JPH01301972A - Scroll type compressor - Google Patents
Scroll type compressorInfo
- Publication number
- JPH01301972A JPH01301972A JP13151188A JP13151188A JPH01301972A JP H01301972 A JPH01301972 A JP H01301972A JP 13151188 A JP13151188 A JP 13151188A JP 13151188 A JP13151188 A JP 13151188A JP H01301972 A JPH01301972 A JP H01301972A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- space
- hole
- thrust receiver
- supplied
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003921 oil Substances 0.000 claims description 124
- 239000010687 lubricating oil Substances 0.000 claims description 19
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 238000000034 method Methods 0.000 abstract description 4
- 230000001955 cumulated effect Effects 0.000 abstract 1
- 230000007423 decrease Effects 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
（産業上の利用分野）
本発明は、スラスト受、オルダムリングへの給油構造お
よび給油後の油戻し構造を改良したスクロール形圧縮機
に関する。DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Field of Application) The present invention relates to a scroll compressor in which a thrust receiver, an oil supply structure to an Oldham ring, and an oil return structure after oil supply are improved.
（従来の技術）
空気調和機などに用いられる圧縮機としてスクロール形
圧縮機が知られている。(Prior Art) Scroll compressors are known as compressors used in air conditioners and the like.
従来のスクロール形圧縮機においては、フレーム、旋回
スクロールおよびスラスト受によって形成される第１の
空間部に供給された潤滑油は全てスラスト受のスラスト
面に形成された給油溝を経てこのスラスト受の外周部、
つまりオルダムリングが内装されている第２の空間部に
給油されたのち、この第２の空間部からフレームの外周
部に通じる油戻し孔を経て圧縮機底部の油溜部に戻すも
のが一般的であった。In a conventional scroll compressor, all the lubricating oil supplied to the first space formed by the frame, the orbiting scroll, and the thrust receiver passes through the oil supply groove formed on the thrust surface of the thrust receiver. The outer periphery,
In other words, after oil is supplied to the second space where the Oldham ring is installed, it is generally returned to the oil sump at the bottom of the compressor through an oil return hole that leads from the second space to the outer periphery of the frame. Met.
しかしながら、このような構成では第１の空間部に供給
された潤滑油の全てが第２の空間部に給油されるため、
この第２の空間部への給油量が多すぎる欠点があった。However, in such a configuration, all of the lubricating oil supplied to the first space is supplied to the second space, so
There was a drawback that the amount of oil supplied to this second space was too large.
そのため、固定スクロールと旋回スクロールとの間の微
小隙間から圧縮空間に吸込まれ、被圧縮ガスとともに吐
出されて再吸入される吐油量が増大し、性能、信頼性の
低下を招いていた。また、圧縮機内の油量が減少し、ス
ラスト受やオルダムリングの給油不足を招いていた。As a result, the amount of oil that is sucked into the compression space through the small gap between the fixed scroll and the orbiting scroll, discharged together with the compressed gas, and then sucked back in increases, resulting in a decrease in performance and reliability. Additionally, the amount of oil in the compressor decreased, leading to insufficient oil supply to the thrust receiver and Oldham ring.
そこで、前記第１の空間部に供給された潤滑油の一部を
前記経路で油溜部に戻し、残りの油を第１の空間部から
フレームを貫通して電動機部側に穿設された油戻し孔を
経て油溜部に直接戻すものがあった。Therefore, a part of the lubricating oil supplied to the first space is returned to the oil sump through the path, and the remaining oil is transferred from the first space to a hole drilled in the motor section side through the frame. Some oil was returned directly to the oil sump via an oil return hole.
（発明が解決しようとする課題）
ところが、前記後者の構成では残りの潤滑油が第１の空
間部から油戻し孔を経て油溜部に直接戻されるので、ス
ラスト受およびオルダムリングへの給油量が少なくなり
、この場合においてもスラスト受やオルダムリングの給
油不足を発生していた。(Problem to be Solved by the Invention) However, in the latter configuration, the remaining lubricating oil is directly returned from the first space through the oil return hole to the oil sump, so the amount of oil supplied to the thrust receiver and Oldham ring is reduced. In this case, the thrust receiver and Oldham ring were also under-lubricated.
また、前記前者および後者のいずれの場合でも、圧縮機
の軸方向中途部に設けられたフレームの油戻し孔から圧
縮機底部の油溜部に潤滑油を流下させていたため、油の
流下間隔が長く、よって流下油が圧縮機内の被圧縮ガス
の流れや電動機部のロータの゛回転に影響を受は易かっ
た。そのため、これが原因で油が被圧縮ガスとともに飛
沫化される問題があった。In addition, in both the former and latter cases, the lubricating oil was allowed to flow down from the oil return hole in the frame provided midway in the axial direction of the compressor to the oil sump at the bottom of the compressor, so the interval between oil flows was limited. Because of the long length, the flowing oil was easily affected by the flow of compressed gas in the compressor and the rotation of the rotor of the electric motor. Therefore, this caused a problem in that the oil was turned into droplets together with the compressed gas.
本発明は前記事情に着目してなされたもので、その目的
とするところは、スラスト受やオルダムリングの給油不
足゛を防止でき、しかも被圧縮ガスとともに飛沫化され
る吐油量を極少とすることができるスクロール形圧縮機
を提供することにある。The present invention has been made in view of the above-mentioned circumstances, and its purpose is to prevent insufficient oil supply to the thrust receiver and Oldham ring, and to minimize the amount of oil discharged into droplets together with the compressed gas. The object of the present invention is to provide a scroll compressor that can
（課題を解決するための手段）
本発明は、スラスト受に、フレーム、旋回スクロールお
よびスラスト受によって形成される第１の空間部に供給
された潤滑油の一部をオルダムングが内装されている第
２の空間部に導く給油通路を設けるとともに、フレーム
およびステータに、前記第２の空間部を経た潤滑油およ
びスラスト受を経た残りの潤滑油を圧縮機底部の油溜部
に戻す油戻し通路を設けたものである。(Means for Solving the Problems) The present invention provides a thrust receiver with a part of lubricating oil supplied to a first space formed by a frame, an orbiting scroll, and a thrust receiver. An oil supply passage leading to the second space is provided, and an oil return passage is provided in the frame and stator to return the lubricating oil that has passed through the second space and the remaining lubricating oil that has passed through the thrust receiver to the oil sump at the bottom of the compressor. It was established.
（作用）
このような構成によれば、第１の空間部に供給された潤
滑油の全てがスラスト受に給油され、このスラスト受の
給油を終えた油の一部が第２の空間部に給油され、した
がってスラスト受には多量の給油ができるとともに、オ
ルダムリングには必要にして充分な量の給油ができる。(Function) According to such a configuration, all of the lubricating oil supplied to the first space is supplied to the thrust receiver, and part of the oil that has finished lubricating the thrust receiver is transferred to the second space. Therefore, the thrust receiver can be supplied with a large amount of oil, and the Oldham ring can be supplied with a necessary and sufficient amount of oil.
（実施例）
以下、本発明の一実施例について図面に基づき説明する
。(Example) Hereinafter, an example of the present invention will be described based on the drawings.
第１図は本発明におけるスクロール形圧縮機の要部を示
し、１はフレームである。このフレーム１の上部には圧
縮機部２、下部には電動機部３が設けられている。圧縮
機部２はフレーム１の上面に固定された固定スクロール
４と、この固定スクロール４の下部に固定スクロール４
との間に圧縮空間５を形成して偏心回転自在に設けられ
た旋回スクロール６とからなる。また、電動機部３はフ
レーム１の下面に固定されたステータ３ａと、このステ
ータ３ａ内に回転自在に設けられたロータ３ｂとからな
る。このロータ３ｂには回転軸７が一体に嵌挿されてお
り、この回転軸７の上部はフレーム１４の軸受部１ａに
回転自在に支持されている。さらに、回転軸７の上端に
は偏心部７ａが形成されており、この偏心部７ａは旋回
スクロール６の下面に設けられたボス部６ａに回転自在
に嵌合されている。また、偏心部７ａの下部にはバラン
サ８が設けられており、このバランサ８はフレーム１．
旋回スクロール６および後述するスラスト受９によって
形成される第１の空間部１ｏに内装されている。このバ
ランサ８の下面にはスラストリング１１が設けられてお
り、このスラストリング１１の上面には、第７図に示す
ように、ラジアル溝１２が９０″間隔で形成されている
。FIG. 1 shows the main parts of a scroll compressor according to the present invention, and 1 is a frame. A compressor part 2 is provided in the upper part of this frame 1, and an electric motor part 3 is provided in the lower part. The compressor section 2 includes a fixed scroll 4 fixed to the upper surface of the frame 1 and a fixed scroll 4 fixed to the lower part of the fixed scroll 4.
and an orbiting scroll 6 which is eccentrically rotatably provided with a compression space 5 formed therebetween. Further, the electric motor section 3 includes a stator 3a fixed to the lower surface of the frame 1, and a rotor 3b rotatably provided within the stator 3a. A rotary shaft 7 is integrally fitted into the rotor 3b, and the upper portion of the rotary shaft 7 is rotatably supported by the bearing portion 1a of the frame 14. Further, an eccentric portion 7a is formed at the upper end of the rotating shaft 7, and this eccentric portion 7a is rotatably fitted into a boss portion 6a provided on the lower surface of the orbiting scroll 6. Further, a balancer 8 is provided at the lower part of the eccentric portion 7a, and this balancer 8 is connected to the frame 1.
It is housed in a first space 1o formed by the orbiting scroll 6 and a thrust receiver 9, which will be described later. A thrust ring 11 is provided on the lower surface of the balancer 8, and radial grooves 12 are formed at 90'' intervals on the upper surface of the thrust ring 11, as shown in FIG.
前記旋回スクロール６とフレーム１との間にはスラスト
受９が設けられており、このスラスト受９は圧縮空間５
での被圧縮ガスの圧縮中に旋回スクロール６に作用する
スラスト荷重を受けるようになっている。また、このス
ラスト受９の外周部に位置する第２の空間部１３にはオ
ルダムリング１４が内装されており、このオルダムリン
グ１４は旋回スクロール６の下面およびフレーム１の上
面に形成されたオルダム溝１５．１６に嵌合され、旋回
スクロール６の自転を防止するようになっている。A thrust receiver 9 is provided between the orbiting scroll 6 and the frame 1, and this thrust receiver 9 is connected to the compression space 5.
The orbiting scroll 6 receives a thrust load acting on the orbiting scroll 6 during compression of the compressed gas. In addition, an Oldham ring 14 is installed in a second space 13 located on the outer periphery of the thrust receiver 9. 15 and 16 to prevent rotation of the orbiting scroll 6.
前記回転軸７には吸込通路１７が設けられている。つま
り、回転軸７の下端には給油ポンプ１８が設けられてお
り、この給油ポンプ１８は圧縮機底部の油溜部１９に貯
留された潤滑油Ｏ中に浸漬されている。この給油ポンプ
１８は円筒状をなしたポンプケース２０内にねじり成形
された羽根ポンプ２１を一体に嵌挿してなり、この羽根
ポンプ２１の下端一部はポンプケース２０の外周部に設
けられた係合口２２に係合されている。また、回転軸７
には第１の吸込縦孔２３、第２の吸込縦孔２４が軸方向
に沿って穿設されており、第１の吸込縦孔２３の下端は
回転軸７の下面に開口し、上端は吸込横孔２５を介して
フレーム１の軸受部１ａ下部と対向する回転軸７の外周
部に開口している。さらに、軸受部１ａと対向する回転
軸７の外周部には第１のスパイラル溝２６が形成されて
おり、この第１のスパイラル溝２６の下端は吸込横孔２
５の開口部と連通し、上端は第１の空間部１０に開口し
ている。一方、第２の吸込縦孔２４の下端は回転軸７の
下面に開口し、上端は旋回スクロール６のボス部６ａと
偏心部７ａとの間の第３の空間部３１に開口している。The rotating shaft 7 is provided with a suction passage 17 . That is, an oil supply pump 18 is provided at the lower end of the rotating shaft 7, and this oil supply pump 18 is immersed in lubricating oil O stored in an oil reservoir 19 at the bottom of the compressor. This oil supply pump 18 is constructed by integrally inserting a twist-molded vane pump 21 into a cylindrical pump case 20, and a part of the lower end of this vane pump 21 is connected to an engagement provided on the outer circumference of the pump case 20. It is engaged with the abutment 22. In addition, the rotating shaft 7
A first vertical suction hole 23 and a second vertical suction hole 24 are bored along the axial direction, the lower end of the first vertical suction hole 23 opens on the lower surface of the rotating shaft 7, and the upper end It opens through the horizontal suction hole 25 to the outer circumference of the rotating shaft 7 facing the lower part of the bearing portion 1a of the frame 1. Furthermore, a first spiral groove 26 is formed in the outer circumference of the rotating shaft 7 facing the bearing part 1a, and the lower end of this first spiral groove 26 is connected to the horizontal suction hole 2.
5, and its upper end opens into the first space 10. On the other hand, the lower end of the second vertical suction hole 24 opens to the lower surface of the rotating shaft 7, and the upper end opens to the third space 31 between the boss portion 6a and the eccentric portion 7a of the orbiting scroll 6.
また、ボス部６ａと対向する偏心部７ａの外周部には第
２のスパイラル溝２７が形成されており、この第２のス
パイラル溝２７の上端は第３の空間部３１に開口し、下
端は第１の空間部１０に開口している。さらに、第２の
吸込縦孔２４の上端開口部にはオイルストッパ２８が設
けられている。このオイルストッパ２８は第２の吸込縦
孔２４内に挿入される有底筒状部２９の上端に、偏心部
７ａの上面に係止される鍔部３０を設けてなり、第２の
吸込縦孔２４内を第３の空間部３１の上下隙間の範囲内
で可動に設けられている。また、有底筒状部２９の底面
には第１の絞り孔３２が設けられ、外周部には第２の絞
り孔３３が設けられている。Further, a second spiral groove 27 is formed in the outer peripheral part of the eccentric part 7a facing the boss part 6a, the upper end of this second spiral groove 27 opens into the third space part 31, and the lower end opens into the third space part 31. It opens into the first space 10. Furthermore, an oil stopper 28 is provided at the upper end opening of the second vertical suction hole 24 . This oil stopper 28 is provided with a flange 30 that is secured to the upper surface of the eccentric part 7a at the upper end of the bottomed cylindrical part 29 inserted into the second suction vertical hole 24. It is provided movably within the hole 24 within the range of the vertical gap of the third space 31. Further, a first throttle hole 32 is provided in the bottom surface of the bottomed cylindrical portion 29, and a second throttle hole 33 is provided in the outer peripheral portion.
また、前記スラスト受９には給油通路３４が設けられて
いる。すなわち、第２図ないし第５図に示すように、ス
ラスト受９のスラスト面９ａには給油溝３５が９０″間
隔で形成され、この給油溝３５の外周部にはこれと連通
する第１のリング状溝３６が周方向に沿って形成されて
いる。また、給油溝３５と第１のリング状溝３６との連
通部には給油縦孔３７が穿設されており、この給油縦孔
３７の中途部は給油横孔３８を介して前記第２の空間部
１３に開口し、下端はスラスト受９の下面に周方向に沿
って形成された第２のリング状溝３９と連通している。Further, the thrust receiver 9 is provided with an oil supply passage 34 . That is, as shown in FIGS. 2 to 5, oil supply grooves 35 are formed at 90" intervals on the thrust surface 9a of the thrust receiver 9, and first grooves communicating with the oil supply grooves 35 are formed on the outer periphery of the oil supply grooves 35. A ring-shaped groove 36 is formed along the circumferential direction.In addition, an oil supply vertical hole 37 is bored in the communication portion between the oil supply groove 35 and the first ring-shaped groove 36. The midway portion opens into the second space 13 through the horizontal oil supply hole 38, and the lower end communicates with a second ring-shaped groove 39 formed along the circumferential direction on the lower surface of the thrust receiver 9. .
さらに、前記フレーム１およびステータ３ａの鉄心部３
Ｃには油戻し通路４０が設けられている。すなわち、フ
レーム１には第１の油戻し縦孔４１、第２の油戻し縦孔
４２が複数穿設されており、第１の油戻し縦孔４１の上
端は前記スラスト受９の第２のリング状溝３９と対向連
通し、第２の油戻し縦孔４２の上端は前記第３の空間部
３１に開口している。また、これら第１および第２の油
戻し縦孔４１．４２の下端はフレーム１の外周部から内
方に向けて複数穿設された油戻し横孔４３の内方端と連
通し、この油戻し横孔４３の外方端はフレーム１の外周
部近傍に複数穿設された第３の油戻し縦孔４４の上端と
連通している。この第３の油戻し縦孔４４の下端はフレ
ーム１の下面に開口している。さらに、第６図に示すよ
うに、ステータ３ａの鉄心部３Ｃの外周部近傍には第４
の油戻し縦孔４５が複数穿設されており、この第４の油
戻し縦孔４５の上端はフレームｌの第３の油戻し縦孔４
４と連通し、下端は鉄心部３Ｃの下面に開口している。Further, the frame 1 and the iron core 3 of the stator 3a
An oil return passage 40 is provided at C. That is, a plurality of first oil return vertical holes 41 and second oil return vertical holes 42 are bored in the frame 1, and the upper end of the first oil return vertical hole 41 is connected to the second oil return vertical hole 42 of the thrust receiver 9. The upper end of the second oil return vertical hole 42, which faces and communicates with the ring-shaped groove 39, opens into the third space 31. The lower ends of the first and second oil return vertical holes 41, 42 communicate with the inner ends of a plurality of oil return horizontal holes 43, which are bored inward from the outer circumference of the frame 1. The outer end of the return horizontal hole 43 communicates with the upper end of a plurality of third oil return vertical holes 44 bored near the outer periphery of the frame 1 . The lower end of this third oil return vertical hole 44 opens on the lower surface of the frame 1. Furthermore, as shown in FIG. 6, a fourth
A plurality of oil return vertical holes 45 are bored, and the upper end of this fourth oil return vertical hole 45 is connected to the third oil return vertical hole 4 of the frame l.
4, and its lower end is open to the lower surface of the iron core portion 3C.
なお、油戻し横孔４３の開口部は盲栓４６によって閉塞
されている。Note that the opening of the oil return horizontal hole 43 is closed by a blind plug 46.
つぎに、前記の構成につきその作用を説明する。Next, the operation of the above structure will be explained.
まず、通常運転時に回転軸７が回転すると、給油ポンプ
１８の回転によるポンプ作用によって油溜部１９の潤滑
油Ｏが第１の吸込縦孔２３および第２の吸込縦孔２４に
流入する。第１の吸込縦孔２３に流入した油Ｏは吸込横
孔２５、第１のスパイラル溝２６を流れ、その過程でフ
レーム１の軸受部１ａと回転軸７との間の摺動部に給油
され、さらにスラストリング１１のラジアル溝１２を通
って第１の空間部１０に溜る。一方、第２の吸込縦孔２
４に流入した油Ｏはオイルストッパ２８を通って第３の
空間部３１に溜り、さらに第２のスパイラル溝２７を流
れ、その過程でボス部６ａと偏心部７ａとの間の摺動部
に給油される。さらに、第１の空間部１０に流れ、前記
第１の吸込縦孔２３を経由した油Ｏと合流する。この第
１の空間部１０に溜った油Ｏはバランサ８の回転により
加速されてスラスト受９の給油溝３５、第１のリング状
溝３６を流れ、その過程でスラスト面９ａに給油され、
さらに給油縦孔３７に流入する。そして、その一部が給
油横孔３８から第２の空間部１３に流入し、オルダムリ
ング１４に給油され、さらにフレーム１の第２の油戻し
縦孔４２、油戻し横孔４３に流れる。一方、給油縦孔３
７に導がれた残りの油Ｏは第２のリング状溝３９、第１
の油戻し縦孔４１を通って油戻し横孔４３に導がれ、前
記第２の空間部１３を経由した一部の油０と合流する。First, when the rotating shaft 7 rotates during normal operation, the lubricating oil O in the oil reservoir 19 flows into the first vertical suction hole 23 and the second vertical suction hole 24 due to the pumping action caused by the rotation of the oil supply pump 18. The oil O that has flowed into the first vertical suction hole 23 flows through the horizontal suction hole 25 and the first spiral groove 26, and in the process, oil is supplied to the sliding part between the bearing part 1a of the frame 1 and the rotating shaft 7. , further passes through the radial groove 12 of the thrust ring 11 and accumulates in the first space 10 . On the other hand, the second suction vertical hole 2
4 passes through the oil stopper 28 and accumulates in the third space 31, and further flows through the second spiral groove 27, and in the process, it flows into the sliding part between the boss part 6a and the eccentric part 7a. Refueled. Furthermore, it flows into the first space 10 and merges with the oil O that has passed through the first vertical suction hole 23 . The oil O accumulated in this first space 10 is accelerated by the rotation of the balancer 8 and flows through the oil supply groove 35 and the first ring-shaped groove 36 of the thrust receiver 9, and in the process, the thrust surface 9a is oiled.
Further, it flows into the oil supply vertical hole 37. Then, a part of the oil flows into the second space 13 from the horizontal oil supply hole 38, is supplied to the Oldham ring 14, and further flows into the second vertical oil return hole 42 and the horizontal oil return hole 43 of the frame 1. On the other hand, oil supply vertical hole 3
The remaining oil O led to the second ring-shaped groove 39 and the first
The oil is guided to the oil return horizontal hole 43 through the oil return vertical hole 41, and merges with a part of the oil 0 that has passed through the second space 13.
さらに、この油戻し横孔４３に流れた油Ｏは第３の油戻
し縦孔４４、鉄心部３ｃの第４の油戻し縦孔４５を通っ
て前記油溜部１９に戻される。Further, the oil O flowing into the horizontal oil return hole 43 is returned to the oil reservoir portion 19 through the third oil return vertical hole 44 and the fourth oil return vertical hole 45 of the iron core portion 3c.
なお、第２の吸込縦孔２４に流入した潤滑油Ｏがオイル
ストッパ２８を通過する際、回転軸７の低〜中回転数域
では、第８図に示すように、給油量が少ないために第１
の絞り孔３２の流通抵抗が小さく、よってオイルストッ
パ２８が下がった状態で開口面積の大きな上端開口４７
がら油０が吐出される。また、中〜高回転数域では、第
９図に示すように、給油量が増加するために第１の絞り
孔３２の流通抵抗が大きくなり、よってオイルストッパ
２８が上昇した状態で開口面積の小さな第２の絞り孔３
３から浦０が吐出される。したかって、回転軸７の低〜
中回転数域では第３の空間部３１への給油量が増加し、
中〜高回転数域では減少するようになっている。Note that when the lubricating oil O that has flowed into the second vertical suction hole 24 passes through the oil stopper 28, in the low to medium rotational speed range of the rotating shaft 7, as shown in FIG. 1st
The flow resistance of the throttle hole 32 is small, so when the oil stopper 28 is lowered, the upper end opening 47 has a large opening area.
Zero oil is discharged. In addition, in the medium to high rotational speed range, as shown in FIG. 9, as the amount of oil supplied increases, the flow resistance of the first throttle hole 32 increases, so that the opening area decreases when the oil stopper 28 is raised. Small second aperture hole 3
Ura 0 is discharged from 3. Therefore, the low level of the rotating shaft 7
In the medium rotation speed range, the amount of oil supplied to the third space 31 increases,
It is designed to decrease in the medium to high rotation speed range.
このような構成によれば、第１の空間部１０に供給され
た潤滑油０の全てがスラスト受９のスラスト面９ａに給
油され、このスラスト面９ａの給油を終えた油Ｏの一部
が第２の空間部１３に給油されるので、スラスト受９に
は多量の給油ができるとともに、オルダムリング１４に
は必要にして充分な量の給油ができる。したがって、固
定スクロール４と旋回スクロール６との間の微小隙間か
ら圧縮空間５に吸込まれ、被圧縮ガスとともに吐出され
て再吸入される吐油量を極少とすることができ、性能、
信頼性を向上することができる。According to such a configuration, all of the lubricating oil 0 supplied to the first space 10 is supplied to the thrust surface 9a of the thrust receiver 9, and a part of the oil O that has finished supplying the thrust surface 9a is Since the second space 13 is supplied with oil, the thrust receiver 9 can be supplied with a large amount of oil, and the Oldham ring 14 can be supplied with a necessary and sufficient amount of oil. Therefore, the amount of oil that is sucked into the compression space 5 through the minute gap between the fixed scroll 4 and the orbiting scroll 6, discharged together with the compressed gas, and re-suctioned can be minimized.
Reliability can be improved.
また、圧縮機内の油量の減少量を少なくでき、スラスト
受９やオルダムリング１４の給油不足を解消できる。さ
らに、圧縮機の軸方向下部に設けられたステータ３ａの
鉄心部３ｃに第４の油戻し縦孔４５を設け、この第４の
油戻し縦孔４５から圧縮機底部の油溜部１９に油Ｏを流
下させたので、油Ｏの流下間隔、つまり第４の油戻し縦
孔４５の下端から油溜部１９の油面までの間隔が短くな
り、よって流下油０が圧縮機内の被圧縮ガスの流れやロ
ータ３ｂの回転にほとんど影響されなくなる。Moreover, the decrease in the amount of oil in the compressor can be reduced, and the lack of oil supply in the thrust receiver 9 and the Oldham ring 14 can be solved. Furthermore, a fourth oil return vertical hole 45 is provided in the iron core 3c of the stator 3a provided at the lower part of the compressor in the axial direction, and oil is supplied from the fourth oil return vertical hole 45 to the oil sump 19 at the bottom of the compressor. Since the oil O is allowed to flow down, the interval between the oil O flows down, that is, the distance from the lower end of the fourth oil return vertical hole 45 to the oil surface of the oil sump 19 becomes shorter, so that the flowing oil 0 becomes the compressed gas in the compressor. It is almost unaffected by the flow of water and the rotation of the rotor 3b.
したがって、被圧縮ガスとともに飛沫化される吐油量を
極少とすることができる。Therefore, the amount of oil discharged into droplets together with the compressed gas can be minimized.
また、オイルストッパ２８によって回転軸７の低〜中回
転数域では第３の空間部３１への給油量を増加させ、中
〜高回転数域では減少させたので、必要以上の潤滑油０
が各摺動部に供給されることを防止でき、よって不要な
動力がががらなくなる。しかも、不要な油０が排出され
ないため、サイクルの冷却効果を向上できるとともに、
圧縮機の潤滑油不足を防止できる。In addition, the oil stopper 28 increases the amount of oil supplied to the third space 31 in the low to medium rotation speed range of the rotary shaft 7, and decreases it in the medium to high rotation speed range, so that no lubricating oil is needed.
can be prevented from being supplied to each sliding part, thereby preventing unnecessary power from being lost. Moreover, since unnecessary oil 0 is not discharged, the cooling effect of the cycle can be improved, and
This prevents the compressor from running out of lubricating oil.
加えて、羽根ポンプ２１の下端一部をポンプケース２０
の係合口２２に係止して確実１強固に取付けたので、摂
動や衝撃による羽根ポンプ２１のずれ、脱落を防１Ｆで
きる。しかも、羽根ポンプ２１の下端一部が係合口２２
に係合するように挿入、すればよく、その確認も容易に
行なえ、よって挿入方向の間違いを防止できる。In addition, a part of the lower end of the vane pump 21 is attached to the pump case 20.
Since the vane pump 21 is securely and securely attached to the engagement opening 22 of the blade pump 21, it is possible to prevent the vane pump 21 from shifting or falling off due to perturbation or impact. Moreover, a part of the lower end of the vane pump 21 is connected to the engagement port 22.
It is only necessary to insert it so that it engages with the holder, and this can be easily confirmed, thereby preventing mistakes in the insertion direction.
以上説明したように、本発明によれば、第１の空間部に
供給された潤滑油の全てがスラスト受に給油され、この
スラスト受の給油を終えた油の一部が第２の空間部に給
油されるから、スラスト受には多量の給油ができるとと
もに、オルダムリングには必要にして充分な量の給油が
でき、よってスラスト受やオルダムリングの給油不足を
防止でき、しかも被圧縮ガスとともに飛沫化される吐油
量を極少とすることができるという効果を奏する。As explained above, according to the present invention, all of the lubricating oil supplied to the first space is supplied to the thrust receiver, and a part of the oil that has finished lubricating the thrust receiver is transferred to the second space. Since the thrust receiver is supplied with oil, a large amount of oil can be supplied to the thrust receiver, and a sufficient amount of oil can be supplied to the Oldham ring, which prevents insufficient oil supply to the thrust receiver and Oldham ring. This has the effect of minimizing the amount of oil that is turned into droplets.
図面は本発明の一実施例を示し、第１図はスクロール形
圧縮機の要部の断面図、第２図はスラスト受の平面図、
第３図は第２図の■−■線断面図、第４図は第２図のＩ
Ｖ−ＩＶ線断面図、第５図は第２図のｖ−ｖ線断面図、
第６図はステータの斜視図、第７図はスラストリングの
斜視図、第８図および第９図はオイルストッパの動作を
示す図である。
１・・・フレーム、３・・・電動機部、３ａ・・・ステ
ータ、４・・・固定スクロール、５・・・圧縮空間、６
・・・旋回スクロール、９・・・スラスト受、１０・・
・第１の空間部、１３・・・第２の空間部、１４・・・
オルダムリング、１９・・・油溜部、３４・・・給油通
路、４０・・・油戻し通路。
出願人代理人 弁理士 鈴江武彦
第１図
第６図
第７図
第８図 叢９図The drawings show an embodiment of the present invention, with FIG. 1 being a sectional view of the main parts of a scroll compressor, and FIG. 2 being a plan view of the thrust receiver.
Figure 3 is a sectional view taken along the line ■-■ in Figure 2, and Figure 4 is a cross-sectional view taken along the line I in Figure 2.
A sectional view taken along the line V-IV; FIG. 5 is a sectional view taken along the line v-v in FIG. 2;
FIG. 6 is a perspective view of the stator, FIG. 7 is a perspective view of the thrust ring, and FIGS. 8 and 9 are views showing the operation of the oil stopper. DESCRIPTION OF SYMBOLS 1... Frame, 3... Electric motor part, 3a... Stator, 4... Fixed scroll, 5... Compression space, 6
...Orbiting scroll, 9...Thrust receiver, 10...
- First space part, 13... Second space part, 14...
Oldham ring, 19... oil reservoir section, 34... oil supply passage, 40... oil return passage. Applicant's Representative Patent Attorney Takehiko Suzue Figure 1 Figure 6 Figure 7 Figure 8 Figure 9
Claims (1)
クロールとの間に圧縮空間を形成して旋回スクロールを
設けるとともに、他端に電動機部のステータを設け、前
記旋回スクロールとフレームとの間に、圧縮空間での圧
縮によって旋回スクロールに作用するスラスト荷重を受
けるスラスト受を設け、このスラスト受の外周部に旋回
スクロールの自転を防止するオルダムリングを設けたス
クロール形圧縮機において、前記スラスト受に、前記フ
レーム，旋回スクロールおよびスラスト受によって形成
される第１の空間部に供給された潤滑油の一部を前記オ
ルダムリングが内装されている第２の空間部に導く給油
通路を設けるとともに、前記フレームおよびステータに
、前記第２の空間部を経た潤滑油およびスラスト受を経
た残りの潤滑油を圧縮機底部の油溜部に戻す油戻し通路
を設けたことを特徴とするスクロール形圧縮機。An orbiting scroll is provided at one end of the frame with a compressed space formed between the fixed scroll and the fixed scroll, and a stator of the electric motor section is provided at the other end, and a compressed space is provided between the orbiting scroll and the frame. A scroll compressor is provided with a thrust receiver that receives a thrust load acting on the orbiting scroll due to the compression of An oil supply passage is provided that guides a portion of the lubricating oil supplied to the first space formed by the orbiting scroll and the thrust receiver to the second space in which the Oldham ring is installed, and the frame and the stator are provided with an oil supply passage. A scroll compressor, characterized in that an oil return passage is provided for returning the lubricating oil that has passed through the second space and the remaining lubricating oil that has passed through the thrust receiver to an oil reservoir at the bottom of the compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13151188A JPH01301972A (en) | 1988-05-31 | 1988-05-31 | Scroll type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13151188A JPH01301972A (en) | 1988-05-31 | 1988-05-31 | Scroll type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01301972A true JPH01301972A (en) | 1989-12-06 |
Family
ID=15059747
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13151188A Pending JPH01301972A (en) | 1988-05-31 | 1988-05-31 | Scroll type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01301972A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2708677A1 (en) * | 1993-08-05 | 1995-02-10 | Zexel Corp | Compressor of the type having a shell |
| US5431550A (en) * | 1993-09-14 | 1995-07-11 | Sanden Corporation | Hermetic motor driven scroll apparatus having improved lubricating mechanism |
| US6196817B1 (en) * | 1998-12-15 | 2001-03-06 | Denso Corporation | Compresser with lubricating oil control |
| CN100455811C (en) * | 2004-06-21 | 2009-01-28 | 乐金电子(天津)电器有限公司 | Oil supplier of rotary compressor |
| US7736135B2 (en) * | 2007-12-25 | 2010-06-15 | Industrial Technology Research Institute | Structure for controlling lubricant's flow rate in scroll compressor |
| CN103388583A (en) * | 2013-07-24 | 2013-11-13 | 西安交通大学 | Closed scroll compressor with oilless compression cavity |
| CN107787410A (en) * | 2015-01-13 | 2018-03-09 | 丹佛斯商用压缩机公司 | Scroll compressor with discharge equipment |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63117186A (en) * | 1986-11-05 | 1988-05-21 | Mitsubishi Electric Corp | Scroll compressor |
-
1988
- 1988-05-31 JP JP13151188A patent/JPH01301972A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63117186A (en) * | 1986-11-05 | 1988-05-21 | Mitsubishi Electric Corp | Scroll compressor |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2708677A1 (en) * | 1993-08-05 | 1995-02-10 | Zexel Corp | Compressor of the type having a shell |
| US5472328A (en) * | 1993-08-05 | 1995-12-05 | Zexel Corporation | Scroll type compressor having an oil seal bearing for the drive shaft |
| US5431550A (en) * | 1993-09-14 | 1995-07-11 | Sanden Corporation | Hermetic motor driven scroll apparatus having improved lubricating mechanism |
| US6196817B1 (en) * | 1998-12-15 | 2001-03-06 | Denso Corporation | Compresser with lubricating oil control |
| CN100455811C (en) * | 2004-06-21 | 2009-01-28 | 乐金电子(天津)电器有限公司 | Oil supplier of rotary compressor |
| US7736135B2 (en) * | 2007-12-25 | 2010-06-15 | Industrial Technology Research Institute | Structure for controlling lubricant's flow rate in scroll compressor |
| CN103388583A (en) * | 2013-07-24 | 2013-11-13 | 西安交通大学 | Closed scroll compressor with oilless compression cavity |
| CN107787410A (en) * | 2015-01-13 | 2018-03-09 | 丹佛斯商用压缩机公司 | Scroll compressor with discharge equipment |
| CN107787410B (en) * | 2015-01-13 | 2019-07-05 | 丹佛斯商用压缩机公司 | Scroll compressor with discharge equipment |
| US10578109B2 (en) | 2015-01-13 | 2020-03-03 | Danfoss Commercial Compressors | Scroll compressor having an oil discharge device |
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