201035448 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種在密閉容器内具備電動元件與回轉 壓縮元件之密閉型回轉壓縮機。尤有關於一種在密閉容器 内下部收納回轉壓縮元件，並於此回轉壓縮元件之上方收 納電動元件，而電動元件係由定子及轉子所構成者，該轉 子係以可藉由該定子之磁場轉動之方式插裝於内，而且固 定在兼作回轉壓縮元件驅動用之曲柄（crank)轴之回轉軸。 【先前技術】 以往此種密閉型回轉壓縮機係由收納於密閉容器内下 部之回轉壓縮元件、及收納於密閉容器内上部之電動元件 所構成。電動元件係由定子與轉子所構成，該定子係沿著 密閉容器之上部空間之内周面安裝成環狀、而該轉子係以 可藉由該定子之磁場轉動之方式插裝於内，而且，固定在 兼作回轉壓縮元件驅動用曲柄轴之回轉軸。 回轉壓縮元件係由壓縮缸（cylinder)、嵌合於形成在 回轉軸之偏心部並在壓縮缸内偏心轉動之滚柱（roller)、 及與壓縮缸抵接並將壓縮缸内劃分為低壓室側與高壓室側 之葉片（vane)所構成。此外，在密閉容器内底部係儲存有 用以使該回轉壓縮元件或回轉轴等滑動部潤滑之油（oil)。 再者，當對電動元件之定子之定子繞線通電而產生回 轉磁場時，設於内側之轉子即因此磁場而回轉。藉由此回 轉，使嵌合於回轉轴之偏心部之滾柱在壓縮缸内偏心回 轉。藉此，低壓冷媒被吸入在壓縮缸内之低壓室側，且藉 321798 201035448 由滾柱與葉片之動作而受到壓縮。在此壓縮缸内被壓縮而 成為高溫高壓之冷媒氣體，從高壓室側經由喷出口喷出至 噴出消音器（muffler)。喷出至噴出消音器之冷媒氣體，係 從用以將該噴出消音器與密閉容器内連通且指向上方電動 元件而設置之喷出孔喷出至密閉容器内。此時，供給至回 轉壓縮元件之油成為霧（mist)狀混入於冷媒氣體中，該油 亦與冷媒氣體一同喷出至密閉容器内。 喷出至密閉容器内之冷媒氣體係設計成通過形成於電 ^ 動元件内之冷媒通路，而從設於電動元件上侧之噴出管噴 出至外部之構成（參照例如專利文獻1)。 【發明内容】 [發明所欲解決之課題] 然而，在此種習知之密閉型回轉壓縮機中，無法在密 閉容器内充分進行冷媒氣體與油的分離，而會產生從喷出 管喷出至外部之油量較多，且因為油流出至外部迴路而產 Q 生性能降低或對滑動部供油不足的問題。 本發明係為了解決此種習知技術之問題而研創者，其 目的在促進密閉容器内之油分離，並降低油喷出至壓縮機 外部。 [解決課題之手段] 申請專利範圍第1項之發明，係一種密閉型回轉壓縮 機，其係在密閉容器内下部收納回轉壓縮元件，並於此回 轉壓縮元件之上方收納電動元件，而電動元件係由定子及 轉子所構成，該轉子係以可藉由該定子之磁場轉動之方式 5 321798 201035448 裝；内❿且固疋在兼作回轉應縮元件驅動用曲柄轴之 回轉轴，其特徵為具備：喷出孔，設於與轉子之端面相對 2位置’且將來自__元件之_冷媒料至密閉 谷器内；及冷媒流路，將自該喷出孔所嘴出之壓縮冷媒， 經過從轉子之端面朝回㈣縮元件側突出之定子之線圈端 部（⑺U end)所包圍之空間，並通過轉子與定子之氣隙 (町_空間，而導引至電動元件的回轉元件相反 ^ ’此冷媒流路的回轉塵縮元件相反側之出口係與密閉容 =内壁面相對向’並且密閉容器之内壁面與電動元件間 之空間體積’係設為回轉麼縮元件與電動元件間之空間體 積之1.5倍以上、；15倍以下。 甲請專利範圍第2項之發明係—種密閉型回轉屡縮 機，係在㈣容器内下部收納回轉壓縮元件，並於此回轉 壓縮元件之上方收納電動元件，而電動元件係由定子及轉 =斤構成者，該轉子係以可藉由該定子之磁場轉動之方式 、於内部’而且固定在兼作_壓縮元件驅動用曲柄轴 之回轉轴，其特徵為具備1出孔，設於 料^位置，心絲自__元件之壓縮冷媒 密閉谷裔内，及冷媒流路，將自該喷出孔所嘴出之廢縮冷 媒，經過從轉子之端面朝回轉壓縮元件側突出之定子之: 3销包圍之空間’並通過轉子與定子之氣隙空間，而 = 動元件㈣髓縮元件相反側；此冷媒流路的回 轉Κ牛相反側之出口係與密閉容器之内壁面相對向。 申清專利範圍第3項之發明，係在上述中請專利範圍 321798 6 201035448 第2項之發明中，將密閉容器内之壓縮冷媒引導至密閉容 器外之噴出管之一方開口，係指向於在密閉容器内呈環狀 之冷媒流路之内側。 申請專利範圍第4項之發明，係在上述申請專利範圍 第3項之發明中，從轉子的回轉壓縮元件相反側之端面至 密閉容器之内壁面之回轉軸方向之距離係設定為25mm以 上。 [發明之功效] 依據本發明，由於係在密閉容器内下部收納回轉壓縮 元件，並於此回轉壓縮元件之上方收納電動元件，而此電 動元件係由定子及轉子所構成，該轉子係以可藉由該定子 之磁場轉動之方式插裝於内，而且固定在兼作回轉壓縮元 件驅動用曲柄軸之回轉軸的密閉型回轉壓縮機中具備：噴 出孔，設於與轉子之端面相對向之位置，用以將來自回轉 壓縮元件之壓縮冷媒喷出至密閉容器内；及冷媒流路，將 Q 自該喷出孔所喷出之壓縮冷媒，經過從轉子之端面朝回轉 壓縮元件侧突出之定子之線圈端部（coil end)所包圍之空 間，並通過轉子與定子之氣隙（air gap)空間，而引導至電 動元件的回轉壓縮元件相反側。因此，可使從噴出孔所喷 出之壓縮冷媒，碰撞到轉動之轉子之端面而被攪拌。藉此， 即可促進由定子之線圈端部所包圍之空間内之油分離。 此外，由於經過上述定子之線圈端部所包圍之空間之 壓縮冷媒，會在通過定子與轉子之氣隙空間的過程中，被 定子與轉動之轉子之壁面所扭轉，因此可藉此更進一步使 7 321798 201035448 油分離。 再者，由於此冷媒流路的回轉壓縮元件相反側之出口 係與密閉容器之内壁面相對向，因此通過冷媒流路而到達 電動元件的回轉壓縮元件相反側之冷媒會與密閉容器之内 壁面碰撞，且擴散於電動元件的回轉壓縮元件相反侧之空 間之後，喷出至密閉容器外。如此，藉由在電動元件的回 轉壓縮元件相反側之空間之擴散可進一步使油分離。藉 此，即可有效率地進行油分離，而大幅降低油喷出至機外 之情形。 尤其，藉由將密閉容器之内壁面與電動元件間之空間 體積，設定為回轉壓縮元件與電動元件間之空間體積之1. 5 倍以上、15倍以下，可確保密閉容器之内壁面與電動元件 間之空間體積，而不會擴大密閉容器之上下尺寸，且可確 保最終段之冷媒擴散所形成之油分離空間，而能提升油分 離效果。 由於申請專利範圍第3項之發明，係在上述發明中， 將密閉容器内之壓縮冷媒導引至密閉容器外之喷出管之一 方開口係指向於在密閉容器内作成環狀之冷媒流路之内 側，因此經過冷媒流路而到達電動元件的回轉壓縮元件相 反侧之壓縮冷媒直達喷出管之情形得以抑制。藉此，即可 提升油分離性能。 由於申請專利範圍第4項之發明係在申請專利範圍第 3項之發明中，從轉子的回轉壓縮元件相反侧之端面至密 閉容器之内壁面之回轉軸方向之距離係設定為25mm以 321798 201035448 上，因此可充分確保電動元件的回轉壓縮元件相反側之油 分離空間，而可更進一步提升油分離性鸫。 【實施方式】 以下根據圖式詳細說明本發明之密閉型回轉壓縮機之 實施形態。第1圖係為概略性顯示具備第1及第2回轉壓 縮元件之内部高麼型迴轉壓縮機（rotary compressor)l之 縱剖侧面作為應用本發明之密閉型回轉壓縮機之一實施 例。 Θ 本實施例之迴轉壓縮機1係為在由鋼板所構成之縱型 圓筒狀之密閉容器2之内部空間之下部收納由第1及第2 回轉壓縮元件10、20所構成之回轉壓縮機構部3，且於密 閉容器2之内部空間之上方收納電動元件4而成之2壓縮 缸之密閉型回轉壓縮機。 密閉容器2係由用以收納電動元件4與第1及第2回 轉壓縮元件10、20(回轉壓縮機構部3)之容器本體2A、將 ❹該容器本體2A之上部開口封閉之大致碗狀之端蓋（end cap) (蓋體）2B、及將容器本體2A之下部開口封閉之底（bottom) 部2C所構成。在此端蓋2B之上面係形成有未圖示之圓形 安裝孔，而於此安裝孔安裝有用以供給電力至位於密閉容 器2内之上方之電動元件4之端子（terminal)(省略配線） 35。再者，在此端蓋2B之中心部係安裝有後述之冷媒喷出 管9 〇 該密閉容器2内之底部之空間係作為油槽，在此儲存 有用以使第1及第2回轉壓縮元件10、20或回轉軸8等滑 9 321798 201035448 動部潤滑之油。此外，在底部2C：之外側底部係設有安裝用 基座70。 回轉壓縮機構部3係由第1回轉壓縮元件10、第2回 轉慶縮元件34、及由兩回轉盧縮元件1〇、2〇所挟持之中 間隔板30所構成。本實施例之回轉壓縮機構部3，係隔著 中間隔板3G而在下侧設有第}回轉壓縮元件1()，且於上 側設有第2回轉壓縮元件2〇。第！回轉壓縮元件1〇與第2 回轉壓縮元件20係由··配置於中間隔板％之上下之塵縮 缸12、22 ;嵌合於在壓縮缸12、22内具有⑽度相位差 而設於回轉軸8之偏心部13、23，並於各壓縮缸12、22 内分別偏心轉動之滾柱14、24 ;與各滾柱14、％抵接， 而將各壓縮红12、22内分別劃分為低壓室側與高壓室側之 未圖示葉片；及將壓餘12之下側之開口面及壓縮缸U 之上側之開口面封閉，兼用作回轉轴8之轴承，且 撐構件之下敎撐構件15及±部域構件25所構成; A在上下壓縮缸12、22係形成有與各壓縮紅12、22内 权麗縮室分麟狀吸人料16、26。此外， 電動元件4相反側(下側)及上部支撐㈣ 兀4側（上側）’係分別設有嘴出消音器η、2?。 ^於下部支撐構件15之下側之噴㈣音器17，係夢 下蓋(CaP)17A覆蓋下部支撲構件15之下： 15 i下盖17 A在中心具有供回轉軸8及下部支撐構件 貫通之孔。此嘴出消音器17與壓縮缸 内係错由喷出通路19來連接，且構成為可藉由設於該 321798 10 201035448 =出通路19之嘴出消音器】7側之開口之噴出間挪之開 閉而使喷出消音器17内與I縮缸12内01縮幻2内之高 壓室側）連通。 ❹ 〇 此外位於上部支撐構件25之上側之嗔出消音哭27， _由大致碗狀的上蓋“）27Α覆蓋上部支樓構件^之 形成’而該上蓋27Α係在中心具有供回轉轴8及上 1 „牙構件25之上部軸承25Α貫通之孔。此外，此喷出消 / 27與麼縮紅22内係藉由嘴出通路29來連接，且構成 =藉由設於該嘴出通路29之嘴出消音器27側= ==之開閉而使嘴出消音器27内與壓縮缸_ 縮虹22内之南壓室側）連通。 上述噴出消音器17鱼嘻出、、古立— 撑構件15、下_㈣、中間隔精由將下部支 部支_25朝轴心方向J=、4=22及上 路而連通。 下方向）貝通之未圖示連通 圖所示’在形成噴出消音器27之上蓋27A，係 至 =二將來自各嘯縮元件1。，之壓縮冷媒嘴出 至达閉谷斋12内之複數個噴出 、、 蓋27朝轴心方向（上下方向^28。喷出孔28係為將上 出孔28均為餘設置於上^2?通^圓形孔，且設成任一嘴 並與電動元件4之轉子回轉軸8附近’ 介Pdi^面（下端面）相對向之位置。 第二 =成為指向於轉子7之端*(下端面)。 第2圖所不之本實施例 之流向係左迴轉，並考慮到出孔:益27内之冷媒氣體 貨出孔28的孔徑、數量及配 321798 201035448 置，俾有效吸收（降低）冷媒氣體在噴出消音器27内之脈 動。第2圖所示之本實施例之噴出孔28，係由：内徑⑺咖 之噴出孔28a ;以回轉軸8為中心而與該喷出孔咖大致 對稱方式配置之内徑8匪之喷出孔28b ;及内徑6咖之3 個嗔出孔28c所構成。此外，在喷出孔施係設有相對向 但未圖示之喷出用閥。另外，第2圖所示之49係為形成於 上蓋27A之溝。 另外，第1圖所示之75係為用以將上部支撐構件託、 上壓縮缸22、中間隔板30、下壓縮缸12、下部支撐構件 15予以一體化固定的螺栓（13〇11：)。 另一方面，前述之電動元件4係由沿著密閉容器2之 上部空間之内周面熔接固定成環狀之定子（stat〇r)5、及以 可藉由此定子5之磁場轉動之方式插設於内部之轉子 (rotor)7所構成。 疋子5係由：由大致環狀之電磁鋼板（矽鋼板）所構成 之定子用鐵板疊層所構成之定子鐵心36 ;及繞設於該定子 鐵心36之定子線圈（stat〇r c〇u)37所構成。此定子線圈 37之線圈端部37E係以從轉子7之端面（下端面）朝回轉壓 縮機構部3側（下側）突出之方式設置’藉此，在轉子7之 端面（下端面）之回轉壓縮機構部3側（下侧），形成以線圈 端部37E將周圍包圍的空間S1。此外，在定子鐵心祁之 外周侧之面’係沿著容器本體Μ之内周面在軸心方向形成 有複數條縱溝39，而此縱溝39係設為後述之回油用的通 路。 321798 12 201035448 轉子7係由：由電磁鋼板（矽鋼板）所構成，且埋設有 永久磁鐵（未圖示），而上下端面為平坦之圓筒狀轉子鐵心 38;及以壓入狀態插入固定於貫穿形成於該轉子鐵心38之 中心孔内的回轉軸8所構成。此回轉轴8係兼作前述第1 及第2回轉壓縮元件10' 20之驅動用曲柄軸，且通過密閉 容器之中心朝垂直方向（上下方向）延伸，而回轉軸8之上 端係位於轉子鐵心38之上端。此外，回轉轴8之下端係位 於回轉壓縮機構部3之下側之油槽，且浸潰於儲存於該油 槽内之油。在此回轉軸8之下部（下端）係設有用以吸取油 槽内之油的油泵（pump)50。 此外，在轉子7(轉子鐵心38)之上下端面係設有重量 平衡調整用的平衡器（balancer)42、43，其係用以抑制因 為前述第1及第2回轉壓縮元件10、20之偏心部13、23 或滾柱14、24之重量偏移所導致之回轉軸8偏心回轉而產 生之振動，以使回轉穩定化，而在此平衡器42之上面係設 ❹有平衡器之擋止板45。再者，配置於此等轉子鐵心38之 端面之上述構件（平衡器42、43及擋止板45)係藉由鉚釘 (rivet)47而固定於轉子鐵心38。 再者，從轉子7之回轉壓縮機構部3相反侧之端面至 密閉容器2之内壁面之回轉轴8方向之距離D，亦即，在 本實施例中，從設於轉子7之上端面之擋止板45之上表面 至與其上方向對應之密閉容器2之端蓋2B之内壁面之距離 D ’係設為2 5 πππ以上。 然而，在電動元件4係形成有用以將從前述之喷出孔 13 321798 201035448 、28b及28c)喷出至密閉容器2内之[Technical Field] The present invention relates to a hermetic rotary compressor including an electric component and a rotary compression element in a hermetic container. More particularly, the present invention relates to a rotary compression element housed in a lower portion of a sealed container, and a motor element is housed above the rotary compression element, and the motor element is composed of a stator and a rotor, and the rotor is rotated by a magnetic field of the stator. The method is inserted into the inside, and is fixed to a rotary shaft that also serves as a crank shaft for driving the rotary compression element. [Prior Art] Conventionally, such a hermetic rotary compressor is composed of a rotary compression element housed in a lower portion of a sealed container and an electric element housed in an upper portion of the sealed container. The electric component is composed of a stator and a rotor which are mounted in a ring shape along an inner circumferential surface of the upper space of the hermetic container, and the rotor is inserted into the inner surface of the stator by the magnetic field of the stator, and It is fixed to a rotary shaft that also serves as a crankshaft for driving a rotary compression element. The rotary compression element is a cylinder, is fitted to a roller formed in an eccentric portion of the rotary shaft and eccentrically rotated in the compression cylinder, and abuts against the compression cylinder and divides the compression cylinder into a low pressure chamber. The side is formed by a vane on the side of the high pressure chamber. Further, in the bottom of the sealed container, an oil for lubricating the sliding portion such as the rotary compression element or the rotary shaft is stored. Further, when the stator of the stator of the electric element is energized to generate a returning magnetic field, the inner rotor is rotated by the magnetic field. By this rotation, the roller fitted to the eccentric portion of the rotary shaft is eccentrically rotated in the compression cylinder. Thereby, the low-pressure refrigerant is sucked into the low-pressure chamber side in the compression cylinder, and is compressed by the action of the rollers and the blades by 321798 201035448. The refrigerant gas compressed in the compression cylinder to become high temperature and high pressure is discharged from the high pressure chamber side to the discharge muffler via the discharge port. The refrigerant gas ejected to the discharge muffler is ejected into the sealed container from a discharge hole provided to communicate the discharge muffler with the inside of the sealed container and directed to the upper motor element. At this time, the oil supplied to the reversing compression element is mist-mixed in the refrigerant gas, and the oil is also ejected together with the refrigerant gas into the sealed container. The refrigerant gas system that is discharged into the sealed container is designed to be ejected from the discharge pipe provided on the upper side of the electric element to the outside through a refrigerant passage formed in the electric element (see, for example, Patent Document 1). [Problem to be Solved by the Invention] However, in such a conventional hermetic rotary compressor, it is not possible to sufficiently separate the refrigerant gas from the oil in the sealed container, and to eject from the discharge pipe to the discharge pipe. The amount of oil outside is large, and the oil is degraded due to oil flowing out to the external circuit or the problem of insufficient oil supply to the sliding portion. The present invention has been made in order to solve the problems of the prior art, and its object is to promote oil separation in a closed container and to reduce oil discharge to the outside of the compressor. [Means for Solving the Problem] The invention of claim 1 is a hermetic rotary compressor in which a rotary compression element is housed in a lower portion of a hermetic container, and an electric component is housed above the rotary compression element, and the electric component It is composed of a stator and a rotor which are mounted by means of the magnetic field of the stator 5 321798 201035448; the inner shaft is fixed and fixed to a rotary shaft which also serves as a crank shaft for driving the rotary contracting element, and is characterized by : the discharge hole is disposed at a position 2 opposite to the end surface of the rotor and the refrigerant from the __ component is introduced into the closed valley; and the refrigerant flow path is compressed from the nozzle of the discharge hole. The space enclosed by the coil end ((7) U end) of the stator protruding from the end face of the rotor toward the back (four) contracting element side, and passing through the air gap of the rotor and the stator (the opposite of the rotary element of the electric component) ^ 'The outlet of the opposite side of the rotary dust-reducing element of the refrigerant flow path is closed to the closed volume = the inner wall surface is opposite ' and the space volume between the inner wall surface of the closed container and the electric component is set to revolve. The space volume between the component and the electric component is 1.5 times or more and 15 times or less. The invention of the second aspect of the patent scope is a closed type rotary retracting machine, which accommodates the rotary compression element in the lower part of the (4) container, and The motor element is housed above the rotary compression element, and the motor element is composed of a stator and a rotor. The rotor is internally fixed by the magnetic field of the stator and is also fixed for driving the compression element. The rotary shaft of the crankshaft is characterized in that it has one outlet hole and is disposed at the material position, and the core wire is sealed from the compressed refrigerant in the __ component, and the refrigerant flow path is discharged from the discharge hole. The refrigerant shrinks through the stator protruding from the end face of the rotor toward the side of the rotary compression element: 3 the space surrounded by the pin 'and passes through the air gap space between the rotor and the stator, and the opposite side of the moving element (4) the reaming element; this refrigerant flow path The outlet on the opposite side of the rotary yak is opposite to the inner wall surface of the closed container. The invention of the third paragraph of the patent scope of the patent is in the invention of the above-mentioned patent scope 321798 6 201035448 item 2, which will be sealed. The inside of the discharge pipe which is guided by the compressed refrigerant to the outside of the closed container is directed to the inside of the refrigerant flow path which is annular in the closed container. The invention of claim 4 is the third of the above-mentioned patent application. In the invention, the distance from the end surface on the opposite side of the rotary compression element of the rotor to the direction of the rotation axis of the inner wall surface of the sealed container is set to 25 mm or more. [Effect of the Invention] According to the present invention, it is housed in the lower portion of the closed container. Rotating the compression element and accommodating the electric component above the rotary compression element, and the electric component is composed of a stator and a rotor, and the rotor is inserted in the magnetic field of the stator, and is fixed in the A hermetic rotary compressor which also serves as a rotary shaft for a crankshaft for driving a rotary compression element includes a discharge hole provided at a position facing the end surface of the rotor for discharging compressed refrigerant from the rotary compression element into the closed container And the refrigerant flow path, the compressed refrigerant that Q is ejected from the ejection hole passes through the end face of the rotor toward the side of the rotary compression element A rotation of the coil end of the stator (coil end) of the enclosed space, and through the air gap of the stator and the rotor of the (air gap) space, is guided to the electromotive element opposite to the compression element side. Therefore, the compressed refrigerant discharged from the discharge holes can be agitated by colliding with the end faces of the rotating rotor. Thereby, oil separation in the space surrounded by the coil ends of the stator can be promoted. In addition, since the compressed refrigerant passing through the space surrounded by the coil end portion of the stator is twisted by the wall surface of the stator and the rotating rotor during passage through the air gap space between the stator and the rotor, it is possible to further 7 321798 201035448 Oil separation. Further, since the outlet on the opposite side of the rotary compression element of the refrigerant flow path faces the inner wall surface of the hermetic container, the refrigerant on the opposite side of the rotary compression element that reaches the electric element through the refrigerant flow path and the inner wall surface of the closed container After colliding and diffusing into the space on the opposite side of the rotary compression element of the electric component, it is discharged to the outside of the sealed container. Thus, the oil can be further separated by diffusion of the space on the opposite side of the rotary element of the electric element. As a result, oil separation can be efficiently performed, and the situation in which the oil is ejected out of the machine is greatly reduced. In particular, the space volume between the inner wall surface of the hermetic container and the electric component is set to 1.5 times or more and 15 times or less the space volume between the rotary compression element and the electric element, thereby ensuring the inner wall surface of the sealed container and the electric motor. The volume of space between the components does not enlarge the upper and lower dimensions of the closed container, and ensures the oil separation space formed by the diffusion of the final section of the refrigerant, thereby improving the oil separation effect. According to the invention of claim 3, in the above invention, the opening of the discharge pipe that guides the compressed refrigerant in the sealed container to the outside of the sealed container is directed to the refrigerant flow path formed in the closed space in the closed container. On the inner side, it is suppressed that the compressed refrigerant that reaches the opposite side of the rotary compression element of the electric component passes through the refrigerant flow path to the discharge pipe. This will improve oil separation performance. The invention of claim 4 is in the invention of claim 3, wherein the distance from the end face of the opposite side of the rotary compression element of the rotor to the direction of the axis of rotation of the inner wall surface of the closed container is set to 25 mm to 321798 201035448 Therefore, the oil separation space on the opposite side of the rotary compression element of the electric component can be sufficiently ensured, and the oil separation property can be further improved. [Embodiment] Hereinafter, an embodiment of a hermetic rotary compressor according to the present invention will be described in detail based on the drawings. Fig. 1 is a view schematically showing an embodiment of a hermetic rotary compressor to which the present invention is applied, which schematically shows a longitudinal section of an internal rotary compressor 1 having first and second rotary compression elements. The rotary compressor 1 of the present embodiment is a rotary compression mechanism including the first and second rotary compression elements 10 and 20 in a lower portion of the internal space of the vertical cylindrical sealed container 2 formed of a steel plate. The unit 3 is a sealed type rotary compressor in which two compression cylinders are formed by accommodating the electric component 4 above the internal space of the hermetic container 2. The hermetic container 2 is a container body 2A for accommodating the motor element 4 and the first and second rotary compression elements 10 and 20 (rotation compression mechanism unit 3), and a substantially bowl-shaped opening that closes the upper portion of the container body 2A. An end cap (lid) 2B and a bottom portion 2C that closes the opening of the lower portion of the container body 2A are formed. A circular mounting hole (not shown) is formed on the upper surface of the end cover 2B, and the mounting hole is provided with a terminal for supplying electric power to the electric component 4 located above the sealed container 2 (omission of wiring) 35. Further, a refrigerant discharge pipe 9 to be described later is attached to a center portion of the end cover 2B, and a space at the bottom of the sealed container 2 is used as an oil groove, and the first and second rotary compression elements 10 are stored therein. , 20 or rotary shaft 8 and so on 9 321798 201035448 moving parts lubrication oil. Further, a mounting base 70 is provided on the bottom portion of the bottom portion 2C: the outer side. The rotary compression mechanism unit 3 is composed of a first rotary compression element 10, a second return expansion and contraction element 34, and a partition plate 30 sandwiched between the two rotary contraction elements 1A and 2B. In the rotary compression mechanism unit 3 of the present embodiment, the first rotary compression element 1 () is provided on the lower side via the intermediate partition 3G, and the second rotary compression element 2 is provided on the upper side. The first! The rotary compression element 1A and the second rotary compression element 20 are arranged by the dust reduction cylinders 12 and 22 disposed above the intermediate partition %; and are fitted to the compression cylinders 12 and 22 with a phase difference of (10) degrees. The eccentric portions 13 and 23 of the rotary shaft 8 are eccentrically rotated by the rollers 14 and 24 in the respective compression cylinders 12 and 22; the rollers 14 and % are abutted, and the respective compression reds 12 and 22 are respectively divided. The blade is not shown in the low pressure chamber side and the high pressure chamber side; and the opening surface on the lower side of the pressure reserve 12 and the opening surface on the upper side of the compression cylinder U are closed, and also serves as a bearing of the rotary shaft 8 and the lower member of the support member The support member 15 and the ± partial member 25 are formed; A is formed in the upper and lower compression cylinders 12 and 22, and the compressed red, 12, and 22 are formed in the respective compressed red portions 12 and 22. Further, the opposite sides (lower side) and the upper support (4) 兀4 side (upper side) of the electric element 4 are provided with nozzle dampers η, 2, respectively. The sprayer (four) 17 on the lower side of the lower support member 15 and the lower cover (CaP) 17A cover the lower flap member 15: 15 i The lower cover 17 A has a rotary shaft 8 and a lower support member at the center. Through the hole. The nozzle muffler 17 and the compression cylinder are connected by a discharge passage 19, and are configured to be ejected by an opening provided on the side of the 311798 10 201035448 = outlet 19 Opening and closing, the inside of the discharge muffler 17 is communicated with the high pressure chamber side in the depression 12 of the I cylinder 12. Further, the 位于 消 消 哭 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 27 1 „The hole in the upper part of the tooth member 25 that passes through the bearing 25Α. Further, the discharge/27 and the red reduction 22 are connected by the nozzle outlet passage 29, and the configuration is made by opening and closing the nozzle muffler 27 side === provided on the nozzle outlet passage 29. The inside of the nozzle muffler 27 is in communication with the compression chamber _ the south pressure chamber side in the reduction rainbow 22). The above-mentioned discharge muffler 17 is connected to the fish, the Guli-support member 15, the lower _(four), and the middle partition by the lower branch branch _25 toward the axial direction J=, 4=22 and the upper path. In the downward direction, the connection between the Betons and the figure is shown in the figure. The upper cover 27A is formed to form the discharge muffler 27, and the second to the second reduction element 1 is obtained. The compressed refrigerant mouth is discharged to a plurality of sprays in the closed valley, and the cover 27 is oriented in the axial direction (up and down direction ^28. The discharge hole 28 is such that the upper and lower holes 28 are all disposed on the upper ^2 A circular hole is provided and is placed in any position with respect to the position of the Pdi^ surface (lower end surface) near the rotor rotating shaft 8 of the motor element 4. The second = becomes the end pointing to the rotor 7* ( The lower end face). The flow direction of the embodiment of Fig. 2 is left-handed, and the hole diameter, the number of the refrigerant gas outlet holes 28 in the hole 27, and the ratio of the 321798 201035448 are effectively taken into consideration. The refrigerant gas is pulsated in the discharge muffler 27. The discharge hole 28 of the present embodiment shown in Fig. 2 is composed of an inner diameter (7) discharge hole 28a; the discharge shaft 8 is centered on the rotary shaft 8 The coffee machine is arranged in a substantially symmetrical manner with a discharge hole 28b having an inner diameter of 8 inches, and three discharge holes 28c having an inner diameter of 6 coffee. Further, a discharge hole (not shown) is provided in the discharge hole. In addition, the 49 shown in Fig. 2 is a groove formed in the upper cover 27A. In addition, the 75 series shown in Fig. 1 is for the upper support structure. The bolts (13〇11:) of the upper and lower compression cylinders 22, the intermediate partition plate 30, the lower compression cylinder 12, and the lower support member 15 are integrally fixed. On the other hand, the aforementioned electric component 4 is along the closed container 2 The inner surface of the upper space is welded and fixed to a ring-shaped stator (5), and a rotor 7 which is inserted into the inner portion by the magnetic field of the stator 5. The stator core 36 composed of a stack of iron plates for stators composed of a substantially annular electromagnetic steel plate (矽 steel plate); and a stator coil (stat rc〇u) 37 wound around the stator core 36 The coil end portion 37E of the stator coil 37 is provided so as to protrude from the end surface (lower end surface) of the rotor 7 toward the side of the rotary compression mechanism portion 3 (lower side), whereby the end surface (lower end surface) of the rotor 7 is formed. On the side of the rotary compression mechanism unit 3 (lower side), a space S1 surrounded by the coil end portion 37E is formed. Further, the surface on the outer peripheral side of the stator core ' is along the inner peripheral surface of the container body 在 at the axial center. A plurality of longitudinal grooves 39 are formed in the direction, and the longitudinal grooves 39 are set to be rear 321798 12 201035448 The rotor 7 is composed of an electromagnetic steel plate (矽 steel plate) and is provided with a permanent magnet (not shown), and the upper and lower end faces are flat cylindrical rotor cores 38; The rotary shaft 8 is inserted and fixed to the rotary shaft 8 formed in the center hole of the rotor core 38. The rotary shaft 8 also serves as a crank shaft for driving the first and second rotary compression elements 10'20, and The center of the closed container extends in the vertical direction (up and down direction), and the upper end of the rotary shaft 8 is located at the upper end of the rotor core 38. Further, the lower end of the rotary shaft 8 is located in the oil groove on the lower side of the rotary compression mechanism portion 3, and is immersed. Broken into the oil stored in the oil tank. At the lower portion (lower end) of the rotary shaft 8, a pump 50 for sucking oil in the oil groove is provided. Further, balancers 42 and 43 for adjusting the weight balance are provided on the lower end surface of the rotor 7 (the rotor core 38) for suppressing the eccentricity of the first and second rotary compression elements 10 and 20. The vibration generated by the eccentric rotation of the rotary shaft 8 caused by the weight shift of the portions 13, 23 or the rollers 14, 24 is stabilized, and the balance of the balancer 42 is provided with the balancer Board 45. Further, the above-described members (balancers 42, 43 and stopper plates 45) disposed on the end faces of the rotor cores 38 are fixed to the rotor core 38 by rivets 47. Further, the distance D from the end surface on the opposite side of the rotary compression mechanism portion 3 of the rotor 7 to the direction of the rotary shaft 8 of the inner wall surface of the hermetic container 2, that is, in the present embodiment, is provided from the upper end surface of the rotor 7. The distance D' between the upper surface of the stopper plate 45 and the inner wall surface of the end cap 2B of the hermetic container 2 corresponding to the upper direction is set to be 2 5 πππ or more. However, the electric component 4 is formed to be ejected from the aforementioned ejection holes 13 321798 201035448, 28b, and 28c) into the hermetic container 2.
28(亦即喷出孔28a、28b及28幻喷出至 轉壓縮機構部3與電動元件4間之空間 之端面（下端面）朝回轉壓縮機構部3側（下側）突 出之前述定子5之線圈端部所包圍、而該空間％係為轉子 7與定子5間之氣隙。 亦即，從喷出孔28喷出至密閉容器2内之回㈣縮機 構部3與電動元件4之間之空間A的冷媒，係經過從轉子 7之端面朝回轉壓縮機構部3側（下側）突出之定 圈:部所包圍之空間S卜並通過轉子7與定子5之環2 宇:間S2從其上端開口（亦即冷媒流路之出口）噴出至密 1谷器2之内壁面與電動元件間之空間（亦即密閉容器2内 之電動元件4的回轉壓縮機構部3相反側之空間）B。此冷 、L路的回轉壓Ifg機構部3相反側之出口（亦即氣隙之空 間S2之上端開口）係與密閉容器2之内壁面相對向。 另一方面，在密閉容器2之容器本體2A之側面，係於 與各壓縮幻2、22之吸人通路16、26對應之位置分別溶 接固定有套筒60。此等套筒60與61係上下鄰接。 再者’在套筒60内係插入連接有用以將冷媒氣體導入 於下壓縮缸12之冷媒導入管4〇，而此冷媒導入管4〇之一 端係與下麗縮缸12之吸入通路16連通。冷媒導入管仙之 下端係在儲存器（accumulator)65内之上部開口。 在套筒61内係插入連接有用以將冷媒氣體導入於上 321798 14 201035448 壓縮缸22之冷媒導入管41，而此冷媒導入管41之一端係 與上壓縮缸22之吸入通路26連通。此冷媒導入管41之另 一端係與前述冷媒導入管40同樣在儲存器65内之上部開 π ° 上述儲存器65係用以進行吸入冷媒之氣液分離之槽 (tank)，其係透過托架（bracket)67而安裝於密閉容器2 之容器本體2A之上部側面。再者，在儲存器65係從底部 插入有冷媒導入管40及冷媒導入管41，且另一端開口分 Γ) 別位於該儲存器65内之上方。此外，在儲存器65内之上 端部係插入有冷媒配管68之一端。 另一方面，在密閉容器2之端蓋2B係於與回轉軸8相 對應之位置之大致中心部形成有圓形孔62。在此孔62内 係插入連接有前述之冷媒喷出管9，而此冷媒喷出管9之 一端係在密閉容器2内之上部開口。該冷媒喷出管9之一 端之開口，係指向於前述之環狀冷媒流路（亦即定子5與轉 Q 子7之間之氣隙之空間S2)之内侧。 尤其是，在本發明中，將密閉容器2之内壁面與電動 元件4間之空間（電動元件4的回轉壓縮機構部3相反側之 空間）B之體積設為較回轉壓縮機構部3與電動元件4間之 空間A之體積大時，為了提升油分離性能，乃以電動元件 上之空間B之體積成為電動元件下之空間A之體積之1. 5 倍以上、15倍以下之方式考慮密閉容器2内之電動元件4 之高度尺寸而配置者。 茲以上述構成說明本實施例之迴轉壓縮機1之動作。 15 321798 201035448 當經由端子35及未圖示之配線對電動元件4之定子線圈 37通電時，電動元件4即啟動，而使轉子7回轉。藉由此 回轉，嵌合於與回轉軸8 —體設置之偏心部13、23的滾柱 14、24即在各壓縮缸12、22内偏心回轉。 藉此，低壓冷媒即從迴轉壓縮機1之冷媒配管68流入 至儲存器65内。流入於儲存器65内之低壓冷媒，係在此 經氣液分離之後，只有冷媒氣體進入在該儲存器65内開口 之各冷媒導入管40、41内。進入冷媒導入管40之低壓冷 媒氣體係經過吸入通路16而吸入至第1回轉壓縮元件10 之壓縮缸12之低壓室側。 吸入至冷媒導入管40之低壓室側之冷媒氣體，係藉由 滾柱14與未圖示之葉片之動作而壓縮，成為高溫高壓之冷 媒氣體，從壓縮缸12之高壓室側通過送出通路19而喷出 至喷出消音器17。喷出至喷出消音器17之冷媒氣體，係 經過未圖示之連通路而喷出至喷出消音器27,而與經第2 回轉壓縮元件22壓縮之冷媒氣體合流。 另一方面，進入冷媒導入管41之低壓冷媒氣體係經過 吸入通路26而吸入於第2回轉壓縮元件20之上壓縮缸22 之低壓室側。吸入至上壓縮缸22之低壓室侧之冷媒氣體係 藉由滾柱24與未圖示之葉片之動作而壓縮，成為高溫高壓 之冷媒氣體，從上壓縮缸22之高壓室側通過喷出通路29 而喷出至喷出消音器27,而與來自上述第1回轉壓縮元件 12之冷媒氣體合流。 再者，經合流之冷媒氣體係從貫通形成於上蓋27A之 16 321798 4 201035448 噴出孔28喷出至密閉容器12内之回轉壓縮機構部3與電 動元件4之間之工間a。此時，供給至回轉壓縮機構部3 之滑動部等之油係成為霧狀狀在冷媒氣體中 ，且油亦與 •冷媒氣體—同從各噴出孔28噴出。另外，第丨圖所示箭頭 係顯示與壓縮冷媒-同嘴出至密閉容器2内之油的流向。 在此’由於喷出孔28係設於與轉子7之轉子鐵心38 之下端面相對向之位置’因此從喷出孔28噴出之壓縮冷 〇媒會與轉動之轉子7之轉子鐵心38之下端面碰撞，且經 由授拌而擴散至由定子5之定子線圈37之線圈端部3 包圍之空間S1。 在此，使用第6圖說明設於上蓋27之習知之嘴出g 、在第6圖中’ 128a係為内徑i〇mm之喷出孔、12此^ 為内控8觸之喷出孔、128c係為内徑6随之喷出孔，任_ 者均係考慮W料！！ 27狀冷縣社脈動吸收幻 Ο =配置5。然而，如第6圖所示習知之喷出孔128均設方 ^離上蓋27之中心的外周緣附近，且與電動元件4之轉^ /、定子5間之氣隙之空間S2相對向的位置。亦即，則 各;㈣容器2内之壓縮冷媒，係直接流财 28所‘向之轉子7與定子5間之氣隙空間S2。 動除該㈣空間S2外’尚有用以將冷媒導入於電 如:的回轉壓職構部3相反側之其他冷媒流路，例 轉壓m7娜"方向（上下方向）貫通，而形成將回 内辟面與電動元件4間之㈣A與密閉容器2之 "/、電動70件4之間空間6連通之冷媒通路，且將從 321798 17 201035448 喷出孔所喷出之壓縮冷媒引導至此冷媒通路，或引導至該 冷媒通路與氣隙空間S2者。 如此，在習知之構成中，從喷出孔所喷出之壓縮冷媒， 在回轉壓縮機構部3與電動元件4之間之空間A皆幾乎不 會進行油分離，而是均直接流通於用以導引至電動元件4 的回轉壓縮機構部3相反側之冷媒流路。 相對於此，本發明則是藉由將喷出孔28與轉子7之轉 子鐵心38之端面（下端面）相對向設置，即可使從喷出孔 28喷出至密閉容器2内之壓縮冷媒，分別與喷出孔28所 指向之轉子7之轉子鐵心38之下端面碰撞。藉此，即可使 油在密閉容器2内之回轉壓縮機構部3與電動元件4間之 空間A分離。尤其是，藉由使來自喷出孔28之壓縮冷媒與 轉動之轉子7之轉子鐵心38之下端面碰撞，即可藉由轉子 鐵心38之轉動來攪拌冷媒，而使其廣泛擴散到由定子5之 定子線圈37之線圈端部37E所包圍之整個空間S1。藉此， 即可促進由定子5之線圈端部37E所包圍之空間S1内之油 分離。 之後，經過此空間S1之冷媒，係通過定子5與轉子7 之氣隙空間S2。由於此氣隙空間S2係些微形成於定子5 與轉子7間之間隙，並且有位於該些微間隙之内側之轉子 7轉動，因此通過空間S2之冷媒，會受到轉子7之轉動之 影響，一面朝轉子7之轉動方向扭轉，一面以上升於該空 間S2之方式流通。藉此，即可在通過該空間S2之過程中 使油更進一步從冷媒分離。 18 321798 201035448 通過定子5與轉子7之氣隙空間S2而經進一步油分離 之冷媒，係從該空間S2之出口噴出至電動元件4的回轉壓 縮機構部3相反側之空間B。此時，由於此出口係與密閉 容器2之内壁面相對向而設置，因此從該出口所喷出之冷 媒會與密閉容器2之内壁面碰撞而擴散於空間B。如此， 可藉由在電動元件4的回轉壓縮機構部3相反側之空間B 的擴散使油更進一步分離。 尤其是，用以將擴散於密閉容器2内之空間B之壓縮 f) 冷媒引導至密閉容器2外之該冷媒喷出管9之一端之開 口，係指向於在密閉容器2内呈環狀之冷媒流路（亦即前述 之氣隙空間S2)之内側。因此可抑制經過冷媒流路到達電 動元件4的回轉壓縮機構部3相反側之壓縮冷媒直接到達 冷媒喷出管9。藉此，即可提升油分離性能。 再者，如前所述，從設於轉子7之上端面之擋止板45 之上表面至與其上方向對應之密閉容器2之端蓋2B之内壁 ❹面之距離D係設為25mm以上，因此可充分確保電動元件4 的回轉壓縮機構部3相反側之油分離空間，而更進一步提 升油分離性能。 尤其是，電動元件4的回轉壓縮機構部3相反側之空 間B之體積，係設為回轉壓縮機構部3與電動元件4間之 空間A之體積之1. 5倍以上、15倍以下。具體而言，採用 上述之本發明構成時，為了提升密閉容器2内之油分離性 能，需確保足以使冷媒充分擴散至即將喷出至密閉容器2 外之前（最終段）之電動元件4的回轉壓縮機構部3相反側 19 321798 201035448 之充分油分離空間。如此，為了充分碟保電動元件4的回 轉壓縮機構部3相反側之油分離空間，若將密閉容器2之 上下尺寸擴大’則會產生迴轉壓縮機1之大型化，且因為 密閉容器2之設計變更而導致成本大增之問題。 因此’為了不需擴大密閉容器2之上下尺寸，而確保 回轉壓縮機構部3相反側之油分離空間，在本發明中，電 動元件4的回轉壓縮機構部3相反側之空間β，係藉由調 整為較回轉壓縮機構部3與電動元件4 大，以確保適當的油分離空間。 之體積 藉由將電動元件4的回轉壓縮機構部^相反 之空間Β之體積設為回轉壓縮機構部3與電動元件4間之 ::上的體積之L 5倍以上、15倍以下，即可不需擴大密 才合斋2之上下尺寸，而可確保密閉容器2之内壁面與電 =件4 B之體積’且確保最終段之冷媒擴散所 也成之油分離空間，而提升油分離效果。 隙擴散至空㈣之冷媒，餘指向於冷媒流路（氣 之開口進人冷媒噴出管9,並喷出至密閉 下，而返回密閉容器2内二::子广述縱溝39流 2内媒:據本發：’即可使喷出至密閉容器 離，而可㈤在該密閉容112内有效率地分 11田降低從冷媒喷出管9噴出至迴轉壓縮機1外 321798 20 r201035448 部之油。藉此，即可順暢地進行對於迴轉壓縮機丨的滑動 部之供油，而可確保迴轉壓縮機10之性能，而謀求可靠性 之提升。 4 〇28 (that is, the stator 5 in which the discharge holes 28a, 28b, and 28 are squirted to the end surface (lower end surface) of the space between the compression mechanism portion 3 and the electric component 4 toward the side of the rotary compression mechanism portion 3 (lower side) The space is surrounded by the coil end portion, and the space % is an air gap between the rotor 7 and the stator 5. That is, the back (four) reduction mechanism portion 3 and the electric component 4 are ejected from the ejection hole 28 into the sealed container 2. The refrigerant in the space A is a ring that protrudes from the end surface of the rotor 7 toward the side of the rotary compression mechanism portion 3 (lower side): a space surrounded by the portion S and passes through the ring of the rotor 7 and the stator 5: The space S2 is ejected from the upper end opening (i.e., the outlet of the refrigerant flow path) to the space between the inner wall surface of the dense cell 2 and the electric component (that is, the opposite side of the rotary compression mechanism portion 3 of the electric component 4 in the hermetic container 2 Space) B. The outlet of the cold and L-way rotary pressure Ifg mechanism portion 3 (i.e., the upper end of the space S2 of the air gap) is opposed to the inner wall surface of the hermetic container 2. On the other hand, the airtightness is closed. The side of the container body 2A of the container 2 is corresponding to the suction passages 16, 26 of the respective compression illusions 2, 22. The sleeve 60 is fixedly attached to the sleeve 60. The sleeves 60 and 61 are vertically adjacent to each other. Further, 'the sleeve 60 is inserted and connected to the refrigerant introduction tube 4 for introducing the refrigerant gas into the lower compression cylinder 12, and One end of the refrigerant introduction pipe 4 is in communication with the suction passage 16 of the lower condensing cylinder 12. The lower end of the refrigerant introduction pipe is opened in the upper portion of the accumulator 65. The refrigerant gas is introduced into the refrigerant introduction pipe 41 of the upper 32798 14 201035448 compression cylinder 22, and one end of the refrigerant introduction pipe 41 communicates with the suction passage 26 of the upper compression cylinder 22. The other end of the refrigerant introduction pipe 41 is connected to the refrigerant. The introduction tube 40 is also opened at an upper portion of the reservoir 65 by π. The reservoir 65 is for performing a tank for taking in a gas-liquid separation of the refrigerant, and is attached to the hermetic container 2 via a bracket 67. The upper side of the upper portion of the container body 2A. Further, the reservoir 65 is inserted with the refrigerant introduction tube 40 and the refrigerant introduction tube 41 from the bottom, and the other end opening is branched, and is located above the reservoir 65. Further, one end of the refrigerant pipe 68 is inserted into the upper end portion of the reservoir 65. On the other hand, the end cap 2B of the hermetic container 2 is formed with a circular hole 62 at a substantially central portion of the position corresponding to the rotary shaft 8. A refrigerant discharge pipe 9 to which the above-described refrigerant discharge pipe 9 is connected is inserted into the hole 62, and one end of the refrigerant discharge pipe 9 is opened in the upper portion of the hermetic container 2. The opening of one end of the refrigerant discharge pipe 9 is directed to the inside of the above-mentioned annular refrigerant flow path (i.e., the space S2 of the air gap between the stator 5 and the turning Q 7). In the present invention, the volume of the space between the inner wall surface of the hermetic container 2 and the electric element 4 (the space on the opposite side of the rotary compression mechanism portion 3 of the electric component 4) B is set to be larger than the rotary compression mechanism portion 3 and the electric motor. When the volume of the space A between the components 4 is large, in order to improve the oil separation performance, it is considered that the volume of the space B on the electric component becomes 1. 5 times or more and 15 times or less the volume of the space A under the electric element. The height of the electric component 4 in the container 2 is arranged. The operation of the rotary compressor 1 of the present embodiment will be described with the above configuration. 15 321798 201035448 When the stator coil 37 of the motor element 4 is energized via the terminal 35 and a wiring (not shown), the motor element 4 is activated to rotate the rotor 7. By this rotation, the rollers 14 and 24 fitted to the eccentric portions 13 and 23 provided integrally with the rotary shaft 8 are eccentrically rotated in the respective compression cylinders 12 and 22. Thereby, the low-pressure refrigerant flows into the reservoir 65 from the refrigerant pipe 68 of the rotary compressor 1. The low-pressure refrigerant that has flowed into the accumulator 65 is separated from the refrigerant introduction pipes 40, 41 opened in the accumulator 65 after the gas-liquid separation. The low-pressure refrigerant gas system that has entered the refrigerant introduction pipe 40 is sucked into the low-pressure chamber side of the compression cylinder 12 of the first rotary compression element 10 through the suction passage 16. The refrigerant gas sucked into the low pressure chamber side of the refrigerant introduction pipe 40 is compressed by the operation of the rollers 14 and the blades (not shown), and becomes a high-temperature high-pressure refrigerant gas, and passes through the delivery passage 19 from the high pressure chamber side of the compression cylinder 12. It is ejected to the discharge muffler 17. The refrigerant gas discharged to the discharge muffler 17 is discharged to the discharge muffler 27 via a communication path (not shown), and merges with the refrigerant gas compressed by the second rotary compression element 22. On the other hand, the low-pressure refrigerant gas system that has entered the refrigerant introduction pipe 41 is sucked into the low-pressure chamber side of the compression cylinder 22 above the second rotary compression element 20 through the suction passage 26. The refrigerant gas system sucked into the low pressure chamber side of the upper compression cylinder 22 is compressed by the operation of the rollers 24 and the blades (not shown) to become high temperature and high pressure refrigerant gas, and passes through the discharge passage 29 from the high pressure chamber side of the upper compression cylinder 22. The discharge to the discharge muffler 27 merges with the refrigerant gas from the first rotary compression element 12. Further, the merged refrigerant gas system is ejected from the discharge hole 28 formed in the upper cover 27A to the work space a between the rotary compression mechanism portion 3 and the electric component 4 in the hermetic container 12. At this time, the oil supplied to the sliding portion of the rotary compression mechanism unit 3 is in a mist form in the refrigerant gas, and the oil is also discharged from the respective discharge holes 28 in the same manner as the refrigerant gas. Further, the arrow shown in the second figure shows the flow direction of the oil which is discharged into the sealed container 2 with the compressed refrigerant. Here, since the discharge hole 28 is disposed at a position opposite to the lower end surface of the rotor core 38 of the rotor 7, the compressed cold medium discharged from the discharge hole 28 and the rotor core 38 of the rotating rotor 7 are disposed. The end face collides and is diffused to the space S1 surrounded by the coil end portion 3 of the stator coil 37 of the stator 5 by the mixing. Here, the conventional nozzle provided in the upper cover 27 will be described with reference to Fig. 6, and in Fig. 6, '128a is a discharge hole having an inner diameter of i〇mm, and 12 is an internal control 8-contact discharge hole. 128c is the inner diameter of 6 and then the hole is ejected. ! 27-shaped cold county pulsation absorption illusion = configuration 5. However, as shown in Fig. 6, the conventional ejection holes 128 are disposed adjacent to the outer peripheral edge of the center of the upper cover 27, and are opposed to the space S2 of the air gap between the motor element 4 and the stator 5. position. That is, each of the (4) compressed refrigerants in the container 2 directly flows into the air gap space S2 between the rotor 7 and the stator 5. Except for the (4) space S2, it is also useful to introduce the refrigerant into the other refrigerant flow path on the opposite side of the rotary pressure working portion 3, for example, the pressure m7 Na " direction (up and down direction) is penetrated, and the formation Returning to the refrigerant passage between the inner surface of the inner surface and the electric component 4 (A) A and the space between the sealed container 2 "/, the electric 70 piece 4, and the compressed refrigerant discharged from the ejection hole of 321798 17 201035448 is guided thereto. The refrigerant passage or the guide to the refrigerant passage and the air gap space S2. As described above, in the conventional configuration, the compressed refrigerant discharged from the discharge holes is hardly separated from the space A between the rotary compression mechanism portion 3 and the electric component 4, and is directly used for the flow. The refrigerant flow path is guided to the opposite side of the rotary compression mechanism unit 3 of the electric component 4. On the other hand, in the present invention, the discharge hole 28 and the end surface (lower end surface) of the rotor core 38 of the rotor 7 are opposed to each other, so that the compressed refrigerant discharged from the discharge hole 28 into the hermetic container 2 can be compressed. And colliding with the lower end surface of the rotor core 38 of the rotor 7 to which the discharge hole 28 is directed. Thereby, the oil can be separated from the space A between the rotary compression mechanism portion 3 and the electric component 4 in the hermetic container 2. In particular, by causing the compressed refrigerant from the discharge port 28 to collide with the lower end surface of the rotor core 38 of the rotating rotor 7, the refrigerant can be stirred by the rotation of the rotor core 38 to spread it widely to the stator 5. The entire space S1 surrounded by the coil end portion 37E of the stator coil 37. Thereby, the oil separation in the space S1 surrounded by the coil end portion 37E of the stator 5 can be promoted. Thereafter, the refrigerant passing through the space S1 passes through the air gap space S2 of the stator 5 and the rotor 7. Since the air gap space S2 is slightly formed in the gap between the stator 5 and the rotor 7, and the rotor 7 located inside the micro gaps rotates, the refrigerant passing through the space S2 is affected by the rotation of the rotor 7, and one side It is twisted in the direction of rotation of the rotor 7, and flows in such a manner as to rise in the space S2. Thereby, the oil can be further separated from the refrigerant during the passage of the space S2. 18 321798 201035448 The refrigerant which is further oil-separated by the air gap space S2 of the stator 5 and the rotor 7 is ejected from the outlet of the space S2 to the space B on the opposite side of the rotary compression mechanism portion 3 of the electric component 4. At this time, since the outlet is provided to face the inner wall surface of the hermetic container 2, the refrigerant discharged from the outlet collides with the inner wall surface of the hermetic container 2 and diffuses into the space B. In this manner, the oil can be further separated by the diffusion of the space B on the opposite side of the rotary compression mechanism portion 3 of the motor element 4. In particular, the opening of one end of the refrigerant discharge pipe 9 for guiding the compression f) of the space B diffused in the sealed container 2 to the outside of the hermetic container 2 is directed to be annular in the hermetic container 2. The inside of the refrigerant flow path (that is, the aforementioned air gap space S2). Therefore, it is possible to suppress the compressed refrigerant that has reached the opposite side of the rotary compression mechanism portion 3 of the electric component 4 passing through the refrigerant flow path from directly reaching the refrigerant discharge pipe 9. Thereby, the oil separation performance can be improved. Further, as described above, the distance D from the upper surface of the stopper plate 45 provided on the upper end surface of the rotor 7 to the inner wall surface of the end cover 2B of the hermetic container 2 corresponding to the upper direction is set to 25 mm or more. Therefore, the oil separation space on the opposite side of the rotary compression mechanism portion 3 of the motor element 4 can be sufficiently ensured, and the oil separation performance can be further improved. In particular, the volume of the space B on the opposite side of the rotary compression mechanism unit 3 of the electric component 4 is set to be 1.5 times or more and 15 times or less the volume of the space A between the rotary compression mechanism unit 3 and the electric element 4. Specifically, in the case of the above-described configuration of the present invention, in order to improve the oil separation performance in the hermetic container 2, it is necessary to ensure sufficient rotation of the refrigerant to the motor element 4 immediately before being discharged to the outside of the hermetic container 2 (final stage). A sufficient oil separation space on the opposite side 19 321798 201035448 of the compression mechanism portion 3. As described above, in order to sufficiently secure the oil separation space on the opposite side of the rotary compression mechanism portion 3 of the electric component 4, if the size of the upper and lower sides of the sealed container 2 is enlarged, the size of the rotary compressor 1 is increased, and the design of the closed container 2 is required. The change caused the problem of a large increase in costs. Therefore, in order to ensure the oil separation space on the opposite side of the rotary compression mechanism portion 3 without expanding the size of the upper and lower sides of the hermetic container 2, in the present invention, the space β on the opposite side of the rotary compression mechanism portion 3 of the electric component 4 is caused by It is adjusted to be larger than the rotary compression mechanism portion 3 and the electric component 4 to secure an appropriate oil separation space. The volume of the space 相反 which is opposite to the rotary compression mechanism of the motor element 4 is set to be 5 times or more and 15 times or less the volume L of the rotary compression mechanism unit 3 and the electric element 4, and It is necessary to enlarge the upper and lower dimensions of the dense rubber, and to ensure the volume of the inner wall of the closed container 2 and the volume of the electric material 4 B and to ensure that the final stage of the refrigerant diffusion also becomes an oil separation space, thereby improving the oil separation effect. The gap diffuses to the air (4), and the remainder is directed to the refrigerant flow path (the opening of the gas enters the refrigerant discharge pipe 9 and is ejected to the closed state, and returns to the closed container 2: 2: the sub-longitudinal groove 39 flow 2 Medium: According to the present invention: 'It is possible to eject the container to the closed container, and (5) efficiently discharge the 11 field in the sealed container 112 from the refrigerant discharge pipe 9 to the rotary compressor 1 outside the 321798 20 r201035448 By this, the oil supply to the sliding portion of the rotary compressor 顺 can be smoothly performed, and the performance of the rotary compressor 10 can be ensured, and the reliability can be improved.
再者’藉由噴出至迴轉壓縮機1外部之油量減少，因 為油對外部迴路造成不良影響之缺失亦得以抑制。 另外，在本發明中，喷出孔係只要為設於與轉子之端 :相對向之位置即可，只要是可有效地吸收（降低）喷出消 音态27内之冷媒氣體之脈動而設者，則不限定於第2圖所 示之實施例之噴出孔28之直徑或數量及配置等。例如，亦 可如第3圖所示以回轉軸8為中心、將内徑6咖4 6個喷出 孔28c予以大致均等地配置，或如第4圖所示將内徑恤 之4個噴出孔28b與内徑6mm之1個喷出孔28c設置於回 轉轴8附近。此外，亦可如第5圖所示，僅由内徑_之 喷出孔28a、及以回轉軸8為中心與該喷出孔咖大致對 稱之方式配置之内徑8mm之喷出孔28b來構成。 此外，在本實施例中雖將本發明應用於2壓缸之密閉 型回轉壓㈣騎㈣，惟不限^此，杨將本發明應 用於1壓缸之密閉型回轉壓縮機或多縣縮型之壓厂 亦仍屬有效。 【圖式簡單說明】 實施例之密閉 弟1圖係為概略性顯示應用本發明之一 型回轉壓縮機之縱剖側面圖。 縮機之喷出孔 苐2圖係為具有第1圖之密閉型回轉壓 之喷出消音器之平面圖。 321798 21 201035448 第3圖係為具有另一 圖 圖 圖 第4圖係為具有再另—C肖音器之平面圖。 。之噴出消音器之平面 第5圖係為具有又再另 貰出孔之噴出消音器之平面 第6圖係為具有f知之噴出孔H肖音器之平面 【主要元件符號說明】 1 迴轉屋縮機（密閉型回轉壓縮機） 2 密閉容器 9A — 端蓋 回轉壓縮機構部 定子 回轉軸 第1回轉壓縮元件 23偏心部 2C 4 7 9 12、 14 > 15Α 2β _ 2Α 容器本體 底部 電動元件 轉子 冷媒噴出管 22壓縮缸 24滾柱 下部軸承 3 5 8 10 13、 15、 25支撐構件 Π ' 27喷出消音器 19、 29喷出通路 20、 34第2回轉壓縮元件 27A 上蓋 28c、128、128a、128b、128c 噴出孔 35 端子 37 定子線圈 16、 26吸入通路 17Α 下蓋 19V、29V噴出閥 25Α 上部軸承 28、28a、28b 3〇 中間隔板 36 定子鐵心 22 321798 201035448 37E 線圈端部 38 39 縱溝（回油用之通路） 40、 42、 43 平衡器 45 47 鉚釘 50 60、 61 套筒 62 65 儲存器 67 68 冷媒配管 70 75 螺栓 A、B D 距離 轉子鐵心 ii冷媒導入管 播止板 油泵 托架 安裝用基座 、C、SI、S2 空間 〇 23 321798Furthermore, the amount of oil that is ejected to the outside of the rotary compressor 1 is reduced because the lack of adverse effects of the oil on the external circuit is also suppressed. Further, in the present invention, the discharge hole may be provided at a position facing the end of the rotor as long as it is capable of effectively absorbing (decreasing) the pulsation of the refrigerant gas in the discharge muffling state 27. The diameter, the number, the arrangement, and the like of the discharge holes 28 of the embodiment shown in Fig. 2 are not limited. For example, as shown in Fig. 3, the inner diameter 6 of the six discharge holes 28c may be substantially equally arranged around the rotary shaft 8, or four of the inner diameter shirts may be ejected as shown in Fig. 4. The hole 28b and one discharge hole 28c having an inner diameter of 6 mm are provided in the vicinity of the rotary shaft 8. Further, as shown in Fig. 5, the discharge hole 28a having an inner diameter of 8 mm and the discharge hole 28b having an inner diameter of 8 mm disposed substantially symmetrically with respect to the discharge hole 8 around the rotary shaft 8 may be used. Composition. In addition, in the present embodiment, the present invention is applied to the closed type rotary pressure (four) ride (four) of the two cylinders, but it is not limited thereto, and the invention applies the invention to the closed type rotary compressor of one pressure cylinder or the multi-county contraction. The type of pressure plant is still valid. BRIEF DESCRIPTION OF THE DRAWINGS The sealed body 1 is a longitudinal sectional side view showing a rotary compressor of the present invention. The discharge hole of the reduction machine 苐 2 is a plan view of the discharge muffler having the closed type rotary pressure of Fig. 1. 321798 21 201035448 Fig. 3 is a diagram showing another figure. Fig. 4 is a plan view with a further C-sound. . The plane of the squirting muffler is shown in Fig. 5. The plane of the squirting muffler having another hole is shown in Fig. 6. The plane of the ventilating hole H is the plane of the oscillating device. [Main component symbol description] 1 Slewing house Machine (closed rotary compressor) 2 Closed container 9A — End cap rotary compression mechanism part Stator rotary shaft 1st rotary compression element 23 Eccentric part 2C 4 7 9 12, 14 > 15Α 2β _ 2Α The bottom of the container body is the rotor of the electric component rotor Discharge pipe 22 compression cylinder 24 roller lower bearing 3 5 8 10 13 , 15 , 25 support member Π ' 27 discharge muffler 19, 29 discharge passage 20, 34 second rotary compression element 27A upper cover 28c, 128, 128a, 128b, 128c discharge hole 35 terminal 37 stator coil 16, 26 suction passage 17 Α lower cover 19V, 29V discharge valve 25 上部 upper bearing 28, 28a, 28b 3 〇 intermediate partition 36 stator core 22 321798 201035448 37E coil end 38 39 longitudinal groove (Returning oil passage) 40, 42, 43 Balancer 45 47 Rivet 50 60, 61 Sleeve 62 65 Storage 67 68 Refrigerant piping 70 75 Bolts A, BD Distance rotor core ii refrigerant guide Inlet pipe arresting plate oil pump bracket mounting base, C, SI, S2 space 〇 23 321798