JPS6363752B2 - - Google Patents
Info
- Publication number
- JPS6363752B2 JPS6363752B2 JP54157223A JP15722379A JPS6363752B2 JP S6363752 B2 JPS6363752 B2 JP S6363752B2 JP 54157223 A JP54157223 A JP 54157223A JP 15722379 A JP15722379 A JP 15722379A JP S6363752 B2 JPS6363752 B2 JP S6363752B2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- coating
- peripheral surface
- recess
- circumferential surface
- 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
Links
- 239000011248 coating agent Substances 0.000 claims description 30
- 238000000576 coating method Methods 0.000 claims description 30
- 230000002093 peripheral effect Effects 0.000 claims description 15
- 239000000463 material Substances 0.000 claims description 2
- 230000000694 effects Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 125000000816 ethylene group Chemical group [H]C([H])([*:1])C([H])([H])[*:2] 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 229920001577 copolymer Polymers 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- -1 vinyl compound Chemical class 0.000 description 2
- 229920002554 vinyl polymer Polymers 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 238000005422 blasting Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000032798 delamination Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007598 dipping method Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000001179 sorption measurement Methods 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000000758 substrate Substances 0.000 description 1
- BFKJFAAPBSQJPD-UHFFFAOYSA-N tetrafluoroethene Chemical group FC(F)=C(F)F BFKJFAAPBSQJPD-UHFFFAOYSA-N 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は特にピストンがシリンダ室内を往復動
して流体を圧縮する形式の圧縮機に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention particularly relates to a compressor in which a piston reciprocates within a cylinder chamber to compress fluid.
（従来の技術）
従来、圧縮機のピストンの外周面とシリンダ室
内周面との摺動部には気密性及び耐摩耗性が要求
され、この要求を満足するために従来から種々の
提案がなされてきた。その第１の従来例としてピ
ストンにピストンリングを嵌合するものがあつ
た。(Prior Art) Conventionally, the sliding part between the outer peripheral surface of the piston of a compressor and the inner peripheral surface of the cylinder has been required to be airtight and wear resistant, and various proposals have been made to meet this requirement. It's here. The first conventional example is one in which a piston ring is fitted onto a piston.
又、第２の従来例として第８図に示すような技
術が提案された。これはピストン１０の外周部を
フツ素樹脂よりなるカツプ状の被覆体１１で包囲
して金属どうしの接触を避け、耐摩耗性が高く比
較的良好な摺動性が得られるようにしたものであ
る。 Further, as a second conventional example, a technique as shown in FIG. 8 has been proposed. This is a device in which the outer circumference of the piston 10 is surrounded by a cup-shaped covering 11 made of fluororesin to avoid metal-to-metal contact and provide high wear resistance and relatively good sliding performance. be.
さらに、第３の従来例として第９図に示すよう
にピストン１２の外周面に薄い（20〜100μm）被
覆１３を形成するようにしたものが提案された。 Furthermore, as a third prior art example, as shown in FIG. 9, a thin (20 to 100 μm) coating 13 was proposed on the outer peripheral surface of the piston 12.
（発明が解決しようとする問題点）
ところが、第１の従来例は、ピストン外周面か
らピストンリングが突出しているので組付けが困
難であるばかりでなく、シリンダ室内周面とピス
トン外周面との直線的な摺動は不可避であり、加
工上どうしても避けられない摺動面上の凹凸に起
因して、ピストンギヤツプ（サイドクリアラン
ス）をある程度（約25μm）以下の値にすること
ができず、従つて運転中にピストンの周側面とシ
リンダ室内周面とが衝突して衝撃音を発生すると
ともに、摩耗を促進するという欠陥があつた。
又、この技術が冷媒圧縮機のピストンに応用さ
れ、液圧縮を生起した場合等においては、摺動部
に供給される潤滑油が洗い落されて金属接触を余
儀なくされ、このことも摩耗を促進する原原因と
なり、その結果運転騒音が高く耐久性が低くなる
という欠陥が生じた。(Problems to be Solved by the Invention) However, in the first conventional example, the piston ring protrudes from the outer circumferential surface of the piston, so it is not only difficult to assemble, but also the piston ring protrudes from the outer circumferential surface of the piston. Linear sliding is unavoidable, and due to the unevenness on the sliding surface that is unavoidable in machining, it is impossible to reduce the piston gap (side clearance) to a certain value (approximately 25 μm) or less. During operation, the circumferential surface of the piston collides with the circumferential surface of the cylinder chamber, producing impact noise and accelerating wear.
In addition, when this technology is applied to the piston of a refrigerant compressor and liquid compression occurs, the lubricating oil supplied to the sliding parts is washed away and metal contact is forced, which also accelerates wear. This resulted in defects such as high operating noise and low durability.
又、第２の従来例においては前記被覆体１１が
予めカツプ状に形成されてからピストン１０に被
せられるため、同被覆体１１の円筒部肉厚を約３
mm程度と比較的大きくする必要があつた。従つて
その部分の熱膨脹量は比較的大きく（80℃の温度
変化において約24μm）なるので、ピストンギヤ
ツプは温度変化によつて大きく変動し、圧縮機の
運転状態の変化によつてその体積効率も大きく変
化することとなり、性能的に不安定なものである
という欠陥があつた。 In addition, in the second conventional example, since the covering 11 is formed into a cup shape in advance and then placed on the piston 10, the thickness of the cylindrical portion of the covering 11 is approximately 3.
It was necessary to make it relatively large, about mm. Therefore, the amount of thermal expansion in that part is relatively large (approximately 24 μm at a temperature change of 80°C), so the piston gap fluctuates greatly due to temperature changes, and its volumetric efficiency also increases due to changes in compressor operating conditions. The problem was that the performance was unstable.
又、この技術においては起動後温度上昇するま
で大きなサイドクリアランスのままで運転される
ことになり、ガタツキに起因する衝撃が大きく、
被覆体１１の摩耗が極度に激しくなるとともに、
この技術が空調装置等の冷媒圧縮機である場合に
は、前記フツ素樹脂（四フツ化エチレン等）は冷
媒のフレオンガスによつて経時的に少しづつ膨脹
する性質があるため、前記サイドクリアランスは
次第に減少し、ついにはシリンダ室内にピストン
が密着した状態となつて運転不能となるおそれも
あつた。このようなことから、設計に際してサイ
ドクリアランスを予め最適値に厳密に設定する必
要があるが、これは極めて困難なことである。 In addition, with this technology, the engine is operated with a large side clearance until the temperature rises after startup, causing a large impact due to rattling.
As the wear of the covering 11 becomes extremely severe,
When this technology is used in a refrigerant compressor for an air conditioner or the like, the side clearance is It gradually decreased, and there was a risk that the piston would become stuck in the cylinder chamber, making it impossible to operate. For this reason, it is necessary to strictly set the side clearance to an optimum value in advance during design, but this is extremely difficult.
さらに、第３の従来例では前述したカツプ状の
被覆体をピストンに嵌合するという技術に存する
欠陥を解消することはできるが、同被覆１３の膨
脹が期待できないため、サイドクリアランスの許
容幅を厳しく制限しないと体積効率が低下すると
いう欠陥があつた。 Furthermore, in the third conventional example, although it is possible to eliminate the above-mentioned defect in the technique of fitting the cup-shaped covering to the piston, the expansion of the covering 13 cannot be expected, so the permissible width of the side clearance is limited. There was a drawback that volumetric efficiency would decrease unless strict restrictions were imposed.
発明の構成
（問題を解決するための手段）
本発明は前記問題点を解消するため、シリンダ
室内を往復動するピストンの外周面に対し、周方
向に連続し、かつ幅１〜５mmで幅方向中央部へ行
くに従い深くなる傾斜面を有する最深部が0.1〜
0.5mmの深さを有する凹部を形成するとともに、
同凹部以外の外周面には厚さが20〜100μmのフツ
素樹脂により構成される被膜を、前記凹部にはそ
の最深部の厚さが120〜600μmの同材料よりなる
被膜をそれぞれ連続して設けてピストン外周径を
同一径と成し、同被膜の前記凹部と対応する部分
を厚肉部とし、凹部以外の部分を薄肉部とすると
いう手段を採つている。Structure of the Invention (Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention has provided a piston that is continuous in the circumferential direction and has a width of 1 to 5 mm in the width direction with respect to the outer peripheral surface of the piston that reciprocates within the cylinder chamber. The deepest part is 0.1~
While forming a recess with a depth of 0.5 mm,
A coating made of fluororesin with a thickness of 20 to 100 μm is applied to the outer circumferential surface other than the concave portion, and a coating made of the same material with a thickness of 120 to 600 μm at the deepest part is applied to the concave portion. The outer peripheral diameter of the piston is made the same diameter, the portion of the coating corresponding to the recess is a thick portion, and the portion other than the recess is a thin portion.
（作用）
本発明は前記手段を採つたことにより、次のよ
うに作用する。(Function) By adopting the above-mentioned means, the present invention functions as follows.
圧縮機の運転時には薄肉部と厚肉部が加熱さ
れ、薄肉部よりも厚肉部の熱膨脹が大きくなつ
て、厚肉部とシリンダ室内周面との間隙が小さく
なりシール性が向上され、体積効率が高められ
る。 When the compressor is operating, the thin and thick parts are heated, and the thermal expansion of the thick part is larger than that of the thin part, which reduces the gap between the thick part and the circumferential surface of the cylinder chamber, improving sealing performance and increasing the volume. Efficiency is increased.
又、被膜がフツ素樹脂のため、シリンダ室内周
面にうねりがあつても厚肉部が容易に変形しなが
ら摺動して、衝撃に起因する騒音の発生が抑制さ
れる。摺動部の摩擦係数（抵抗）が低くなり、所
要動力が軽減され、耐焼付性が向上する。 Furthermore, since the coating is made of fluororesin, even if there are undulations on the inner circumferential surface of the cylinder chamber, the thick portion easily deforms and slides, thereby suppressing the generation of noise caused by impact. The friction coefficient (resistance) of the sliding part is lowered, the required power is reduced, and the seizure resistance is improved.
さらに、シリンダ室内周面とピストン外周面と
のサイドクリアランスの許容幅が大きくなり、加
工精度及び組付精度が低下され、製作及び組付が
容易となる。 Furthermore, the permissible width of the side clearance between the inner peripheral surface of the cylinder and the outer peripheral surface of the piston is increased, processing accuracy and assembly accuracy are reduced, and manufacturing and assembly are facilitated.
（実施例）
以下、本発明を空調用の圧縮機に具体化した一
実施例を第１図〜第３図について説明すると、圧
縮機のシリンダ室１内には往復動可能にピストン
２が嵌装されている。前記シリンダ室１を構成す
るシリンダブロツク３及び前記ピストン２は、熱
膨脹率がほぼ同程度の同系の金属材料により形成
され、特に軽量化の観点からアルミニウム合金材
より構成されるのが近時の傾向である。(Example) Hereinafter, an example in which the present invention is embodied in a compressor for air conditioning will be described with reference to FIGS. equipped. The cylinder block 3 and the piston 2 constituting the cylinder chamber 1 are made of similar metal materials having approximately the same coefficient of thermal expansion, and the recent trend is for them to be made of an aluminum alloy material from the viewpoint of weight reduction. It is.
前記ピストン２の外周面には断面円弧状をなす
環状の凹部２ａ（深さ0.1〜0.5mm、幅１〜５mm）
が形成され、四フツ化エチレン等のフツ化エチレ
ン若しくはフツ化エチレンとビニル化合物との共
重合体よりなるフツ素樹脂により構成される被膜
４が施され、この被膜４の前記凹部２ａと対応す
る部分に外周の直径は変化しない厚肉部４ａが一
体に形成されている。 The outer peripheral surface of the piston 2 has an annular recess 2a (depth 0.1 to 0.5 mm, width 1 to 5 mm) having an arcuate cross section.
is formed, and a coating 4 made of a fluororesin made of fluorinated ethylene such as tetrafluoroethylene or a copolymer of fluorinated ethylene and a vinyl compound is applied, and the coating 4 corresponds to the recess 2a of the coating 4. A thick wall portion 4a whose outer circumferential diameter does not change is integrally formed in the portion.
前記被膜４はピストン２の外周面に対し、次の
ような行程で形成される。第２図ａに示すように
連続した円周状の凹部２ａを形成したピストン２
の外周面に例えばシヨツトブラスト等の処理を施
した後、粉末吹付け若しくはデイツピングによつ
て前記フツ素子樹脂Ｆを同図ｂに示すように厚く
（60〜300μm）塗布し、その後250〜350℃の炉中
にて約30分焼成する。さらにこの焼成されたフツ
素樹脂Ｆの外周面を切削して第２図ｃに示すよう
な膜厚20〜100μmの被膜４を形成する。この被膜
４の膜厚は、ほぼ20〜100μmに設定されるが、そ
の理由は膜厚20μm以下の場合には、摩耗によつ
て地肌がでやすく、耐久性が劣り、弾性変形しに
くいため、なじみ性及び衝撃吸収能力が低下する
という欠点があらわれ、又、前記膜厚が100μm以
上の場合には、被膜４が剥離しやすいという欠点
があるためである。 The coating 4 is formed on the outer peripheral surface of the piston 2 in the following steps. A piston 2 having a continuous circumferential recess 2a as shown in FIG. 2a.
After applying a treatment such as shot blasting to the outer circumferential surface of the substrate, apply the foot element resin F thickly (60 to 300 μm) by powder spraying or dipping as shown in FIG. Bake in a furnace at ℃ for about 30 minutes. Further, the outer peripheral surface of the fired fluororesin F is cut to form a coating 4 having a thickness of 20 to 100 .mu.m as shown in FIG. 2c. The film thickness of this coating 4 is set to approximately 20 to 100 μm, because if the film thickness is less than 20 μm, the bare skin is likely to appear due to abrasion, the durability is poor, and it is difficult to elastically deform. This is because there is a drawback that conformability and shock absorption ability are reduced, and when the film thickness is 100 μm or more, there is a drawback that the coating 4 is easily peeled off.
第７図は運転条件が回転数：700rpm、吐出
圧：25〜28Kg／cm2、吸入圧：３〜４Kg／cm2の低速
高負荷のもとで、各膜厚に応じて運転時間を実験
的に測定した結果を示す。このグラフから明らか
なように、膜厚20μm以下の場合には焼き付きが
生じ、膜厚が100μm以上の場合には、層間剥離摩
耗が生じて問題となる。 Figure 7 shows an experiment under low speed and high load operating conditions: rotation speed: 700 rpm, discharge pressure: 25-28 Kg/cm 2 , suction pressure: 3-4 Kg/cm 2 , and the operating time depending on each film thickness. The results are shown below. As is clear from this graph, when the film thickness is 20 μm or less, seizure occurs, and when the film thickness is 100 μm or more, delamination wear occurs, which becomes a problem.
次に、前記のように構成した圧縮機についてそ
の作用及び効果を説明する。 Next, the operation and effects of the compressor configured as described above will be explained.
常温時には第３図ａに示すようにピストン２の
外径が均一であるから、ピストン２をシリンダ室
１内へスムーズに嵌入でき組付を容易に行うこと
ができる。 Since the outer diameter of the piston 2 is uniform as shown in FIG. 3a at room temperature, the piston 2 can be smoothly inserted into the cylinder chamber 1 and assembly can be easily performed.
運転時には断熱圧縮や摩擦に起因する熱影響に
よつてピストン２の温度が上昇し被膜４の厚肉部
４ａは熱膨脹で他の部分（薄肉部）４ｂよりも径
が大きくなる。このため厚肉部４ａではシリンダ
ブロツク３内周面３ａとのサイドクリアランスが
非常に小さくなるか、又は第３図ｂに示すように
零になつてシール性が向上してブローバイガスが
減少し、体積効率を向上することができる。 During operation, the temperature of the piston 2 rises due to heat effects caused by adiabatic compression and friction, and the thick wall portion 4a of the coating 4 expands thermally and becomes larger in diameter than the other portion (thin wall portion) 4b. Therefore, in the thick wall portion 4a, the side clearance with the inner circumferential surface 3a of the cylinder block 3 becomes very small, or becomes zero as shown in FIG. 3b, improving sealing performance and reducing blow-by gas. Volumetric efficiency can be improved.
又、運転時にはシリンダ室１の内周面３ａと被
膜４の外周表面との間で摺動が行われるが、同被
膜４はフツ化エチレン若しくはフツ化エチレンと
ビニル化合物との共重合体等のフツ素樹脂により
形成されているため、ピストンの側圧の大きい側
では厚肉部４ａは弾性変形し、ピストン摺動面全
体で圧力を受け、厚肉部４ａのみが異常摩耗する
ことはなく、シリンダ室内周面３ａにうねりがあ
つても容易に変形しながら摺動し、衝撃に起因す
る騒音の発生を抑制できる。さらに、前記フツ素
樹脂の良好な摺動特性により、摺動部の摩耗係数
（抵抗）が低くなり、運転のための所要動力を低
減でき、耐焼付性を向上でき、その上被膜４の表
面は製作方法上多孔質になり易い傾向から、油の
吸着性が良く、上記作用をなお一層向上させるこ
とができる。 Furthermore, during operation, sliding occurs between the inner circumferential surface 3a of the cylinder chamber 1 and the outer circumferential surface of the coating 4, and the coating 4 is made of fluorinated ethylene or a copolymer of fluorinated ethylene and a vinyl compound. Since it is made of fluororesin, the thick wall portion 4a is elastically deformed on the side of the piston where the lateral pressure is high, and the entire sliding surface of the piston receives pressure, preventing only the thick wall portion 4a from experiencing abnormal wear. Even if the indoor circumferential surface 3a has undulations, it can easily deform and slide, thereby suppressing the generation of noise caused by impact. Furthermore, due to the good sliding properties of the fluororesin, the coefficient of wear (resistance) of the sliding parts is lowered, the power required for operation can be reduced, the seizure resistance can be improved, and the surface of the coating 4 can be improved. Because they tend to be porous due to the manufacturing method, they have good oil adsorption properties and can further improve the above effects.
さらに、本発明においては前述したように、被
膜４の厚肉部４ａの熱膨脹によるシール性が期待
でき、又、凹部以外の外周面における被膜４の膜
厚が20〜100μmでしかないため、その熱膨脹量は
ごく微小でほとんど無視できることから、サイド
クリアランスを小さくしたり大きくしたりするこ
とができ、その許容幅を大きくすることができ
る。この結果、加工上ピストン２に凹部２ａを形
成する工程を増えるが、加工精度及び組付精度を
厳密にとる必要がなくなり、従つて製作が簡単に
行えるという特徴がある。 Furthermore, in the present invention, as described above, sealing performance can be expected due to thermal expansion of the thick portion 4a of the coating 4, and since the thickness of the coating 4 on the outer circumferential surface other than the recessed portion is only 20 to 100 μm, Since the amount of thermal expansion is extremely small and can be almost ignored, the side clearance can be made smaller or larger, and its allowable width can be increased. As a result, although the process of forming the concave portion 2a in the piston 2 is increased, there is no need to ensure strict machining accuracy and assembly accuracy, and therefore manufacturing is easy.
なお、前記実施例では被膜４の厚肉部４ａの断
面を内側へ凸の円弧状にしたが、この場合には厚
肉部４ａの径変化が非常に滑らかであるため、シ
リンダ室内周面３ａとの間に第３図ｂに示すよう
にくさび状空間Ｐができ、従つて摺動部に油膜が
でき易く動力及び摩耗の軽減に寄与することがで
きる。 In the above embodiment, the cross section of the thick walled portion 4a of the coating 4 was formed into an inwardly convex arc shape, but in this case, since the diameter change of the thick walled portion 4a is very smooth, the cylinder interior circumferential surface 3a As shown in FIG. 3b, a wedge-shaped space P is formed between the two, and therefore an oil film is likely to form on the sliding part, contributing to reduction of power and wear.
なお、本発明は次のような実施例で具体化する
ことも可能である。 Note that the present invention can also be embodied in the following embodiments.
(1) 第４図及び第５図ａ，ｂに示すように、斜板
式圧縮機のピストン５の両頭部分６外周面に対
し、前述したように連続した円周状の凹部５ａ
を形成するとともに、被膜７及び厚肉部７ａを
施すこともできる。又、前記被膜７の上縁及び
下縁は丸みを与えるか、若しくはピストンの上
端面及び下端面にわずかに回り込んで覆い被せ
るようにして、端縁部での剥離を有効に防止す
るようにしてもよい。(1) As shown in FIGS. 4 and 5 a and b, a continuous circumferential recess 5 a is formed on the outer circumferential surface of the double-end portion 6 of the piston 5 of the swash plate compressor as described above.
It is also possible to form a coating 7 and a thick portion 7a. Further, the upper and lower edges of the coating 7 are rounded or slightly wrapped around the upper and lower end surfaces of the piston to effectively prevent peeling at the edge portions. It's okay.
(2) 第６図ａに示すようにピストン２の凹部２ａ
の両側部にアールをつけたり、同図ｂに示すよ
うに凹部２ａの断面を緩やかなＶ字状に形成し
たり、同図ｃに示すよに凹部２ａの中央部に平
面部ｈを形成して運転時における厚肉部４ａと
シリンダ室内周面３ａの摺動面積を大きくして
シール性を向上するようにしたり、さらに同図
ｄに示すように２箇所以上に厚肉部４ａを形成
したりすることもできる。(2) As shown in Figure 6a, the recess 2a of the piston 2
The cross section of the recess 2a may be formed into a gentle V-shape as shown in FIG. The sliding area between the thick wall portion 4a and the cylinder indoor peripheral surface 3a during operation may be increased to improve sealing performance, and the thick wall portion 4a may be formed at two or more locations as shown in d of the same figure. You can also.
発明の効果
以上詳述したように、本発明は次のような効果
がある。Effects of the Invention As detailed above, the present invention has the following effects.
圧縮機は、車室内温度あるいは吸入圧力の変
動に呼応して自動的にON・OFF制御が頻繁に
行われ、ピストンの熱膨脹が常に変化するた
め、運転状態の変化に適応したシリンダブロツ
ク内周面とのサイドクリアランスの設定が非常
に困難であつたが、本案によれば、圧縮機の起
動時は、ピストンは常温であるため被膜の熱膨
脹はなくピストン外径が均一であることからサ
イドクリアランスの変動はなく、起動時に生起
し易い液圧縮によるシリンダ室内圧力の異常上
昇は、サイドクリアランスからの逃がし作用に
よつて回避でき、吐出弁、ガスケツト等の破損
を防止するとともに起動シヨツクの緩和をも行
い、また運転時には、ピストンの温度上昇に伴
い被膜厚肉部の熱膨脹で他の部分よりも径が大
きくなり、サイドクリアランスが非常に小さく
なるか又は零となつてシール性が向上してグロ
ーバイガスが減少し、体積効率の向上に大きく
貢献できる。すなわち、圧縮機の作動状況に順
応してサイドクリアランスが自動的に制御可能
となつた。 Compressors are frequently automatically turned on and off in response to changes in vehicle interior temperature or suction pressure, and the thermal expansion of the piston is constantly changing. However, according to this proposal, when the compressor is started, the piston is at room temperature, so there is no thermal expansion of the coating and the outer diameter of the piston is uniform, so it is possible to set the side clearance. There is no fluctuation, and the abnormal rise in pressure in the cylinder chamber due to liquid compression, which tends to occur during startup, can be avoided by the relief action from the side clearance, which prevents damage to the discharge valve, gasket, etc., and also alleviates the startup shock. Also, during operation, as the temperature of the piston rises, the thick part of the coating thermally expands, making the diameter larger than other parts, and the side clearance becomes very small or becomes zero, improving sealing performance and preventing glow-by gas. This can greatly contribute to improving volumetric efficiency. In other words, the side clearance can now be automatically controlled in accordance with the operating conditions of the compressor.
被膜がフツ素樹脂のため、シリンダ室内周面
にうねりがあつても厚肉部が容易に変形しなが
ら摺動して、衝撃に起因する騒音の発生を防止
することができる。又、摺動部の摩耗係数が低
くなり、所要動力を軽減でき、耐焼付性を向上
することができる。 Since the coating is made of fluororesin, even if there are undulations on the inner circumferential surface of the cylinder, the thick portion easily deforms and slides, thereby preventing the generation of noise caused by impact. Furthermore, the wear coefficient of the sliding portion is reduced, the required power can be reduced, and the seizure resistance can be improved.
シリンダ室内周面とピストン外周面とのサイ
ドクリアランスの許容幅を大きくして、加工精
度及び組付精度を低下させ、製作及び組付を容
易に行うことができる。 By increasing the permissible width of the side clearance between the inner peripheral surface of the cylinder and the outer peripheral surface of the piston, processing accuracy and assembly accuracy can be reduced, and manufacturing and assembly can be performed easily.
第１図は本発明の圧縮機の要部を示す断面図、
第２図ａ〜ｃはそれぞれピストンに被膜を形成す
る工程の説明図、第３図ａは常温時のピストンと
シリンダ室の関係を示す断面図、第３図ｂは運転
時のピストンとシリンダ室の関係を示す断面図、
第４図は斜板式圧縮機用のピストンに実施した別
例を示す斜視図、第５図ａ，ｂは同じく常温時と
運転時の要部の状態を示す断面図、第６図ａ〜ｄ
はそれぞれ被膜の厚肉部の別例を示す断面図、第
７図は各膜厚ごとの運転時間を実験した結果を示
すグラフ、第８図及び第９図はそれぞれ従来の圧
縮機の要部を示す断面図である。
シリンダ室……１、ピストン……２，５、凹部
……２ａ，５ａ、シリンダブロツク……３、シリ
ンダ室内周面……３ａ、被膜……４，７、厚肉部
……４ａ，７ａ、薄肉部……４ｂ。
FIG. 1 is a sectional view showing the main parts of the compressor of the present invention;
Figures 2 a to c are explanatory diagrams of the process of forming a coating on the piston, Figure 3 a is a sectional view showing the relationship between the piston and the cylinder chamber at room temperature, and Figure 3 b is the piston and cylinder chamber during operation. A cross-sectional view showing the relationship between
Fig. 4 is a perspective view showing another example implemented in a piston for a swash plate compressor, Figs.
are cross-sectional views showing different examples of thick-walled parts of the coating, Fig. 7 is a graph showing the results of an experiment of operating time for each film thickness, and Figs. 8 and 9 are main parts of a conventional compressor, respectively. FIG. Cylinder chamber...1, Piston...2, 5, Recess...2a, 5a, Cylinder block...3, Cylinder interior circumferential surface...3a, Coating...4, 7, Thick wall part...4a, 7a, Thin wall portion...4b.
Claims (1)
に対し、周方向に連続し、かつ幅１〜５mmで幅方
向中央部へ行くにしたがい深くなる傾斜面を有す
る最深部が0.1〜0.5mmの深さを有する凹部を形成
するとともに、同凹部以外の外周面には厚さが20
〜100μmのフツ素樹脂により構成される被膜を、
前記凹部にはその最深部の厚さが120〜600μmの
同材料よりなる被膜をそれぞれ連続して続けてピ
ストン外周径を同一径と成し、同被膜の前記凹部
と対応する部分を厚肉部とし、凹部以外の部分を
薄肉部としたことを特徴とする圧縮機。1 Continuous in the circumferential direction of the outer peripheral surface of the piston that reciprocates in the cylinder chamber, and having a width of 1 to 5 mm and an inclined surface that becomes deeper as it goes toward the center in the width direction, the deepest part has a depth of 0.1 to 0.5 mm. A recess with a thickness of 20 mm is formed on the outer peripheral surface other than the recess.
A coating composed of ~100μm fluororesin,
A coating made of the same material having a thickness of 120 to 600 μm at the deepest part is continuously applied to the concave portion so that the piston outer circumferential diameter is the same, and the portion of the coating corresponding to the concave portion is called a thick wall portion. A compressor characterized in that the parts other than the recessed parts are thin-walled parts.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15722379A JPS5681280A (en) | 1979-12-03 | 1979-12-03 | Compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15722379A JPS5681280A (en) | 1979-12-03 | 1979-12-03 | Compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5681280A JPS5681280A (en) | 1981-07-03 |
| JPS6363752B2 true JPS6363752B2 (en) | 1988-12-08 |
Family
ID=15644907
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15722379A Granted JPS5681280A (en) | 1979-12-03 | 1979-12-03 | Compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5681280A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20190106906A (en) * | 2019-08-29 | 2019-09-18 | 엘지전자 주식회사 | Tool changer and tool change system |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0085687B1 (en) * | 1981-08-13 | 1988-11-09 | Commonwealth Scientific And Industrial Research Organisation | Reciprocatory piston and cylinder machine |
| EP3418568A1 (en) * | 2017-06-19 | 2018-12-26 | Nidec Global Appliance Germany GmbH | Piston for the drive unit of a refrigerant compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5438569Y2 (en) * | 1973-12-22 | 1979-11-16 | ||
| JPS50106106U (en) * | 1974-02-07 | 1975-09-01 |
-
1979
- 1979-12-03 JP JP15722379A patent/JPS5681280A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20190106906A (en) * | 2019-08-29 | 2019-09-18 | 엘지전자 주식회사 | Tool changer and tool change system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5681280A (en) | 1981-07-03 |
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