JPH0291495A - Feeding device for low pressure rotary compressor - Google Patents
Feeding device for low pressure rotary compressorInfo
- Publication number
- JPH0291495A JPH0291495A JP24283788A JP24283788A JPH0291495A JP H0291495 A JPH0291495 A JP H0291495A JP 24283788 A JP24283788 A JP 24283788A JP 24283788 A JP24283788 A JP 24283788A JP H0291495 A JPH0291495 A JP H0291495A
- Authority
- JP
- Japan
- Prior art keywords
- pressure chamber
- cylinder
- low pressure
- rotor
- oil
- 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
- 239000003507 refrigerant Substances 0.000 claims description 3
- 230000010349 pulsation Effects 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 30
- 238000007789 sealing Methods 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分骨〕
この発明は、低圧式回転彫工ｍｍの給油装置に関するも
のである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application] The present invention relates to a lubricating device for a low-pressure rotary engraver.
第５図は例えば、特願昭６３−１６１２９９に示された
従来の回転式圧縮機で図において、（１）は密閉容器、
（２１はこの密閉容器（１）内に配設されたシリンダ、
（３）はこのシリンダ（２）の軸心位置に配置され、偏
心軸部を有する回転軸、（４）は上記シリンダ（２）の
一端部に配置されたフレーム、（団はフレーム（４）の
反対側のシリンダ（２）端部に配置されたシリンダヘッ
ド、（６）はシリンダ（２）内を傷心回転するロータ、
（７）はシリンダ等により形成される低圧室、（８）は
高圧室である。（９）は低圧室と高圧室とを仕切るベー
ン、 Ｑｌは吐出マフラー （１１）は給油のためのギ
アポンプ、 （１２）は電動機要素、 （１３）は潤滑
油である。FIG. 5 shows, for example, a conventional rotary compressor shown in Japanese Patent Application No. 63-161299, in which (1) is a closed container;
(21 is a cylinder arranged in this airtight container (1),
(3) is a rotating shaft that is placed at the axial center position of this cylinder (2) and has an eccentric shaft portion; (4) is a frame that is placed at one end of the cylinder (2); a cylinder head disposed at the end of the cylinder (2) opposite to the rotor (6), which rotates centripetally within the cylinder (2);
(7) is a low pressure chamber formed by a cylinder or the like, and (8) is a high pressure chamber. (9) is a vane that partitions the low pressure chamber and high pressure chamber, Ql is a discharge muffler, (11) is a gear pump for oil supply, (12) is an electric motor element, and (13) is lubricating oil.
次に動作について説明する。Next, the operation will be explained.
ｆｆｉ動機要素（１２）により回転軸（３）が駆動され
ると。When the rotary shaft (3) is driven by the ffi motive element (12).
回転軸（３）端部に設けられたギアポンプ（１１）が給
油装置により２回転軸（３）のフレーム（４）及びシリ
ンダヘッド（５）の軸受部及びロータ（６）内周部へ給
油される。また、ロータ（６）がシリンダ（２）内を偏
心回転し。A gear pump (11) installed at the end of the rotating shaft (3) supplies oil to the frame (4) of the two rotating shafts (3), the bearings of the cylinder head (5), and the inner circumference of the rotor (6). Ru. Further, the rotor (6) rotates eccentrically within the cylinder (2).
そのロータ（６）にベーン（９）が常に圧接することに
より、低圧室（７）と高圧室（８）が形成され、吸入管
（図示せず）からあるいは密閉容器（１）内から低圧室
（ηに導かれたガスは圧縮され高圧室（８）から吐出さ
れ。A low pressure chamber (7) and a high pressure chamber (8) are formed by the vane (9) always being in pressure contact with the rotor (6), and the low pressure chamber is (The gas led to η is compressed and discharged from the high pressure chamber (8).
吐出マフラーαのを通り、吐出パイプ（図示せず）を介
して密閉容器（１）の外の高圧配管へ放出される。It passes through the discharge muffler α and is discharged to the high-pressure pipe outside the closed container (1) via a discharge pipe (not shown).
従来の給油装置は以上のように構成されているので、＠
転輪（３）を軸支する軸受部への給油は十分なされ、シ
リンダ（２）の低圧室（７）と高圧室（８）への給油は
、高圧式容器内が高圧圧縮機の場合は、ロータ（６）と
各部材のすきまからの油流出によりなされるが２本件の
低圧式容器内が低圧圧縮機の場合には、ロータ（６）内
側の圧力が高圧室（８）より常に低くなり、低圧室（７
）とほぼ同じになるため、ロータ（６）と各部材のすき
まからの油の流出はほとんどない。Since the conventional oil supply device is configured as described above, @
The bearings that support the rollers (3) should be sufficiently lubricated, and the low-pressure chamber (7) and high-pressure chamber (8) of the cylinder (2) should be lubricated if the high-pressure container is a high-pressure compressor. This is caused by oil leaking from the gaps between the rotor (6) and each member, but if the low-pressure container in this case is a low-pressure compressor, the pressure inside the rotor (6) is always lower than the high-pressure chamber (8). The low pressure chamber (7
), so there is almost no oil leakage from the gaps between the rotor (6) and each member.
そのためシール性の低下による漏れの増大、性能の低下
、ロータ（６）とベーン（９）の接触面の温度上昇等が
問題点となっていた。Therefore, there have been problems such as increased leakage due to decreased sealing performance, decreased performance, and increased temperature at the contact surface between the rotor (6) and the vane (9).
この発明は、上記のような問題点を解決するためになさ
れたもので、低圧式（低圧容器式）回転形圧縮機におい
て、シリンダの低圧室への安定した給油ができる給油装
置を得ることを目的とする。This invention was made to solve the above-mentioned problems, and aims to provide a lubricating device that can stably supply lubricant to the low-pressure chamber of the cylinder in a low-pressure type (low-pressure container type) rotary compressor. purpose.
この発明に係る低圧式回転形圧縮機の給油装置は、シリ
ンダの開口端を閉塞するシリンダヘッド及びフレームの
いずれか一方に設けられ、前記シリンダ内に形成された
低圧室と前記シリンダに収納され冷媒を圧縮するロータ
の内側空間とを連通ずる給油流路を備えた構成にしたも
のである。The oil supply device for a low-pressure rotary compressor according to the present invention is provided in either a cylinder head that closes an open end of a cylinder or a frame, and includes a low-pressure chamber formed in the cylinder and a refrigerant stored in the cylinder. The structure includes an oil supply passage that communicates with the inner space of the rotor that compresses the oil.
この発明における給油装置は、フレームあるいはシリン
ダヘッドに設けたロータ内側とシリンダ低圧室とを連通
ずる給油流路により、シリンダ低圧室へ安定した給油を
行い、シール性向上による圧縮機の性能向上、潤滑特性
改善による特にロータとベーンの接触面の摩耗を抑制す
る。The oil supply device according to the present invention provides stable oil supply to the cylinder low pressure chamber through an oil supply passage provided in the frame or cylinder head that communicates the inside of the rotor with the cylinder low pressure chamber, improves compressor performance by improving sealing performance, and lubricates the cylinder low pressure chamber. Improved characteristics particularly suppress wear on the contact surface between the rotor and vanes.
以下、この発明の一実施例を図について説明する。第１
図〜第２図において、（１）〜（１３）は上記従来装置
と全く同一のものである。第１図、第２図において？
（１４）はフレーム（４）あるいはシリンダヘッド（５
）に設けられた連通給油流路である。An embodiment of the present invention will be described below with reference to the drawings. 1st
In FIGS. 2 to 2, (1) to (13) are completely the same as the conventional device described above. In Figures 1 and 2?
(14) is the frame (4) or the cylinder head (5).
) is a communicating oil supply flow path provided in the
次に本発明における給油装置の動作について説明する。Next, the operation of the oil supply device according to the present invention will be explained.
電動要素（１２）により回転軸（３）が駆動されると。When the rotating shaft (3) is driven by the electric element (12).
回転軸（３）端部に設けられたギアポンプ（１１）等の
給油装置により、各軸受部へ給油される。Each bearing portion is supplied with oil by an oil supply device such as a gear pump (11) provided at the end of the rotating shaft (3).
この際、ロータ（６）の内側の圧力は密閉容Ｗｉ１１）
内及びシリンダ低圧室（ηとほぼ同じ圧力であるが。At this time, the pressure inside the rotor (6) is a closed volume Wi11)
Inside and cylinder low pressure chamber (with approximately the same pressure as η.
シリンダ低圧室（７）は、その容積変化に伴い回転軸一
回転中０．１〜０．５ Ｋｇ／ｃｉ程度の脈動を生じる
。The cylinder low pressure chamber (7) generates pulsations of about 0.1 to 0.5 Kg/ci during one rotation of the rotating shaft as its volume changes.
この脈動現象により、シリンダ低圧室（７）の圧力の方
がロータ（６）内側圧力より低い時に給油流路（１４）
シリ・ンダ室（７）へ油が流入する。流入した油はガス
と同様に搬送され一部は高圧室（８）から吐出され高圧
配管に流出する。また一部は低圧室（７）、ロータ（６
）内側へ副れる。Due to this pulsation phenomenon, when the pressure in the cylinder low pressure chamber (7) is lower than the pressure inside the rotor (6), the oil supply channel (14)
Oil flows into the cylinder chamber (7). The inflowing oil is transported like gas, and a portion is discharged from the high pressure chamber (8) and flows out into the high pressure piping. In addition, some parts include the low pressure chamber (7) and the rotor (6).
) fall inward.
この低圧室（７）、ロータ（６）内側への油の漏れによ
り、ガスのシール性が向上し、性能向上に寄与する。し
かし、高圧室（８）から吐出され図示しない高圧配管に
流出する油が増加すると２図示しない熱交換器の熱交換
率の低下をまねき、能力低下をきたすことになるため、
高圧配管への油流出量を一定値以下に抑えておく必要が
ある。This leakage of oil into the low pressure chamber (7) and the inside of the rotor (6) improves gas sealing performance, contributing to improved performance. However, if the amount of oil discharged from the high pressure chamber (8) and flowing into the high pressure piping (not shown) increases, the heat exchange efficiency of the heat exchanger (not shown) will decrease, resulting in a decrease in capacity.
It is necessary to keep the amount of oil leaking into high-pressure piping below a certain value.
この油の流出量を実使用上問題ない程度とするためには
、実験結果より給油流路（１４）の場合、溝幅を１職園
とすると、その深さを０．０５〜０．２ ａｍとする必
要がある。In order to keep the amount of oil flowing out to a level that does not pose a problem in actual use, the experiment results show that in the case of the oil supply channel (14), the depth should be 0.05 to 0.2, assuming that the width of the groove is one channel. It is necessary to set it as am.
第３図〜第４図はこの発明の他の実施例を示すもので１
図において（１５）は回転軸（３）のスラスト軸受部で
あり、 （１Ｂ）はシリンダヘッド（５）に設けられ。Figures 3 and 4 show other embodiments of this invention.
In the figure, (15) is the thrust bearing of the rotating shaft (3), and (1B) is provided on the cylinder head (5).
スラスト軸受部（１５）の最内周部とは連通していない
給油流路である。この場合スラスト軸受部（１５）によ
る給油流路（ＩＢ）の開閉作用により、溝幅を１職園と
するとその深さを０．３以上としても、高圧配管への油
流出量は一定値以下になることが可能で。This is an oil supply flow path that does not communicate with the innermost peripheral portion of the thrust bearing portion (15). In this case, due to the opening/closing action of the oil supply channel (IB) by the thrust bearing (15), the amount of oil flowing into the high-pressure pipe will be below a certain value even if the groove width is 0.3 or more and the depth is 0.3 or more. It is possible to become.
溝形状をラフに設定することが可能となる。It becomes possible to set the groove shape roughly.
この発明によれば、シリンダの開口端を閉塞するシリン
ダヘッド及びフレームのいずれか一方に設けられ、前記
シリンダ内に形成された低圧室と前記シリンダに収納さ
れ冷媒を圧縮するロータの内側空間とを連通する給油流
路を備えた構成にしたので、シリンダの低圧室と高圧室
への安定した給油ができ、その結果、ガスのシール性向
上による性能向上及びロータとベーンの接触摩耗の低減
等の効果を奏する。According to this invention, the low pressure chamber formed in the cylinder is provided in either the cylinder head that closes the open end of the cylinder or the frame, and the inner space of the rotor that is housed in the cylinder and compresses the refrigerant. Since the structure is equipped with a communicating oil supply flow path, stable oil supply to the low pressure chamber and high pressure chamber of the cylinder is possible, resulting in improved performance due to improved gas sealing and reduced contact wear between the rotor and vane. be effective.
第１図はこの発明の一実施例の断面図、第２図は第１図
のｎ−［線部分断面図、第３図はこの発明の他の実施例
の断面図、第４図は第３図の■−■線部分断面図、第５
図は従来の回転形圧縮機の給油装置を示す断面図である
。
図において、 （２１はシリング、 （４）はフレーム
、 （５１はシリンダヘッド、（６）はロータ、 （
１４）、 （１Ｂ）は給油流路である。
なお２図中、同一符号は同−又は相当部分を示す。FIG. 1 is a cross-sectional view of one embodiment of the present invention, FIG. 2 is a cross-sectional view along line n-[ of FIG. 1, FIG. Partial cross-sectional view along the ■-■ line in Figure 3, No. 5
The figure is a sectional view showing a conventional oil supply device for a rotary compressor. In the figure, (21 is the cylinder, (4) is the frame, (51 is the cylinder head, (6) is the rotor, (
14), (1B) is an oil supply flow path. Note that in the two figures, the same reference numerals indicate the same or equivalent parts.
Claims (1)
ムのいずれか一方に設けられ、前記シリンダ内に形成さ
れた低圧室と前記シリンダに収納され冷媒を圧縮するロ
ータの内側空間とを連通する給油流路を備えた低圧式回
転形圧縮機の給油装置。A refueling channel is provided in either the cylinder head that closes the open end of the cylinder or the frame, and communicates between the low pressure chamber formed in the cylinder and the inner space of the rotor that is housed in the cylinder and compresses refrigerant. Oil supply system for low pressure rotary compressor.
Priority Applications (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24283788A JPH0291495A (en) | 1988-09-28 | 1988-09-28 | Feeding device for low pressure rotary compressor |
| KR1019890013809A KR900005076A (en) | 1988-09-28 | 1989-09-26 | Rolling Piston Compressor |
| US07/412,409 US4983108A (en) | 1988-09-28 | 1989-09-26 | Low pressure container type rolling piston compressor with lubrication channel in the end plate |
| EP89117816A EP0361421B1 (en) | 1988-09-28 | 1989-09-27 | Low pressure container type rolling piston compressor |
| CN89108180A CN1015194B (en) | 1988-09-28 | 1989-09-27 | Low pressure container type rotation piston compressor |
| ES198989117816T ES2041927T3 (en) | 1988-09-28 | 1989-09-27 | ROLLING PISTON COMPRESSOR OF LOW PRESSURE CONTAINER TYPE. |
| DE89117816T DE68906997T2 (en) | 1988-09-28 | 1989-09-27 | Hermetic low pressure compressor with roller piston. |
| DK198904782A DK173180B1 (en) | 1988-09-28 | 1989-09-28 | Capsule compressor with roller piston. |
| KR2019910019276U KR930007433Y1 (en) | 1988-09-28 | 1991-11-13 | Rolling piston type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24283788A JPH0291495A (en) | 1988-09-28 | 1988-09-28 | Feeding device for low pressure rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0291495A true JPH0291495A (en) | 1990-03-30 |
Family
ID=17095031
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24283788A Pending JPH0291495A (en) | 1988-09-28 | 1988-09-28 | Feeding device for low pressure rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0291495A (en) |
-
1988
- 1988-09-28 JP JP24283788A patent/JPH0291495A/en active Pending
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