JP2510639B2 - Rotary type hermetic compressor - Google Patents
Rotary type hermetic compressorInfo
- Publication number
- JP2510639B2 JP2510639B2 JP62326928A JP32692887A JP2510639B2 JP 2510639 B2 JP2510639 B2 JP 2510639B2 JP 62326928 A JP62326928 A JP 62326928A JP 32692887 A JP32692887 A JP 32692887A JP 2510639 B2 JP2510639 B2 JP 2510639B2
- Authority
- JP
- Japan
- Prior art keywords
- roller
- end surface
- shaft
- bearing
- lower bearing
- 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.)
- Expired - Fee Related
Links
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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明はロータリー式密閉形圧縮機に係り、特に信頼
性の向上に好適な構造に関する。The present invention relates to a rotary hermetic compressor, and more particularly to a structure suitable for improving reliability.
従来のロータリー式密閉形圧縮機を第4図、第5図に
より説明する。第4図はロータリー式圧縮機の縦断面
図、第5図は第4図のシリンダ部の断面図である。図に
おいて、密閉形容器1の上部に電動要素2、下部に圧縮
要素3が配設され、電動要素2は固定子4と回転子5と
から成る。上記圧縮要素3はシャフト6と、このシャフ
ト6を保持する上軸受7及び下軸受8と、上軸受7と下
軸受8とによって挟持されたシリンダ9と、シャフト6
の偏心部(図示せず)に回転自在に嵌合されたローラ10
と、シリタン9室内でローラ10に押圧されたベーン11と
によって構成される。吸込管(図示せず)から吸い込ま
れた冷媒ガスは圧縮要素3内にはいり、ローラ10の回転
により徐々に圧縮され、高圧になったのち、バルブ(図
示せず)を通って高圧の密閉形容器1内へ吐出され、さ
らに吐出管13よりサイクル(図示せず)へ吐出される。A conventional rotary hermetic compressor will be described with reference to FIGS. 4 and 5. FIG. 4 is a vertical sectional view of the rotary compressor, and FIG. 5 is a sectional view of the cylinder portion of FIG. In the figure, an electric element 2 is arranged in the upper part of a closed container 1, and a compression element 3 is arranged in the lower part. The electric element 2 comprises a stator 4 and a rotor 5. The compression element 3 includes a shaft 6, an upper bearing 7 and a lower bearing 8 that hold the shaft 6, a cylinder 9 sandwiched between the upper bearing 7 and the lower bearing 8, and a shaft 6.
Roller 10 rotatably fitted to the eccentric part (not shown) of
And a vane 11 pressed against the roller 10 in the chamber of the Silytan 9. The refrigerant gas sucked from the suction pipe (not shown) enters the compression element 3 and is gradually compressed by the rotation of the roller 10 to become a high pressure, and then passes through a valve (not shown) to form a high-pressure sealed type container. It is discharged into the container 1, and further discharged from the discharge pipe 13 into a cycle (not shown).
本構造では一般に冷凍能力を小さくする場合、シリン
ダの大きさは一定のままで、シャフト偏心部の偏心寸法
を小さくして対応する場合が多い。シャフト偏心部の偏
心寸法を小さくすることはローラ1回転当たりの押除量
を小さくすること、即ち、ローラ10の外径を大きくする
ものである。従ってローラ10の肉厚tが大となる。ロー
ラ10の肉厚tが大となると、第5図の如く、ローラ10の
外径の最も内側の軌跡15は、ローラ10の内径の最も外側
の軌跡14より径が大となり、軌跡14と軌跡15の間は常時
ローラ10と下軸受8が摺動する。従ってその範囲の潤滑
油は移動しにくいため熱の逃げが悪く、シリンダ室16内
が高温となり易い。In this structure, in general, when the refrigerating capacity is reduced, the size of the cylinder remains constant and the eccentric dimension of the shaft eccentric portion is reduced. Reducing the eccentric dimension of the shaft eccentric portion reduces the pushing amount per one rotation of the roller, that is, increases the outer diameter of the roller 10. Therefore, the wall thickness t of the roller 10 becomes large. When the wall thickness t of the roller 10 becomes large, the innermost locus 15 of the outer diameter of the roller 10 becomes larger in diameter than the outermost locus 14 of the inner diameter of the roller 10, as shown in FIG. During the period of 15, the roller 10 and the lower bearing 8 always slide. Therefore, since the lubricating oil in that range is difficult to move, the heat escape is poor, and the temperature inside the cylinder chamber 16 tends to become high.
押除量を小さくする手段としては例えば特公昭58-361
96の様にローラ端面のシリンダ側板との半径方向接触幅
を一定としつつ、シャフト偏心部の偏心寸法を小さくす
る手段かある。As a means for reducing the amount of pushing, for example, Japanese Patent Publication No. 58-361
As in 96, there is a means for reducing the eccentric dimension of the shaft eccentric portion while keeping the radial contact width of the roller end surface with the cylinder side plate constant.
従来技術はシャフト6の偏心部の偏心量に対するロー
ラ10の肉厚の最適値について配慮されておらず、ローラ
20と下軸受8との間に潤滑油が停溜したり、異物が停溜
し摩耗を発生する可能性があった。The prior art does not consider the optimum value of the wall thickness of the roller 10 with respect to the eccentric amount of the eccentric part of the shaft 6,
Lubrication oil may accumulate between the lower bearing 20 and the lower bearing 8, and foreign matter may accumulate and wear may occur.
本発明の目的は、潤滑油の停溜や摩耗の発生を防止し
たりロータリー式圧縮機を提供することにある。An object of the present invention is to provide a rotary compressor that prevents accumulation of lubricating oil and occurrence of wear.
上記目的は、密閉形容器の上部に電動要素と下部に圧
縮要素を配設し、上記圧縮要素はシャフトを保持する上
軸受及び下軸受のフランジ端面にてシリンダを挟持し、
上記シャフトの偏心部に回転自在に嵌合したローラがシ
リンダ内を回転圧縮し、上記ローラの肉厚がシャフト偏
心部の偏心寸法の2倍より大きい寸法を有するロータリ
ー式密閉形圧縮機において、上記上軸受または下軸受ま
たはその両軸受のフランジ端面に接する上記ローラの端
面にテーパまたは段差をつけ、上記ローラの端面と上記
上軸受または下軸受またはその両軸受の上記フランジ端
面との半径方向接触幅を上記偏心寸法の2倍より小さく
し、上記ローラの端面と上記上軸受または下軸受または
その両軸受の上記フランジ端面との接触面のうち常時接
触し摺動し続ける面がないようにしたことにより達成さ
れる。The above-mentioned object is to arrange an electric element and a compression element in the lower part of the closed container, and the compression element holds the cylinder at the flange end surfaces of the upper bearing and the lower bearing that hold the shaft,
A rotary hermetic compressor in which a roller rotatably fitted to the eccentric portion of the shaft rotationally compresses in the cylinder, and the wall thickness of the roller is larger than twice the eccentric dimension of the shaft eccentric portion. A taper or step is formed on the end surface of the roller that is in contact with the flange end surface of the upper bearing, the lower bearing, or both bearings, and the radial contact width between the end surface of the roller and the flange end surface of the upper bearing, the lower bearing, or both bearings. Is smaller than twice the eccentric dimension so that there is no contact surface between the end surface of the roller and the flange end surface of the upper bearing or the lower bearing or both of the bearings that is constantly in contact with and continues to slide. Achieved by
ローラの内径側の最も外側の点の軌跡14は、ローラの
外径側の最も内側の点の軌跡15より外側になるから、ロ
ーラと下軸受との間にある潤滑油はシャフトが1回転す
る毎にローラの外径では外寄りに、内径では内寄りに掃
拭されるため、外側に寄せられるとガスと共にシリンダ
室から吐出され、内側に寄せられるとシャフトの油溝
(図示せず)を流れる潤滑油に合流し、上軸受の上端及
び下軸受の下端より密閉形容器内へ排出される。従っ
て、ローラと下軸受との間に潤滑油が停溜することはな
い。Since the locus 14 of the outermost point on the inner diameter side of the roller is outside the locus 15 of the innermost point on the outer diameter side of the roller, the shaft of the lubricating oil between the roller and the lower bearing rotates once. The outer diameter of the roller is wiped outward, and the inner diameter is wiped inward, so that it is discharged from the cylinder chamber with the gas when it is moved to the outside, and the oil groove (not shown) of the shaft is moved when it is moved to the inside. It merges with the flowing lubricating oil and is discharged from the upper end of the upper bearing and the lower end of the lower bearing into the sealed container. Therefore, the lubricating oil does not accumulate between the roller and the lower bearing.
以下、本発明の一実施例を第1図、第2図により説明
する。第1図はロータリー式密閉形圧縮機の要部断面
図、第2図は第1図のA−A矢視断面図である。尚、第
4図、第5図と同一符号は均等物、または同一物を示
す。図において、ローラ20にはシャフト6偏心部との嵌
合部の半径Rpは変えずに段差21、22が内径側に設けられ
ており、ローラ20の端面接触幅lはシャフトと偏心部の
偏心寸法Eの2倍より小さい。かかる構成によればロー
ラ端面の半径方向接触幅l、偏心寸法E、ローラ外半径
Rr、シリンダ半径Rcとすると、ローラ10または20の内径
側の最も外側の点の軌跡14の半径は(Rr−l+E)とな
る。一方、ローラ10または20の外径側の最も内側の点の
軌跡15の半径は(Rr−E)となる。ここで軌跡14と軌跡
15との間の範囲の領域は潤滑油が移動しにくくなる。An embodiment of the present invention will be described below with reference to FIGS. 1 and 2. 1 is a sectional view of a main part of a rotary hermetic compressor, and FIG. 2 is a sectional view taken along the line AA of FIG. In addition, the same reference numerals as those in FIGS. 4 and 5 indicate equivalents or the same. In the figure, the roller 20 is provided with steps 21 and 22 on the inner diameter side without changing the radius R p of the fitting portion with the eccentric portion of the shaft 6, and the end face contact width l of the roller 20 is the same as that of the shaft and the eccentric portion. It is smaller than twice the eccentric dimension E. According to this structure, the radial contact width l of the roller end surface, the eccentricity E, the roller outer radius
When R r is the cylinder radius R c , the radius of the locus 14 at the outermost point on the inner diameter side of the roller 10 or 20 is (R r −l + E). On the other hand, the radius of the locus 15 of the innermost point on the outer diameter side of the roller 10 or 20 is (R r −E). Where locus 14 and locus
In the area in the range between 15 and 15, it becomes difficult for the lubricating oil to move.
従って、軌跡14と軌跡15の間の領域を失くすためには
軌跡14の半径(Rr−l+E)を軌跡15の半径(Rr−E)
より大きくすればよく(Rr−E)<(Rr−l+E)従っ
てl<2・Eを満たすようにローラ端面半径方向接触幅
lを決めればよい。すなわち偏心寸法Eとローラ端面半
径方向接触幅lとの関係は第3図の領域Iの範囲内にな
るようにする。Therefore, in order to lose the area between the loci 14 and 15, the radius of the locus 14 (R r −l + E) is changed to the radius of the locus 15 (R r −E).
It is sufficient to make it larger (R r −E) <(R r −l + E). Therefore, the contact width l in the radial direction of the roller end surface may be determined so as to satisfy l <2 · E. That is, the relationship between the eccentric dimension E and the contact width l in the radial direction of the roller end surface is set within the range of the region I in FIG.
上記第3図は本発明のローラ端面の接触幅と偏心寸法
との関係を説明する線図であり、縦軸はローラ端面の接
触幅を示し、横軸は偏心寸法を示す。以上の如く、シャ
フト6偏心部との嵌合部の半径Rpは変えずに、ローラ20
に段差21、22を内径側に設け、ローラ端面半径方向接触
幅lを偏心寸法Eの2倍より小さくする。FIG. 3 is a diagram illustrating the relationship between the contact width of the roller end surface and the eccentric dimension of the present invention, the vertical axis represents the contact width of the roller end surface, and the horizontal axis represents the eccentric dimension. As described above, without changing the radius R p of the fitting portion with the eccentric portion of the shaft 6, the roller 20
Steps 21 and 22 are provided on the inner diameter side, and the contact width l in the radial direction of the roller end surface is made smaller than twice the eccentric dimension E.
従って、ローラ20と下軸受8間に潤滑油が停溜し高熱
化したり、摩耗粉などの異物が停滞して異常摩耗を起し
たりすることを防止できるという効果がある。また、シ
ャフト6偏心部における摺動損失の増加を防止できると
いう効果がある。Therefore, there is an effect that it is possible to prevent the lubricating oil from being accumulated between the roller 20 and the lower bearing 8 and becoming high in heat, and the foreign matter such as abrasion powder from being stagnant and causing abnormal wear. Further, there is an effect that it is possible to prevent an increase in sliding loss in the eccentric portion of the shaft 6.
尚、本実施例では、ローラ20の上下に段差を設けたが
上側はクリアランスが大きいから段差はなくとも効果に
おいては大きな差はない。また、段差はテーパでももち
ろん代替できる。In this embodiment, steps are provided above and below the roller 20, but there is no significant difference in effect even if there is no step because the clearance is large on the upper side. Also, the step can be replaced by a taper.
本発明によれば、上軸受または下軸受またはその両軸
受のフランジ端面に接するローラの端面にテーパまたは
段差をつけ、ローラの端面と上軸受または下軸受または
その両軸受のフランジ端面との半径方向接触幅を偏心寸
法の2倍より小さくし、ローラの端面と上軸受または下
軸受またはその両軸受のフランジ端面との接触面のうち
常時接触し摺動し続ける面がないようにしたので、ロー
ラと上軸受または下軸受またはその両軸受との間に潤滑
油が停溜したり、摩耗粉等異物が停溜し異常摩耗を発生
したりすることを防止できる効果がある。According to the present invention, the end surface of the roller, which is in contact with the flange end surface of the upper bearing or the lower bearing or both of the bearings, is tapered or stepped, and the end surface of the roller and the flange end surface of the upper bearing or the lower bearing or the both end bearings are radially arranged. The contact width is made smaller than twice the eccentric dimension so that there is no contact surface between the end surface of the roller and the flange end surface of the upper bearing or the lower bearing or both of the bearings that is always in contact with and sliding on. There is an effect that it is possible to prevent the lubricating oil from being accumulated between the upper bearing and the lower bearing, or both the bearings, and the foreign matter such as abrasion powder from being accumulated to cause abnormal wear.
第1図は本発明の一実施例のロータリー式密閉形圧縮機
の要部断面図、第2図は第1図のA−A矢視断面図、第
3図は本発明のローラ端面接触幅と偏心寸法の関係を説
明する線図、第4図は従来のロータリー式密閉形圧縮機
の縦断面図、第5図は第4図の要部断面図である。 1……密閉形容器、2……電動要素、3……圧縮要素、
4……固定子、5……回転子、6……シャフト、7……
上軸受、8……下軸受、9……シリンダ、10……ロー
ラ、11……ベーン、12……低圧室、13……吐出管、14,1
5……軌跡、20……ローラ、21,22……段差、16……シリ
ンダ室。FIG. 1 is a sectional view of a main part of a rotary hermetic compressor of an embodiment of the present invention, FIG. 2 is a sectional view taken along the line AA of FIG. 1, and FIG. 3 is a roller end surface contact width of the present invention. And FIG. 4 is a vertical sectional view of a conventional rotary hermetic compressor, and FIG. 5 is a sectional view of a main part of FIG. 1 ... Closed container, 2 ... Electric element, 3 ... Compression element,
4 ... Stator, 5 ... Rotor, 6 ... Shaft, 7 ...
Upper bearing, 8 ... Lower bearing, 9 ... Cylinder, 10 ... Roller, 11 ... Vane, 12 ... Low pressure chamber, 13 ... Discharge pipe, 14,1
5 …… Locus, 20 …… Roller, 21, 22 …… Step, 16 …… Cylinder chamber.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 上妻 康夫 茨城県日立市久慈町4026番地 株式会社 日立製作所日立研究所内 (72)発明者 中川 雄策 茨城県日立市久慈町4026番地 株式会社 日立製作所日立研究所内 (72)発明者 岩田 博 神奈川県横浜市戸塚区吉田町292番地 株式会社日立製作所家電研究所内 (56)参考文献 特公 昭58−36196(JP,B2) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yasuo Uezuma 4026 Kujimachi, Hitachi, Hitachi, Ibaraki Prefecture Hitachi Research Laboratory Ltd. (72) Yusaku Nakagawa 4026 Kujicho, Hitachi, Hitachi Ibaraki Hitachi, Ltd. In the laboratory (72) Inventor Hiroshi Iwata 292 Yoshida-cho, Totsuka-ku, Yokohama-shi, Kanagawa Inside the Home Appliances Research Laboratory, Hitachi, Ltd. (56) References Japanese Patent Publication Sho 58-36196 (JP, B2)
Claims (1)
要素を配設し、上記圧縮要素はシャフトを保持する上軸
受及び下軸受のフランジ端面にてシリンダを挟持し、上
記シャフトの偏心部に回転自在に嵌合したローラがシリ
ンダ内を回転圧縮し、上記ローラの肉厚がシャフト偏心
部の偏心寸法の2倍より大きな寸法を有するロータリー
式密閉形圧縮機において、上記上軸受または下軸受また
はその両軸受のフランジ端面に接する上記ローラの端面
にテーパまたは段差をつけ、上記ローラの端面と上記上
軸受または下軸受またはその両軸受の上記フランジ端面
との半径方向接触幅を上記偏心寸法の2倍より小さく
し、上記ローラの端面と上記上軸受または下軸受または
その両軸受の上記フランジ端面との接触面のうち常時接
触し摺動し続ける面がないようにしたことを特徴とする
ロータリー式密閉形圧縮機。1. An electric element is disposed on an upper part of a hermetic container, and a compression element is disposed on a lower part thereof. The compression element holds a cylinder between flange end faces of an upper bearing and a lower bearing for holding a shaft, and the eccentricity of the shaft. In a rotary hermetic compressor having a roller that is rotatably fitted in the shaft portion and rotationally compresses in the cylinder, and the wall thickness of the roller is larger than twice the eccentric dimension of the shaft eccentric portion, the upper bearing or the lower bearing The end surface of the roller that is in contact with the flange end surface of the bearing or both bearings is tapered or stepped, and the radial contact width between the end surface of the roller and the flange end surface of the upper bearing or the lower bearing or both bearings is the eccentric dimension. Of the contact surface between the end surface of the roller and the flange end surface of the upper bearing or the lower bearing or both of the bearings, which is in constant contact and continues to slide. Rotary hermetic compressor, characterized in that it has so no.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62326928A JP2510639B2 (en) | 1987-12-25 | 1987-12-25 | Rotary type hermetic compressor |
KR1019880017024A KR890010427A (en) | 1987-12-25 | 1988-12-20 | Rotary Hermetic Compressor |
KR9201285U KR920008773Y1 (en) | 1987-12-25 | 1992-01-29 | Hermetic rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62326928A JP2510639B2 (en) | 1987-12-25 | 1987-12-25 | Rotary type hermetic compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH01170784A JPH01170784A (en) | 1989-07-05 |
JP2510639B2 true JP2510639B2 (en) | 1996-06-26 |
Family
ID=18193329
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP62326928A Expired - Fee Related JP2510639B2 (en) | 1987-12-25 | 1987-12-25 | Rotary type hermetic compressor |
Country Status (2)
Country | Link |
---|---|
JP (1) | JP2510639B2 (en) |
KR (1) | KR890010427A (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103742411B (en) * | 2013-12-23 | 2016-07-06 | 广东美芝制冷设备有限公司 | Compressor, air-conditioner and hot water machine |
CN106122019B (en) * | 2016-08-09 | 2018-06-08 | 珠海凌达压缩机有限公司 | Rotary compressor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5836196A (en) * | 1981-08-27 | 1983-03-03 | Mitsubishi Heavy Ind Ltd | Controlling method for stepping motor |
-
1987
- 1987-12-25 JP JP62326928A patent/JP2510639B2/en not_active Expired - Fee Related
-
1988
- 1988-12-20 KR KR1019880017024A patent/KR890010427A/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
KR890010427A (en) | 1989-08-08 |
JPH01170784A (en) | 1989-07-05 |
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