JPS5848787A - Lubricating oil supplying device for electric compressor - Google Patents
Lubricating oil supplying device for electric compressorInfo
- Publication number
- JPS5848787A JPS5848787A JP15662382A JP15662382A JPS5848787A JP S5848787 A JPS5848787 A JP S5848787A JP 15662382 A JP15662382 A JP 15662382A JP 15662382 A JP15662382 A JP 15662382A JP S5848787 A JPS5848787 A JP S5848787A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic pressure
- bearing
- oil
- pressure chamber
- high hydraulic
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
Abstract
Description
【発明の詳細な説明】
不発明は密閉形電動圧縮機の潤滑油供給装置に関するも
のである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a lubricating oil supply device for a hermetic electric compressor.
従来のとの検温滑油供給装置を第1図および第2図につ
いて説明するに、1はクランク軸2に取付けられたロー
タ、3.4はクランク軸2の上、下部をそれぞれ支持す
る主軸受および副軸受、5はクランク軸1の端部を支持
するスラスト軸受、6はスラスト軸受5を保持するスラ
スト軸受支え、7はスラスト軸受6およびスラスト軸受
5に設けられた潤滑油吸入口、8はクランク軸2に設け
られた偏心穴で、前記潤滑油吸入ロアに連通さnている
。9は偏心穴8に連通ずる高油圧室、10はクランク軸
1の中心に設けられた通路、11はスラスト軸受5とス
ラスト軸受支え6の間に設けられ、かつ前記通路10に
連通された通路、12はクランク軸1に取付けられたコ
ネクチングロッド、13は潤滑油14を蓄える油ためで
ある。To explain a conventional temperature measuring lubricant supply device with reference to FIGS. 1 and 2, 1 is a rotor attached to the crankshaft 2, and 3.4 is a main bearing that supports the upper and lower parts of the crankshaft 2, respectively. 5 is a thrust bearing that supports the end of the crankshaft 1; 6 is a thrust bearing support that holds the thrust bearing 5; 7 is a thrust bearing 6 and a lubricating oil inlet provided in the thrust bearing 5; 8 is a thrust bearing that supports the end of the crankshaft 1; An eccentric hole provided in the crankshaft 2 communicates with the lubricating oil suction lower. 9 is a high hydraulic pressure chamber communicating with the eccentric hole 8; 10 is a passage provided at the center of the crankshaft 1; 11 is a passage provided between the thrust bearing 5 and the thrust bearing support 6 and communicating with the passage 10. , 12 is a connecting rod attached to the crankshaft 1, and 13 is an oil reservoir for storing lubricating oil 14.
上記のような構成からなる潤滑油供給装置では、圧縮機
の運転によりロータ1およびクランク軸2が回転すると
、油ため13内の潤滑油14はスラスト軸受支え6およ
びスラスト軸5の潤滑油吸入ロアより吸入さnlり′ラ
ンク軸2の偏心穴8で遠心力を付加されて高油圧室9へ
供給される。In the lubricating oil supply device configured as described above, when the rotor 1 and crankshaft 2 rotate due to the operation of the compressor, the lubricating oil 14 in the oil reservoir 13 is transferred to the thrust bearing support 6 and the lubricating oil suction lower of the thrust shaft 5. When the oil is sucked in, centrifugal force is applied through the eccentric hole 8 of the rank shaft 2, and the oil is supplied to the high oil pressure chamber 9.
上記高油圧室9内の潤滑油の一部は通路17、+1.1
0を峠て主軸受3およびコネクチングロッド12へ給油
され、これらを潤滑した彼に油ため13内に渦)する。A part of the lubricating oil in the high oil pressure chamber 9 is in the passage 17, +1.1
The main bearing 3 and the connecting rod 12 are supplied with oil through the 0-pass, and the oil that lubricates them is swirled in the oil reservoir 13).
また高油圧室9内の潤滑油の一部は通路15を経て副軸
受4へ給油される。Further, a part of the lubricating oil in the high oil pressure chamber 9 is supplied to the sub-bearing 4 through the passage 15.
上述した従来の潤滑油供給装flILは下記のような欠
点がある。The conventional lubricating oil supply system flIL described above has the following drawbacks.
(Al 副軸受側給油路の断面積を広くすると、副軸
受へ多量に給油されるため、主軸受およびコネクチング
ロッド稠の給油tは不足する。(Al) If the cross-sectional area of the sub-bearing side oil supply passage is widened, a large amount of lubricant will be supplied to the sub-bearing, resulting in a shortage of lubricant t for the main bearing and connecting rod.
(Bl 上記欠点を解消するために副軸受働給油路の
加工精度を向上させ、主軸受およびコネクチングロッド
匈給油量を確保しようとすると加工コストが高くなる。(Bl) In order to eliminate the above-mentioned drawbacks, if the machining accuracy of the auxiliary bearing working oil supply path is improved to ensure the amount of oil supplied to the main bearing and the connecting rod, the machining cost will increase.
(C1副軸受働給油と主軸受側給油路と主軸受側給油路
の各抵抗の比率によシ、その給油路の油量が決定される
ので、副軸受側給油路の加工精度を決定するのが困難で
ある。(The amount of oil in the oil supply passage is determined by the ratio of the resistance of the C1 secondary bearing working oil supply, the main bearing side oil supply passage, and the main bearing side oil supply passage, so the machining accuracy of the secondary bearing side oil supply passage is determined. It is difficult to
(鞠 給油量自体を増加させるには、フランク軸の径を
大にし、かつ遠心力により油圧を上昇させる必要がある
。ところがこのように構成すると、部品が大形化してコ
ス鼾高となり、かつ軸受摺動面の増加によシ損失が増大
する恐れがある。(Mari) In order to increase the amount of oil supplied, it is necessary to increase the diameter of the flank shaft and increase the oil pressure by centrifugal force. However, with this configuration, the parts become large and costs are high. There is a risk that loss will increase due to an increase in the number of bearing sliding surfaces.
(ICI 軸受の摩耗による軸受ギャップの増加ある
いは油温上昇による潤滑油粘度の低下により、副軸受か
らの油流出量は増大するため高油圧室の油圧が低下し、
主軸受へ十分に給油されないから事故を起す恐れがある
。(Due to an increase in the bearing gap due to ICI bearing wear or a decrease in lubricant viscosity due to an increase in oil temperature, the amount of oil leaking from the secondary bearing increases, causing the oil pressure in the high hydraulic chamber to decrease.
There is a risk of an accident because the main bearing is not sufficiently lubricated.
本発明は上記諸欠点を解消し、各軸受類へ過不足なく給
油して信頼性を向上させることを目的とするもので、電
動圧縮機のクランク軸端部に設は九スラスト軸受および
スラスト軸受支えの吸入口から吸入された潤滑油を、ク
ランク軸の偏心穴を経て高油圧室へ供給した後に、副軸
受と主軸受およびコネクチングロッドへそれぞれ供給す
る潤滑油供給装置において、前記高油圧室を仕切シ壁に
よシ2分し、その一方の高油圧室を副軸受に、他方の高
油圧室を主軸受およびコネクチングロッドにそれぞれ連
通したことを%黴とするものである以下本発明の一冥施
例を図面を参照して説明する。The purpose of the present invention is to eliminate the above-mentioned drawbacks and to improve reliability by lubricating each bearing in the correct quantity and quantity. In the lubricating oil supply device, the lubricating oil sucked from the suction port of the support is supplied to the high hydraulic chamber through the eccentric hole of the crankshaft, and then to the sub bearing, the main bearing, and the connecting rod, respectively. The partition is divided into two by a wall, and one of the high hydraulic pressure chambers is connected to the sub bearing, and the other high hydraulic pressure chamber is connected to the main bearing and the connecting rod. A detailed example will be explained with reference to the drawings.
第3図は本実施例における第1図のX−X断面に相当す
る断面図で、2はクランク軸、8はクランク軸2に設け
られた偏心穴、9A、9Bは仕切壁16によ多区分され
た高油圧室で、その一方の高油圧室9Aは1g1図に示
す通路17.11.10を経て主軸受3およびコネクチ
ングロッド11に、他方の高油圧室9Bは通路15を経
て副軸受4にそれぞれ連通されている。FIG. 3 is a cross-sectional view corresponding to the X-X cross section of FIG. The high hydraulic pressure chambers are divided into sections, one of which is connected to the main bearing 3 and the connecting rod 11 through passages 17, 11, and 10 shown in Figure 1g1, and the other high hydraulic chamber 9B is connected to the sub bearing through passage 15. 4 are connected to each other.
本実施例は上記のような構成からなり、クランク軸2を
回転して第3図から第4図に示す状態に移行させた場合
でも、偏心穴8Aは主軸受およびコネクチングロッド用
高油圧室9Aに連通しているため、この高油圧室9A内
の油圧は第5図(イ)の実線に示すように一定に保持さ
れる。This embodiment has the above-mentioned configuration, and even when the crankshaft 2 is rotated to shift from the state shown in FIG. 3 to the state shown in FIG. Since the high oil pressure chamber 9A is in communication with the high oil pressure chamber 9A, the oil pressure in the high oil pressure chamber 9A is kept constant as shown by the solid line in FIG. 5(a).
一方、クランク軸2を第3図から第4図に示す状態に移
行させた場合、偏心穴8Bと副軸受用高圧呈9Bとの連
通は遮断されるため、この高油圧室9B内の油圧は第5
図(cllの実線に示すように低下する。On the other hand, when the crankshaft 2 is moved from the state shown in FIG. 3 to the state shown in FIG. Fifth
Figure (cll) decreases as shown by the solid line.
上記のように仕切りICI6を任意位置に設定すること
によシ、副軸受給油用高油圧室9Bの油圧印加時間を変
化させることかで睡るため、副軸受4への給油通路15
と、主軸受3およびコネクチングロッド12にへの給油
通路17、IL 10の寸法および形状に影響される
ことなく、副軸受4、主軸受3およびコネクチングロッ
ド12への給油量を任意に設定することができる。By setting the partition ICI 6 to an arbitrary position as described above, the oil supply passage 15 to the secondary bearing 4 can be controlled by changing the hydraulic pressure application time of the secondary bearing oil supply high oil pressure chamber 9B.
And, the amount of oil to be supplied to the secondary bearing 4, the main bearing 3 and the connecting rod 12 can be arbitrarily set without being affected by the dimensions and shapes of the oil supply passage 17 and IL 10 to the main bearing 3 and the connecting rod 12. I can do it.
以上説明したように本発明によれば、副軸受、主軸受お
よびコネクチングロッドへ給油する高油圧室に仕切シ壁
を設けることによシ、前記各軸受類へ潤滑油を過不足な
く給油して信頼性を向上させることかで色る。゛As explained above, according to the present invention, by providing a partition wall in the high hydraulic pressure chamber that supplies oil to the secondary bearing, main bearing, and connecting rod, lubricating oil can be supplied to each of the bearings in just the right amount. It depends on whether it improves reliability or not.゛
第1図は従来の電動圧縮機の潤滑油供給装置の断面図、
第2図は第1図のX−X@における断面図、第3wJお
よび第4図は本発明に係わる亀動圧llA41&の潤滑
油供給装置の一実施例の像部を示す断面図、第5図(イ
+、 (ロ)は一実施例の作用説明図である。
3・・・主軸受 4・・・副軸受 9A、9B・・
・高油圧家 12・・・コネクチングロッド 16
・・・仕切シ壁
2わイbq
第21
15″
婆4圓
第51
(0)
−一今時間Figure 1 is a cross-sectional view of a conventional electric compressor lubricating oil supply device.
FIG. 2 is a sectional view taken along line X-X@ in FIG. Figures (a + and b) are action explanatory diagrams of one embodiment. 3...Main bearing 4...Sub bearing 9A, 9B...
・High hydraulic pressure house 12...Connecting rod 16
・・・Partition wall 2 bq 21st 15″ 4th round 51st (0) - This time
Claims (1)
よびスラスト軸壺支えの吸入口から吸入された潤滑油を
、クランク軸の偏心穴を経て高油圧室へ供給した後に、
副軸受と主軸受およびコネクチングロッドへそれぞれ供
給する潤滑油供給装置において、前記高油圧室を仕切り
壁によ92分し、その一方の高油圧室を副軸受に、他方
の高油圧室を主軸受およびコネクチングロッドにそれぞ
れ連通したことを特徴とする電動圧動機の潤滑油供給装
置。 2、上−ピ副軸受給油用高加圧室を主軸受およびコネク
チングロッド給油用高油圧室より小に形成したことを特
徴とする特許請求の範囲第1項記載の電動圧llA1m
の潤滑油供給装置。[Claims] 1 is a dynamic compressor in which lubricating oil is sucked in from the thrust bearing provided at the end of the crankshaft and the suction port of the thrust shaft pot support and is supplied to the high hydraulic pressure chamber through the eccentric hole of the crankshaft. later,
In the lubricating oil supply device that supplies lubricating oil to the secondary bearing, main bearing, and connecting rod, the high hydraulic pressure chamber is divided into 92 parts by a partition wall, one of the high hydraulic pressure chambers is used as the secondary bearing, and the other high hydraulic pressure chamber is used as the main bearing. and a connecting rod, respectively. 2. The electric pressure llA1m according to claim 1, characterized in that the high pressure chamber for lubricating the upper pi sub-bearing is formed smaller than the high hydraulic chamber for lubricating the main bearing and connecting rod.
lubricating oil supply device.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15662382A JPS5848787A (en) | 1982-09-10 | 1982-09-10 | Lubricating oil supplying device for electric compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15662382A JPS5848787A (en) | 1982-09-10 | 1982-09-10 | Lubricating oil supplying device for electric compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5848787A true JPS5848787A (en) | 1983-03-22 |
Family
ID=15631750
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15662382A Pending JPS5848787A (en) | 1982-09-10 | 1982-09-10 | Lubricating oil supplying device for electric compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5848787A (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60191744U (en) * | 1984-05-29 | 1985-12-19 | 三菱自動車工業株式会社 | flywheel |
JPS6123544U (en) * | 1984-07-19 | 1986-02-12 | アイシン精機株式会社 | Torque fluctuation absorber |
JPS6152440A (en) * | 1984-08-18 | 1986-03-15 | ダイムラ−ベンツ・アクチエンゲゼルシャフト | Apparatus for reducing transmission of vibration |
JPS61189343A (en) * | 1985-02-14 | 1986-08-23 | ダイムラー‐ベンツ アクチエンゲゼルシヤフト | Device for damping vibration of transmission line generated by engine |
JPS61139331U (en) * | 1985-02-20 | 1986-08-29 | ||
JPS622038A (en) * | 1985-06-04 | 1987-01-08 | ダイムラ−ベンツ・アクチエンゲゼルシャフト | Device for damping vibration of transmission line generated by engine |
-
1982
- 1982-09-10 JP JP15662382A patent/JPS5848787A/en active Pending
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60191744U (en) * | 1984-05-29 | 1985-12-19 | 三菱自動車工業株式会社 | flywheel |
JPS6123544U (en) * | 1984-07-19 | 1986-02-12 | アイシン精機株式会社 | Torque fluctuation absorber |
JPH0235077Y2 (en) * | 1984-07-19 | 1990-09-21 | ||
JPS6152440A (en) * | 1984-08-18 | 1986-03-15 | ダイムラ−ベンツ・アクチエンゲゼルシャフト | Apparatus for reducing transmission of vibration |
JPS61189343A (en) * | 1985-02-14 | 1986-08-23 | ダイムラー‐ベンツ アクチエンゲゼルシヤフト | Device for damping vibration of transmission line generated by engine |
JPS61139331U (en) * | 1985-02-20 | 1986-08-29 | ||
JPH028119Y2 (en) * | 1985-02-20 | 1990-02-27 | ||
JPS622038A (en) * | 1985-06-04 | 1987-01-08 | ダイムラ−ベンツ・アクチエンゲゼルシャフト | Device for damping vibration of transmission line generated by engine |
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