JP6134903B2 - Positive displacement compressor - Google Patents
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- JP6134903B2 JP6134903B2 JP2013025189A JP2013025189A JP6134903B2 JP 6134903 B2 JP6134903 B2 JP 6134903B2 JP 2013025189 A JP2013025189 A JP 2013025189A JP 2013025189 A JP2013025189 A JP 2013025189A JP 6134903 B2 JP6134903 B2 JP 6134903B2
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Description
本発明は、例えば空調・冷凍機等に搭載される容積型圧縮機に関するもので、さらに詳しくは、軸受摺動部の潤滑性能向上により、効率向上と信頼性向上を実現する容積型圧縮機に関するものである。 The present invention relates to a positive displacement compressor mounted on, for example, an air conditioner / refrigerator, and more specifically, relates to a positive displacement compressor that improves efficiency and reliability by improving the lubrication performance of a bearing sliding portion. Is.
従来、空気調和装置等の冷凍サイクルの圧縮機として容積型圧縮機が用いられている。図４は、従来のスクロール型圧縮機の縦断面図を示すものである。その容積型圧縮機の代表的なスクロール型圧縮機１は、例えば図４に示される構成になっている（特許文献１）。両端が閉鎖された筒状の密閉容器２の内側には電動要素３とスクロール圧縮要素４とが内蔵されている。電動要素３は密閉容器２の内壁面側に固定されたステータ３ａと、このステータ３ａの内側に回転自在に支持されたロータ３ｂとからなり、このロータ３ｂには回転軸６が貫通し固定結合されている。この回転軸６の上方の端部はスクロール圧縮要素４の一部を構成する第１支持フレーム７に回転自在に支持されている。回転軸６の下方端部はロータ３ｂから突出されており、この下方の端部は第２支持フレーム１０に回転自在に支持されている。そして、回転軸６の油吸込管９は密閉容器２の底部の貯油部２ａの潤滑油８に没するように下方に延長されており、潤滑油８は回転軸６の回転に伴い油吸込管９内で回転して、生じた遠心力で、油吸込管９を上昇し、さらに回転軸６の軸方向に偏心貫通する給油縦孔１２も上昇し上方の偏心軸受部１４まで給油される。 Conventionally, a positive displacement compressor is used as a compressor of a refrigeration cycle such as an air conditioner. FIG. 4 is a longitudinal sectional view of a conventional scroll compressor. A typical scroll compressor 1 of the positive displacement compressor has a configuration shown in FIG. 4, for example (Patent Document 1). The electric element 3 and the scroll compression element 4 are built in the inside of the cylindrical airtight container 2 whose both ends are closed. The electric element 3 includes a stator 3a fixed to the inner wall surface side of the hermetic container 2, and a rotor 3b rotatably supported inside the stator 3a. A rotating shaft 6 passes through the rotor 3b and is fixedly coupled. Has been. An upper end portion of the rotary shaft 6 is rotatably supported by a first support frame 7 constituting a part of the scroll compression element 4. The lower end portion of the rotating shaft 6 protrudes from the rotor 3 b, and the lower end portion is rotatably supported by the second support frame 10. The oil suction pipe 9 of the rotating shaft 6 is extended downward so as to be immersed in the lubricating oil 8 of the oil storage section 2 a at the bottom of the hermetic container 2, and the lubricating oil 8 is moved along with the rotation of the rotating shaft 6. The oil suction pipe 9 is lifted by the generated centrifugal force by rotating within 9, and the oil supply vertical hole 12 that is eccentrically penetrated in the axial direction of the rotating shaft 6 is also lifted and supplied to the eccentric bearing portion 14 above.
第２支持フレーム１０には、密閉容器２内に装着されて回転軸６のラジアル荷重を支持する副軸受（ジャーナル軸受）１０ａ、軸受ブッシュ１０ｂおよびスラスト荷重を支持するスラスト軸受１０ｄを備え、フレーム支持部１０ｃを介して密閉容器２に固定されている。また、回転軸６の回転に伴い貯油部２ａの潤滑油８は油吸込管９の下端方吸込み口より吸入され、その潤滑油８は給油縦孔１２を経て副軸受１０ａや第１支持フレーム７などの各摺動部に供給された後、密閉容器２の内側の隙間を経由して貯油部２ａに戻ることによって再循環されるようになっている。 The second support frame 10 includes a secondary bearing (journal bearing) 10a that is mounted in the sealed container 2 and supports the radial load of the rotary shaft 6, a bearing bush 10b, and a thrust bearing 10d that supports the thrust load. It is being fixed to the airtight container 2 via the part 10c. Further, as the rotary shaft 6 rotates, the lubricating oil 8 in the oil storage section 2a is sucked from the lower suction port of the oil suction pipe 9, and the lubricating oil 8 passes through the oil supply vertical hole 12 and the auxiliary bearing 10a and the first support frame 7. After being supplied to each sliding part such as the above, it is recirculated by returning to the oil storage part 2a through the gap inside the sealed container 2.
そして、第１支持フレーム７を貫通し支持された回転軸６の一端部には回転軸６の軸心から偏心した偏心軸（クランク部）１３が形成されており、この偏心軸１３には揺動スクロール４ａが連接されている。この揺動スクロール４ａは、円盤の一側面（後述する固定スクロール５ａと反対側）の中央部に偏心軸１３が接続されるボス状の偏心軸受部１４が形成され、他方の側面（後述する固定スクロール５ａと同じ側）には渦巻き形状のラップ４ｂが一体に形成されている。また、第１支持フレーム７には、固定スクロール５ａが結合されている。この固定スクロール５ａには揺動スクロール４ａに対面する部分に渦巻き形状のラップ５ｂが形成され、中央部に両側面を貫通して設けた吐出ポート１７が形成されている。そして、ラップ４ｂ、５ｂとで形成された複数の圧縮室１５は、吸入管１６から密閉容器２の低圧空間２ｃに収容された低圧の冷媒ガスを外周部で吸込み、回転軸６の回転に伴い漸次中心に移動していくことで容積を縮小して冷媒ガスを圧縮し、圧縮された冷媒ガスは吐出ポート１７から密閉容器２の高圧空間２ｂに吐出され、吐出管１８から吐出される。 An eccentric shaft (crank portion) 13 that is eccentric from the axis of the rotary shaft 6 is formed at one end portion of the rotary shaft 6 that is supported through the first support frame 7. The dynamic scroll 4a is connected. The orbiting scroll 4a has a boss-shaped eccentric bearing portion 14 to which an eccentric shaft 13 is connected at the center of one side surface (opposite side of a fixed scroll 5a, which will be described later) of the disk, and the other side surface (fixed, which will be described later). A spiral wrap 4b is integrally formed on the same side as the scroll 5a. A fixed scroll 5 a is coupled to the first support frame 7. In the fixed scroll 5a, a spiral wrap 5b is formed at a portion facing the rocking scroll 4a, and a discharge port 17 provided through both side surfaces is formed at the center. The plurality of compression chambers 15 formed by the wraps 4 b and 5 b suck low-pressure refrigerant gas stored in the low-pressure space 2 c of the sealed container 2 from the suction pipe 16 at the outer peripheral portion, and with the rotation of the rotary shaft 6. By gradually moving to the center, the volume is reduced and the refrigerant gas is compressed. The compressed refrigerant gas is discharged from the discharge port 17 to the high-pressure space 2 b of the sealed container 2 and discharged from the discharge pipe 18.
図５は、従来のスクロール型圧縮機の第２支持フレームの近傍の縦断面図を示すものである。図５に示すように、副軸受１０ａの内面側には軸受ブッシュ１０ｂが圧入してあり、その内面は回転軸６の外周面と摺動している。回転軸６に給油縦孔１２と連通して給油横孔２１が半径方向に穿設され、さらに回転軸６の外周に給油横孔２１と連通してジャーナル給油溝２２が軸方向に伸びて設けられており、潤滑油８を給油縦孔１２から軸受ブッシュ１０ｂの摺動部へ供給する。ジャーナル給油溝２２の上方は軸受ブッシュ１０ｂより伸びて開口して、下方は軸受ブッシュ１０ｂ内で閉じている。この給油構成では、潤滑油８は図中の矢印ａ、ｂ、ｃで示すように給油縦孔１２から給油横孔２１を通り（矢印ｂ）
を上方に流れて副軸受１０ａの摺動部を潤滑した後に上方（矢印ｃ）に排出されるようになっている。軸受ブッシュ１０ｂの下方にはスラスト軸受１０ｄの周囲に通じた油溜空間２３が設けられ、軸受ブッシュ１０ｂの軸受隙間から下方の油溜空間２３へ漏れ出た潤滑油は、油溜空間２３に充満し停滞しない様に油排出孔２４から下方の貯油部２ａへ排出される（図中矢印ｄ参照）。
FIG. 5 is a longitudinal sectional view of the vicinity of a second support frame of a conventional scroll compressor. As shown in FIG. 5, a bearing bush 10 b is press-fitted on the inner surface side of the auxiliary bearing 10 a, and the inner surface slides on the outer peripheral surface of the rotating shaft 6. An oil supply lateral hole 21 is formed in the radial direction in the rotary shaft 6 in communication with the oil supply vertical hole 12, and a journal oil supply groove 22 is provided in the outer periphery of the rotary shaft 6 in communication with the oil supply horizontal hole 21 in the axial direction. The lubricating oil 8 is supplied from the oil supply vertical hole 12 to the sliding portion of the bearing bush 10b. The upper part of the journal oil supply groove 22 extends from the bearing bush 10b and opens, and the lower part is closed in the bearing bush 10b. In this oil supply configuration, the lubricating oil 8 passes from the oil supply vertical hole 12 through the oil supply horizontal hole 21 as shown by arrows a, b, and c (arrow b).
And then the sliding portion of the auxiliary bearing 10a is lubricated and then discharged upward (arrow c). An oil reservoir space 23 is provided below the bearing bush 10b so as to communicate with the periphery of the thrust bearing 10d. Lubricating oil leaking from the bearing gap of the bearing bush 10b into the oil reservoir space 23 is filled in the oil reservoir space 23. Then, the oil is discharged from the oil discharge hole 24 to the lower oil storage portion 2a so as not to stagnate (see arrow d in the figure).
しかし、この構成では油排出孔２４は図の上方にのみ開口し、下方のスラスト軸受１０ｄの給油は軸受ブッシュ１０ｂと回転軸６の摺動面の隙間から漏れ出る潤滑油であり、十分な油量が確実に給油される必要があった。 However, in this configuration, the oil discharge hole 24 is opened only in the upper part of the figure, and the oil supply of the lower thrust bearing 10d is lubricating oil that leaks from the gap between the bearing bush 10b and the sliding surface of the rotary shaft 6, and sufficient oil The amount needed to be refueled reliably.
そこで、スラスト軸受１０ｄあるいは回転軸６のスラストの摺動面の給油量を十分確保し潤滑性能を良好とすることで、摺動損失の低減による性能向上、さらには、より潤滑条件の厳しい運転条件でも耐摩耗や耐焼付き性向上による信頼性向上を実現できる容積型圧縮機を提供する必要があった。 Therefore, by ensuring a sufficient amount of lubrication on the thrust sliding surface of the thrust bearing 10d or the rotating shaft 6 to improve the lubrication performance, the performance is improved by reducing the sliding loss, and the operating conditions are more severe. However, it was necessary to provide a positive displacement compressor capable of improving reliability by improving wear resistance and seizure resistance.
本発明の目的は、回転軸の給油縦孔から連通しスラスト摺動面に開口した給油通路を設けてスラスト軸受へ確実に給油を可能とすることで、スラスト軸受での潤滑性能を向上させ、高効率で信頼性の高い容積型圧縮機を提供することである。 The object of the present invention is to improve the lubrication performance in the thrust bearing by providing an oil supply passage that opens from the oil supply vertical hole of the rotating shaft to the thrust sliding surface and enables reliable oil supply to the thrust bearing, A high-efficiency and reliable positive displacement compressor is provided.
すなわち、前記課題を解決するために、本発明の容積型圧縮機は、密閉容器内に設けられた電動要素と、前記電動要素によって回転駆動される回転軸と、前記電動要素の上方に設置され前記回転軸を介して駆動される圧縮要素と、前記電動要素と前記圧縮要素の間に設置され前記密閉容器内に固着されて回転軸を回転支持する第１支持フレームと、前記密閉容器内に固着されて前記回転軸の下方端部を回転支持する第２支持フレームと、前記密閉容器の底部に潤滑油の貯油部と、を備え、前記回転軸の下方端面から前記回転軸を貫通して設けられた給油縦孔を介して前記潤滑油を各摺動部に送る容積型圧縮機であって、前記第２支持フレームは、前記回転軸のラジアル力を受けるジャーナル軸受と、スラスト力を受けるスラスト軸受と、から構成され、前記回転軸の外周に設けられ、前記回転軸の軸方向に伸びたジャーナル給油通路と、前記スラスト軸受に設けられ、前記回転軸の半径方向に伸びたスラスト給油通路と、を有し、前記スラスト給油通路は、前記回転軸と前記スラスト軸受の摺動面に開口し、油排出通路を介して前記貯油部と連通しており、前記貯油部の潤滑油は、前記給油縦孔から前記回転軸に設けられた半径方向の給油横孔を経て、前記ジャーナル軸受の摺動面に供給され、さらに、前記ジャーナル軸受の摺動面に供給された前記潤滑油は、前記ジャーナル給油通路を経て、前記スラスト軸受周辺の油溜空間に供給され、さらに、前記油溜空間に供給された前記潤滑油は、前記回転軸の半径方向に伸びたスラスト給油通路によって、前記回転軸と前記スラスト軸受の摺動面に供給されるものである。 That is, in order to solve the above-mentioned problem, the positive displacement compressor of the present invention is installed above the electric element, the electric element provided in the hermetic container, the rotating shaft driven to rotate by the electric element. A compression element driven via the rotating shaft; a first support frame which is installed between the electric element and the compression element and is fixed in the sealed container to rotatably support the rotating shaft; and in the sealed container a second support frame for rotatably supporting the lower end of the rotary shaft is fixed, said and a oil storage portion of the lubricating oil in a bottom portion of the closed container, through said rotary shaft from the lower end surface of the rotary shaft the lubricating oil via the provided oil supply longitudinal bore a positive displacement compressor to be sent to each sliding portion, the second support frame, a journal bearing which receives a radial force of the rotating shaft, the scan last force and a thrust bearing to receive, from the A journal oil supply passage formed on the outer periphery of the rotary shaft and extending in the axial direction of the rotary shaft; and a thrust oil supply passage provided in the thrust bearing and extending in the radial direction of the rotary shaft. The thrust oil supply passage opens to the sliding surface of the rotary shaft and the thrust bearing, and communicates with the oil storage portion via an oil discharge passage, and the lubricating oil in the oil storage portion passes through the oil supply vertical hole. The lubricating oil supplied to the sliding surface of the journal bearing through a radial oil supply lateral hole provided in the rotating shaft, and further supplied to the sliding surface of the journal bearing, passes through the journal oil supply passage. Then, the lubricating oil supplied to the oil reservoir space around the thrust bearing is further supplied to the rotating shaft and the thrust shaft by a thrust oil supply passage extending in a radial direction of the rotating shaft. It is those of the supply to the sliding surface.
これによれば、給油縦孔から軸受ブッシュとスラスト軸受への給油経路が一経路となっているため、給油縦孔から軸受ブッシュとスラスト軸受へ流れる給油量を多く確保できる。According to this, since the oil supply path from the oil supply vertical hole to the bearing bush and the thrust bearing is one path, it is possible to secure a large amount of oil flowing from the oil supply vertical hole to the bearing bush and the thrust bearing.
また、これによれば、軸受ブッシュとスラスト軸受の摺動面に確実に潤滑油が供給されThis also ensures that the lubricating oil is supplied to the sliding surfaces of the bearing bush and thrust bearing.
るため、軸受ブッシュとスラスト軸受の各々との回転軸の摺動部で良好な潤滑状態が確保され、摺動部の摺動損失を抑えることができる。Therefore, a good lubrication state is ensured at the sliding portion of the rotating shaft of each of the bearing bush and the thrust bearing, and the sliding loss of the sliding portion can be suppressed.
また、これによれば、スラスト軸受と回転軸のスラスト摺動部の摩耗や焼付き等の発生も抑制することできる。Moreover, according to this, generation | occurrence | production of abrasion, seizure, etc. of the thrust sliding part of a thrust bearing and a rotating shaft can also be suppressed.
本発明の容積型圧縮機によれば、回転軸の給油縦孔に連通した給油横穴を介してジャーナル軸受、スラスト軸受の摺動面に開口して設けた給油通路により両軸受摺動面に確実な給油を可能とするとともに、給油通路は簡便な構成で実現できるため、高効率で信頼性の高い容積型圧縮機を、高い生産性で安価に提供することができる。 According to the positive displacement compressor of the present invention, the sliding surfaces of both the bearings are reliably provided by the oil supply passages that are opened in the slide surfaces of the journal bearing and the thrust bearing through the oil supply horizontal holes communicating with the oil supply vertical holes of the rotary shaft. Since the oil supply passage can be realized with a simple configuration, a highly efficient and reliable positive displacement compressor can be provided with high productivity and at low cost.
第１の発明は、密閉容器内に設けられた電動要素と、前記電動要素によって回転駆動される回転軸と、前記電動要素の上方に設置され前記回転軸を介して駆動される圧縮要素と、前記電動要素と前記圧縮要素の間に設置され前記密閉容器内に固着されて回転軸を回転支持する第１支持フレームと、前記密閉容器内に固着されて前記回転軸の下方端部を回転支持する第２支持フレームと、前記密閉容器の底部に潤滑油の貯油部と、を備え、前記回転軸の下方端面から前記回転軸を貫通して設けられた給油縦孔を介して前記潤滑油を各摺動部に送る容積型圧縮機であって、前記第２支持フレームは、前記回転軸のラジアル力を受けるジャーナル軸受と、スラスト力を受けるスラスト軸受と、から構成され、前記回転軸の外周に設けられ、前記回転軸の軸方向に伸びたジャーナル給油通路と、前記スラスト軸受に設けられ、前記回転軸の半径方向に伸びたスラスト給油通路と、を有し、前記スラスト給油通路は、前記回転軸と前記スラスト軸受の摺動面に開口し、油排出通路を介して前記貯油部と連通しており、前記貯油部の潤滑油は、前記給油縦孔から前記回転軸に設けられた半径方向の給油横孔を経て、前記ジャーナル軸受の摺動面に供給され、さらに、前記ジャーナル軸受の摺動面に供給された前記潤滑油は、前記ジャーナル給油通路を経て、前記スラスト軸受周辺の油溜空間に供給され、さらに、前記油溜空間に供給された前記潤滑油は、前記回転軸の半径方向に伸びたスラスト給油通路によって、前記回転軸と前記スラスト軸受の摺動面に供給されるものである。 The first invention includes an electric element provided in an airtight container, a rotating shaft that is rotationally driven by the electric element, a compression element that is installed above the electric element and driven via the rotating shaft, A first support frame that is installed between the electric element and the compression element and is fixed in the sealed container and rotatably supports the rotating shaft, and is fixed in the sealed container and rotatably supports the lower end portion of the rotating shaft. a second support frame, the oil storage portion of the lubricating oil in a bottom portion of the closed container, equipped with a, the lubricating oil through the oil supply vertical hole provided through the rotating shaft from the lower end surface of the rotary shaft a displacement type compressor to be sent to each sliding portion, the second support frame, a journal bearing which receives a radial force of said rotary shaft, and a thrust bearing for receiving the scan last power and a, of the rotary shaft Provided on the outer periphery, the rotation A journal oil supply passage extending in the axial direction, and a thrust oil supply passage provided in the thrust bearing and extending in a radial direction of the rotary shaft, wherein the thrust oil supply passage is formed between the rotary shaft and the thrust bearing. It opens to the sliding surface and communicates with the oil storage part through an oil discharge passage, and the lubricating oil in the oil storage part passes through the oil supply vertical hole and the radial oil supply horizontal hole provided in the rotary shaft. The lubricating oil supplied to the sliding surface of the journal bearing and further supplied to the sliding surface of the journal bearing is supplied to an oil reservoir space around the thrust bearing through the journal oil supply passage. The lubricating oil supplied to the oil reservoir space is supplied to the sliding surface of the rotary shaft and the thrust bearing by a thrust oil supply passage extending in the radial direction of the rotary shaft .
これによれば、給油縦孔から軸受ブッシュとスラスト軸受への給油経路が一経路となっているため、給油縦孔から軸受ブッシュとスラスト軸受へ流れる給油量を多く確保できる。According to this, since the oil supply path from the oil supply vertical hole to the bearing bush and the thrust bearing is one path, it is possible to secure a large amount of oil flowing from the oil supply vertical hole to the bearing bush and the thrust bearing.
また、これによれば、軸受ブッシュとスラスト軸受の摺動面に確実に潤滑油が供給されるため、軸受ブッシュとスラスト軸受の各々との回転軸の摺動部で良好な潤滑状態が確保され、摺動部の摺動損失を抑えることができる。Further, according to this, since the lubricating oil is reliably supplied to the sliding surfaces of the bearing bush and the thrust bearing, a good lubrication state is ensured at the sliding portion of the rotating shaft between the bearing bush and the thrust bearing. The sliding loss of the sliding part can be suppressed.
また、これによれば、スラスト軸受と回転軸のスラスト摺動部の摩耗や焼付き等の発生も抑制することできる。Moreover, according to this, generation | occurrence | production of abrasion, seizure, etc. of the thrust sliding part of a thrust bearing and a rotating shaft can also be suppressed.
したがって、効率の向上と信頼性の向上を実現できる容積型圧縮機を提供できる。Therefore, it is possible to provide a positive displacement compressor capable of improving efficiency and improving reliability.
以下、本発明の実施の形態について、図面を参照しながら説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
尚、この実施の形態によって本発明が限定されるものではない。 The present invention is not limited to the embodiment.
尚、図示されていない部分は、図４の従来例の圧縮機と同等であるため説明を省略する。 In addition, since the part which is not shown in figure is equivalent to the compressor of the prior art example of FIG. 4, description is abbreviate | omitted.
また、従来例の圧縮機と同等の機能を有する部分は、図４および図５と同じ符号を付け、説明を省略する。 Parts having the same functions as those of the conventional compressor are given the same reference numerals as those in FIGS. 4 and 5 and description thereof is omitted.
（参考例１）
本発明の参考例１について、図１を用いて説明する。図１は、本発明の参考例１における、第２支持フレームの近傍の縦断面図を示すものである。
( Reference Example 1 )
Reference Example 1 of the present invention will be described with reference to FIG. FIG. 1 shows a longitudinal sectional view of the vicinity of a second support frame in Reference Example 1 of the present invention.
副軸受１０ａの内面側には軸受ブッシュ１０ｂが圧入されてあり、その内面は回転軸６の外周面と摺動している。回転軸６に給油縦孔１２と連通して給油横孔２１が半径方向に穿設され、この給油横孔２１を介して給油縦孔１２と、回転軸６の外周に軸方向に伸びたジャーナル給油溝２２と連通して設けられている。ジャーナル給油溝２２の上方は軸受ブッシュ１０ｂより伸びて低圧空間２ｃへ開口して、下方は軸受ブッシュ１０ｂ内で閉じている。 A bearing bush 10 b is press-fitted on the inner surface side of the auxiliary bearing 10 a, and the inner surface slides on the outer peripheral surface of the rotating shaft 6. An oil supply horizontal hole 21 communicates with the rotary shaft 6 in the radial direction so as to communicate with the oil supply vertical hole 12, and the journal extending in the axial direction to the oil supply vertical hole 12 and the outer periphery of the rotary shaft 6 through the oil supply horizontal hole 21. It is provided in communication with the oil supply groove 22. The upper part of the journal oil supply groove 22 extends from the bearing bush 10b and opens to the low pressure space 2c, and the lower part is closed in the bearing bush 10b.
したがって、密閉容器２の底部の貯油部２ａの潤滑油８は、スクロール型圧縮機１の運転中は回転軸６の回転により、油吸込管９の下方より給油縦孔１２上方へ遠心ポンプの原理により吸上げられ、給油縦孔１２を流れる潤滑油８の一部が、図中の矢印ａ、ｂ、ｃで示すように給油縦孔１２から給油横孔２１を通り（矢印ｂ）ジャーナル給油溝２２を上方に流れて軸受ブッシュ１０ｂの摺動部を潤滑した後、ジャーナル給油溝２２上方より排出（矢印ｃ）された後、底部の貯油部２ａに戻るようになっている。 Therefore, the lubricating oil 8 in the oil storage section 2a at the bottom of the closed container 2 is driven by the rotation of the rotary shaft 6 during the operation of the scroll compressor 1 from the bottom of the oil suction pipe 9 to the top of the oil supply vertical hole 12 and the principle of the centrifugal pump. As shown by arrows a, b, c in the figure, part of the lubricating oil 8 sucked up by the oil supply vertical hole 12 passes from the oil supply vertical hole 12 through the oil supply horizontal hole 21 (arrow b), and the journal oil supply groove After flowing through 22 and lubricating the sliding portion of the bearing bush 10b, it is discharged from above the journal oil supply groove 22 (arrow c) and then returned to the oil storage portion 2a at the bottom.
一方、副軸受１０ａ内側の軸受ブッシュ１０ｂの下方には、スラスト軸受１０ｄの周囲に通じた油溜空間２３が設けられており、油溜空間２３は回転軸６の半径方向に穿設された給油横孔２５を介して給油縦孔１２と連通されている。スラスト軸受１０ｄには、回転軸６とスラスト軸受１０ｄの摺動面に開口して回転軸６の半径方向に伸びたスラスト給油溝２６が、油溜空間２３連通して設けられており、油吸込管９とスラスト軸受１０ｄの間の油排出通路２７を介して低圧空間２ｃへ連通している。 On the other hand, an oil reservoir space 23 is provided below the bearing bush 10b inside the auxiliary bearing 10a. The oil reservoir space 23 communicates with the periphery of the thrust bearing 10d. The oil reservoir space 23 is lubricated in the radial direction of the rotary shaft 6. The oil supply vertical hole 12 communicates with the horizontal hole 25. The thrust bearing 10d is provided with a thrust oil supply groove 26 that opens in the sliding surface of the rotary shaft 6 and the thrust bearing 10d and extends in the radial direction of the rotary shaft 6 in communication with the oil reservoir space 23. It communicates with the low pressure space 2c through an oil discharge passage 27 between the pipe 9 and the thrust bearing 10d.
したがって、貯油部２ａから給油縦孔１２を流れる潤滑油８の一部が、図中の矢印ａ、ｄ、ｅで示すように、給油横孔２５を通り（矢印ｄ）油溜空間２３に流れ込み、スラスト給油溝２６の中を回転軸６の中心方向に流れながらスラスト軸受１０ｄの摺動部を潤滑した後、油排出通路２７を通じて貯油部２ａへ排出（矢印ｅ）されるようになっている。 Accordingly, a part of the lubricating oil 8 flowing from the oil storage portion 2a through the oil supply vertical hole 12 flows into the oil reservoir space 23 through the oil supply horizontal hole 25 (arrow d) as indicated by arrows a, d and e in the figure. The sliding portion of the thrust bearing 10d is lubricated while flowing in the thrust oil supply groove 26 toward the center of the rotary shaft 6, and then discharged to the oil storage portion 2a through the oil discharge passage 27 (arrow e). .
参考例１によれば、スラスト軸受１０ｄの摺動面に確実に潤滑油８が供給されるため、スラスト軸受１０ｄと回転軸６のスラスト摺動部の良好な潤滑状態が確保され、スラスト摺動損失を抑えることができる。併せて、スラスト軸受１０ｄと回転軸６のスラスト摺動部の摩耗や焼付き等の発生も抑制することできる。したがって、効率の向上と信頼性の向上を実現できる容積型圧縮機を提供できる。 According to the reference example 1 , since the lubricating oil 8 is reliably supplied to the sliding surface of the thrust bearing 10d, a good lubrication state between the thrust bearing 10d and the thrust sliding portion of the rotary shaft 6 is ensured, and the thrust sliding is performed. Loss can be suppressed. In addition, the occurrence of wear or seizure of the thrust sliding portion of the thrust bearing 10d and the rotating shaft 6 can be suppressed. Therefore, it is possible to provide a positive displacement compressor capable of improving efficiency and improving reliability.
尚、スラスト給油溝２６は、回転軸６の端面のスラスト摺動面側に設ける事もできるが、スラスト給油溝２６内の潤滑油８の流れ方向と逆方向に遠心力が作用するため、図１の形態のようにスラスト軸受１０ｄの摺動面側に設けた方が、給油量を確保しやすく、より
確実に安定してスラスト摺動面に給油が可能となる。
Although the thrust oil supply groove 26 can be provided on the thrust sliding surface side of the end face of the rotary shaft 6, a centrifugal force acts in a direction opposite to the flow direction of the lubricating oil 8 in the thrust oil supply groove 26. When the thrust bearing 10d is provided on the sliding surface side as in the first embodiment, it is easier to secure the amount of oil supply, and the thrust sliding surface can be more reliably and stably supplied.
（実施の形態１）
次に、本発明の実施の形態１について、図２を用いて説明する。
( Embodiment 1 )
Next, Embodiment 1 of the present invention will be described with reference to FIG.
図２は、本発明の実施の形態１における、第２支持フレームの近傍の縦断面図を示すものである。 FIG. 2 is a longitudinal sectional view of the vicinity of the second support frame in the first embodiment of the present invention.
実施の形態１と参考例１との違いは、回転軸６の外周に軸方向に伸び設けられたジャーナル給油溝２８の下方は軸受ブッシュ１０ｂより伸びて油溜空間２３に連通し、ジャーナル給油溝２８の上方が軸受ブッシュ１０ｂ内で閉じている点である。また、油溜空間２３と給油縦孔１２を連通している給油横孔２５（参考例１参照）を備えていない点である。 The difference between the first embodiment and the reference example 1 is that the journal oil groove 28 extending in the axial direction on the outer periphery of the rotary shaft 6 extends from the bearing bush 10b and communicates with the oil reservoir space 23, so that the journal oil groove The upper side of 28 is a point closed in the bearing bush 10b. Further, the oil supply lateral hole 25 (see Reference Example 1 ) that communicates the oil reservoir space 23 with the oil supply vertical hole 12 is not provided.
この給油構成は、密閉容器２の底部の貯油部２ａの潤滑油８は、図２中の矢印ａ、ｂ、ｃで示すように、スクロール型圧縮機１の運転中は回転軸６の回転により、油吸込管９の下方より給油縦孔１２を介して上方へ遠心ポンプの原理により吸上げられる（矢印ａ）。その給油縦孔１２を流れる潤滑油８の一部が、給油縦孔１２から給油横孔２１を通り（矢印ｂ）、ジャーナル給油溝２２を下方に流れて軸受ブッシュ１０ｂの摺動部を潤滑した後、油溜空間２３に流れ込み、スラスト給油溝２６の中を回転軸６の中心方向に流れながらスラスト軸受１０ｄの摺動部を潤滑した後、油排出通路２７を通じて貯油部２ａへ排出（矢印ｃ）されるようになっている。 In this oil supply configuration, the lubricating oil 8 in the oil storage portion 2a at the bottom of the sealed container 2 is caused by the rotation of the rotary shaft 6 during the operation of the scroll compressor 1, as indicated by arrows a, b and c in FIG. Then, the oil is sucked up from the lower side of the oil suction pipe 9 through the oil supply vertical hole 12 by the principle of a centrifugal pump (arrow a). Part of the lubricating oil 8 flowing through the oil supply vertical hole 12 passes through the oil supply horizontal hole 21 (arrow b) from the oil supply vertical hole 12 and flows downward in the journal oil supply groove 22 to lubricate the sliding portion of the bearing bush 10b. Thereafter, the oil flows into the oil reservoir space 23, lubricates the sliding portion of the thrust bearing 10d while flowing in the thrust oil supply groove 26 toward the center of the rotating shaft 6, and then discharges it to the oil storage portion 2a through the oil discharge passage 27 (arrow c). ).
実施の形態１によれば、給油縦孔１２から軸受ブッシュ１０ｂとスラスト軸受１０ｄへの給油経路が一経路となっているため、別経路となっている図１の参考例１の場合よりも、給油縦孔１２から軸受ブッシュ１０ｂとスラスト軸受１０ｄへ流れる給油量を多く確保できる。そして、軸受ブッシュ１０ｂとスラスト軸受１０ｄの摺動面に確実に潤滑油８が供給されるため、軸受ブッシュ１０ｂとスラスト軸受１０ｄの各々との回転軸６の摺動部で良好な潤滑状態が確保され、摺動部の摺動損失を抑えることができる。併せて、スラスト軸受１０ｄと回転軸６のスラスト摺動部の摩耗や焼付き等の発生も抑制することできる。したがって、図１の参考例１よりもさらに効率の向上と信頼性の向上を実現できる容積型圧縮機を提供できる。 According to the first embodiment, since the oil supply path from the oil supply vertical hole 12 to the bearing bush 10b and the thrust bearing 10d is one path, compared to the case of the reference example 1 in FIG. A large amount of oil flowing from the oil supply vertical hole 12 to the bearing bush 10b and the thrust bearing 10d can be secured. Since the lubricating oil 8 is reliably supplied to the sliding surfaces of the bearing bush 10b and the thrust bearing 10d, a good lubricating state is ensured at the sliding portion of the rotating shaft 6 between the bearing bush 10b and the thrust bearing 10d. Thus, the sliding loss of the sliding portion can be suppressed. In addition, the occurrence of wear or seizure of the thrust sliding portion of the thrust bearing 10d and the rotating shaft 6 can be suppressed. Therefore, it is possible to provide a positive displacement compressor that can realize further improvement in efficiency and reliability as compared with Reference Example 1 in FIG.
（参考例２）
次に、本発明の参考例２について、図３を用いて説明する。図３は、本発明の参考例２における、第２支持フレームの近傍の縦断面図を示すものである。
( Reference Example 2 )
Next, Reference Example 2 of the present invention will be described with reference to FIG. FIG. 3 is a longitudinal sectional view in the vicinity of the second support frame in Reference Example 2 of the present invention.
参考例１、実施の形態１との違いは、スラスト軸受１０ｄが軸受ブッシュ１０ｂの上方にあり回転軸６に設けた段付部３１の端面を、スラスト軸受１０ｄでスラスト支持摺動する点である。 Reference Example 1 is different from Embodiment 1 in that the thrust bearing 10d is above the bearing bush 10b and the end surface of the stepped portion 31 provided on the rotating shaft 6 is thrust-supported and slid by the thrust bearing 10d. .
回転軸６の外周に軸方向に伸び設けられたジャーナル給油溝２９は、その上方においては軸受ブッシュ１０ｂより伸びてスラスト給油溝３０に連通し、その下方においては軸受ブッシュ１０ｂ内で閉じている。またスラスト給油溝３０は、回転軸６の段付部３１側にスラスト摺動面に開口して半径方向に向かって設けられ、ジャーナル給油溝２９と連通されている。 The journal oil supply groove 29 extending in the axial direction on the outer periphery of the rotary shaft 6 extends from the bearing bush 10b in the upper part thereof and communicates with the thrust oil supply groove 30 and is closed in the bearing bush 10b in the lower part thereof. The thrust oil supply groove 30 is provided on the stepped portion 31 side of the rotating shaft 6 so as to open in a thrust sliding surface in the radial direction and communicate with the journal oil supply groove 29.
そして、密閉容器２の底部の貯油部２ａの潤滑油８は、図３中の矢印ａ、ｂ、ｃで示すように、まずスクロール型圧縮機１の回転軸６の回転により、油吸込管９の下方より給油縦孔１２の上方へ遠心ポンプの原理により吸上げられる（矢印ａ）。 Then, the lubricating oil 8 in the oil storage part 2a at the bottom of the closed container 2 is, as indicated by arrows a, b and c in FIG. Is sucked up from below the oil supply vertical hole 12 by the principle of a centrifugal pump (arrow a).
その給油縦孔１２を流れる潤滑油８の一部が、給油縦孔１２から給油横孔２１を通り（矢印ｂ）、ジャーナル給油溝２９を上方に流れて軸受ブッシュ１０ｂの摺動部を潤滑した後、スラスト給油溝３０の中を回転軸６の中心から外周方向に流れながらスラスト軸受１０ｄの摺動部を潤滑した後、スラスト給油溝３０の出口から貯油部２ａへ排出（矢印ｃ）されるようになっている。 Part of the lubricating oil 8 flowing through the oil supply vertical hole 12 passes from the oil supply vertical hole 12 through the oil supply horizontal hole 21 (arrow b) and flows upward in the journal oil supply groove 29 to lubricate the sliding portion of the bearing bush 10b. Thereafter, the sliding portion of the thrust bearing 10d is lubricated while flowing in the thrust oil supply groove 30 from the center of the rotating shaft 6 toward the outer periphery, and then discharged from the outlet of the thrust oil supply groove 30 to the oil storage portion 2a (arrow c). It is like that.
参考例２によれば、スラスト軸受１０ｄが軸受ブッシュ１０ｂより上方で回転軸６の段付部３１の端面に設けられた場合も、給油縦孔１２から軸受ブッシュ１０ｂとスラスト軸受１０ｄへの給油経路が一経路に構成できるため、別経路となっている図１の参考例１の場合よりも、給油縦孔１２から軸受ブッシュ１０ｂとスラスト軸受１０ｄへ流れる給油量を多く確保できる。また、スラスト給油溝３０を回転軸６の段付部３１のスラスト端面側の摺動面側に設けたことで、スラスト給油溝３０内の潤滑油８の流れ方向と同方向に遠心力が作用し、遠心ポンプの作用によりスラスト給油溝３０を流れる給油量を確保しやすく、より確実に安定してスラスト摺動面に給油が可能となる。 According to the reference example 2 , even when the thrust bearing 10d is provided on the end surface of the stepped portion 31 of the rotating shaft 6 above the bearing bush 10b, the oil supply path from the oil supply vertical hole 12 to the bearing bush 10b and the thrust bearing 10d. Therefore, it is possible to secure a larger amount of oil flowing from the oil supply vertical hole 12 to the bearing bush 10b and the thrust bearing 10d than in the case of the reference example 1 of FIG. Further, since the thrust oil supply groove 30 is provided on the sliding surface side of the thrust end face side of the stepped portion 31 of the rotating shaft 6, centrifugal force acts in the same direction as the flow direction of the lubricating oil 8 in the thrust oil supply groove 30. In addition, it is easy to ensure the amount of oil flowing through the thrust oil supply groove 30 by the action of the centrifugal pump, and it is possible to supply oil to the thrust sliding surface more reliably and stably.
すなわち、軸受ブッシュ１０ｂとスラスト軸受１０ｄの摺動面に確実に潤滑油８が供給されるため、軸受ブッシュ１０ｂとスラスト軸受１０ｄの各々との回転軸６の摺動部で良好な潤滑状態が確保され、摺動部の摺動損失を抑えることができる。併せて、スラスト軸受１０ｄと回転軸６のスラスト摺動部の摩耗や焼付き等の発生も抑制することできる。したがって、さらに効率の向上と信頼性の向上を実現できる容積型圧縮機を提供できる。 That is, since the lubricating oil 8 is reliably supplied to the sliding surfaces of the bearing bush 10b and the thrust bearing 10d, a good lubricating state is secured at the sliding portion of the rotating shaft 6 between the bearing bush 10b and the thrust bearing 10d. Thus, the sliding loss of the sliding portion can be suppressed. In addition, the occurrence of wear or seizure of the thrust sliding portion of the thrust bearing 10d and the rotating shaft 6 can be suppressed. Therefore, it is possible to provide a positive displacement compressor that can further improve efficiency and reliability.
尚、半径方向に伸びたスラスト給油溝３０は、等幅の直線状に限らず、放射状、スパイラル状、ステップ状等でも、前記同様に効果を得られることはいうまでもない。特に、スパイラル状のスラスト給油溝３０を設ける場合は、渦方向を回転軸６の回転に対し正逆を選定することで、スラスト給油溝３０内の潤滑油８の流れと同方向に粘性力を作用させることで給油量をより確保することができる。 Needless to say, the thrust lubrication groove 30 extending in the radial direction is not limited to a straight line having an equal width, but can be obtained in the same manner as described above, even in a radial shape, a spiral shape, a step shape, and the like. In particular, when the spiral thrust oil supply groove 30 is provided, the viscous force is applied in the same direction as the flow of the lubricating oil 8 in the thrust oil supply groove 30 by selecting the vortex direction to be normal or reverse with respect to the rotation of the rotary shaft 6. By making it act, the amount of oil supply can be secured more.
例えば図３の場合は、摺動面側から見た渦巻きの回転方向（中心から外側に向かう回転方向）と回転軸６の回転方向を、逆方向となるように渦巻状のスラスト給油溝３０を設けることで、外周方向に潤滑油を流す方向に粘性力を作用させ、給油量をより確保することができる。 For example, in the case of FIG. 3, the spiral thrust oil supply groove 30 is formed so that the rotational direction of the spiral viewed from the sliding surface side (the rotational direction from the center toward the outside) and the rotational direction of the rotary shaft 6 are opposite. By providing, a viscous force can be applied in the direction in which the lubricating oil flows in the outer peripheral direction, and the amount of oil supply can be further ensured.
一方の図１の場合は、摺動面側から見た渦巻きの回転方向（渦中心から外側に向かう回転方向）と回転軸６の回転方向を、同方向となるように渦巻状のスラスト給油溝３０を設けることで、潤滑油が流れる回転軸６の中心方向に粘性力を作用させ、給油量をより確保することができる。 On the other hand, in the case of FIG. 1, a spiral thrust oil supply groove is formed so that the rotation direction of the spiral viewed from the sliding surface side (the rotation direction toward the outside from the center of the spiral) and the rotation direction of the rotary shaft 6 are the same. By providing 30, a viscous force can be applied in the central direction of the rotating shaft 6 through which the lubricating oil flows, and the amount of oil supply can be further ensured.
尚、図３のスラスト給油溝３０は、スラスト軸受１０ｄの端面のスラスト摺動面側に設けても、前記同様に効果を得られることはいうまでもない。 It is needless to say that the same effect as described above can be obtained even if the thrust oil supply groove 30 in FIG. 3 is provided on the thrust sliding surface side of the end face of the thrust bearing 10d.
以上のように、本発明にかかる容積型圧縮機は、回転軸の軸方向支持するスラスト軸受の潤滑性能を高め効率も向上、信頼性を向上ができるため、スクロール型圧縮機に限らず、広く空調・冷凍機等の容積型圧縮機にも適用できる。 As described above, the positive displacement compressor according to the present invention can improve the lubrication performance of the thrust bearing that supports the axial direction of the rotating shaft, improve the efficiency, and improve the reliability. It can also be applied to positive displacement compressors such as air conditioners and refrigerators.
１ スクロール型圧縮機
２ 密閉容器
２ａ 貯油部
２ｂ 高圧空間（吐出圧）
２ｃ 低圧空間（吸入圧）
３ 電動要素
３ａ ステータ
３ｂ ロータ
４ スクロール圧縮要素
４ａ 揺動スクロール
４ｂ ラップ
５ａ 固定スクロール
５ｂ ラップ
６ 回転軸
７ 第１支持フレーム
８ 潤滑油
９ 油吸込管
１０ 第２支持フレーム
１０ａ 副軸受
１０ｂ 軸受ブッシュ
１０ｃ フレーム支持部
１０ｄ スラスト軸受（スラストプレート）
１２ 給油縦孔
１３ 偏心軸
１４ 偏心軸受部
１５ 圧縮室
１６ 吸入管
１７ 吐出ポート
１８ 吐出管
２１ 給油横孔
２２ ジャーナル給油溝
２３ 油溜空間
２４ 油排出孔
２５ 給油横孔
２６、３０ スラスト給油溝
２８、２９ ジャーナル給油溝
２７ 油排出通路
３１ 段付部
DESCRIPTION OF SYMBOLS 1 Scroll type compressor 2 Airtight container 2a Oil storage part 2b High pressure space (discharge pressure)
2c Low pressure space (suction pressure)
DESCRIPTION OF SYMBOLS 3 Electric element 3a Stator 3b Rotor 4 Scroll compression element 4a Rocking scroll 4b Wrap 5a Fixed scroll 5b Wrap 6 Rotating shaft 7 First support frame 8 Lubricating oil 9 Oil suction pipe 10 2nd support frame 10a Sub bearing 10b Bearing bush 10c Frame Supporting part 10d Thrust bearing (thrust plate)
DESCRIPTION OF SYMBOLS 12 Oil supply vertical hole 13 Eccentric shaft 14 Eccentric bearing part 15 Compression chamber 16 Intake pipe 17 Discharge port 18 Discharge pipe 21 Oil supply horizontal hole 22 Journal oil supply groove 23 Oil reservoir space 24 Oil discharge hole 25 Oil supply horizontal hole 26, 30 Thrust oil supply groove 28 , 29 Journal oil groove 27 Oil discharge passage 31 Stepped part
Claims (1)
前記電動要素によって回転駆動される回転軸と、
前記電動要素の上方に設置され前記回転軸を介して駆動される圧縮要素と、
前記電動要素と前記圧縮要素の間に設置され前記密閉容器内に固着されて回転軸を回転支持する第１支持フレームと、
前記密閉容器内に固着されて前記回転軸の下方端部を回転支持する第２支持フレームと、前記密閉容器の底部に潤滑油の貯油部と、を備え、
前記回転軸の下方端面から前記回転軸を貫通して設けられた給油縦孔を介して前記潤滑油を各摺動部に送る容積型圧縮機であって、
前記第２支持フレームは、前記回転軸のラジアル力を受けるジャーナル軸受と、スラスト力を受けるスラスト軸受と、から構成され、
前記回転軸の外周に設けられ、前記回転軸の軸方向に伸びたジャーナル給油通路と、前記スラスト軸受に設けられ、前記回転軸の半径方向に伸びたスラスト給油通路と、を有し、前記スラスト給油通路は、前記回転軸と前記スラスト軸受の摺動面に開口し、油排出通路を介して前記貯油部と連通しており、
前記貯油部の潤滑油は、前記給油縦孔から前記回転軸に設けられた半径方向の給油横孔を経て、前記ジャーナル軸受の摺動面に供給され、さらに、前記ジャーナル軸受の摺動面に供給された前記潤滑油は、前記ジャーナル給油通路を経て、前記スラスト軸受周辺の油溜空間に供給され、さらに、前記油溜空間に供給された前記潤滑油は、前記回転軸の半径方向に伸びたスラスト給油通路によって、前記回転軸と前記スラスト軸受の摺動面に供給されることを特徴とする容積型圧縮機。 An electric element provided in a sealed container;
A rotating shaft that is rotationally driven by the electric element;
A compression element installed above the electric element and driven via the rotating shaft;
A first support frame that is installed between the electric element and the compression element and is fixed in the sealed container to rotatably support the rotating shaft;
Wherein comprises a second support frame is fixed in a sealed container for rotatably supporting the lower end of the rotary shaft, and a lubricant storage portion of the lubricating oil in a bottom portion of the closed container,
A positive displacement compressor that sends the lubricating oil to each sliding part through an oil supply vertical hole penetrating the rotary shaft from the lower end surface of the rotary shaft,
It said second support frame includes a journal bearing which receives a radial force of said rotary shaft, and a thrust bearing for receiving the scan last power and a,
A journal oil supply passage provided on an outer periphery of the rotary shaft and extending in an axial direction of the rotary shaft; and a thrust oil supply passage provided in the thrust bearing and extending in a radial direction of the rotary shaft. The oil supply passage opens to the sliding surface of the rotary shaft and the thrust bearing, and communicates with the oil storage portion via an oil discharge passage.
Lubricating oil in the oil storage section is supplied from the oil supply vertical hole to the slide surface of the journal bearing through a radial oil supply horizontal hole provided in the rotary shaft, and further to the slide surface of the journal bearing. The supplied lubricating oil is supplied to the oil reservoir space around the thrust bearing through the journal oil supply passage, and the lubricating oil supplied to the oil reservoir space extends in the radial direction of the rotating shaft. The positive displacement compressor is supplied to the sliding surface of the rotary shaft and the thrust bearing through a thrust oil supply passage .
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013025189A JP6134903B2 (en) | 2013-02-13 | 2013-02-13 | Positive displacement compressor |
| CN201310388424.5A CN103982437B (en) | 2013-02-13 | 2013-08-30 | Displacement type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| JP2013025189A JP6134903B2 (en) | 2013-02-13 | 2013-02-13 | Positive displacement compressor |
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| JP2014152747A JP2014152747A (en) | 2014-08-25 |
| JP6134903B2 true JP6134903B2 (en) | 2017-05-31 |
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| Application Number | Title | Priority Date | Filing Date |
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| JP2013025189A Active JP6134903B2 (en) | 2013-02-13 | 2013-02-13 | Positive displacement compressor |
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| CN (1) | CN103982437B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104763631A (en) * | 2015-04-02 | 2015-07-08 | 合肥通用机械研究院 | Vortex refrigeration compressor with sliding and rolling friction pair bent axle supporting structure |
| US10047799B2 (en) * | 2015-04-10 | 2018-08-14 | Emerson Climate Technologies, Inc. | Scroll compressor lower bearing |
| CN105485017A (en) * | 2016-01-26 | 2016-04-13 | 广东美的暖通设备有限公司 | Mounting structure of thrust bearing and vortex-compressor |
| JP6748874B2 (en) * | 2017-01-27 | 2020-09-02 | パナソニックＩｐマネジメント株式会社 | Hermetic compressor |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3830341A (en) * | 1972-11-24 | 1974-08-20 | Carrier Corp | Lubrication system for a motor compressor unit |
| US4131396A (en) * | 1977-04-07 | 1978-12-26 | Sundstrand Corporation | Hermetic compressor lubrication system with two-stage oil pump |
| JPS62113879A (en) * | 1985-11-11 | 1987-05-25 | Daikin Ind Ltd | Lubricating structure for scroll type fluid machine |
| US4767293A (en) * | 1986-08-22 | 1988-08-30 | Copeland Corporation | Scroll-type machine with axially compliant mounting |
| JPH04100088U (en) * | 1991-02-01 | 1992-08-28 | ||
| US5168960A (en) * | 1991-03-19 | 1992-12-08 | Bristol Compressors | Compressor crankshaft bearing cap and assembly |
| JPH11182473A (en) * | 1997-12-17 | 1999-07-06 | Sanyo Electric Co Ltd | Scroll compressor |
| JP2007170540A (en) * | 2005-12-21 | 2007-07-05 | Toyota Industries Corp | Gear meshing portion lubricating structure |
| CN101205922A (en) * | 2006-12-20 | 2008-06-25 | 乐金电子(天津)电器有限公司 | Thrust plate and cyclone compressor with the same |
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2013
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| Publication number | Publication date |
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| CN103982437A (en) | 2014-08-13 |
| JP2014152747A (en) | 2014-08-25 |
| CN103982437B (en) | 2016-08-31 |
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