danfoss Commercial Compressors | Variable speed cooling compressor with spirals |
| FR2916813A1 (en) * | 2007-05-29 | 2008-12-05 | Danfoss Commercial Compressors | SPIRAL REFRIGERATOR COMPRESSOR WITH VARIABLE SPEED |
| WO2012147145A1 (en) * | 2011-04-25 | 2012-11-01 | 株式会社日立製作所 | Refrigerant compressor and refrigeration cycle apparatus using same |
| CN103492719A (en) * | 2011-04-25 | 2014-01-01 | 株式会社日立制作所 | Refrigerant compressor and refrigeration cycle apparatus using same |
| EP2703649A1 (en) * | 2011-04-25 | 2014-03-05 | Hitachi, Ltd. | Refrigerant compressor and refrigeration cycle apparatus using same |
| EP2703649A4 (en) * | 2011-04-25 | 2014-10-01 | Hitachi Ltd | REFRIGERANT FLUID COMPRESSOR AND REFRIGERATION CYCLE APPARATUS USING THE SAME |
| JP5695187B2 (en) * | 2011-04-25 | 2015-04-01 | 株式会社日立製作所 | Refrigerant compressor and refrigeration cycle apparatus using the same |
| US9470230B2 (en) | 2011-04-25 | 2016-10-18 | Johnson Controls-Hitachi Air Conditioning Technology (Hong Kong) Limited | Refrigerant compressor and refrigeration cycle apparatus using the same |
| CN108591064A (en) * | 2018-04-23 | 2018-09-28 | 珠海格力电器股份有限公司 | Compressor, air conditioner and control method of compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2621574B2 (en) | 1997-06-18 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |