JPS60145479A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPS60145479A JPS60145479A JP25131683A JP25131683A JPS60145479A JP S60145479 A JPS60145479 A JP S60145479A JP 25131683 A JP25131683 A JP 25131683A JP 25131683 A JP25131683 A JP 25131683A JP S60145479 A JPS60145479 A JP S60145479A
- Authority
- JP
- Japan
- Prior art keywords
- vane
- spring
- set value
- cylinder
- rotor
- 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.)
- Granted
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
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は家庭用空調装置などに用いられる回転式圧縮機
、特にローリングピストン式ロータリ圧縮機に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in household air conditioners, and more particularly to a rolling piston rotary compressor.
従来例の構成とその問題点
家庭用空調装置に用いられるローリングピストン式ロー
タリ圧縮機の多くは第１図に示すように、シリンダ内を
低圧室４と高圧室５とに仕切るベーン６がシリンダブロ
ック２ａに設けられ吐出室に通じた案内溝８に沿ってシ
リンダ内に出入りし、ベー７６の背面にはベー７６の先
端がロータ３の外周壁に常時押接するようにばね装置９
ａを設けており、圧縮機運転中は、ベーン６の背面に作
用する吐出圧力荷重とばね装置９ａの反力との合成３
ｌニー：ｊ
荷重の作用によってベーン６の先端はロータ３の外周壁
に押圧されたシリンダ内を低圧室４と高圧室６とに仕切
りながらロータ３の偏心回転に追従して往復運動をする
。Conventional configurations and their problems In many rolling piston rotary compressors used in domestic air conditioners, as shown in Figure 1, the vane 6 that partitions the inside of the cylinder into a low pressure chamber 4 and a high pressure chamber 5 is a cylinder block. A spring device 9 is installed on the back surface of the bay 76 so that the tip of the bay 76 is always pressed against the outer circumferential wall of the rotor 3.
During compressor operation, the combination 3 of the discharge pressure load acting on the back surface of the vane 6 and the reaction force of the spring device 9a is provided.
l knee:j Due to the action of the load, the tip of the vane 6 makes a reciprocating motion following the eccentric rotation of the rotor 3 while partitioning the inside of the cylinder pressed against the outer circumferential wall of the rotor 3 into a low pressure chamber 4 and a high pressure chamber 6.
しかし、冷時起動後など吐出室７の圧力上昇が遅い時に
はベーン６の背面に作用する力は定常運転時にベーン６
の先端とロータ３の外周壁との間の摩擦損失を少なくす
るために比較的低荷重に設定されたばね装置９ａの反力
荷重のみである。したがって、ベーン６の往復運動はロ
ータ３の偏心高速回転に追従しなくなる。この結果、ベ
ーン６はジャンピング現象を生じて圧縮効率が低下し、
起に
動直後の吐出室圧力の立上り〜より一層遅らせると共に
ベーンノイズの発生、ベーン先端とロータ外周壁の耐久
性の低下をひきおこすなど多くの欠点を有していた。However, when the pressure rise in the discharge chamber 7 is slow, such as after a cold start, the force acting on the back surface of the vane 6 is
The only reaction load is the reaction force of the spring device 9a, which is set to a relatively low load in order to reduce friction loss between the tip of the rotor 3 and the outer circumferential wall of the rotor 3. Therefore, the reciprocating motion of the vanes 6 no longer follows the eccentric high-speed rotation of the rotor 3. As a result, the vane 6 causes a jumping phenomenon and the compression efficiency decreases.
It has many drawbacks, such as a delay in the rise of the discharge chamber pressure immediately after startup, the generation of vane noise, and a decrease in the durability of the vane tip and rotor outer peripheral wall.
発明の目的
本発明は温度変化によってばね特性の変わるばね装置を
使用することにより上記欠点を改善するものである。OBJECTS OF THE INVENTION The present invention improves the above-mentioned drawbacks by using a spring device whose spring characteristics change with temperature changes.
発明の構成
そのだめの構成として、本発明は、シリンダブロックの
シリンダ内をロータが内接しながら回転し、前記シリン
ダの内壁と前記ロータの外周壁と前記シリンダブロック
の両側に設けられた側板とで形成されるシリンダ空間を
低圧室と高圧室とに仕切るベーンが前記シリンダブロッ
クまたは前記ロータに吐出室に通じて設けられた案内溝
に沿って前記シリンダ空間へ出入りし、前記ベーンの背
面には前記ベーンの先端を前記ロータの外周壁に押接さ
せるためのばね装置を設け、前記ばね装置はその温度が
設定値を越える場合はばね定数が急減し、その温度が設
定値よりも低くなった場合はばね定数かもとの値に復帰
するような形状記憶合金材料からなるものである。Structure of the Invention As a further structure, the present invention provides a rotor that rotates in a cylinder of a cylinder block while being inscribed therein, and an inner wall of the cylinder, an outer circumferential wall of the rotor, and side plates provided on both sides of the cylinder block. A vane that partitions the formed cylinder space into a low pressure chamber and a high pressure chamber moves in and out of the cylinder space along a guide groove provided in the cylinder block or the rotor leading to the discharge chamber. A spring device is provided for pressing the tip of the vane against the outer circumferential wall of the rotor, and the spring constant of the spring device sharply decreases when the temperature exceeds a set value, and when the temperature becomes lower than the set value. The spring constant is made of a shape memory alloy material that returns to its original value.
また、本発明の回転式圧縮機のばね装置は、その・温度
が設定値を越える場合に前記ベーンの背面を押圧しなく
なる丑で変化するばね特性を有したものである。Further, the spring device of the rotary compressor of the present invention has spring characteristics that change depending on whether the spring device stops pressing the back surface of the vane when the temperature exceeds a set value.
捷だ、本発明の回転式圧縮機のばね装置は、前記６ ＼
−
ベーンと反対側の端部が固定されたものである。However, the spring device of the rotary compressor of the present invention is the same as the above-mentioned 6 ＼
– the end opposite the vane is fixed;
実施例の説明
以下、本発明の一実施例を第２図、第３図に沿って説明
する。第２図は家庭用空調機などに使用されるローリン
グピストン式ロータリ圧縮機とそれに関連する冷凍サイ
クルの糸路を示し、シェル１の内壁に装嵌されたシリン
ダブロック２のシリンダ内にはロータ３がシリンダ内壁
に接しながら回転し、シリンダ内壁とロータ３の外周壁
とシリンダブロック１の両側に設けられた側板（図示な
し）とで構成されるシリンダ空間を低圧室４と高圧室６
とに仕切るベー７６がシリンダブロック１に設けられ、
ベー７６は、吐出室７に通じた案内溝８に沿ってシリン
ダ空間へ出入りするように装着されている。ベーン６の
背面にはばね装置としてコイルスプリング９が配置され
、第３図のようにコイルスプリング９はベーン６と反対
側の端部がシェル１の内壁に固定されると共に、その温
度が設定値（例えば６０″Ｃ）を越えるとその線膨張係
数が極めて小さくなってベー７６の背面を押さ６ ＼−
ない程度の長さに設定されており、その温度が設定値よ
り低くなると線膨張係数が大きくなってベーン６の背面
を押すような長さにまで復帰するような形状記憶合金材
料からなっている。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 2 and 3. Figure 2 shows the thread path of a rolling piston rotary compressor used in household air conditioners and the related refrigeration cycle. rotates while contacting the cylinder inner wall, and the cylinder space consisting of the cylinder inner wall, the outer peripheral wall of the rotor 3, and side plates (not shown) provided on both sides of the cylinder block 1 is divided into a low pressure chamber 4 and a high pressure chamber 6.
A bay 76 is provided in the cylinder block 1 and partitions into two parts.
The bay 76 is mounted so as to move in and out of the cylinder space along a guide groove 8 communicating with the discharge chamber 7. A coil spring 9 is arranged as a spring device on the back side of the vane 6, and as shown in FIG. (for example, 60"C), the coefficient of linear expansion becomes extremely small and the length is set to such a degree that it does not push the back of the bee 76. When the temperature is lower than the set value, the coefficient of linear expansion becomes extremely small. It is made of a shape memory alloy material that increases in size and returns to a length that pushes the back surface of the vane 6.
また、シリンダブロック２には吐出口１０．吐出弁装置
１１、吸入口１２が設けられて、シェル１以上の構成に
おいて、圧縮機が冷時状態から運転を開始した直後の数
分間は冷媒吐出温度、冷媒吐出圧力が低く、ベーン６の
背面には吐出室７の圧力とシリンダ内圧力との差圧荷重
はあ一！、シ作用しない。しかし、コイルスプリング９
および雰囲気温度が設定値よりも低いのでコイルスプリ
ング９はベーン６の背面を押す状態にまで伸長している
。The cylinder block 2 also has a discharge port 10. In a configuration in which the discharge valve device 11 and the suction port 12 are provided, and the shell 1 or more is provided, the refrigerant discharge temperature and refrigerant discharge pressure are low for several minutes immediately after the compressor starts operating from a cold state, and the back surface of the vane 6 is The differential pressure load between the pressure in the discharge chamber 7 and the pressure inside the cylinder is ah! , it doesn't work. However, coil spring 9
Since the ambient temperature is lower than the set value, the coil spring 9 is extended to the point where it presses against the back surface of the vane 6.
したがって、冷媒圧縮機はベーン６の先端がコイルスプ
リング９によってロータ３の外周壁に押圧された状態で
運転される。その後、冷媒吐出温度、圧力が上昇し、コ
イルスプリング９の温度が７ ＼−
設定値を越えるとコイルスプリング９は短縮してベーン
６の背面から離れ、ベーンの背面には吐出室７の圧力と
シリンダ内圧力との差圧荷重のみが作用する。Therefore, the refrigerant compressor is operated with the tips of the vanes 6 being pressed against the outer peripheral wall of the rotor 3 by the coil springs 9. After that, the refrigerant discharge temperature and pressure rise, and when the temperature of the coil spring 9 exceeds the set value of 7\-, the coil spring 9 shortens and separates from the back of the vane 6, and the pressure of the discharge chamber 7 and the pressure of the discharge chamber 7 appear on the back of the vane. Only the differential pressure load with the cylinder internal pressure acts.
上記実施例ではローリングピストン式ロータリ圧縮機に
ついて説明したが、シリンダ内を低圧室と高圧室とに仕
切るためのスライドベーンがロータに設けられた案内溝
に沿って往復運動をし、吐出室圧力を利用した圧力荷重
とばね装置の弾性荷重とによってシリンダ内へ出入りす
るような構造を有する他の回転式圧縮機についても同様
の作用をする。In the above embodiment, a rolling piston type rotary compressor was described, but a slide vane for partitioning the inside of the cylinder into a low pressure chamber and a high pressure chamber reciprocates along a guide groove provided in the rotor to control the discharge chamber pressure. The same effect applies to other rotary compressors having a structure in which the compressor moves in and out of the cylinder depending on the applied pressure load and the elastic load of the spring device.
発明の効果
上記実施例から明らかなように本発明の回転式圧縮機は
、シリンダ内を低圧室と高圧室とに仕切るベーンの先端
を相手摺動壁面傾押圧させるためにベーンの背面にばね
装置と圧縮気体（または液体）の圧力荷重を作用させ、
ばね装置はその温度が設定値を越える場合に弾性係数、
または線膨張係数が小さくなり、その温度が設定値よシ
低い場特開昭ＧＯ−１４５４７９（３）
合は弾性係数、または線膨張係数が大きい状態に復帰す
るような形状記憶合金材料から成っているので、冷時起
動直後などベーン背面に作用する圧縮気体（まだは液体
）の圧力が低く圧力荷重が小さい場合でもばね装置の適
当な弾性荷重によってベーンの先端を相手摺動壁面に押
圧しベーンのジャンピング現象を少なくすることができ
るので、圧縮効率の低下がなく、ベーン先端と相手摺動
面の耐久性が著しく向上し、ベーン音などの少ない圧縮
機ができると共に、定常運転時など吐出圧力、周囲温度
が高い場合には不必要なベーン抑圧力が少なくなってベ
ーン先端の摺動摩擦損失が少なくベーン先端などの耐久
性も向上する。Effects of the Invention As is clear from the above embodiments, the rotary compressor of the present invention has a spring device on the back surface of the vane to tilt the tip of the vane that partitions the inside of the cylinder into a low-pressure chamber and a high-pressure chamber against the opposing sliding wall. and apply a pressure load of compressed gas (or liquid),
The spring device has an elastic modulus when its temperature exceeds the set value.
Or, if the coefficient of linear expansion becomes small and the temperature is lower than the set value, the material is made of a shape memory alloy material that returns to a state with a large coefficient of elasticity or coefficient of linear expansion. Therefore, even when the pressure of the compressed gas (still liquid) acting on the back of the vane is low and the pressure load is small, such as immediately after startup in cold weather, the vane tip is pressed against the mating sliding wall by the appropriate elastic load of the spring device, and the vane Since the jumping phenomenon can be reduced, there is no drop in compression efficiency, and the durability of the vane tip and mating sliding surface is significantly improved.A compressor with less vane noise can be created, and the discharge pressure during steady operation can be reduced. When the ambient temperature is high, unnecessary vane suppressing force is reduced, resulting in less sliding friction loss at the vane tip and improved durability of the vane tip.
また、本発明の回転圧縮機におけるばね装置は、その温
度が設定値を越えるとベーンの背面にばね装置の弾性荷
重が作用しない程度にまで変化するので、定常運転時の
ばね装置は無負荷状態になってばね装置の疲労耐久性が
著るしぐ向上する。Furthermore, when the temperature of the spring device in the rotary compressor of the present invention exceeds a set value, the elastic load of the spring device does not act on the back surface of the vane, so that the spring device is in an unloaded state during steady operation. This significantly improves the fatigue durability of the spring device.
また、本発明の回転式圧縮機におけるばね装置は、ベー
ンと反対側の端部が固定されているので定常９ ＼−′
運転時などばね装置が無負荷状態の場合には、ベーンの
背面とばね装置が衝突しないのでベーンの背面や、ばね
装置の端部の損傷が少ないなど数多くの優れた効果を奏
するものである。In addition, since the end of the spring device in the rotary compressor of the present invention is fixed on the side opposite to the vane, when the spring device is in an unloaded state such as during steady 9\-' operation, the back side of the vane and Since the spring devices do not collide, there are many excellent effects such as less damage to the back surface of the vane and the ends of the spring devices.
第１図は従来のローリングピストン式圧縮機の断面図、
第２図は本発明の一実施例を示す回転式圧縮機の断面図
を含む冷凍サイクルの系統図、第３図は第２図のＡ部拡
大図である。
１・・・・・・シェル、２・・・・・・シリンダブロッ
ク、３・・・・・・ロータ、４・・・・・・低圧室、６
・・・・・・高圧室、６・・・・・・ベーン、７・・・
・・・吐出室、８・・・・・・案内溝、９・・・・・・
コイルスプリング（ばね装置）。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名Ｗ、
１ 図Figure 1 is a cross-sectional view of a conventional rolling piston compressor.
FIG. 2 is a system diagram of a refrigeration cycle including a sectional view of a rotary compressor showing an embodiment of the present invention, and FIG. 3 is an enlarged view of part A in FIG. 2. 1... Shell, 2... Cylinder block, 3... Rotor, 4... Low pressure chamber, 6
...High pressure chamber, 6... Vane, 7...
...Discharge chamber, 8...Guide groove, 9...
Coil spring (spring device). Name of agent: Patent attorney Toshio Nakao and one other person W,
1 figure
Claims (1)
ら回転するロータと、前記シリンダの内壁と前記ロータ
の外周壁と前記シリンダブロックの両側に設けられた側
板とで形成されるシリンダ空間を低圧室と高圧室とに仕
切るベーンを有し前記ベーンは前記シリンダブロックま
たは前記ロータに吐出室に通じて設けられた案内溝に沿
って前記シリンダ空間へ出入多自在に設け、前記ベーン
の背面には前記ベーンの先端を前記ロータの外周壁に押
接させるためのばね装置を設け、前記ぼね装置をその温
度が設定値を越える場合はぼね定数が急減しその温度が
設定値よシも低くなった場合はばね定数かもとの値に復
帰する形状記憶合金材料で構成した回転式圧縮機。 に））ばね装置は、その温度が設定値を越える場合に前
記ベーンの背面を押圧しなくなるまで変化す２ベソ るばね特性を有する特許請求の範囲第１項記載の回転式
圧縮機。 （３）ばね装置は、前記ベーンと反対側の端部が固定さ
れた特許請求の範囲第２項記載の回転式圧縮機・[Scope of Claims] (1) A cylinder formed by a rotor that rotates while inscribed in the inner surface of a cylinder of a cylinder block, an inner wall of the cylinder, an outer peripheral wall of the rotor, and side plates provided on both sides of the cylinder block. The vane is provided to partition the space into a low pressure chamber and a high pressure chamber, and the vane is provided to freely move in and out of the cylinder space along a guide groove provided in the cylinder block or the rotor leading to the discharge chamber. A spring device is provided on the back surface for pressing the tip of the vane against the outer peripheral wall of the rotor, and when the temperature of the spring device exceeds a set value, the spring constant decreases rapidly and the temperature becomes lower than the set value. A rotary compressor made of a shape memory alloy material whose spring constant returns to its original value when the spring constant becomes low. 2)) The rotary compressor according to claim 1, wherein the spring device has a spring characteristic that changes until it no longer presses the back surface of the vane when the temperature thereof exceeds a set value. (3) The rotary compressor according to claim 2, wherein the spring device has an end opposite to the vane fixed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25131683A JPS60145479A (en) | 1983-12-29 | 1983-12-29 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25131683A JPS60145479A (en) | 1983-12-29 | 1983-12-29 | Rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60145479A true JPS60145479A (en) | 1985-07-31 |
| JPH0138200B2 JPH0138200B2 (en) | 1989-08-11 |
Family
ID=17220991
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25131683A Granted JPS60145479A (en) | 1983-12-29 | 1983-12-29 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60145479A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106593872A (en) * | 2016-10-18 | 2017-04-26 | 广东美芝精密制造有限公司 | Slide sheet for variable capacity compressor, variable capacity compression mechanism and variable capacity compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5130006U (en) * | 1974-08-26 | 1976-03-04 | ||
| JPS5149607U (en) * | 1974-10-11 | 1976-04-14 |
-
1983
- 1983-12-29 JP JP25131683A patent/JPS60145479A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5130006U (en) * | 1974-08-26 | 1976-03-04 | ||
| JPS5149607U (en) * | 1974-10-11 | 1976-04-14 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106593872A (en) * | 2016-10-18 | 2017-04-26 | 广东美芝精密制造有限公司 | Slide sheet for variable capacity compressor, variable capacity compression mechanism and variable capacity compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0138200B2 (en) | 1989-08-11 |
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