JPH02149793A - Bearing of rotary compressor - Google Patents
Bearing of rotary compressorInfo
- Publication number
- JPH02149793A JPH02149793A JP30303288A JP30303288A JPH02149793A JP H02149793 A JPH02149793 A JP H02149793A JP 30303288 A JP30303288 A JP 30303288A JP 30303288 A JP30303288 A JP 30303288A JP H02149793 A JPH02149793 A JP H02149793A
- Authority
- JP
- Japan
- Prior art keywords
- hole
- large diameter
- bearing
- ceramics
- parts
- 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
- 239000000919 ceramic Substances 0.000 claims abstract description 18
- 150000002736 metal compounds Chemical class 0.000 claims description 3
- 229910052751 metal Inorganic materials 0.000 abstract description 13
- 239000002184 metal Substances 0.000 abstract description 13
- 229910001018 Cast iron Inorganic materials 0.000 abstract description 3
- 229910052582 BN Inorganic materials 0.000 abstract description 2
- PZNSFCLAULLKQX-UHFFFAOYSA-N Boron nitride Chemical compound N#B PZNSFCLAULLKQX-UHFFFAOYSA-N 0.000 abstract description 2
- 229910052581 Si3N4 Inorganic materials 0.000 abstract description 2
- TWNQGVIAIRXVLR-UHFFFAOYSA-N oxo(oxoalumanyloxy)alumane Chemical compound O=[Al]O[Al]=O TWNQGVIAIRXVLR-UHFFFAOYSA-N 0.000 abstract description 2
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 abstract description 2
- 229910010271 silicon carbide Inorganic materials 0.000 abstract description 2
- HQVNEWCFYHHQES-UHFFFAOYSA-N silicon nitride Chemical compound N12[Si]34N5[Si]62N3[Si]51N64 HQVNEWCFYHHQES-UHFFFAOYSA-N 0.000 abstract description 2
- 229910000765 intermetallic Inorganic materials 0.000 abstract 1
- 150000002505 iron Chemical class 0.000 abstract 1
- 238000000034 method Methods 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 150000002739 metals Chemical class 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 1
- CPSYWNLKRDURMG-UHFFFAOYSA-L hydron;manganese(2+);phosphate Chemical compound [Mn+2].OP([O-])([O-])=O CPSYWNLKRDURMG-UHFFFAOYSA-L 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000004381 surface treatment Methods 0.000 description 1
Landscapes
- Applications Or Details Of Rotary Compressors (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、例えばエアコン、冷蔵庫等の冷凍回路に使用
されるロータリコンプレッサの軸受に関するものである
。DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a bearing for a rotary compressor used, for example, in a refrigeration circuit of an air conditioner, a refrigerator, or the like.
（従来の技術）
従来コンプレッサーは、その高速化に伴なうＰＶ値の上
昇、あるいは軸の曲がりによる第５図に示すような極圧
上昇を防止するため、摺動部にリン酸マンガン処理等の
表面処理を施すようにしている。また、軸の剛性アップ
させることによって、曲がりを減らしたり、摺動部分の
長さを増すことによって、圧力の分散を図るようにして
いる。(Prior art) In conventional compressors, sliding parts are treated with manganese phosphate, etc. in order to prevent an increase in PV value due to higher speeds or an increase in extreme pressure as shown in Figure 5 due to bending of the shaft. surface treatment. In addition, by increasing the rigidity of the shaft, bending is reduced, and by increasing the length of the sliding portion, pressure is distributed.
しかしながら上記の方法には次のような欠点があった。However, the above method had the following drawbacks.
すなわち、摺動部に表面処理を施す方法にあっては、長
期摺動により処理層が消失すると、その効果が激減する
。That is, in the method of surface-treating the sliding portion, when the treated layer disappears due to long-term sliding, the effect is drastically reduced.
また、軸剛性をアップさせる方法にあっては、剛性向上
に伴ない加工条件が厳しくなり加工しにくくなるととも
にコストが大１１】に上昇する。Furthermore, in the method of increasing the shaft rigidity, the processing conditions become stricter as the rigidity is improved, making it difficult to process and increasing the cost by a large amount.
さらに、摺動部長さを増加させると逆に摺動ロスが増大
する。Furthermore, increasing the length of the sliding portion conversely increases sliding loss.
そこで、このような欠点を解消するために、第６図に示
すような軸受が開発された。この軸受は、金属製の軸受
本体１１の孔１２の端部内周面に、前記孔１２の内径よ
り大径の大径部１３を設けるとともに、孔に金属製のブ
ツシュ１４を嵌合し、ブツシュ１４と大径部１３との間
に空間１５を形成するように構成されている。Therefore, in order to eliminate such drawbacks, a bearing as shown in FIG. 6 was developed. This bearing is provided with a large diameter portion 13 having a larger diameter than the inner diameter of the hole 12 on the inner circumferential surface of the end of a hole 12 of a metal bearing body 11, and a metal bushing 14 is fitted into the hole. A space 15 is formed between the large diameter portion 14 and the large diameter portion 13 .
（発明が解決しようとする課題）
ところで、上記の軸受にあっては、ブツシュ１４の耐摩
耗性が充分にｉ４られないという問題点があった。(Problems to be Solved by the Invention) However, in the above-mentioned bearing, there was a problem in that the wear resistance of the bushing 14 was not sufficiently improved.
一方、内周面に大径部１３を有しない軸受本体にセラミ
ックブツシュを嵌合した軸受にあっては、セラミックの
耐摩耗性が高く金属との移着が起こりにくいが、一定の
軸受負荷になると結局金属がセラミックスに転移して金
属同士の凝着が起こるという問題点があった。On the other hand, in the case of a bearing in which a ceramic bushing is fitted to a bearing body that does not have a large diameter part 13 on the inner circumferential surface, ceramic has high wear resistance and is less likely to transfer to metal; However, there was a problem in that the metals eventually transferred to the ceramics and the metals adhered to each other.
本発明は、上記問題点を解決し、高い運転圧力および高
い周波数での運転を可能としたロータリコンプレッサの
軸受を提供することを目的とする。SUMMARY OF THE INVENTION An object of the present invention is to provide a bearing for a rotary compressor that solves the above problems and enables operation at high operating pressures and high frequencies.
（課題を解決するための手段）
本発明は、上記課題を解決するためになされたものであ
って、金属化合物からなり筒状に形成された軸受本体と
、この軸受本体の孔の両端部内周面に前記孔の内径より
大径に形成された大径部と、セラミックからなり前記孔
の内周に嵌合された筒状のブツシュとを備えた構成とさ
れている。(Means for Solving the Problems) The present invention has been made to solve the above problems, and includes a bearing body formed in a cylindrical shape made of a metal compound, and an inner periphery of both ends of a hole in the bearing body. It is configured to include a large diameter portion formed on the surface to have a diameter larger than the inner diameter of the hole, and a cylindrical bushing made of ceramic and fitted to the inner periphery of the hole.
（作 用）
本発明にあって、金属化合物からなり筒状に形成された
軸受本体と、この軸受本体の孔の両端部内周面に前記孔
の内径より大径に形成された大径部と、セラミックから
なり前記孔の内周に嵌合された筒状のブツシュとを碕え
ているから、全体負荷は一定でも極圧を下げセラミック
の耐摩耗性能を最大限に生かすことができ、したがって
、コンプレッサーの運転圧力を高くすることができると
ともに、高い周波数での運転を行うことができる。(Function) In the present invention, there is provided a bearing body made of a metal compound and formed into a cylindrical shape, and a large diameter portion formed on the inner circumferential surface of both ends of the hole of the bearing body to have a diameter larger than the inner diameter of the hole. , and a cylindrical bushing made of ceramic and fitted on the inner periphery of the hole, the extreme pressure can be lowered even if the overall load is constant, and the wear resistance performance of the ceramic can be made to the maximum. The operating pressure of the compressor can be increased, and the compressor can be operated at a high frequency.
（実施例）
以下、本発明の一実施例について、第１図ないし第４図
を参照して説明する。(Example) An example of the present invention will be described below with reference to FIGS. 1 to 4.
第２図は本発明に係るロータリコンプレッサの要部を示
す図であって、図中符号２１はモーターローターを示す
。このモーターローター２１には、シャフト２２が設け
られており、このシャフト２２の下端部には、ローター
２３が設けられている。ローター２３の外周にはシリン
ダ２４が配設されており、このシリンダ２４の上側には
主軸受２５、下側には副軸受２６が設けられている。FIG. 2 is a diagram showing the main parts of the rotary compressor according to the present invention, and the reference numeral 21 in the figure indicates a motor rotor. This motor rotor 21 is provided with a shaft 22, and a rotor 23 is provided at the lower end of this shaft 22. A cylinder 24 is arranged around the outer periphery of the rotor 23, and a main bearing 25 is provided on the upper side of the cylinder 24, and a sub-bearing 26 is provided on the lower side.
このうち、主軸受２５は、第１図に示すように構成され
ており、鋳鉄系の金属からなる筒状のボス部２６を有し
ている。このボス部２６の孔２７の両端部には、孔２７
より大径の大径部２８が形成されており、孔２７の内周
には、酸化アルミニウム、炭化ケイ素、窒化ケイ素、窒
化ホウ素等のセラミックスからなる筒状のブツシュ２９
が嵌合されている。そして、ブツシュ２つの両端部と大
径部２８との間にリング溝３０が形成されている。Among these, the main bearing 25 is configured as shown in FIG. 1, and has a cylindrical boss portion 26 made of cast iron metal. Holes 27 are provided at both ends of the hole 27 of this boss portion 26.
A large diameter portion 28 having a larger diameter is formed, and a cylindrical bush 29 made of ceramic such as aluminum oxide, silicon carbide, silicon nitride, boron nitride, etc. is formed on the inner periphery of the hole 27.
are fitted. A ring groove 30 is formed between both ends of the two bushings and the large diameter portion 28.
また、ボス部２６の上端部外周２８には、フランジ状の
ツバ部３１が形成されている。Further, a flange-like collar portion 31 is formed on the outer periphery 28 of the upper end portion of the boss portion 26 .
このように、上記実施例にあっては、鋳鉄系金属からな
るボス部２６の孔２７の両端部に大径部２８を設け、孔
２７の内周にセラミック製のブツシュ２９を嵌合し、大
径部２８とブツシュ２つとの間にリング溝３０を形成し
ているから、第３図に示すように、全体負荷は一定でも
極圧を下げセラミックの耐摩耗性能を最大限に生かすこ
とができるとともに、セラミックスの弱点である衝撃繰
返し圧力をリング溝で吸収することができる。したがっ
て、より高い運転圧力が可能となり、コンプレッサーの
使用圧力範囲を拡大することができる。また、高い周波
数での運転が可能となることから、コンプレッサーの使
用周波数範囲を拡大し、エアコンの最大能力をアップし
、暖房時の立上り特性を向上することができる。Thus, in the above embodiment, the large diameter portions 28 are provided at both ends of the hole 27 of the boss portion 26 made of cast iron metal, and the ceramic bushing 29 is fitted into the inner periphery of the hole 27. Since the ring groove 30 is formed between the large diameter portion 28 and the two bushings, as shown in Fig. 3, even if the overall load is constant, the extreme pressure can be lowered and the wear resistance performance of the ceramic can be maximized. At the same time, the ring groove can absorb repeated impact pressure, which is a weak point of ceramics. Therefore, a higher operating pressure is possible, and the working pressure range of the compressor can be expanded. Additionally, since it is possible to operate at a higher frequency, it is possible to expand the operating frequency range of the compressor, increase the maximum capacity of the air conditioner, and improve the startup characteristics during heating.
第４図は、限界吐出圧力範囲を示す図であって、メタル
軸とメタル軸受の組合せの場合、メタル軸とメタル軸受
の組合せでリング溝が形成されている場合、メタル軸と
セラミックブツシュの組合せの場合、メタル軸とセラミ
ックブツシュの組合せでリング溝をａする場合を示して
いる。この図から、メタル軸とセラミックブツシュとの
組合せでリング溝を有する場合に、吐出圧力範囲か増加
することがわかる。FIG. 4 is a diagram showing the limit discharge pressure range, in the case of a combination of a metal shaft and a metal bearing, in the case of a combination of a metal shaft and a metal bearing with a ring groove formed, and in the case of a combination of a metal shaft and a ceramic bushing. In the case of a combination, a ring groove is formed using a combination of a metal shaft and a ceramic bushing. From this figure, it can be seen that the discharge pressure range increases when the combination of a metal shaft and a ceramic bushing has a ring groove.
以上説明したように、本発明にあっては、全体負荷は一
定でも極圧を下げセラミックの耐摩耗性能を最大限に生
かすことができ、したがって、コンプレッサーの運転圧
力を高くすることができるとともに、高い周波数での運
転を行なうことができるという効果が得られる。As explained above, in the present invention, even if the overall load is constant, the extreme pressure can be lowered and the wear resistance performance of the ceramic can be maximized, and therefore the operating pressure of the compressor can be increased. This provides the advantage of being able to operate at a high frequency.
示す断面図である。FIG.
２６・・・軸受本体、 ２９・・・ブツシュ。26...Bearing body, 29...Butshu.
Claims (1)
軸受本体の孔の両端部内周面に前記孔の内径より大径に
形成された大径部と、セラミックからなり前記孔の内周
に嵌合された筒状のブッシュとを備えたことを特長とす
るロータリコンプレッサの軸受。A bearing body made of a metal compound and formed into a cylindrical shape, a large diameter part formed on the inner circumferential surface of both ends of the hole of the bearing body with a diameter larger than the inner diameter of the hole, and a large diameter part made of ceramic and formed on the inner circumference of the hole. A rotary compressor bearing characterized by comprising a fitted cylindrical bush.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30303288A JPH02149793A (en) | 1988-11-30 | 1988-11-30 | Bearing of rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30303288A JPH02149793A (en) | 1988-11-30 | 1988-11-30 | Bearing of rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02149793A true JPH02149793A (en) | 1990-06-08 |
Family
ID=17916111
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30303288A Pending JPH02149793A (en) | 1988-11-30 | 1988-11-30 | Bearing of rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02149793A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008180228A (en) * | 2008-04-21 | 2008-08-07 | Daikin Ind Ltd | Rotary type fluid machine |
| JP2009287473A (en) * | 2008-05-29 | 2009-12-10 | Toshiba Carrier Corp | Hermetic compressor and refrigerating cycle device |
| JP2009299649A (en) * | 2008-06-17 | 2009-12-24 | Mitsubishi Electric Corp | Rotary compressor |
-
1988
- 1988-11-30 JP JP30303288A patent/JPH02149793A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008180228A (en) * | 2008-04-21 | 2008-08-07 | Daikin Ind Ltd | Rotary type fluid machine |
| JP2009287473A (en) * | 2008-05-29 | 2009-12-10 | Toshiba Carrier Corp | Hermetic compressor and refrigerating cycle device |
| JP2009299649A (en) * | 2008-06-17 | 2009-12-24 | Mitsubishi Electric Corp | Rotary compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0417762Y2 (en) | ||
| US20040022646A1 (en) | Compressor | |
| JPH02149793A (en) | Bearing of rotary compressor | |
| US4548558A (en) | Rotary compressor housing | |
| JPH0436549A (en) | Sliding member and variable frequency type refrigerant compressor using this sliding member | |
| US4084920A (en) | Arrangement for maintaining optimum minimum operating clearance between rotor and stator components of fluid-flow machines and method of operating the same | |
| EP2789807B1 (en) | Turbocharger | |
| EP0833057A2 (en) | Scroll compressor | |
| US4149823A (en) | Method of maintaining optimum minimum operating clearance between rotor and stator components of fluid-flow machines | |
| EP3555476B1 (en) | Pump sealing | |
| JPS623193A (en) | Rotary compressor | |
| JPH0436458A (en) | Sliding parts and frequency variable type refrigerant compressor using these parts | |
| JPS5934496A (en) | Vane type compressor | |
| JPH02248676A (en) | Scroll type fluid machine | |
| JPS5929793A (en) | Rotary compressor | |
| JPS6388294A (en) | Blade of rotary compressor | |
| CN207715571U (en) | A kind of rolling bearing structure of large-size asynchronous motor | |
| JPS59119087A (en) | Compressor | |
| JPH0134718Y2 (en) | ||
| US4147466A (en) | Arrangement for maintaining optimum minimum operating clearance between rotor and stator components of fluid-flow machines and the like | |
| JPS6124715Y2 (en) | ||
| JP3829616B2 (en) | Hermetic electric compressor | |
| JPH0125913B2 (en) | ||
| JPS63162987A (en) | Rotary compressor | |
| KR200218413Y1 (en) | Axial and bearing structure of rotary compressor |