JPS6146486A - Vane type rotary compressor - Google Patents
Vane type rotary compressorInfo
- Publication number
- JPS6146486A JPS6146486A JP16901584A JP16901584A JPS6146486A JP S6146486 A JPS6146486 A JP S6146486A JP 16901584 A JP16901584 A JP 16901584A JP 16901584 A JP16901584 A JP 16901584A JP S6146486 A JPS6146486 A JP S6146486A
- Authority
- JP
- Japan
- Prior art keywords
- vane
- rotor
- cam ring
- sliding
- rotary compressor
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
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】
(産業上の利用分野)
本発明はベーン型回転圧縮機、たとえば、冷房装置に使
用される冷媒ガス等の気体を圧縮するベーン型回転圧縮
機に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane-type rotary compressor, for example, a vane-type rotary compressor that compresses gas such as refrigerant gas used in an air-conditioning device.
(従来の技術)
従来のこの種のベーン型回転圧縮機としては、たとえば
第2図および第3図に示されるような技術(実開昭58
−106582号公報)が知られている。第2図は、従
来のベーン型回転圧縮機のカムリング1およびロータ2
の周辺部を示すものである。カムリング1は第2図(a
lに示すように、内周の断面が略楕円形の筒体に形成さ
れており、その内周面形状は小径部と大径部とにより構
成されている。カムリング1の両端は第2図(b)に示
すようにフロントプレート3およびリヤプレート4によ
り閉止され、カムリング1内に、沖に小径部に摺接して
収納されたロータ2は、これらの両プレート3.4に軸
受5a、5bを介して回転自在に支持されている。すな
わち、ロータ2の回転軸2aは両プレート3.4にニー
ドル軸受5a、5bを介して支持されている。また、ロ
ータ2には略半径方向に形成されたスリット2bが、円
周方向に間隔をおいて複数設けられている。スリン)
2 bはロータ2の半径外方に開口し、半径内方は途中
で閉止し、軸方向は両端面に開口している。(Prior Art) Conventional vane type rotary compressors of this type include, for example, the technology shown in FIGS.
-106582) is known. Figure 2 shows the cam ring 1 and rotor 2 of a conventional vane type rotary compressor.
This shows the surrounding area of . The cam ring 1 is shown in Figure 2 (a
As shown in FIG. 1, the inner periphery is formed into a cylindrical body with a substantially elliptical cross section, and the shape of the inner periphery is composed of a small diameter portion and a large diameter portion. Both ends of the cam ring 1 are closed by a front plate 3 and a rear plate 4, as shown in FIG. 3.4 via bearings 5a and 5b so as to be rotatable. That is, the rotating shaft 2a of the rotor 2 is supported by both plates 3.4 via needle bearings 5a, 5b. Further, the rotor 2 is provided with a plurality of slits 2b formed substantially in the radial direction at intervals in the circumferential direction. Surin)
2b is opened radially outward of the rotor 2, closed radially inward partway, and opened at both end faces in the axial direction.
スリット2bには第3図(alに示すような矩形板状の
ベーン6が、ロータ2の略半径方向に摺動自在に嵌合し
ている。ベーン6の先端部6aはスIル;zト2bから
ロータ2の半径外方に突出し、ヘーン6の背面部6bは
スリ7)2bの閉止側に収納され、ベーン6の背面部6
bにはスリット2bの閉止側に充填された潤滑油の背圧
が働いている。ベーン6はロータ2の回転に伴いスリン
1−2b内を摺動し、遠心力および前記背圧によりその
先端が常にカムリング1の内周面に摺接して、カムリン
グ1とロータ2との間にポンプ室7を画成する。このポ
ンプ室7はロータ2の回転により吸入室として、あるい
は圧縮室として作用する。ベーン6は、従来たとえば、
Al−3t合金を熱処理後に研削およびバレル研摩にて
仕上げたものを用いており、その硬度はHRB 70〜
90(ロックウェルBスケール)、第3図(blに示す
ような表面粗度は0.2〜086μRα(平均粗度)で
ある。A rectangular plate-shaped vane 6 as shown in FIG. The back side 6b of the vane 6 is housed in the closing side of the slot 7) 2b, and the back side 6b of the vane 6 protrudes outward from the radius of the rotor 2.
The back pressure of the lubricating oil filled on the closing side of the slit 2b is acting on the slit 2b. The vane 6 slides within the ring 1-2b as the rotor 2 rotates, and due to the centrifugal force and the back pressure, the tip of the vane 6 always slides against the inner circumferential surface of the cam ring 1, so that there is a gap between the cam ring 1 and the rotor 2. A pump chamber 7 is defined. This pump chamber 7 acts as a suction chamber or a compression chamber as the rotor 2 rotates. Conventionally, the vane 6 is, for example,
The Al-3t alloy is heat-treated and finished by grinding and barrel polishing, and its hardness is HRB 70~
90 (Rockwell B scale), the surface roughness as shown in FIG. 3 (bl) is 0.2 to 086 μRα (average roughness).
(発明が解決しようとする問題点)
しかしながら、どのような従来のベーンにあっては、ロ
ータ2の回転に伴ってベーン6の背面部6bに働く背圧
(7〜15 kg / c+a )および遠心力Fによ
りベーン6の先端部6aは常にカムリング1の内周面に
強く押圧されているため、カムリング1とベーン6との
間に油膜切れが生じてフリクションが増大し、カムリン
グ1の内周面およびベーン6の先端部6aに著しく摩耗
が生じるおそれがある。また、ベーン6は回転方向と反
対方向に反力を受けながらスリット2b内を出没摺動す
るため、ベーン6の回転方向と反対側の面はその面と接
するスリット2bの摺動面2Cに大きな力で押圧されて
摺接し、やはりロータ2とベーン6との間に油膜切れが
生じてフリクションが増大し、ベーン6の回転方向と反
対側の面6Cおよびその面と接するスリット2bの摺動
面2Cに著しく摩耗が生じるおそれがあるという問題点
があった。そこで、本flは、ベーン6の、少なくとも
スリット2bの摺動面2Cおよびカムリング1の内周面
と接触する表面を所定の粗度で形成するとともに、その
ベーン6の表面にその所定の粗度より大きな深さの油溜
用穴を多数散在させて形成することにより、カムリング
1、ロータ2、およびベーン6に摩耗が生じることを防
止することを目的とする。(Problems to be Solved by the Invention) However, in any conventional vane, back pressure (7 to 15 kg/c+a) and centrifugal Since the tip 6a of the vane 6 is always strongly pressed against the inner circumferential surface of the cam ring 1 by the force F, an oil film breaks down between the cam ring 1 and the vane 6, increasing friction, and the inner circumferential surface of the cam ring 1 Also, there is a risk that the tip portion 6a of the vane 6 will be significantly worn. In addition, since the vane 6 slides in and out of the slit 2b while receiving a reaction force in the direction opposite to the rotation direction, the surface opposite to the rotation direction of the vane 6 has a large contact with the sliding surface 2C of the slit 2b. The rotor 2 and the vane 6 are pressed by force and come into sliding contact, and as expected, an oil film breaks down between the rotor 2 and the vane 6, increasing friction, and the surface 6C opposite to the rotational direction of the vane 6 and the sliding surface of the slit 2b in contact with that surface. There was a problem in that there was a risk that 2C would be significantly worn. Therefore, in this fl, the surface of the vane 6 that contacts at least the sliding surface 2C of the slit 2b and the inner peripheral surface of the cam ring 1 is formed with a predetermined roughness, and the surface of the vane 6 is formed with the predetermined roughness. The purpose is to prevent wear on the cam ring 1, rotor 2, and vane 6 by forming a large number of oil sump holes with a larger depth in a scattered manner.
(問題点を解決するための手段)
このような目的を達成するため、本発明は、ロータに略
半径方向に形成されたスリットに摺動自在に嵌合し、そ
の先端部がロータの回転に伴ないロータを収納するカム
リングの内周面に常に摺接するベーンを有するベーン型
回転圧縮機において、少なくとも前記スリットの摺動面
および前記カムリングの内周面と接触する前記ベーンの
表面を所定の粗度で形成するとともに、この表面に前記
粗度より大きな深さの油溜用穴を多数散在させて形成し
たことを構成としている。(Means for Solving the Problems) In order to achieve such an object, the present invention is provided with a slit that is slidably fitted into a slit formed in a substantially radial direction in a rotor, and whose tip portion is adapted to rotate as the rotor rotates. In a vane-type rotary compressor having vanes that are always in sliding contact with the inner circumferential surface of a cam ring that accommodates a rotor, the surface of the vane that is in contact with at least the sliding surface of the slit and the inner circumferential surface of the cam ring is roughened to a predetermined roughness. The surface roughness is formed with a large number of oil sump holes having a depth greater than the roughness described above.
(作用)
このような構成を有する本発明は、ベーンの表面に多数
形成された油溜用穴に一時的に潤滑油を貯えることがで
きるため、油膜切れが生じようとすると速やかに油を油
膜部に供給して油膜切れを防止することができる。(Function) The present invention having such a configuration can temporarily store lubricating oil in the many oil sump holes formed on the surface of the vane, so that when the oil film is about to run out, the oil can be quickly removed from the oil film. It is possible to prevent the oil film from running out by supplying it to the parts.
(実施例) 以下、本発明の実施例に基づいて説明する。(Example) Hereinafter, the present invention will be explained based on examples.
第1図は本発明の一実施例に係るベーン型回転圧縮機の
ベーンを示す図である。他の構成は前記従来のベーン型
回転圧縮機と共通するため省略する。FIG. 1 is a diagram showing a vane of a vane type rotary compressor according to an embodiment of the present invention. The other configurations are the same as those of the conventional vane type rotary compressor and will therefore be omitted.
第1図(a)において、16はロータ2に略半径方向に
形成さ棺たスリット2bに摺動自在に嵌合するベーンで
あり、16aはロータ2の回転に伴いカムリング1の内
周面に常に摺接する先端部であり、16bはスリット2
bの閉止側に収納される背面部であり、16Cはロータ
2のスリ・ノ)2bの摺動面2Cと摺動する摺動面であ
る。In FIG. 1(a), 16 is a vane that is slidably fitted into a slit 2b formed in the rotor 2 in a substantially radial direction, and 16a is a vane that fits into the inner peripheral surface of the cam ring 1 as the rotor 2 rotates. The tip is always in sliding contact, and 16b is the slit 2.
16C is a sliding surface that slides on the sliding surface 2C of the slot 2b of the rotor 2.
ベーン16の先端部16aおよび摺動面16cの表面は
、第1図(blに示すように、相手部材と接触する最表
層面は0.1μRa以下の表面粗度(所定の粗度)で形
成されており、さらに、このような面にこの粗度より大
きな深さ、たとえば最大深さが少なくとも1μの油溜用
穴20が多数散在して形成されている。このような表面
を形成する方法としては、熱処理、研削後のベーンに以
下のような処理を施すことが考えられる。As shown in FIG. 1 (bl), the surfaces of the tip portion 16a and the sliding surface 16c of the vane 16 are formed with a surface roughness (predetermined roughness) of 0.1 μRa or less on the outermost surface that contacts the mating member. Further, a large number of oil sump holes 20 having a depth greater than this roughness, for example, a maximum depth of at least 1 μm, are scattered and formed on such a surface. As a possible solution, the following treatment may be applied to the vane after heat treatment and grinding.
(イ)Pタイプ(粒状)あるいはNタイプ(くさび状)
のメディア(砥石)を用いた荒バレルにより前記の深い
油溜用穴20をまず形成し、次にSタイプ(粒状)のメ
ディアを用いた仕上バレルにより0.1μRa以下の粗
度の表面を形成する。(a) P type (granular) or N type (wedge shape)
First, the deep oil sump hole 20 is formed using a rough barrel using S type media (grindstone), and then a surface with a roughness of 0.1 μRa or less is formed using a finishing barrel using S type (granular) media. do.
(ロ)粒径20μ前後のアルミナ砥粒にてラッピング加
工を行うことにより前記の深い油溜用穴20をまず形成
し、次に粒径0.3μ前後のアルミナ砥粒にてボリシン
グ加工を行うことにより0゜1μRa以下の粗度の表面
を形成する。(b) The deep oil sump hole 20 is first formed by lapping with alumina abrasive grains with a grain size of around 20 μm, and then boring is performed with alumina abrasive grains with a grain size of around 0.3 μm. This forms a surface with a roughness of 0°1 μRa or less.
(ハ)粒径20μ前後のアルミナ砥粒を用いてショツト
ブラスト加工を行うことにより前記の深い油溜用穴20
を形成し、次に粒径0.3μ前後のアルミナ砥粒にてポ
リシング加工を行うことによ、す0.1μRa以下の粗
度の表面を形成する。(c) The deep oil sump hole 20 is formed by shot blasting using alumina abrasive grains with a grain size of around 20μ.
is formed, and then polished using alumina abrasive grains having a grain size of approximately 0.3 μm to form a surface with a roughness of 0.1 μRa or less.
(ニ)電解研摩加工により前記の深い油溜用穴20を形
成し、次に粒径0.3μ前後のアルミナ砥粒にでボリシ
ング加工を行うことにより0.1μRa以下の粗度の表
面を形成する。(d) The deep oil sump hole 20 is formed by electrolytic polishing, and then a surface with a roughness of 0.1 μRa or less is formed by boring with alumina abrasive grains having a particle size of around 0.3 μ. do.
(ホ)エツチング腐食加工により前記の深い油溜用穴2
0を形成し、次に粒径0.3μ前後のアルミナ砥粒にて
ボリシング加工を行うことにより0.1μRa以下の粗
度の表面を形成する。(E) The deep oil sump hole 2 is made by etching corrosion processing.
0 is formed, and then a surface with a roughness of 0.1 μRa or less is formed by performing a boring process using alumina abrasive grains having a particle size of approximately 0.3 μRa.
この実施例に係るベーン16をベーン型回転圧縮機に用
いた場合、ベーン16の表面に多数散在して形成された
油溜用穴20に一時的に潤滑油を貯えることができるた
め、カムリング1の内周面とベーン16の先端部16a
、あるいはロータ2のスリット2bの摺動面2Cとベー
ン16の摺動面16cとがたがいに強い力で押圧されて
油膜切れが生じようとしても、油溜用穴20内の油が速
やかに油膜部に供給されて油膜切れを防止することがで
きる。このことにより、相互間のフリクションの増大を
防止して、カムリング1の内周面、ベーン16の先端部
16aおよび摺動面16C1あるいはロータ2回転時の
反力によりベーン16の摺動面16cと摺動するロータ
2の摺動面2cに摩耗が生じることを有効に防止するこ
とができる。When the vane 16 according to this embodiment is used in a vane-type rotary compressor, lubricating oil can be temporarily stored in the oil reservoir holes 20 formed in large numbers scattered on the surface of the vane 16, so that the cam ring 1 The inner peripheral surface of the vane 16 and the tip 16a of the vane 16
, or even if the sliding surface 2C of the slit 2b of the rotor 2 and the sliding surface 16c of the vane 16 are pressed against each other with a strong force and an oil film is about to run out, the oil in the oil sump hole 20 will quickly form an oil film. This can prevent the oil film from running out. This prevents an increase in friction between the inner peripheral surface of the cam ring 1, the tip 16a of the vane 16, and the sliding surface 16C1, or the sliding surface 16c of the vane 16 due to the reaction force when the rotor rotates twice. It is possible to effectively prevent wear on the sliding surface 2c of the sliding rotor 2.
なお、前記実施例においては、少なくともベーン16の
先端部16aおよび摺動面16cに多数の油溜用穴20
を設ければ足りるが、その形成方法によってはベーン1
6の全表面に油溜用穴20を設けてもよい。In the embodiment described above, a large number of oil sump holes 20 are provided at least in the tip portion 16a and the sliding surface 16c of the vane 16.
It is sufficient to provide vane 1, but depending on the method of formation, vane 1
Oil sump holes 20 may be provided on the entire surface of 6.
(発明の効果)
以上説明したように、本発明によれば、各摺動部の油膜
切れを防止することにより、カムリング、ロータ、およ
びベーンに摩耗が生じることを防止することができる。(Effects of the Invention) As described above, according to the present invention, by preventing the oil film from running out on each sliding portion, it is possible to prevent wear on the cam ring, rotor, and vane.
第1図(a)は本発明の一実施例に係るベーン型回転圧
縮機のベーンの斜視図、第1図(blは第1図(a)に
示すベーンの表面の状態を示す拡大断面図、第2図は従
来のベーン型回転圧縮機のカムリングおよびロータの周
辺部を示し、第2図(alはその部分断面正面図、第2
図(b)はその断面側面図、第3図は第2図に示すベー
ン型回転圧縮機に応用されるベーンを示し、第3図(a
lはその斜視図、第3図(b)はその表面の粗さ状態を
示す拡大断面図である。
1−・−一カムリング、
2−−−−−一ロータ、
2b−−−−−−スリット、
2cm−−−−一摺動面、
16−−−−−−ベーン、
16 a −−−−−一先端部、
16cm・−・摺動面、
20−・−油溜用穴。FIG. 1(a) is a perspective view of a vane of a vane-type rotary compressor according to an embodiment of the present invention, and FIG. 1(bl is an enlarged sectional view showing the state of the surface of the vane shown in FIG. 1(a). , FIG. 2 shows the cam ring and rotor surroundings of a conventional vane-type rotary compressor, and FIG.
Figure (b) is its cross-sectional side view, Figure 3 shows the vane applied to the vane type rotary compressor shown in Figure 2, and Figure 3 (a) shows the vane applied to the vane type rotary compressor shown in Figure 2.
1 is a perspective view thereof, and FIG. 3(b) is an enlarged sectional view showing the roughness of the surface. 1-----One cam ring, 2-------One rotor, 2b-----Slit, 2cm----One sliding surface, 16-------Vane, 16 a---- -One tip, 16cm--Sliding surface, 20--Oil sump hole.
Claims (1)
いロータを収納するカムリングの内周面に常に摺接する
ベーンを有するベーン型回転圧縮機において、少なくと
も前記スリットの摺動面および前記カムリングの内周面
と接触する前記ベーンの表面を所定の粗度で形成すると
ともに、この表面に前記粗度より大きな深さの油溜用穴
を多数散在させて形成したことを特徴とするベーン型回
転圧縮機。[Claims] A vane that is slidably fitted into a slit formed in a substantially radial direction in the rotor, and whose tip always slides into contact with the inner circumferential surface of a cam ring that houses the rotor as the rotor rotates. In the vane type rotary compressor, at least the surface of the vane that contacts the sliding surface of the slit and the inner circumferential surface of the cam ring is formed with a predetermined roughness, and the surface is provided with a surface having a depth greater than the roughness. A vane-type rotary compressor characterized by a large number of oil sump holes formed in a scattered manner.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16901584A JPS6146486A (en) | 1984-08-13 | 1984-08-13 | Vane type rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16901584A JPS6146486A (en) | 1984-08-13 | 1984-08-13 | Vane type rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6146486A true JPS6146486A (en) | 1986-03-06 |
Family
ID=15878746
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP16901584A Pending JPS6146486A (en) | 1984-08-13 | 1984-08-13 | Vane type rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6146486A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8480386B2 (en) | 2008-11-04 | 2013-07-09 | Joma-Polytec Gmbh | Vane for a single-vane vacuum pump |
CN106014985A (en) * | 2016-06-12 | 2016-10-12 | 浙江百达精工股份有限公司 | Rotary piston compressor blade, manufacturing method of oil storing grains in rotary piston compressor blade, and compressor |
WO2018154716A1 (en) * | 2017-02-24 | 2018-08-30 | 三菱電機株式会社 | Rotary compressor and manufacturing method for rotary compressor |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5114642U (en) * | 1974-07-17 | 1976-02-03 | ||
JPS5851419U (en) * | 1981-10-02 | 1983-04-07 | 株式会社東芝 | Oil-filled electrical equipment with pressure-sensitive relay |
-
1984
- 1984-08-13 JP JP16901584A patent/JPS6146486A/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5114642U (en) * | 1974-07-17 | 1976-02-03 | ||
JPS5851419U (en) * | 1981-10-02 | 1983-04-07 | 株式会社東芝 | Oil-filled electrical equipment with pressure-sensitive relay |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8480386B2 (en) | 2008-11-04 | 2013-07-09 | Joma-Polytec Gmbh | Vane for a single-vane vacuum pump |
CN106014985A (en) * | 2016-06-12 | 2016-10-12 | 浙江百达精工股份有限公司 | Rotary piston compressor blade, manufacturing method of oil storing grains in rotary piston compressor blade, and compressor |
WO2018154716A1 (en) * | 2017-02-24 | 2018-08-30 | 三菱電機株式会社 | Rotary compressor and manufacturing method for rotary compressor |
CN110312870A (en) * | 2017-02-24 | 2019-10-08 | 三菱电机株式会社 | The manufacturing method of rotary compressor and rotary compressor |
JPWO2018154716A1 (en) * | 2017-02-24 | 2019-11-07 | 三菱電機株式会社 | Rotary compressor and method for manufacturing rotary compressor |
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