JPH04101079A - Closed type compressor - Google Patents
Closed type compressorInfo
- Publication number
- JPH04101079A JPH04101079A JP21747190A JP21747190A JPH04101079A JP H04101079 A JPH04101079 A JP H04101079A JP 21747190 A JP21747190 A JP 21747190A JP 21747190 A JP21747190 A JP 21747190A JP H04101079 A JPH04101079 A JP H04101079A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- refrigerant
- closed container
- refrigerating machine
- container
- 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.)
- Pending
Links
- 239000003921 oil Substances 0.000 claims abstract description 54
- 239000010721 machine oil Substances 0.000 claims description 27
- 238000004891 communication Methods 0.000 claims description 13
- 230000006835 compression Effects 0.000 claims description 13
- 238000007906 compression Methods 0.000 claims description 13
- 230000001050 lubricating effect Effects 0.000 claims description 3
- 230000000717 retained effect Effects 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 abstract description 39
- 238000005187 foaming Methods 0.000 abstract description 8
- 230000008016 vaporization Effects 0.000 abstract description 8
- 238000009834 vaporization Methods 0.000 abstract description 8
- 230000003111 delayed effect Effects 0.000 abstract description 4
- 239000010726 refrigerant oil Substances 0.000 abstract description 2
- 230000000903 blocking effect Effects 0.000 abstract 4
- 238000005057 refrigeration Methods 0.000 description 21
- 230000000694 effects Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 239000006260 foam Substances 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 239000003350 kerosene Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/36—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication
- F16N7/366—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication with feed by pumping action of a vertical shaft of the machine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/36—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N2210/00—Applications
- F16N2210/10—Refrigerators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Compressor (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、冷蔵庫等の冷凍装置に使用する密閉型圧縮機
に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a hermetic compressor used in a refrigeration device such as a refrigerator.
従来の技術
近年、冷蔵庫等の冷凍装置用駆動源である密閉型圧縮機
は取付けの省７ベース化に伴なう小型化や高効率、低騒
音、低コスト等の諸要求から小型で軽量化される方向へ
一段と進んでいる。小型化された密閉型圧縮機を使用す
る冷凍装置は一般に冷凍サイクルへの冷凍機油、冷媒の
封入量が少なくなることで省電力などの目的を果たしつ
つ正常な冷凍作用を行う。しかしながら上記したような
冷凍装置で冷却器に付着した霜を取り除くため等で密閉
型圧縮機が長時間停止した場合の再運転時、冷却器の温
度も上昇し、又冷凍サイクルの空間体積が小さい事によ
る冷媒ガヌの圧力上昇がら始動負荷が増大するという問
題点がある。Conventional technology In recent years, hermetic compressors, which are the drive source for refrigerators and other refrigeration equipment, have become smaller and lighter due to various requirements such as miniaturization due to reduced installation, high efficiency, low noise, and low cost. We are making further progress in this direction. A refrigeration system using a miniaturized hermetic compressor generally achieves a normal refrigeration function while achieving the purpose of saving power by reducing the amount of refrigeration oil and refrigerant charged into the refrigeration cycle. However, in the above-mentioned refrigeration system, when the hermetic compressor is stopped for a long time to remove frost that has adhered to the cooler, the temperature of the cooler increases and the space volume of the refrigeration cycle is small. There is a problem in that the starting load increases due to the rise in the pressure of the refrigerant.
従来、密閉型圧縮機が長時間停止した時の冷凍サイクル
内冷媒ガスの圧力を低く抑えて始動負荷を軽減する手段
としては冷凍サイクル内へ封入する冷媒量を適正範囲の
下限に設定するという手段がとられていた。しかしなが
らこの様な方法で冷却器よシの吸熱を目的に封入される
冷媒量を選択するのでは始動負荷低減効果も少ない上に
１冷凍装置が据えられた雰囲気温度が下降した時に冷媒
封入不足に陥いる危険も含んでいて対応が難しい状況と
なっている。Conventionally, as a means to reduce the starting load by keeping the pressure of refrigerant gas in the refrigeration cycle low when the hermetic compressor is stopped for a long time, the method is to set the amount of refrigerant sealed in the refrigeration cycle to the lower limit of the appropriate range. was taken. However, if the amount of refrigerant to be charged is selected in this way for the purpose of absorbing heat from the cooler, the effect of reducing the starting load is small, and the refrigerant charge may be insufficient when the ambient temperature in which the refrigeration equipment is installed falls. The situation is difficult to deal with, as there are risks involved.
以下に図面を参照しながら特開昭６３−１３４８７２号
公報などにみられる従来公知の密閉型電動圧縮機の一例
について説明する。An example of a conventionally known hermetic electric compressor, which can be found in Japanese Unexamined Patent Publication No. 134872/1987, will be described below with reference to the drawings.
第６図は前記した冷凍装置に用いる密閉型圧縮機の断面
を示すものである。１は密閉型圧縮機で密閉容器２内に
弾性支持された圧縮要素３と前記圧縮要素３を駆動する
電動要素４を備え、前記密閉容器２の底部には冷凍機油
５が貯留されている。FIG. 6 shows a cross section of a hermetic compressor used in the above-mentioned refrigeration system. Reference numeral 1 denotes a hermetic compressor, which includes a compression element 3 elastically supported within a hermetic container 2 and an electric element 4 for driving the compression element 3. Refrigerating machine oil 5 is stored at the bottom of the hermetic container 2.
前記電動要素４の回転子６にはクランクシャフト７が圧
入固定されている。前記クランクシャフト７はシリンダ
ブロック８に固定された軸受９によシ軸支持されている
。１ｏはコンロッド、１１はピストンである。A crankshaft 7 is press-fitted into the rotor 6 of the electric element 4 and fixed thereto. The crankshaft 7 is axially supported by a bearing 9 fixed to a cylinder block 8. 1o is a connecting rod, and 11 is a piston.
以上のように構成された密閉型圧縮機について、以下そ
の動作について説明する。密閉型圧縮機１が運転を開始
する時まず電動要素４の回転子６が回転し、回転子６に
固定されたクランクシャフト７が回転し、コンロッド１
０を介してピストン１１を往復運動させることで密閉容
器２内の冷媒ガスを吸入した圧縮ガヌを吐出配管（図示
せず）を通して冷凍サイクルへ送シ出す。The operation of the hermetic compressor configured as above will be described below. When the hermetic compressor 1 starts operating, the rotor 6 of the electric element 4 rotates, the crankshaft 7 fixed to the rotor 6 rotates, and the connecting rod 1
By reciprocating the piston 11 through the refrigerating chamber 0, the compressed gas sucking the refrigerant gas in the closed container 2 is delivered to the refrigeration cycle through a discharge pipe (not shown).
冷凍装置の冷凍サイクルを構成する密閉型圧縮機が通常
運転をしている時は密閉容器内の冷媒ガヌ圧力は低く冷
凍機油も圧縮要素の潤滑と冷却作用によシ温度上昇して
いる。従って密閉容器内の空間残存冷媒ガスと冷凍機油
中に溶解した冷媒量は僅かであって冷凍サイクル内に封
入された冷媒ガヌの大部分は冷却器と凝縮器に適正に分
布している。When the hermetic compressor that constitutes the refrigeration cycle of the refrigeration system is in normal operation, the pressure of the refrigerant in the hermetic container is low, and the temperature of the refrigerating machine oil rises due to the lubrication and cooling effects of the compression element. Therefore, the amount of refrigerant dissolved in the refrigerant gas remaining in the airtight container and the refrigerating machine oil is small, and most of the refrigerant gas sealed in the refrigeration cycle is properly distributed in the cooler and condenser.
次に密閉型圧縮機が停止すると冷媒ガスの吸入。Next, when the hermetic compressor stops, refrigerant gas is sucked.
圧縮作用も停止する。停止直後より雑縮器から冷却器へ
の冷媒移動は冷却器の加湿をしはじめ、凝縮器と冷却器
が均圧する迄継続する。この時密閉容器は冷却器と冷凍
サイクルの低圧配管によシ連通しているので圧力上昇す
る。一方密閉型圧縮機は密閉容器よシの放熱によシ温度
低下し冷凍機油温度も下降する。The compression action also stops. Immediately after the stoppage, refrigerant transfer from the miscellaneous condenser to the cooler begins to humidify the cooler, and continues until the pressures in the condenser and cooler are equalized. At this time, the airtight container is in communication with the cooler and the low pressure piping of the refrigeration cycle, so the pressure increases. On the other hand, in a hermetic compressor, the temperature decreases due to heat radiation from the hermetic container, and the refrigerating machine oil temperature also decreases.
この様に密閉型圧縮機の停止中は運転中より冷凍サイク
ルの低圧空間部に残存する冷媒ガヌと冷凍機油中に溶解
した冷媒量が増すこととなる。特に冷却器に付着した霜
を取シ除くため等密閉型圧縮機の停止時間が長くなる時
は冷却器の温度が霜点以上に高くなることから密閉容器
内の冷媒圧力上昇が増し冷凍機油中に溶解する冷媒量も
増す。In this way, when the hermetic compressor is stopped, the amount of refrigerant dissolved in the refrigerant gas remaining in the low-pressure space of the refrigeration cycle and the refrigerant oil increases compared to when the hermetic compressor is in operation. In particular, when the hermetic compressor is stopped for a long time, such as to remove frost that has adhered to the cooler, the temperature of the cooler rises above the frost point, which increases the refrigerant pressure in the hermetic container and increases the pressure in the refrigerator oil. The amount of refrigerant dissolved in the water also increases.
再び密閉型圧縮機が始動をすると圧縮要素の働きによっ
て、初めに密閉容器内とこれに連通ずる冷却器内の冷媒
ガスが吸入され密閉容器内は減圧される。次に密閉容器
内の減圧によシ底部に貯留された冷凍機油中に溶解する
冷媒の発泡気化によシ密閉容器内の冷媒ガヌ圧が増加す
る。この時点では吐出された冷媒ガスによυ凝縮器内圧
も上昇しているので圧縮要素を駆動する電動要素への負
荷は大きくなっているので、電動要素に印加される電圧
変動などで密閉型圧縮機が始動不良を引き起こすことが
あった。When the hermetic compressor is started again, the compression element first sucks the refrigerant gas inside the hermetic container and the cooler connected thereto, thereby reducing the pressure inside the hermetic container. Next, the refrigerant gas pressure inside the hermetic container increases due to the foaming and vaporization of the refrigerant dissolved in the refrigerating machine oil stored at the bottom of the hermetic container due to the reduced pressure inside the hermetic container. At this point, the internal pressure of the υ condenser has also increased due to the discharged refrigerant gas, so the load on the electric element that drives the compression element has increased. The machine sometimes had trouble starting.
従って、従来よシ再運転時の始動性を確保するために密
閉型圧縮機の電動要素は冷凍サイクルの負荷変動や使用
電圧変動に対して充分なる裕度を持った８力が設定され
ていた。Therefore, conventionally, in order to ensure startability when restarting, the electric element of the hermetic compressor was set to 8 forces with sufficient margin for load fluctuations in the refrigeration cycle and operating voltage fluctuations. .
発明が解決しようとする課題
しかしながら上記のような構成では、密閉型圧縮機の再
運転時直後に密閉容器底部に貯留される冷凍機油中に溶
解した冷媒ガフが発泡気化するので、圧縮要素を駆動す
る電動要素への負荷が上昇するという課題を有していた
。Problems to be Solved by the Invention However, with the above configuration, immediately after restarting the hermetic compressor, the refrigerant gaff dissolved in the refrigerating machine oil stored at the bottom of the hermetic container foams and vaporizes, which drives the compression element. The problem was that the load on the electrically powered elements increases.
本発明は上記課題に鑑み、密閉型圧縮機の停止時、密閉
容器底部に貯留された冷凍機油中に溶解する冷媒が再運
転時直後に発泡気化するのを遅延し始動負荷を抑制する
密閉型圧縮機を提供するものである。In view of the above-mentioned problems, the present invention has been developed to suppress the starting load by delaying the foaming and vaporization of the refrigerant dissolved in the refrigerating machine oil stored at the bottom of the closed container when the hermetic compressor is stopped, and immediately after restarting the compressor. The company provides compressors.
課題を解決するための手段
以上のような課題を解決するために本発明の密閉型圧縮
機は、圧縮要素を潤滑する冷凍機油を密閉容器底部に貯
留し、冷凍機油を滞留させる油槽を形成するよう密閉容
器の底部に固着された遮油板を有し、この遮油板に密閉
容器内と油槽が連通ずる複数の連通孔を備えるとともに
連通孔の少なくとも一ケ所に油槽から密閉容器内への冷
凍機油の流れを止める弁を設けたものである。Means for Solving the Problems In order to solve the above-mentioned problems, the hermetic compressor of the present invention stores refrigerating machine oil for lubricating the compression element at the bottom of the closed container to form an oil tank in which the refrigerating machine oil stays. The oil shield plate is fixed to the bottom of the sealed container, and the oil shield plate is provided with a plurality of communication holes through which the inside of the sealed container communicates with the oil tank, and at least one of the communication holes is provided with a hole for communicating from the oil tank to the inside of the sealed container. It is equipped with a valve that stops the flow of refrigerating machine oil.
作 用
本発明は上記した構成によシ、密閉容器底部に設けた油
槽内に冷凍機油を封することによシ密閉型圧縮機の再運
転時に冷凍機油に溶解した冷媒の発泡気化を遅延し始動
負荷を軽減することとなる。Function The present invention has the above-described structure, and by sealing refrigerating machine oil in an oil tank provided at the bottom of a closed container, foaming and vaporization of the refrigerant dissolved in the refrigerating machine oil is delayed when the hermetic compressor is restarted. This will reduce the starting load.
実施例
以下本発明の一実施例について図面を参照しながら説明
する。尚従来例と同一部品は同一符号を用いて説明し、
構成、動作が同じところは省略する。EXAMPLE An example of the present invention will be described below with reference to the drawings. Parts that are the same as those in the conventional example will be explained using the same reference numerals.
Parts with the same configuration and operation will be omitted.
第１図、第２図、第３図において、１６は密閉容器２に
固着された遮油板で前記密閉器２の底部に貯留された冷
凍機油６内に配設され前記密閉容器２よシ独立した油槽
１７を形成し、前記油槽１７内の封油１８は大径の連通
孔１６と小径の孔２０によシ前記密閉容器内の前記冷凍
機油５と連通している。１９は弁で前記遮油板１６の前
記油槽１７側に固着され前記連通孔１６を覆っている。In FIGS. 1, 2, and 3, reference numeral 16 denotes an oil shielding plate fixed to the sealed container 2, which is disposed in the refrigerating machine oil 6 stored at the bottom of the sealed container 2, and is installed in the refrigerating machine oil 6 stored at the bottom of the sealed container 2. An independent oil tank 17 is formed, and a sealing oil 18 in the oil tank 17 communicates with the refrigerating machine oil 5 in the sealed container through a large-diameter communication hole 16 and a small-diameter hole 20. A valve 19 is fixed to the oil tank 17 side of the oil shield plate 16 and covers the communication hole 16.
上記のように構成された密閉型圧縮機の動作について説
明する。密閉型圧縮機が運転を停止した時、凝縮器の冷
媒が冷却器へ圧力平衡点まで移動しこの間冷却器は加温
される。同時に密閉容器内の冷媒圧力は上昇し冷凍機油
には密閉容器内の冷媒が溶解し、続いて油槽内の封油に
も連通孔及び孔を通して冷媒が溶解される。この時連通
孔部に設けられた弁は開弁じており油槽内封油への冷媒
溶解が容易となる。ここで密閉型圧縮機が運転を再開す
ると、圧縮要素の働きによって密閉容器内の冷媒ガスが
吸入された後冷凍サイクルへ吐出管を通して吐出される
。この時密閉容器内の冷媒ガス圧力は低下し冷凍機油中
に溶解した冷媒が発泡気化し密閉容器内へ出ていくが冷
凍機油の一部は遮油板による油槽に滞留しているので封
油中溶解冷媒の発泡気化は遮油板と連通孔部の弁の閉弁
によシ緩やかに起きて孔を通じて密閉容器内へ導かれる
。従って密閉型圧縮機の停止中に冷凍機油と油槽内の封
油に溶解する冷媒量は遮油板に影響を受けず再運転時直
後の油中溶解冷媒の発泡気化が遅れて始動負荷の軽減が
計れることとなる。The operation of the hermetic compressor configured as above will be explained. When the hermetic compressor shuts down, the refrigerant in the condenser moves to the cooler until it reaches a pressure equilibrium point, during which time the cooler is heated. At the same time, the refrigerant pressure in the sealed container rises, and the refrigerant in the sealed container is dissolved in the refrigerating machine oil, and subsequently, the refrigerant is also dissolved in the sealing oil in the oil tank through the communication holes and holes. At this time, the valve provided in the communication hole is open, making it easy for the refrigerant to dissolve in the oil sealed in the oil tank. When the hermetic compressor resumes operation, the refrigerant gas in the hermetic container is sucked in by the action of the compression element and then discharged to the refrigeration cycle through the discharge pipe. At this time, the refrigerant gas pressure inside the sealed container decreases, and the refrigerant dissolved in the refrigerating machine oil foams and vaporizes and comes out into the sealed container, but some of the refrigerating machine oil remains in the oil tank with an oil shield, so it is sealed. Foaming and vaporization of the dissolved refrigerant occurs slowly when the oil shield plate and the valve in the communication hole are closed, and the refrigerant is guided into the closed container through the hole. Therefore, the amount of refrigerant dissolved in the refrigerating machine oil and sealing oil in the oil tank while the hermetic compressor is stopped is not affected by the oil shield plate, and the foaming and vaporization of the refrigerant dissolved in the oil immediately after restarting is delayed, reducing the starting load. can be measured.
第４図は本発明例による密閉型圧縮機再運転時の始動負
荷推移を表わしたものである。従来例による密閉型圧縮
機再運転時直後の最大負荷はＴ。FIG. 4 shows the starting load transition when restarting the hermetic compressor according to the example of the present invention. The maximum load of the conventional hermetic compressor immediately after restarting is T.
秒後に発生しその大きさはＰｌであるのに対し本発明例
は１２秒後に発生しΔを遅れてＰ２ の大きさとなりΔ
ｐだけ軽減されている。It occurs after 1 second and has a magnitude of Pl, whereas in the example of the present invention it occurs after 12 seconds and has a magnitude of P2 with a delay of Δ.
It is reduced by p.
発明の効果
以上のように本発明は、圧縮要素を潤滑する冷凍機油を
密閉容器底部に貯留し、冷凍機油を滞留させる油槽を形
成するよう密閉容器の底部に固着された遮油板を有しこ
の遮油板に密閉容器内と油槽が連通ずる複数の連通孔を
備えるとともに連通孔の少なくとも一ケ所に油槽から密
閉容器内への冷凍機油の流れを止める弁を設けることで
、密閉型圧縮機の再運転時に冷凍機油中に溶解した冷媒
の発泡気化を遅延気化することになるので、始動負荷を
軽減させることができる。Effects of the Invention As described above, the present invention stores refrigerating machine oil for lubricating the compression element at the bottom of the closed container, and has an oil shield plate fixed to the bottom of the closed container to form an oil tank in which the refrigerating machine oil stays. The oil shield plate has a plurality of communication holes through which the inside of the sealed container and the oil tank communicate with each other, and a valve is provided in at least one of the communication holes to stop the flow of refrigerating machine oil from the oil tank into the sealed container. Since the foaming and vaporization of the refrigerant dissolved in the refrigerating machine oil is delayed when restarting the refrigerating machine, the starting load can be reduced.
第１図は本発明の一実施例における密閉型圧縮機の断面
図、第２図は第１図の密閉型圧縮機の遮油板の斜視図、
第３図は第２図のＡ−Ａ線の矢視図、第４図は同第１図
の密閉型圧縮機における始動負荷の軽減効果を表わした
グラフ、第６図は従来の密閉型圧縮機の断面図である。
１・・・・・・密閉型圧縮機、２・・・・・・密閉容器
、３・・・・・圧縮要素、４・・・・・・電動要素、５
・・・・・・冷凍機油、１６・・・・・・遮油板、１６
・・・・・・連通孔、１７・・・・・・油槽、１８・・
・・・・封油、１９・・・・・・弁、２ｏ・・・・・・
孔。
代理人の氏名 弁理士 粟 野 重 孝 ほか１名７閂
型」ｌ動片−１機
侶閑客器
反扁ｔ？
電動ｌ
〉１デン￥＊ ５Ａ
ｔ′ｉＩ板
５ｉｉ橿
灯油
苛
Ｓ ｔ。
経過時間 （秒）
ｓ
Ｏ
第２図
第 ３
第５図
１５− 遮殖根
ｆ６−達 連孔
１９− 弁
２０− ＪＬ。
２θFIG. 1 is a sectional view of a hermetic compressor according to an embodiment of the present invention, FIG. 2 is a perspective view of an oil shield plate of the hermetic compressor of FIG. 1,
Figure 3 is a view taken along line A-A in Figure 2, Figure 4 is a graph showing the effect of reducing the starting load in the hermetic compressor shown in Figure 1, and Figure 6 is a graph showing the effect of reducing the starting load in the hermetic compressor shown in Figure 1. FIG. 1... Sealed compressor, 2... Sealed container, 3... Compression element, 4... Electric element, 5
... Refrigeration machine oil, 16 ... Oil shield plate, 16
......Communication hole, 17...Oil tank, 18...
...Oil seal, 19...Valve, 2o...
Hole. Name of agent: Patent attorney Shigetaka Awano and 1 other person Electric l 〉1den ￥* 5A t'iI board 5ii Kakeru kerosene S t. Elapsed time (seconds) s O Fig. 2 Fig. 3 Fig. 5 15- Interceptive root f6- Reach Connecting hole 19- Valve 20- JL. 2θ
Claims (1)
収納するとともに、前記圧縮要素を潤滑する冷凍機油を
前記密閉容器底部に貯留し、前記冷凍機油を滞留させる
油槽を形成するように前記密閉容器の底部に固着された
遮油板を有し、前記遮油板に前記密閉容器内と前記油槽
を連通する複数の連通孔を備えるとともに、前記連通孔
の少なくとも一ケ所に前記油槽から前記密閉容器内への
前記冷凍機油の流れを止める弁を設けたことを特徴とす
る密閉型圧縮機。A compression element driven by an electric element is housed in the airtight container, and refrigerating machine oil for lubricating the compression element is stored at the bottom of the airtight container to form an oil tank in which the refrigerating machine oil is retained. has an oil shielding plate fixed to the bottom of the oil tank, the oil shielding plate has a plurality of communication holes that communicate the inside of the sealed container with the oil tank, and at least one of the communication holes has a connection hole between the oil tank and the sealed container. A hermetic compressor characterized by being provided with a valve that stops the flow of the refrigerating machine oil into the compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21747190A JPH04101079A (en) | 1990-08-17 | 1990-08-17 | Closed type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21747190A JPH04101079A (en) | 1990-08-17 | 1990-08-17 | Closed type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04101079A true JPH04101079A (en) | 1992-04-02 |
Family
ID=16704756
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21747190A Pending JPH04101079A (en) | 1990-08-17 | 1990-08-17 | Closed type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04101079A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007275552A (en) * | 2006-03-16 | 2007-10-25 | Sri Sports Ltd | Golf club head and manufacturing method thereof |
-
1990
- 1990-08-17 JP JP21747190A patent/JPH04101079A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007275552A (en) * | 2006-03-16 | 2007-10-25 | Sri Sports Ltd | Golf club head and manufacturing method thereof |
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