JPH03195839A - Air-conditioner - Google Patents
Air-conditionerInfo
- Publication number
- JPH03195839A JPH03195839A JP33720789A JP33720789A JPH03195839A JP H03195839 A JPH03195839 A JP H03195839A JP 33720789 A JP33720789 A JP 33720789A JP 33720789 A JP33720789 A JP 33720789A JP H03195839 A JPH03195839 A JP H03195839A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- gas
- liquid
- liquid separator
- heat source
- 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
- 239000003507 refrigerant Substances 0.000 claims abstract description 78
- 239000007788 liquid Substances 0.000 claims abstract description 37
- 238000010438 heat treatment Methods 0.000 claims description 15
- 238000004378 air conditioning Methods 0.000 claims description 6
- 230000001737 promoting effect Effects 0.000 claims 1
- 238000001816 cooling Methods 0.000 abstract description 21
- 238000005461 lubrication Methods 0.000 abstract description 5
- 238000000034 method Methods 0.000 abstract description 2
- 238000005057 refrigeration Methods 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 7
- 230000032258 transport Effects 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000005514 two-phase flow Effects 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 239000012071 phase Substances 0.000 description 2
- PCTMTFRHKVHKIS-BMFZQQSSSA-N (1s,3r,4e,6e,8e,10e,12e,14e,16e,18s,19r,20r,21s,25r,27r,30r,31r,33s,35r,37s,38r)-3-[(2r,3s,4s,5s,6r)-4-amino-3,5-dihydroxy-6-methyloxan-2-yl]oxy-19,25,27,30,31,33,35,37-octahydroxy-18,20,21-trimethyl-23-oxo-22,39-dioxabicyclo[33.3.1]nonatriaconta-4,6,8,10 Chemical compound C1C=C2C[C@@H](OS(O)(=O)=O)CC[C@]2(C)[C@@H]2[C@@H]1[C@@H]1CC[C@H]([C@H](C)CCCC(C)C)[C@@]1(C)CC2.O[C@H]1[C@@H](N)[C@H](O)[C@@H](C)O[C@H]1O[C@H]1/C=C/C=C/C=C/C=C/C=C/C=C/C=C/[C@H](C)[C@@H](O)[C@@H](C)[C@H](C)OC(=O)C[C@H](O)C[C@H](O)CC[C@@H](O)[C@H](O)C[C@H](O)C[C@](O)(C[C@H](O)[C@H]2C(O)=O)O[C@H]2C1 PCTMTFRHKVHKIS-BMFZQQSSSA-N 0.000 description 1
- 244000089486 Phragmites australis subsp australis Species 0.000 description 1
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- Other Air-Conditioning Systems (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は冷暖房装置の冷媒サイクルに関するものである
。DETAILED DESCRIPTION OF THE INVENTION FIELD OF INDUSTRIAL APPLICATION The present invention relates to a refrigerant cycle for a heating and cooling system.
従来の技術
従来、例えば特開昭６２−２３８９５２号公報に示され
るように熱源側冷媒サイクルと利用側冷媒サイクルに分
離した冷暖房装置の冷媒サイクルは第３図のように構成
されていた。第３図において、１は圧縮機、２は圧力差
で作動するパイロット式の熱源側四方弁、３は熱源側熱
交換器、４は冷房用減圧装置、６は暖房用減圧装置、６
は暖房時冷房用減圧装置４を閉成する逆止弁、７は冷房
時暖房用減圧装置５を閉成する逆止弁、８は第１補助熱
交換器でこれらを環状に連接し、熱源側冷媒サイクル内
を形成している。９は第２補助熱交換器で第１補助熱交
換器８と熱交換するように一体に形成されている。１ｏ
は冷媒量調整タンクで冷房時と暖房時の冷媒量を調整す
るもので、冷房時に不例の冷媒を貯留するものである。2. Description of the Related Art Conventionally, as shown in, for example, Japanese Unexamined Patent Application Publication No. 62-238952, the refrigerant cycle of an air-conditioning system is separated into a heat source side refrigerant cycle and a user side refrigerant cycle, and is configured as shown in FIG. In Fig. 3, 1 is a compressor, 2 is a pilot type heat source side four-way valve operated by pressure difference, 3 is a heat source side heat exchanger, 4 is a cooling pressure reducing device, 6 is a heating pressure reducing device, 6
7 is a check valve that closes the pressure reducing device 4 for air conditioning during heating, 7 is a check valve that closes the pressure reducing device 5 for heating during cooling, and 8 is a first auxiliary heat exchanger, which is connected in an annular manner and connected to the heat source. It forms the inside of the side refrigerant cycle. A second auxiliary heat exchanger 9 is integrally formed to exchange heat with the first auxiliary heat exchanger 8. 1o
The refrigerant amount adjustment tank is used to adjust the amount of refrigerant during cooling and heating, and is used to store unusual refrigerant during cooling.
１１は冷媒搬送装置で冷房時と暖房時で冷媒の流出方向
が反対となる可逆特性をもっておシ、これらは熱源側ユ
ニッ）ａに収納されている。１２は利用側熱交換器で利
用側ユニッ）ｂに収納され接続配管Ｃ１Ｃ′で熱源側ユ
ニッ）ａと接続されている。前記第２補助熱交換器９と
冷媒量調整タンク１０．冷媒搬送装置１１、利用側熱交
換器１２および接続配管ｆを環状に連続し利用側冷媒サ
イクル■を形成している。尚利用側冷媒サイク）ｖ（Ｙ
）と熱源側冷媒サイク／ｌ／（イ）には同一あるいは近
似した凝縮・蒸発特性をもつ冷媒が封入しである。Reference numeral 11 denotes a refrigerant conveying device which has a reversible characteristic such that the outflow direction of the refrigerant is opposite during cooling and heating, and is housed in the heat source side unit a). Reference numeral 12 denotes a heat exchanger on the user side, which is housed in the user side unit)b and connected to the heat source side unit)a through a connecting pipe C1C'. The second auxiliary heat exchanger 9 and the refrigerant amount adjustment tank 10. The refrigerant transport device 11, the user-side heat exchanger 12, and the connecting pipe f are connected in an annular manner to form a user-side refrigerant cycle (2). Furthermore, the refrigerant cycle on the user side) v (Y
) and the heat source side refrigerant cycle /l/(a) are filled with refrigerant having the same or similar condensation and evaporation characteristics.
以上のように構成された冷暖房装置についてその動作を
説明する。The operation of the heating and cooling system configured as described above will be explained.
冷房運転時は図中実線矢印の冷媒サイクルとなシ、熱源
側冷媒サイクルでは、圧縮機１からの高温高圧ガスは熱
源側四方弁２を通υ熱源側熱交換器３で放熱して凝縮液
化し逆止弁６を通って冷房用膨張弁４で減圧され第１補
助熱交換器８で蒸発して熱源側四方弁２を通如圧縮機１
へ循環する。During cooling operation, the refrigerant cycle shown by the solid line arrow in the figure is used.In the refrigerant cycle on the heat source side, high-temperature, high-pressure gas from the compressor 1 passes through the four-way valve 2 on the heat source side, radiates heat in the heat exchanger 3 on the heat source side, and is condensed and liquefied. The pressure is reduced by the cooling expansion valve 4 through the check valve 6, evaporated by the first auxiliary heat exchanger 8, and then passed through the heat source side four-way valve 2 to the compressor 1.
circulate to.
この状態を第４図のモリエル線図で説明すると、一般の
冷凍サイクルＡＢＣＤを示し、Ａ−Ｂが圧縮機１での圧
縮、Ｅ−Ｃが熱源側熱交換器３での放熱、Ｃ−Ｄが冷房
用膨張弁４での減圧、Ｄ−Ａが第１補助熱交換器８での
蒸発である。To explain this state using the Mollier diagram in Fig. 4, it shows a general refrigeration cycle ABCD, where A-B is compression in the compressor 1, E-C is heat radiation in the heat source side heat exchanger 3, and C-D is the Mollier diagram. is the pressure reduction at the cooling expansion valve 4, and DA is the evaporation at the first auxiliary heat exchanger 8.
この時利用側冷媒サイクルの第２補助熱交換器９と前記
第１補助熱交換器８が熱交換（第３図Ｅ −Ｆ）Ｌ利用
側冷媒サイクル内のガス冷媒が冷却されて乾き度が減少
し、冷媒量調整タンク１０を通って冷媒搬送装置１１に
送られ、この冷媒搬送装置１１によって接続配管Ｃを通
って利用側熱交換器１２へ送られ（第３図Ｆ−Ｇ）て冷
房して吸熱蒸発（第３図Ｇ−Ｅ）Ｌ、乾き度が上昇して
接続配管Ｃ′を通って第２補助熱交換器９に循環するこ
とになる。At this time, the second auxiliary heat exchanger 9 of the user-side refrigerant cycle and the first auxiliary heat exchanger 8 exchange heat (Fig. 3 E-F).L The gas refrigerant in the user-side refrigerant cycle is cooled and the dryness is reduced. It is sent to the refrigerant conveying device 11 through the refrigerant amount adjustment tank 10, and by this refrigerant conveying device 11, it is sent to the user-side heat exchanger 12 through the connecting pipe C (FIG. 3 F-G) for cooling. As a result, the heat is endothermically evaporated (FIG. 3 G-E), the dryness increases, and the heat is circulated to the second auxiliary heat exchanger 9 through the connecting pipe C'.
一方、暖房運転時においては、図中破線矢印の冷媒サイ
クルとなシ、熱源側冷媒サイクｐ■では、圧縮機１から
の高温高圧冷媒は熱源側四方弁２から第１補助交換器８
に送られ、放熱して凝縮液化し、逆止弁７から暖房用減
圧装置５で減圧し、熱源側熱交換器３で吸熱蒸発し熱源
側四方弁２を通って圧縮機１へ循環する。この時利用側
冷媒サイクル（７）の第２補助熱交換器９と前記第１補
助熱交換器８が熱交換し、利用側冷媒サイクＡ／（Ｙ）
内の冷媒が加熱され乾き度が上昇しく第４図Ｈ−Ｉ）、
接続配管Ｃ′を通って利用側熱交換器１２へ送られ、暖
房して放熱して乾き度が減少しく第４図Ｊ −Ｇ）接続
配管Ｃを通って冷媒搬送装置１１へ送られ、冷媒量調整
タンク１０から第２補助熱交換器９へ循環する（第４図
１−Ｈ）。On the other hand, during heating operation, in the refrigerant cycle indicated by the broken line arrow in the figure, and in the heat source side refrigerant cycle p■, the high temperature and high pressure refrigerant from the compressor 1 is transferred from the heat source side four-way valve 2 to the first auxiliary exchanger 8.
It radiates heat, condenses and liquefies, reduces the pressure through the check valve 7 in the heating pressure reducing device 5, absorbs heat and evaporates in the heat source side heat exchanger 3, and circulates through the heat source side four-way valve 2 to the compressor 1. At this time, the second auxiliary heat exchanger 9 of the user side refrigerant cycle (7) and the first auxiliary heat exchanger 8 exchange heat, and the user side refrigerant cycle A/(Y)
The refrigerant inside is heated and the degree of dryness increases (Fig. 4 H-I).
The refrigerant is sent to the user-side heat exchanger 12 through the connecting pipe C', where it is heated and radiated to reduce dryness. It circulates from the quantity adjustment tank 10 to the second auxiliary heat exchanger 9 (FIG. 4 1-H).
発明が解決しようとする課題
しかしながら、従来の構成では、冷媒搬送装置１１の吸
入冷媒の状態は第３図のようにモリエル線図上のＦ又は
１点のように常に乾き度の小さい状態であることはまず
なく、気液混合のいわゆる二相流でアシ、液と湿υガヌ
が、断続的に流れ込む。更に、その状況は負荷変動、起
動時等も含めて一定とは限らず、例えば湿シガスの状態
が長く続き、冷媒搬送装置１１に対して、液冷媒による
潤滑不良等の大きなダメージを与えることとなる。Problems to be Solved by the Invention However, in the conventional configuration, the state of the refrigerant sucked into the refrigerant conveying device 11 is always in a state of low dryness, as indicated by point F or point 1 on the Mollier diagram as shown in FIG. This rarely happens, and reeds, liquid, and wet υganu flow intermittently in a so-called two-phase flow of gas-liquid mixture. Furthermore, the situation is not always constant, including load fluctuations, startup times, etc., and, for example, the wet gas state may continue for a long time, causing major damage to the refrigerant conveying device 11, such as poor lubrication due to the liquid refrigerant. Become.
本発明は上記問題点に鑑み、二相流の冷媒搬送を円滑に
行う冷暖房装置を提供するものである。In view of the above-mentioned problems, the present invention provides a heating and cooling device that smoothly transports refrigerant in a two-phase flow.
課題を解決するための手段
上記問題点を解決するために、本発明の冷暖房装置は冷
媒搬送装置の吸入側に、気液分離器を配設し、更に熱源
側冷媒サイクルにて冷却される冷却器を前記気液分離器
と熱交換関係に設けるものである。Means for Solving the Problems In order to solve the above-mentioned problems, the air-conditioning device of the present invention is provided with a gas-liquid separator on the suction side of the refrigerant conveying device, and further includes a cooling device that is cooled by the refrigerant cycle on the heat source side. A vessel is provided in a heat exchange relationship with the gas-liquid separator.
作 用
本発明は上記構成によって、冷媒搬送装置に吸入される
冷媒を、−旦気液分離器で気相（湿シガス）と液相に分
離し、その後に、分離された気相を冷却器にて強制的に
液化促進し、冷媒搬送装置に送シ、長期にわたるガス吸
引を防止し、液冷媒による潤滑不足を解消し、冷媒搬送
装置の事故を防ぐものである。According to the above configuration, the present invention separates the refrigerant sucked into the refrigerant conveying device into a gas phase (wet gas) and a liquid phase in the gas-liquid separator, and then transfers the separated gas phase to the cooler. This system forcibly promotes liquefaction and transports the refrigerant to the refrigerant transport device, prevents long-term gas suction, eliminates the lack of lubrication caused by liquid refrigerant, and prevents accidents in the refrigerant transport device.
実施例
以下本発明の一実施例を示す冷暖房装置について、図面
を参照しながら説明する。第１図は本発明の実施例を示
すもので、従来例（第２図）と同一部分については同一
符号を附し、説明を省略する。EXAMPLE Hereinafter, a heating and cooling system showing an example of the present invention will be described with reference to the drawings. FIG. 1 shows an embodiment of the present invention, and the same parts as those in the conventional example (FIG. 2) are given the same reference numerals, and the explanation thereof will be omitted.
１４は気液分離器であシ、入口１４ａ、液出口１４ｂ、
を有する。１．５はこの気液分離器１４内のガスＲ（上
方部）に配設した冷却器で、熱源側冷媒サイク／Ｉ／Ｇ
Ｋ）の冷媒にて冷却される。即ち熱源側冷媒サイクル（
３）の暖房用、冷房用減圧装置５゜４の上流より専用減
圧器１６．１７および電磁弁１８．１９を介して一端が
接続され、他端は圧縮機１の吸入側に接続しである。14 is a gas-liquid separator, an inlet 14a, a liquid outlet 14b,
has. 1.5 is a cooler installed in the gas R (upper part) in this gas-liquid separator 14, and is connected to the heat source side refrigerant cycle/I/G.
It is cooled with refrigerant K). In other words, the heat source side refrigerant cycle (
3) One end is connected to the upstream side of the heating and cooling pressure reducing device 5゜4 via a dedicated pressure reducer 16.17 and a solenoid valve 18.19, and the other end is connected to the suction side of the compressor 1. .
かかる構成によれば冷房運転時にて説明すると第２補助
熱交換器９で熱交換（第２図に−Ｌ）した二相流状態の
冷媒（第２図り点）は、冷媒量調整タンク１０、利用側
四方弁１３をへて気液分離器１４に入シ、液と湿シガヌ
に一旦分離され、液（第２図Ｍ点）はガス冷却と同時に
冷却されて０点に達し、冷媒搬送装置１１に入シ加圧さ
れて利用側熱交換器１２内にて熱交換（第２図Ｐ−Ｋ）
する。一方、気液分離器１４内のガスは熱源側冷媒サイ
クル囚の冷却器１６にて冷却器液化を促進し、やはりＭ
点に達する。尚第２図Ｖ −Ｗは冷却器１６の冷却を示
す。According to this configuration, during cooling operation, the refrigerant in a two-phase flow state (second control point) that has undergone heat exchange with the second auxiliary heat exchanger 9 (-L in FIG. 2) is transferred to the refrigerant amount adjustment tank 10, It passes through the four-way valve 13 on the user side and enters the gas-liquid separator 14, where it is once separated into liquid and wet liquid.The liquid (point M in Figure 2) is cooled at the same time as gas cooling and reaches the 0 point, and is transferred to the refrigerant conveying device. 11 and is pressurized and heat exchanged in the user side heat exchanger 12 (Fig. 2 P-K)
do. On the other hand, the gas in the gas-liquid separator 14 promotes liquefaction in the cooler 16 of the heat source side refrigerant cycle, and also
Reach the point. Note that FIG. 2 V-W shows cooling of the cooler 16.
また暖房時においては、第２図のＱ−、Ｒ−、Ｒ→Ｓ−
８−Ｔ−Ｕ順で冷媒が循環し、やはシ気液分離器１４に
て分離した液（Ｔ点）は冷却されてＵＱ、に達し、冷媒
搬送装置１１に送られると共に、冷却器１５にてガスの
液化が行なわれるものである。Also, during heating, Q-, R-, R→S- in Fig. 2
The refrigerant circulates in the order of 8-T-U, and the liquid (T point) separated in the gas-liquid separator 14 is cooled and reaches UQ, and is sent to the refrigerant conveying device 11, and is also transferred to the cooler 15. The gas is liquefied in the process.
尚暖房時における冷却器の蒸発温度は冷房時程低温にす
ることなく、減圧器１７の調整によシ、第２図のＶ／
Ｗ／のように温度を上昇してもよい。In addition, the evaporation temperature of the cooler during heating can be adjusted to V/ in Fig. 2 by adjusting the pressure reducer 17 without making it as low as during cooling.
The temperature may be increased like W/.
発明の効果
上記構成によれば、本発明は、利用側冷媒サイクルの冷
媒搬送装置の吸入側に気液分離器を設け、液を吸引する
ように成し、かつ分離ガスを強制的に冷却液化を図るた
め、常に冷媒搬送装置には液が吸引されるので、液冷媒
を潤滑油として構成される回転摺動部がガスの吸引によ
り潤滑不良を生じ焼付く等の事故を防止できる。更にか
かる冷却器は熱源側冷媒サイクルにて構成されるため、
別途冷却装置が不用となり、構成を簡素化できる。Effects of the Invention According to the above structure, the present invention provides a gas-liquid separator on the suction side of the refrigerant conveying device of the user-side refrigerant cycle to suck liquid, and forcibly cools and liquefies the separated gas. In order to achieve this, liquid is always sucked into the refrigerant conveying device, so it is possible to prevent accidents such as seizure due to poor lubrication caused by gas suction in the rotating sliding portion, which is configured using liquid refrigerant as a lubricating oil. Furthermore, since such a cooler is composed of a heat source side refrigerant cycle,
A separate cooling device is not required, and the configuration can be simplified.
第１図は本発明の一実施例における冷暖房装置の冷媒サ
イクル図、第２図は本発明の一実施例を示すモリエル線
図、第３図は従来の冷暖房装置の冷媒サイクル図、第４
図は従来例のモリエル線図である。
３・・・・・・熱源側熱交換器、８・・・・・・第１補
助熱交換器、９・・・・・・第２補助熱交換器、１１・
・・・・・冷媒搬送装置、１２・・・・・・利用側熱交
換器、１３・・・・・・利用側四方弁、１４・・・・・
・気液分離器、１４ａ・・・・・・入口、１４ｂ・・・
・・・液出口、１５・・・・・・冷却器、Ｘ・・・・・
・熱源側冷媒サイ７／Ｉ／。Fig. 1 is a refrigerant cycle diagram of an air conditioning system according to an embodiment of the present invention, Fig. 2 is a Mollier diagram showing an embodiment of the invention, Fig. 3 is a refrigerant cycle diagram of a conventional air conditioning system.
The figure is a Mollier diagram of a conventional example. 3...Heat source side heat exchanger, 8...First auxiliary heat exchanger, 9...Second auxiliary heat exchanger, 11.
...Refrigerant conveyance device, 12...Use side heat exchanger, 13...Use side four-way valve, 14...
・Gas-liquid separator, 14a...Inlet, 14b...
...Liquid outlet, 15...Cooler, X...
・Heat source side refrigerant size 7/I/.
Claims (1)
び第１補助熱交換器を環状に連接してなる熱源側冷媒サ
イクルと、この第１補助熱交換器と一体に形成し、熱交
換する第２補助熱交換器と利用側熱交換器と冷媒搬送装
置とを環状に連接するものであって、前記冷媒搬送装置
の吸入側に、入口、液出口、気液分離器を設け、前記気
液分離器内のガスを液化促進する冷却器を設けると共に
、この冷却器を前記熱源側冷媒サイクルと連結した冷暖
房装置。A heat source side refrigerant cycle is formed by connecting a compressor, a heat source side four-way valve, a heat source side heat exchanger, a pressure reducing device, and a first auxiliary heat exchanger in an annular manner, and this first auxiliary heat exchanger is integrally formed. A second auxiliary heat exchanger to be exchanged, a user-side heat exchanger, and a refrigerant transfer device are connected in an annular manner, and an inlet, a liquid outlet, and a gas-liquid separator are provided on the suction side of the refrigerant transfer device, An air-conditioning/heating system including a cooler for promoting liquefaction of gas in the gas-liquid separator and connecting the cooler to the heat source side refrigerant cycle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33720789A JP2730648B2 (en) | 1989-12-26 | 1989-12-26 | Air conditioning |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33720789A JP2730648B2 (en) | 1989-12-26 | 1989-12-26 | Air conditioning |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03195839A true JPH03195839A (en) | 1991-08-27 |
| JP2730648B2 JP2730648B2 (en) | 1998-03-25 |
Family
ID=18306445
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33720789A Expired - Fee Related JP2730648B2 (en) | 1989-12-26 | 1989-12-26 | Air conditioning |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2730648B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04236064A (en) * | 1991-01-11 | 1992-08-25 | Sanki Eng Co Ltd | Apparatus for transferring hot/warm heat |
-
1989
- 1989-12-26 JP JP33720789A patent/JP2730648B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04236064A (en) * | 1991-01-11 | 1992-08-25 | Sanki Eng Co Ltd | Apparatus for transferring hot/warm heat |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2730648B2 (en) | 1998-03-25 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |