JPH04214970A - Unlubricated type reciprocating compressor and expander - Google Patents
Unlubricated type reciprocating compressor and expanderInfo
- Publication number
- JPH04214970A JPH04214970A JP10883790A JP10883790A JPH04214970A JP H04214970 A JPH04214970 A JP H04214970A JP 10883790 A JP10883790 A JP 10883790A JP 10883790 A JP10883790 A JP 10883790A JP H04214970 A JPH04214970 A JP H04214970A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- oil
- cylinder
- reciprocating compressor
- self
- 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
- 238000007906 compression Methods 0.000 claims abstract description 58
- 239000000463 material Substances 0.000 claims abstract description 42
- 229920005989 resin Polymers 0.000 claims abstract description 34
- 239000011347 resin Substances 0.000 claims abstract description 34
- 238000000465 moulding Methods 0.000 claims abstract description 15
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims abstract description 10
- 125000003367 polycyclic group Chemical group 0.000 claims abstract description 5
- 229920001187 thermosetting polymer Polymers 0.000 claims abstract description 4
- 238000000034 method Methods 0.000 claims description 24
- 239000002131 composite material Substances 0.000 claims description 22
- 230000008569 process Effects 0.000 claims description 22
- 239000003779 heat-resistant material Substances 0.000 claims description 14
- 229910002804 graphite Inorganic materials 0.000 claims description 8
- 239000010439 graphite Substances 0.000 claims description 8
- 229910052751 metal Inorganic materials 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 239000002184 metal Substances 0.000 claims description 6
- 239000004020 conductor Substances 0.000 claims description 5
- 125000003118 aryl group Chemical group 0.000 claims description 4
- 230000000630 rising effect Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 abstract description 47
- 239000012778 molding material Substances 0.000 abstract description 7
- 239000000805 composite resin Substances 0.000 abstract description 2
- 238000000748 compression moulding Methods 0.000 abstract description 2
- 238000001746 injection moulding Methods 0.000 abstract description 2
- 125000000325 methylidene group Chemical group [H]C([H])=* 0.000 abstract description 2
- 125000001997 phenyl group Chemical group [H]C1=C([H])C([H])=C(*)C([H])=C1[H] 0.000 abstract description 2
- 150000001491 aromatic compounds Chemical class 0.000 abstract 2
- 229910052782 aluminium Inorganic materials 0.000 description 13
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 13
- 230000000694 effects Effects 0.000 description 13
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 11
- 239000004810 polytetrafluoroethylene Substances 0.000 description 11
- 230000006866 deterioration Effects 0.000 description 7
- 238000007789 sealing Methods 0.000 description 7
- 229910000838 Al alloy Inorganic materials 0.000 description 5
- 230000001174 ascending effect Effects 0.000 description 5
- 239000007769 metal material Substances 0.000 description 5
- 230000007774 longterm Effects 0.000 description 4
- -1 polytetrafluoroethylene Polymers 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000005855 radiation Effects 0.000 description 3
- 229910052799 carbon Inorganic materials 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 229920000049 Carbon (fiber) Polymers 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 239000004917 carbon fiber Substances 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000004132 cross linking Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 239000005011 phenolic resin Substances 0.000 description 1
- 229920001568 phenolic resin Polymers 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 239000002344 surface layer Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Landscapes
- Compressor (AREA)
Abstract
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は無給油式往復圧縮機と膨張機に係り、特に自己
潤滑性材料で形成したピストンリングが嵌合されたピス
トン体と金属製のシリンダからなる無給油式往復圧縮機
と膨張機に関する。Detailed Description of the Invention "Field of Industrial Application" The present invention relates to an oil-free reciprocating compressor and an expander, and particularly relates to a piston body fitted with a piston ring made of a self-lubricating material and a metal piston body. This invention relates to an oil-free reciprocating compressor and an expander consisting of cylinders.
「従来の技術」
従来より、ピストンとシリンダ間の円滑な摺動性を確保
する為に、例えば第３図に示すように、アルミその他の
金属材で形成したピストン１０のトップ側からスカート
側に至る外周面のほぼ全域に亙って多段状にリング溝Ｉ
ＩＩａ、ＩＩＩｂ、ＩＩＩｃを凹設し、該リング溝にフ
ッ素樹脂その他の自己潤滑性樹脂からなるピストンリン
グ１０５ａ、１０５ｂとライダーリング１０６を環設す
るとともに、該リング外径をピストンのランド部１０２
（ピストンリングをリング溝の上下で保持するリング状
凸部）外径より僅かに大に設定する事により、自己潤滑
性のピストンリング１０５ａ、１０５ｂとライダーリン
グ１０６（以下リング体という）のみがシリンダと接触
し、これによりピストンとシリンダ間の円滑な摺動性を
保証する事が出来る様に構成した無給油式圧縮機や膨張
機は公知である。"Prior Art" Conventionally, in order to ensure smooth sliding between the piston and the cylinder, for example, as shown in FIG. Ring grooves I are formed in multiple stages over almost the entire outer circumferential surface.
IIa, IIIb, and IIIc are recessed, and piston rings 105a, 105b made of fluororesin or other self-lubricating resin and a rider ring 106 are installed in the ring grooves, and the outer diameter of the rings is set to the land portion 102 of the piston.
(The ring-shaped protrusion that holds the piston ring above and below the ring groove) By setting it slightly larger than the outer diameter, only the self-lubricating piston rings 105a and 105b and the rider ring 106 (hereinafter referred to as the ring body) are attached to the cylinder. Oil-free compressors and expanders are known that are configured to be in contact with the piston and the cylinder, thereby ensuring smooth sliding between the piston and the cylinder.
さてかかる流体機械の場合、シリンダがピストンリング
より固い金属材料で形成されている為に、前記摺接によ
りリング体が摩耗し且つ長時間運転によりその摩耗限界
を越えると、ピストンの外周（ランド部）が直接シリン
ダに摺接し、かじり等が発生する場合がある。In the case of such fluid machines, since the cylinder is made of a metal material that is harder than the piston ring, the ring body wears out due to the sliding contact, and if the wear limit is exceeded due to long-term operation, the outer periphery of the piston (land part ) may come into direct sliding contact with the cylinder, causing galling, etc.
特に５ｋｇｆ／ｃｍ２以上の圧縮比を有する圧縮機の場
合、最大圧縮時に３００℃前後の圧縮熱がピストン上面
に印加されているために熱膨張が生じ、僅かなリング体
の摩耗でも前記ピストンがシリンダに摺擦してしまうと
いう問題を生じてしまう。In particular, in the case of a compressor with a compression ratio of 5 kgf/cm2 or more, thermal expansion occurs because compression heat of around 300°C is applied to the top surface of the piston during maximum compression, and even slight wear of the ring body causes the piston to move into the cylinder. This results in the problem of rubbing against the surface.
かかる欠点を解消するために、公知の圧縮機においては
前記リング体に摺動性能のよいポリテトラフルオロエチ
レン（ＰＴＦＥ）系の樹脂材料を用いると共に、ピスト
ン／シリンダ間のクリアランスを、ピストン外径に対し
１〜２％（５０ｍｍφのピストン外径に対し、０．５〜
１ｍｍ）程度に設定している。In order to eliminate such drawbacks, in known compressors, a polytetrafluoroethylene (PTFE) resin material with good sliding performance is used for the ring body, and the clearance between the piston and cylinder is adjusted to the outer diameter of the piston. 1~2% (0.5~2% for 50mmφ piston outer diameter)
1mm).
しかしながらかかる構成を取ると圧縮初期若しくは断続
運転時等においてはピストン／シリンダ間のクリアラン
スが無用に大になり、その分圧縮効率の低下を生じやす
い。However, if such a configuration is adopted, the clearance between the piston and the cylinder becomes unnecessarily large at the initial stage of compression or during intermittent operation, and compression efficiency tends to decrease accordingly.
かかる欠点を解消するために、アルミ材からなるピスト
ンの表面に自己潤滑性樹脂を被膜処理し、ピストン外周
が直接シリンダに摺接した場合でも、かじり等の発生を
防止するようにした技術が開示されているが、従来ピス
トンリング等に多用されている前記ＰＴＦＥ等の自己潤
滑性樹脂の耐熱強度は２００〜２５０℃前後である為に
、前記したように断熱圧縮比を５ｋｇｆ／ｃｍ２以上に
高くした場合に、前記圧縮熱が容易に前記ＰＴＦＥの耐
熱温度以上になり、ピストン表面被膜の劣化、変形、更
にはアルミ材からなるピストン本体との間で生じる熱膨
張率等の差異に起因して剥離や亀裂等が生じる恐れがあ
り、この為かかる技術は圧縮熱による温度上昇の少ない
低圧用の圧縮機以外に適用不可能であるという欠点を有
す。In order to eliminate this drawback, a technology has been disclosed in which the surface of the piston made of aluminum is coated with a self-lubricating resin to prevent the occurrence of galling even when the outer circumference of the piston comes into direct sliding contact with the cylinder. However, since the heat resistance strength of the self-lubricating resin such as PTFE, which is commonly used in piston rings etc., is around 200 to 250°C, as mentioned above, the adiabatic compression ratio has to be increased to 5 kgf/cm2 or more. In this case, the compression heat easily exceeds the heat resistance temperature of the PTFE, resulting in deterioration and deformation of the piston surface coating, and furthermore, due to differences in thermal expansion coefficient between the piston body and the piston body made of aluminum material. There is a risk that peeling, cracking, etc. may occur, and therefore, this technique has the disadvantage that it cannot be applied to anything other than low-pressure compressors where the temperature rise due to compression heat is small.
又、前記いずれの従来技術においてもピストン自体が金
属材、特に軽量化を達成するために、アルミ材で形成し
ているが、アルミ材は熱伝導率が高い為にピストン頂面
で受熱した圧縮熱はピストン全体に伝わり、特にピスト
ンピンを介してピストンを駆動する連接棒の動きを伝え
るピン孔部も高温となり、而も無給油圧縮機の場合前記
ピストンピン部を油冷却する等の手段を取り得ないため
に、耐熱性を有する軸受け部品等を使用したりしなけれ
ばならず、而も該ピストンピン部が他の軸受けに比較し
て単位面積当りの荷重が大であり結果として耐熱性と耐
荷重性を有する軸受けを用いなければならず、前記高コ
スト化と耐久性の低下を引起こしやすい。In addition, in all of the above conventional technologies, the piston itself is made of a metal material, especially aluminum material in order to achieve weight reduction, but since aluminum material has high thermal conductivity, the compression caused by the heat received on the top surface of the piston is Heat is transmitted to the entire piston, and in particular, the pin hole that transmits the movement of the connecting rod that drives the piston through the piston pin also becomes high temperature. Since this is not possible, it is necessary to use heat-resistant bearing parts, etc., and the load per unit area of the piston pin is larger than other bearings, and as a result, heat-resistant A bearing with load resistance must be used, which tends to increase the cost and reduce durability.
さて往復圧縮機は一般に気密シールを行うピストンリン
グを、リング溝内への挿入を可能にするために、円形リ
ングの一端を切断したＣの字形状をしているが、特に無
給油式圧縮機の場合は前記したように、給油式圧縮機に
比較してピストン／シリンダ間のクリアランスが大であ
りこの為前記リング端部同士の接合部（合い口）よりの
ガス洩れが生じやすい。Now, reciprocating compressors generally have a C-shape in which one end of a circular ring is cut off in order to allow the piston ring that provides an airtight seal to be inserted into the ring groove, but oil-free compressors in particular In this case, as described above, the clearance between the piston and cylinder is larger than that in an oil-fed compressor, and therefore gas leakage is likely to occur from the joint between the ring ends.
この為通常の圧縮機と同様に無給油式圧縮機においても
前記合い口部をステップカット等の形状に工夫を懲らす
と共に、該リングを多段状に配置し、各リングの合い口
が軸方向の同一位置に合致しないように周方向に位置を
ずらして配置しているが、このような構成を取っても、
上下のピストンリング間に存在するピストンランド部と
シリンダ間にはリング状のクリアランスが存在する為に
該クリアランスを介して隣接するリングの合い口同士が
連通してしまい、ガス洩れを防止し得ない。For this reason, in oil-free compressors as well as in normal compressors, the abutment portions are designed to have a step-cut shape, etc., and the rings are arranged in multiple stages, so that the abutment of each ring is centered on the shaft. The positions are shifted in the circumferential direction so that they do not coincide in the same position, but even with this configuration,
Since there is a ring-shaped clearance between the piston land between the upper and lower piston rings and the cylinder, the joints of adjacent rings communicate with each other through this clearance, making it impossible to prevent gas leakage. .
かかる欠点を解消する為に、前記ピストンのリング溝内
にピンその他のピストンリングの固定手段を配し前記合
い口部を圧縮工程時のシリンダと密接するサイドスラス
ト側に位置固定させるような技術が考えられる。（かか
る技術は給油タイプの圧縮機の分野では日本国実公昭６
０−２６２３６号にて公知であるが、無給油式圧縮機の
分野では新規である。）
しかしながら無給油式圧縮機においては前記したように
ピストンがシリンダに対し非接触の状態を維持している
為にシリンダと密接するサイドスラスト側をピストンリ
ングの合い口部でシールしようとしても、軸方向に切断
される合い口部が存在する限り、その完全な封止を行う
事が出来ず、而も無給油式圧縮機で使用されるピストン
リングは、金属製ではなく樹脂体である為に一部を切り
欠いて前記ピンに係合させるような構造は取りにくく、
前記合い口部と対応する箇所にピンを設けると、前記合
い口部が離間してその離間部位よりガス洩れが生じてし
まう。In order to eliminate this drawback, a technique has been proposed in which a pin or other piston ring fixing means is arranged in the ring groove of the piston to fix the abutment part on the side thrust side that is in close contact with the cylinder during the compression process. Conceivable. (Such technology was developed in the field of oil-filled compressors in the 6th year of Japan
0-26236, but is new in the field of oilless compressors. ) However, in an oil-free compressor, as mentioned above, the piston maintains a non-contact state with the cylinder, so even if you try to seal the side thrust side that is in close contact with the cylinder with the abutment of the piston ring, the shaft As long as there is a joint that is cut in the same direction, it is impossible to completely seal it, and this is because the piston rings used in oil-free compressors are made of resin rather than metal. It is difficult to create a structure where a part is cut out and engaged with the pin.
If a pin is provided at a location corresponding to the abutting portion, the abutting portion will be spaced apart and gas will leak from the separated portion.
「発明が解決しようとする課題」
本発明はかかる従来技術の欠点に鑑み、かじりや圧縮効
率（膨張効率）が低下する事のない無給油式往復圧縮機
／膨張機を提供する事を目的とする。"Problems to be Solved by the Invention" In view of the drawbacks of the prior art, the present invention aims to provide an oil-free reciprocating compressor/expander that does not cause galling or decrease in compression efficiency (expansion efficiency). do.
本発明の他の目的とする所は、高い圧縮熱がピストン頂
部と接触する場合でもピストンの変形や劣化等が生じる
事のない無給油式往復圧縮機を提供する事にある。Another object of the present invention is to provide an oil-free reciprocating compressor that does not cause deformation or deterioration of the piston even when high compression heat comes into contact with the top of the piston.
本発明の他の目的とする所は、リング合い口よりのガス
洩れやかじりが生じる事なく長期に亙って高圧縮効率（
目張効率）を維持し得る無給油式往復圧縮機／膨張機を
提供する事にある。Another object of the present invention is to maintain high compression efficiency (
The purpose of the present invention is to provide an oil-free reciprocating compressor/expander that can maintain a high density efficiency.
「課題を解決するための手段」
Ａ、請求項１）〜４）に記載した発明（第１発明）かか
る目的を達成するために、請求項１に記載した発明にお
いては、近年開発された熱硬化性縮合多環多核芳香族樹
脂（以下ＣＯＰＮＡ樹脂という）を成形材料に用い、該
樹脂に摺動性を高める耐熱材料、例えば黒鉛と必要に応
じて炭素繊維等の強度性を高める材料等を混入して、耐
熱性と強度性に加えて自己潤滑性を高めた樹脂系複合材
を用い、該複合材でピストン体を形成した点にある。"Means for Solving the Problem" A. The invention described in claims 1) to 4) (first invention) In order to achieve the object, the invention described in claim 1 uses the recently developed thermal A curable condensed polycyclic polynuclear aromatic resin (hereinafter referred to as COPNA resin) is used as a molding material, and a heat-resistant material that increases sliding properties, such as graphite, and if necessary, a material that increases strength such as carbon fiber is added to the resin. The piston body is formed by using a resin-based composite material that has been mixed with other materials to improve heat resistance, strength, and self-lubricating properties.
Ｂ、請求項５）〜９）に記載された発明（第２発明）さ
て前記発明はピストン自体がアルミ材に比較して熱伝導
が低いために、ピストンピンの高熱化は防げるが、逆に
ピストン頂部に高熱が蓄熱され、複合材自体のたい熱温
度を超えないまでも圧縮効率が低下してしまう恐れがあ
る。B. Inventions stated in Claims 5) to 9) (Second Invention) Now, in the above invention, since the piston itself has lower heat conduction than aluminum material, it is possible to prevent the piston pin from becoming hotter, but on the contrary, High heat is stored at the top of the piston, and even if the temperature does not exceed that of the composite material itself, there is a risk that the compression efficiency will decrease.
そこで請求項５）に記載した発明においては、シリンダ
及びピストンピン部との円滑な摺動機能と、吐出／吸込
弁と対面する頂部、言い変えれば圧縮熱と接触するピス
トン頂部側の耐熱（熱伝搬）機能を分離し、外周部の内
少なくともシリンダと摺擦される部位とピストンピン孔
部を自己潤滑性耐熱材料で、又ピストン頂部をアルミ等
の良熱伝導性材料で夫々形成する事により、前記した欠
点の解消を図ったものである。Therefore, in the invention described in claim 5), smooth sliding function with the cylinder and piston pin part, and heat resistance (heat resistance) of the top part facing the discharge/suction valve, in other words, the top part of the piston that comes into contact with compression heat. By separating the functions (propagation), at least the part of the outer periphery that rubs against the cylinder and the piston pin hole are made of a self-lubricating heat-resistant material, and the top of the piston is made of a material with good thermal conductivity such as aluminum. , which aims to eliminate the above-mentioned drawbacks.
Ｃ、請求項１０）〜１３）に記載された発明（第３発明
）本発明は前記したようにピストンリングの合い口部の
ガス洩れを阻止する為に、下記３つの考えより出発して
いる。C. The invention described in Claims 10) to 13) (Third invention) As described above, the present invention is based on the following three ideas in order to prevent gas leakage at the joint portion of the piston ring. .
その第１は圧縮工程時のシリンダと密接するサイドスラ
スト側をピストンリングの合い口部でシールしようとし
ても、軸方向に切断される合い口部が存在する限り、そ
の完全な封止を行う事が出来ず、而も従来の無給油式圧
縮機においてはピストンとシリンダ間は非接触状態を維
持している為に、前記合い口部のみで封止しなければな
らず、給油式圧縮機に比較してその条件が悪い。The first is that even if you try to seal the side thrust side that comes into close contact with the cylinder during the compression process with the abutment of the piston ring, as long as there is an abutment that is cut in the axial direction, it will not be possible to completely seal it. However, in conventional oil-free compressors, the piston and cylinder maintain a non-contact state, so it is necessary to seal only at the joint, which is difficult to achieve in oil-filled compressors. The conditions are poor in comparison.
そこで本発明は前記第１発明の様にピストン若しくはそ
の摺動面を自己潤滑性材料で形成しピストン自体のシリ
ンダとの摺接を可能にし、圧縮工程時のシリンダと密接
するサイドスラスト部に位置するピストン自体の周面で
実質的に気密封止を可能にした点を第１の特徴とする。Therefore, the present invention, as in the first invention, forms the piston or its sliding surface with a self-lubricating material to enable sliding contact between the piston itself and the cylinder, and positions the piston at the side thrust part in close contact with the cylinder during the compression process. The first feature is that it is possible to achieve a substantially airtight seal on the circumferential surface of the piston itself.
この場合、第２発明の様に、シリンダと対峙するピスト
ン摺動面を自己潤滑性材料で形成してもよく、又シリン
ダ側若しくはシリンダとピストンの両者若しくはその表
層部のみを自己潤滑性材料で形成してもよい。In this case, as in the second invention, the piston sliding surface facing the cylinder may be formed of a self-lubricating material, or the cylinder side, both the cylinder and the piston, or only the surface layer thereof may be formed of a self-lubricating material. may be formed.
しかしながら前記の様に構成しても、前記サイドスラス
ト部にリング溝が存在する場合はその封止はピストンリ
ング、言い換えればそのリング溝位置に存在するピスト
ンリングの合い口部に封止条件が依存してしまう。However, even with the above configuration, if a ring groove exists in the side thrust part, the sealing condition depends on the piston ring, or in other words, the sealing condition depends on the abutment of the piston ring that exists at the position of the ring groove. Resulting in.
そこで本発明においては前記サイドスラスト位置にリン
グ溝を設ける事なく、該リング溝を前記サイドスラスト
部で離間されるＣの字状に形成してピストン周面自体で
封止可能にする。Therefore, in the present invention, instead of providing a ring groove at the side thrust position, the ring groove is formed in a C shape separated by the side thrust portion, so that it can be sealed with the piston peripheral surface itself.
「作用」
Ａ、第１発明の作用
かかる発明によれば前記ＣＯＰＮＡ樹脂自体の熱変形温
度が２５０℃以上であり且つ該成形樹脂に黒鉛等のより
高耐熱性の材料を加えて成形するものである為に、耐熱
性を優に３００℃前後若しくはそれ以上に維持出来るた
めに、断熱圧縮比を５ｋｇｆ／ｃｍ２以上（圧縮熱が３
００℃前後）に設定した場合でもピストンに何等熱変形
が生じる事なく長期に亙って耐熱劣化が生じる事はない
。"Function" A. Function of the first invention According to this invention, the heat distortion temperature of the COPNA resin itself is 250°C or higher, and the molding is performed by adding a material with higher heat resistance such as graphite to the molding resin. Therefore, in order to maintain heat resistance well around 300℃ or higher, the adiabatic compression ratio should be set to 5kgf/cm2 or more (the heat of compression is 300℃ or higher).
Even if the piston is set at a temperature of around 00°C, no thermal deformation will occur in the piston, and no deterioration in heat resistance will occur over a long period of time.
而も前記複合材は摺動性を高める黒鉛等を混入して成形
した為に、それ自体で自己潤滑性機能を有し、結果とし
てピストン自体がシリンダと摺接してもかじり等が生じ
る事なく円滑な摺動性能を得る事が出来る。Moreover, because the composite material is molded with graphite, etc. mixed in to improve sliding properties, it has a self-lubricating function by itself, and as a result, even when the piston itself slides into contact with the cylinder, there is no galling or the like. Smooth sliding performance can be obtained.
而も、熱膨張率はアルミ材に比較して数段低いためにピ
ストン／シリンダ間のクリアランスを小にしても問題が
生じる事なく、これにより却って圧縮効率の向上を図る
事が出来る。この場合熱膨張によるかじりが生じる事な
く高圧縮効率を得るために、最も好ましいクリアランス
はかじりが生じない範囲できっちり嵌合可能に、より具
体的にはピストン直径に対し常温で０．１〜０．５％程
度に設定するのがよく、そして特に前記ピストンは熱伝
導率がアルミ材に比して小さいために、ピストン頂部へ
の圧縮熱蓄熱量が多く圧縮運転時にピストン上部と下部
における熱膨張率が異なる結果、ピストン／シリンダ間
のクリアランスが不均一になり圧縮効率に悪影響を及ぼ
し易い。そこで本発明の好ましい実施例においてはピス
トン上部側の直径を下部側の直径に比較して相対的に小
、好ましくは逆テーパ状に形成するのがよい。However, since the coefficient of thermal expansion is several steps lower than that of aluminum material, there is no problem even if the clearance between the piston and the cylinder is made small, and this makes it possible to improve the compression efficiency. In this case, in order to obtain high compression efficiency without galling due to thermal expansion, the most preferable clearance is a tight fit within the range where galling does not occur, more specifically, 0.1 to 0 at room temperature relative to the piston diameter. It is best to set the value to about .5%.In particular, since the piston has a lower thermal conductivity than aluminum, a large amount of compression heat is stored at the top of the piston, resulting in thermal expansion at the top and bottom of the piston during compression operation. As a result of the different ratios, the piston/cylinder clearance tends to be non-uniform, which can adversely affect compression efficiency. Therefore, in a preferred embodiment of the present invention, the diameter of the upper part of the piston is relatively smaller than the diameter of the lower part, preferably in a reverse tapered shape.
一方前記複合材がアルミ材に比較して熱伝導率が数段小
さい事はピストンピン側の軸受け部に取っては逆に好ま
しい作用が生じる。On the other hand, the fact that the thermal conductivity of the composite material is several orders of magnitude lower than that of the aluminum material has a conversely favorable effect on the bearing portion on the piston pin side.
即ち複合材で形成したピストンは熱伝導率が小さいため
に、ピストン頂面で受熱した圧縮熱が該頂部よりピスト
ンピン側に伝わるより、金属製のシリンダより放熱され
る率が多く、結果としてピストンピン孔部の高温化が抑
制される事となり、結果として耐熱性を考慮する事なく
ピストンピン部を形成し得ると共に、該ピストン自体に
自己潤滑性機能をもたせたために、、特別な軸受け部材
を設ける事なく直接ピストンピンを嵌合させる事が可能
となる。In other words, since a piston made of a composite material has a low thermal conductivity, the heat of compression received at the top of the piston is radiated more than a metal cylinder, rather than being transmitted from the top to the piston pin, and as a result, the piston The high temperature of the pin hole is suppressed, and as a result, the piston pin can be formed without considering heat resistance, and since the piston itself has a self-lubricating function, a special bearing member is used. It becomes possible to directly fit the piston pin without providing it.
これにより部品点数の削減と低コスト化が可能になると
共に、前記ピン孔部が高温に曝される事がないために、
耐久性の向上が図れる。This makes it possible to reduce the number of parts and lower costs, and since the pin hole is not exposed to high temperatures,
Durability can be improved.
又前記ピン孔部はピストンの上昇工程から下降工程若し
くは下降工程から上昇工程に移行時に衝撃を受け、従来
の軸受けを用いる構造では前記衝撃により軸受けの劣化
等が生じてしまうが、本発明においては、弾性力を有す
る複合材からなるピストン自体を軸受けとして機能させ
たために、ピストンにより前記衝撃を吸収し、耐久性の
向上を図る事が出来る。In addition, the pin hole receives an impact when the piston moves from the ascending process to the descending process or from the descending process to the ascending process, and in a structure using a conventional bearing, the impact causes deterioration of the bearing, but in the present invention, Since the piston itself made of a composite material having elasticity functions as a bearing, the piston can absorb the impact and improve durability.
Ｂ、第２発明の作用
かかる構成によれば、圧縮熱と接触するピストン頂部側
はアルミ等の材質により形成されている為に、例え断熱
圧縮比を高くし圧縮熱が３００℃前後まで上昇しても該
頂部が変形若しくは劣化する事なく、而も前記頂部は吸
込時の冷気が触れることによって冷却されるので、圧縮
熱が蓄熱される事なく吐出空気を介して容易に放出され
、結果としてその下方に位置する自己潤滑性耐熱材で形
成された部位への伝熱温度が圧縮熱に近いところまで高
温化する事なく、該自己潤滑性材料を例え耐熱温度の低
いフッ素樹脂で形成しても容易に耐熱温度以下に維持す
る事が可能となる。B. Effect of the second invention According to this configuration, since the top side of the piston that comes into contact with the compression heat is formed of a material such as aluminum, even if the adiabatic compression ratio is made high, the compression heat will rise to around 300°C. However, the top part does not deform or deteriorate, and since the top part is cooled by contact with the cold air during suction, the heat of compression is easily released through the discharge air without being stored. The heat transfer temperature to the part formed of the self-lubricating heat-resistant material located below it does not rise to a high temperature close to the heat of compression, and the self-lubricating material is made of, for example, a fluororesin with a low heat resistance temperature. can also be easily maintained below the heat-resistant temperature.
この場合特に、ピストン頂部とともに圧縮熱が最も伝達
し易いトップランド１４部を良熱伝導体を用いて形成す
る事により前記放熱効果が一層向上し、更に耐熱温度の
低いフッ素樹脂の使用が一層可能になるが、この場合は
該トップランド部の外径を、その下方のピストン径より
僅かに小に設定し、シリンダ側との摺擦を避けるように
構成する事によりトップランド部のかじりを防止し、円
滑なピストン摺動性能を保証し得る。即ち前記ピストン
本体の少なくともシリンダと摺擦する外周面側は自己潤
滑性耐熱材で形成され、而も該外周面側は前記したよう
に圧縮熱の伝熱を極力避けている為に、耐熱温度の低い
材料でも円滑な摺動性の確保が容易になる。In this case, the heat dissipation effect is further improved by forming the top land 14, where compression heat is most easily transferred along with the top of the piston, using a good heat conductor, and it is further possible to use fluororesin, which has a low heat resistance temperature. However, in this case, the outer diameter of the top land is set to be slightly smaller than the diameter of the piston below it, and galling is prevented by configuring the top land to avoid rubbing against the cylinder side. This ensures smooth piston sliding performance. That is, at least the outer circumferential surface side of the piston body that slides against the cylinder is formed of a self-lubricating heat-resistant material, and since the outer circumferential surface side is prevented from transferring compression heat as much as possible as described above, it has a heat-resistant temperature. Smooth sliding properties can be easily ensured even with materials with low friction.
従って本発明におけるところの自己潤滑性耐熱材料は、
必ずしもＣＯＰＮＡ樹脂の複合材のみに限定される事な
く、ポリテトラフルオロエチレン（ＰＴＦＥ）系樹脂若
しくはその複合材、更にはフッ素樹脂で形成する事も可
能である。Therefore, the self-lubricating heat-resistant material in the present invention is
It is not necessarily limited to a composite material of COPNA resin, but can also be formed from a polytetrafluoroethylene (PTFE) resin or a composite material thereof, or even a fluororesin.
そして本発明の構成は請求項７）（第４図、優先権主張
１）に記載したように、金属材で形成したピストン芯体
周囲に前記複合材を一体成形してピストンを形成したも
ので、より詳細にはピストン頂部とその背面側に金属材
からなる芯体を露出させた状態で、シリンダと摺接する
ピストン外周と前記ピン孔部位を前記複合材を用いて厚
肉に一体成形してもよく、
又請求項８）に記載したように、ピストン本体を自己潤
滑性耐熱材料で形成しつつ、少なくとも吐出弁と対面す
るピストン頂部側に良熱伝導性の金属体を配し、任意の
固定手段を用いて両者間を一体化してもよい。As described in claim 7) (Fig. 4, priority claim 1), the structure of the present invention is such that a piston is formed by integrally molding the composite material around a piston core made of a metal material. More specifically, with the core body made of metal material exposed at the top of the piston and its back side, the outer periphery of the piston that comes into sliding contact with the cylinder and the pin hole area are integrally formed with a thick wall using the composite material. Also, as described in claim 8), the piston body is formed of a self-lubricating heat-resistant material, and a metal body with good thermal conductivity is arranged at least on the top side of the piston facing the discharge valve, and an arbitrary The two may be integrated using a fixing means.
この場合ピストン頂部側の良熱伝導体を、直接的に若し
くはリベット等の連結体を介して実質的にピストン頂部
の裏面側まで延設する事により、ピストン内部より放熱
させる事によってピストン摺動面側への熱移動を減少さ
せ、外周部側の温度上昇を極力避けピストンとシリンダ
間の円滑な摺動性の確保を図ることが可能となる。In this case, by extending a good heat conductor on the piston top side directly or through a connecting body such as a rivet to the back side of the piston top, heat is radiated from inside the piston and the piston sliding surface It is possible to reduce heat transfer to the side, avoid temperature rise on the outer peripheral side as much as possible, and ensure smooth sliding between the piston and cylinder.
Ｃ、第３発明の作用
そして、前記ピストンリングの合い口の廻り止め機能を
、前記サイドスラスト位置に形成された離間部位を利用
し、該リング溝の離間部とピストンリングの組合せにお
いて円状になり、該シール円を利用して前記シリンダを
気密的にシール可能に構成する事が出来る。C. Effect of the third invention, and the rotation prevention function of the abutment of the piston ring is achieved in a circular shape by utilizing the separated part formed at the side thrust position, in the combination of the separated part of the ring groove and the piston ring. Therefore, the cylinder can be configured to be airtightly sealed using the seal circle.
尚、本発明は前記単段圧縮機のみに限定される事なく、
無給油式単段往復膨張機や無給油式多段往復圧縮機にも
適用可能であり、前者の膨張機の場合は膨張工程時のシ
リンダと密接するサイドスラスト部に位置するピストン
自体に前記構成を取ればよく、又後者の多段往復圧縮機
の場合は、低段側においてはピストン上昇工程時のシリ
ンダと密接するサイドスラスト部に、又高段側において
はピストン上昇工程と下降工程の両サイドスラスト部に
、夫々前記構成を施せばよい。Note that the present invention is not limited to the single-stage compressor, but
It can also be applied to oil-free single-stage reciprocating expanders and oil-free multi-stage reciprocating compressors; in the case of the former expander, the above structure is applied to the piston itself located in the side thrust part that comes into close contact with the cylinder during the expansion process. In the case of the latter multi-stage reciprocating compressor, on the low stage side, the side thrust part that is in close contact with the cylinder during the piston rising process, and on the high stage side, the side thrust part during the piston rising process and the piston falling process. The above structure may be applied to each of the parts.
即ち前記ピストン本体の少なくともシリンダと摺擦する
外周面側は自己潤滑性耐熱材で形成されているとともに
、前記したように圧縮熱の伝熱を極力避けている為に、
前記した円滑な摺動性の確保が容易になる。That is, at least the outer circumferential surface side of the piston body that slides against the cylinder is made of a self-lubricating heat-resistant material, and as mentioned above, the transfer of compression heat is avoided as much as possible.
It becomes easier to ensure the smooth sliding properties described above.
「実施例」
以下、図面を参照して本発明の好適な実施例を例示的に
詳しく説明する。ただしこの実施例に記載されている構
成部品の寸法、材質、形状、その相対配置などは特に特
定的な記載がない限りは、この発明の範囲をそれのみに
限定する趣旨ではなく、単なる説明例に過ぎない。"Embodiments" Hereinafter, preferred embodiments of the present invention will be described in detail by way of example with reference to the drawings. However, unless otherwise specified, the dimensions, materials, shapes, and relative arrangements of the components described in this example are not intended to limit the scope of this invention, but are merely illustrative examples. It's nothing more than that.
先ず第１図に基づいて本発明が適用される無給油圧縮機
の要部構成について説明するに、２及び３はアルミその
他の良導電性の金属材からなるシリンダとシリンダヘッ
ドで、両部材１、２間に吐出弁４Ａと吸込弁４Ｂが組込
まれたスペーサ４が挟持されている。そして前記シリン
ダヘッド３内は隔壁３Ａにより分割されており、夫々対
応する隔室に吸込弁４Ｂと連通する吸込口３Ｂと、吐出
弁４Ａと連通する吐出口３Ｃを設けている。First, the main structure of an oil-free compressor to which the present invention is applied will be explained based on FIG. , a spacer 4 having a discharge valve 4A and a suction valve 4B incorporated therein is sandwiched between them. The interior of the cylinder head 3 is divided by a partition wall 3A, and each corresponding compartment is provided with a suction port 3B communicating with the suction valve 4B and a discharge port 3C communicating with the discharge valve 4A.
一方シリンダ２内にはピストンリング５が環設されたピ
ストン１が嵌装されており、公知のように不図示のクラ
ンク軸８の回転により連接棒６ピストンピン７を介して
前記ピストン１が往復動し、これにより前記吸込弁４Ｂ
を介してピストン１頂部空間に吸い込まれた空気が断熱
圧縮されて吐出弁４Ａより吐出口３Ｃ側に吐出され、所
定の圧縮動作が行われる。かかる動作は既に周知である
為にその説明を省略する。On the other hand, a piston 1 having a piston ring 5 is fitted in the cylinder 2, and as is well known, the piston 1 is reciprocated via a connecting rod 6 and a piston pin 7 by rotation of a crankshaft 8 (not shown). This causes the suction valve 4B to
The air sucked into the top space of the piston 1 through the piston 1 is adiabatically compressed and discharged from the discharge valve 4A to the discharge port 3C side, and a predetermined compression operation is performed. Since this operation is already well known, its explanation will be omitted.
さて第２図は前記無給油圧縮機に組込まれるピストンと
シリンダ部分の要部構成を示す第１発明の実施例にであ
る。Now, FIG. 2 is an embodiment of the first invention showing the main structure of the piston and cylinder portions incorporated in the oil-free compressor.
シリンダ２は、公知の様にアルミ合金からなり、外周面
にフィン２ａを又内周面側のピストン摺動部を硬質アル
マイト処理を施している。The cylinder 2 is made of an aluminum alloy, as is well known, and has fins 2a on its outer circumferential surface, and hard alumite treatment is applied to the piston sliding portion on its inner circumferential surface.
次にピストン１の形状を説明する前に、該ピストン１の
製造手順について詳細に説明する。Next, before explaining the shape of the piston 1, the manufacturing procedure of the piston 1 will be explained in detail.
本ピストン１は、ＵＳＰ４、７５８、６５３に示される
様に、パラ位に１つづつ計２つのメチレン鎖を持つベン
ゼン環が縮合多環芳香族化合物の間を架橋して形成され
るＣＯＰＮＡ樹脂（日本国特許公開公報６２−５２１、
５２２）に基づいて形成されるレジン材料（商品名ＳＫ
レジン：ＳＵＭＩＴＯＭＯ ＭＥＴＡＬＳ ＣＯ．ＬＴ
Ｄ）と黒鉛粉末を６：４の割合で混合した成形材料を用
い、該成形材料を成形温度１７０〜２２０℃、成形圧力
２００〜３００ＫＧ／ｃｍ２、硬化時間を１分／１ｍｍ
厚の成形条件をで公知のフェノール樹脂の成形と同様な
圧縮成形手段又は射出成形手段にて成形を行なう。As shown in US Pat. No. 4,758,653, this piston 1 is made of COPNA resin (COPNA resin) which is formed by cross-linking between fused polycyclic aromatic compounds in which benzene rings have two methylene chains, one at the para position. Japanese Patent Publication No. 62-521,
522) is formed based on the resin material (trade name SK
Resin: SUMITOMO METALS CO. LT
D) and graphite powder mixed at a ratio of 6:4, the molding material was molded at a molding temperature of 170 to 220°C, a molding pressure of 200 to 300 KG/cm2, and a curing time of 1 minute/1 mm.
Molding is carried out using compression molding means or injection molding means similar to those used for molding known phenolic resins under the same molding conditions as the thickness.
そしてこのようにして形成されたピストン１は、熱膨張
率：４．４×１０−５／ｄｅｇ，熱伝導率１．１２ｋｃ
ａｌ／ｍ／．ｈｒ℃の物理的特性を有し、従来のアルミ
合金（熱膨張率：２．３×１０−５／ｄｅｇ、熱伝導率
：０．０１３ｋｃａｌ／ｍ／．ｈｒ℃）で形成したピス
トン１に比して熱膨張率で１．９倍、熱伝導率で１／８
６倍と、断熱性と蓄熱性の高いピストン１が形成し得た
。The piston 1 thus formed has a thermal expansion coefficient of 4.4 x 10-5/deg and a thermal conductivity of 1.12 kc.
al/m/. hr℃, compared to piston 1 made of conventional aluminum alloy (thermal expansion coefficient: 2.3 x 10-5/deg, thermal conductivity: 0.013kcal/m/.hr℃). The thermal expansion coefficient is 1.9 times, and the thermal conductivity is 1/8.
It was possible to form a piston 1 with six times higher heat insulation and heat storage properties.
次にそのピストン１形状について説明するに、外径形状
はピストン頂部１３より下方のスカート部にかけて熱勾
配を配慮した寸法差で下方に広がるテーパ状をなし、例
えばピストン１とシリンダ２との熱膨張率の差△ｂは２
．１×１０−５／ｄｅｇであるために、ピストン１上部
と下部の温度差を△ｔ、ピストン１外径をＰとした場合
に、△ｔ．Ｐ（２．１×１０−５／ｄｅｇ）のテーパ差
に設定すれば、圧縮運転時におけるピストン１／シリン
ダ２のクリアランスを均一に維持する事が出来る。Next, to explain the shape of the piston 1, the outer diameter shape is tapered downward from the piston top 13 to the lower skirt part with a dimensional difference that takes thermal gradients into account. The difference in rates △b is 2
．． 1×10-5/deg, so if the temperature difference between the upper and lower parts of the piston 1 is Δt, and the outer diameter of the piston 1 is P, then Δt. By setting the taper difference to P (2.1×10 −5 /deg), it is possible to maintain a uniform piston 1/cylinder 2 clearance during compression operation.
又前記クリアランスはピストン頂部１３で受熱する圧縮
熱が３００℃前後であるために、ピストン１直径に対し
常温で０．１〜０．５％程度に設定することにより、圧
縮運転時にかじりが生じる事なく、且つピストン１／シ
リンダ２間のクリアランスも往復動に差し支えない最小
値にとどめることが出来、これによりピストン１外周全
体がシリンダ２面との摺動面として機能させる事が出来
る為にピストンの黒鉛がシリンダに転移してより摺動性
並びにシール性を向上させる。これにより、後記ピスト
ンリング５の合い口部５ａその他よりピストン１周面を
通って生じるガス洩れを大幅に低減でき、圧縮効率の向
上が図れる。Also, since the compression heat received at the piston top 13 is around 300°C, the clearance is set to about 0.1 to 0.5% of the piston diameter at room temperature to prevent galling during compression operation. In addition, the clearance between piston 1 and cylinder 2 can be kept to the minimum value that does not interfere with reciprocating motion, and as a result, the entire outer circumference of piston 1 can function as a sliding surface with cylinder 2, so that the piston Graphite transfers to the cylinder and improves sliding and sealing properties. As a result, gas leakage occurring through the circumferential surface of the piston from the abutment portion 5a of the piston ring 5, which will be described later, and the like can be significantly reduced, and compression efficiency can be improved.
又、前記ピストン１の頂部側より順次リング溝１１、及
びピン孔１２が形成されている。Further, a ring groove 11 and a pin hole 12 are sequentially formed from the top side of the piston 1.
リング溝１１は極力ピストン頂部１３近傍にリング円状
に凹設し、該リング溝１１にＰＴＦＥ樹脂で作られたピ
ストンリング５を嵌装する。The ring groove 11 is recessed into a circular ring shape as close as possible to the piston top 13, and the piston ring 5 made of PTFE resin is fitted into the ring groove 11.
尚、本実施例においてはピストン自体にある程度のシー
ル効果を持たせているために、従来装置の様にピストン
リング５を２本設ける必要がなく、１本で所定のシール
効果を得る事が出来る。In addition, in this embodiment, since the piston itself has a certain degree of sealing effect, there is no need to provide two piston rings 5 as in the conventional device, and a predetermined sealing effect can be obtained with just one piston ring. .
前記ピン孔１２は前記ピストン１のほぼ中間位置に貫装
し、該ピン孔１２が直接軸受けとして機能するように研
磨加工を施す。The pin hole 12 is inserted through the piston 1 at a substantially intermediate position, and is polished so that the pin hole 12 directly functions as a bearing.
そして前記ピン孔１２にピストンピン７を装設させて連
接棒６を介してクランク軸の回転運動によりピストン１
の上下運動を行う。Then, the piston pin 7 is installed in the pin hole 12, and the piston 1 is moved by the rotational movement of the crankshaft via the connecting rod 6.
Perform up and down movements.
この場合ピストン１の上昇工程から下降工程若しくは下
降工程から上昇工程に移行時に衝撃を受け、従来の軸受
けを用いる構造では前記衝撃により軸受けの劣化等が生
じてしまうが、本発明においては、弾性力を有するピス
トン１自体を軸受けとして機能させたために、ピストン
１により前記衝撃を吸収し、耐久性の向上を図る事が出
来る。In this case, the piston 1 receives an impact when it transitions from the ascending process to the descending process or from the descending process to the ascending process, and in a structure using a conventional bearing, the impact causes deterioration of the bearing, but in the present invention, the elastic force Since the piston 1 itself functions as a bearing, the piston 1 can absorb the impact and improve durability.
そしてかかる実施例において前記無給油圧縮機に第３図
に示す従来のピストン１０１を用いたもの本実施例にか
かるピストン１を用いたもので（ピストン径５０ｍｍ）
７ｋｇｆ／ｃｍ２の連続負荷運転を行ない、負荷運転１
０００時間運転で夫々分解確認を行なったところ、従来
の圧縮機は１０００時間運転でピストン１のランド部で
かじり跡がみられ、又ピストンピン７部のピン孔１２に
嵌装した軸受けもベアリングが摩耗し負荷運転時の騒音
が大きくなっている事が確認された。一方本実施例のも
のは１０００時間経過してもピストン１の摺動面になじ
み跡がみられるがかじりは発生せず、又ピン孔１２部の
摩耗程度も微小であり、ピストンピン７部との間でガタ
が生じていない事が確認された。又温度の面でみるとピ
ストン部で２５℃の低減が見られた。In this embodiment, the conventional piston 101 shown in FIG. 3 is used in the oil-free compressor, and the piston 1 according to this embodiment is used (piston diameter: 50 mm).
Continuous load operation of 7 kgf/cm2 was performed, and load operation 1
When the conventional compressor was disassembled and confirmed after 1,000 hours of operation, it was found that there were scuff marks on the land of the piston 1 after 1,000 hours of operation, and the bearing fitted in the pin hole 12 of the piston pin 7 was also damaged. It was confirmed that the noise during load operation was increasing due to wear. On the other hand, in the case of this example, even after 1000 hours, there are traces of wear on the sliding surface of the piston 1, but no galling occurs, and the degree of wear on the pin hole 12 is minimal, and the piston pin 7 and It was confirmed that there was no play between the two. In terms of temperature, a 25°C reduction was observed in the piston section.
第４図は前記圧縮機に用いられる第２発明の実施例に係
るピストン１で、金属材で形成したピストン芯体１０Ａ
周囲に前記複合材１０Ｂを厚肉に一体成形してピストン
１０を形成したものである。FIG. 4 shows a piston 1 according to an embodiment of the second invention used in the compressor, with a piston core 10A formed of a metal material.
The piston 10 is formed by integrally molding the composite material 10B into a thick wall around the piston.
その具体的構成を簡単に説明すると、前記ピストン芯体
１０Ａはアルミ合金で形成され、その上面を平面状に形
成するとともに、内周面側に軸方向に沿ってフィン状突
起１４を設けている。To briefly explain its specific configuration, the piston core body 10A is made of aluminum alloy, has a planar upper surface, and has fin-like protrusions 14 provided along the axial direction on the inner peripheral surface side. .
そしてかかるピストン芯体１０Ａの外周囲とピストンピ
ン孔１２部位に前記複合材１０Ｂを厚肉に一体成形して
ピストン１０を形成する。Then, the piston 10 is formed by integrally molding the composite material 10B thickly around the outer periphery of the piston core 10A and at the piston pin hole 12 portion.
即ちピストン頂部１３とその背面側にピストン芯体１０
Ａを露出させた状態で、シリンダ２−と摺接するピスト
ン１０外周と前記ピン孔１２部位に前記複合材１０Ｂが
厚肉に囲繞させる。That is, the piston top 13 and the piston core 10 on the back side thereof.
With A exposed, the composite material 10B thickly surrounds the outer periphery of the piston 10 and the pin hole 12 portion that comes into sliding contact with the cylinder 2-.
尚前記複合材１０Ｂの肉厚は５０φのピストン１０の場
合、好ましくはピン孔１２部に１〜３ｍｍ、外周部に２
〜３ｍｍ前後の肉厚になるように設定するのがよい。In the case of a 50φ piston 10, the thickness of the composite material 10B is preferably 1 to 3 mm at the pin hole 12 portion and 2 mm at the outer circumference.
It is best to set the thickness to around 3 mm.
かかる実施例によれば前記第１実施例と同様な効果が得
られると共に、最も高温となるピストン頂部１３と内周
面側は熱伝導性のよいアルミ合金で形成されているため
に、ピストン頂部１３で発生した圧縮熱がピストン１０
内周面を通って放熱され高圧圧縮機の利用が可能となる
とともに、圧縮効率の向上が図れる。According to this embodiment, the same effects as in the first embodiment can be obtained, and since the piston top 13 and the inner circumferential surface side, which are at the highest temperature, are made of an aluminum alloy with good thermal conductivity, the piston top The compression heat generated in 13 is transferred to the piston 10.
Heat is radiated through the inner peripheral surface, making it possible to use a high-pressure compressor and improving compression efficiency.
例えばピストン１全体を複合材で形成した第２図に示す
実施例１と、本実施例のピストン１０についてその各部
の温度上昇を７ｋｇｆ／ｃｍ２で１Ｈ負荷運転した後に
ついて確認してみるに、実施例１のものはピストン１裏
面で１２５〜１３０℃の温度上昇があるのに対し本実施
例のものは８０〜９０℃と大幅低下がみられ、又ピスト
ンピン孔１２部位に付いても実施例１のものより１０℃
前後の温度低下がみられ、その分耐久性が向上する事が
推定できた。For example, in Example 1 shown in FIG. 2 in which the entire piston 1 is made of a composite material, and in the piston 10 of this example, we will check the temperature rise of each part after 1 hour of load operation at 7 kgf/cm2. In Example 1, there was a temperature rise of 125 to 130°C on the back surface of the piston 1, while in this example there was a significant decrease of 80 to 90°C. 10℃ than that of 1
A decrease in temperature before and after was observed, and it was assumed that the durability improved accordingly.
第５図は前記実施例の変形例を示し、ピストン２０の外
周部全てを前記耐熱性複合材２０Ｂで、該ピストンに囲
繞されるヘッド部２０Ａをアルミ合金で構成し、該ヘッ
ド部２０Ａ内周面側に、下方に垂下する多数の放熱フィ
ン２１を設けたピストン１が開示されており、かかる実
施例によれば前記実施例の効果に加えて、前記放熱フィ
ン２１によりピストン頂部１３の放熱がより大になり、
ピストン１冷却効果が一段と高められるとともに外周部
２１Ｂ全てが自己潤滑性耐熱複合材で形成されている為
に、シリンダ２との摺擦が完全に遮断される。FIG. 5 shows a modification of the above embodiment, in which the entire outer circumference of the piston 20 is made of the heat-resistant composite material 20B, the head portion 20A surrounded by the piston is made of aluminum alloy, and the inner circumference of the head portion 20A is made of the heat-resistant composite material 20B. A piston 1 is disclosed which is provided with a large number of heat radiation fins 21 hanging downward on the surface side. According to this embodiment, in addition to the effects of the above embodiment, the heat radiation from the piston top 13 is improved by the heat radiation fins 21. become bigger,
Since the piston 1 cooling effect is further enhanced and the entire outer circumferential portion 21B is made of a self-lubricating heat-resistant composite material, sliding friction with the cylinder 2 is completely blocked.
さて前記第２実施例においては圧縮熱を直接受熱するト
ップランド１４部１ｂにも樹脂系材料が存在するために
、該樹脂系材料が前記した高耐熱性のコプナ樹脂系複合
材を用いる以外にない。Now, in the second embodiment, since a resin material is also present in the top land 14 portion 1b which directly receives the compression heat, it is possible to do not have.
そこで第６図は前記欠点を解消するために、リング溝１
１部の上側のトップランド１４とピストン頂部１３を所
定肉厚で形成したアルミ材からなるピストンヘッド３０
Ａと、該ヘッド３０Ａと一体成形で形成した自己潤滑性
耐熱材からなるピストン本体３０Ｂからなる。Therefore, Fig. 6 shows a ring groove 1 in order to eliminate the above-mentioned drawback.
A piston head 30 made of aluminum with a top land 14 on the upper side of the first part and a piston top 13 formed with a predetermined thickness.
A, and a piston body 30B made of a self-lubricating heat-resistant material integrally formed with the head 30A.
リング溝１１部の上側のトップランド１４とピストン頂
部１３を所定肉厚でを含むヘッド２０Ａ側をアルミ材で
形成し、その下方のリング溝１１を含むピストン本体３
０Ｂを一体的に成型したものである。The head 20A side including the top land 14 above the ring groove 11 and the piston top 13 with a predetermined thickness is formed of aluminum material, and the piston body 3 includes the ring groove 11 below.
0B is integrally molded.
そしてヘッド３０Ａはトップランド１４部１ｂの外径を
、その下方のピストン本体３０Ｂ径より僅かに小に設定
するとともに、その下端側３１を断面鍵形状に内側に折
曲し、ピストン本体３０Ｂとの組付けの容易化を図って
いる。The head 30A has the outer diameter of the top land 14 portion 1b set to be slightly smaller than the diameter of the piston body 30B below it, and its lower end side 31 is bent inward to have a key-shaped cross section, so that it is connected to the piston body 30B. Efforts are made to make assembly easier.
ピストン本体３０Ｂは前記実施例と同様にＳＫレジンに
黒鉛を４０％混合した成型材料を用い、該成型材料を用
いて前もって成型硬化した前記ヘッド３０Ａと一体的に
鋳込み成形を行う事により形成してもよいが、ピストン
頂部１３側の熱が直接樹脂体に接触しないために、ピス
トンリング５と同様なＰＴＦＥ樹脂若しくはその複合材
を用いる事が可能である。The piston body 30B is formed by using a molding material of SK resin mixed with 40% graphite in the same way as in the previous embodiment, and integrally casting with the head 30A which has been previously molded and hardened using the molding material. However, since the heat on the piston top 13 side does not directly contact the resin body, it is possible to use a PTFE resin similar to the piston ring 5 or a composite material thereof.
又かかる実施例によれば、ピストン頂部１３とともに圧
縮熱が最も伝達し易いトップランド１４まで良熱伝導性
のヘッド３０Ａで形成されている為に放熱効果が一層向
上するとともに、ピストン本体側に前記材料を用いたが
故に耐熱温度が３００℃以上と熱変形の少ない良好なピ
ストン１の形成が可能となる。Further, according to this embodiment, since the head 30A is formed with good thermal conductivity up to the piston top 13 and the top land 14 where compression heat is most easily transferred, the heat dissipation effect is further improved. Since the material is used, it is possible to form a good piston 1 with a heat resistance temperature of 300° C. or higher and less thermal deformation.
第７図はリベットによる結合手段を用いた他の実施例で
ピストン本体４０Ｂとヘッド４０Ａを夫々個別に形成し
た後、両者間をリベット２５で一体的に固定させている
。FIG. 7 shows another embodiment using a rivet coupling means, in which a piston body 40B and a head 40A are formed separately, and then they are integrally fixed with a rivet 25.
即ち前記ヘッド４０Ａは、前記ピストン１をリング溝１
１上面側より水平に切断した形状を有する円板板状をな
し、その直径を下方に位置する自己潤滑性樹脂材料から
なるピストン本体４０Ｂの直径より僅かに小に形成して
いる、そして該ヘッド４０Ａとピストン本体４０Ｂ間は
、第７図（ｂ）（ｃ）に示すように、良熱伝導性の４本
のリベット４１で一体的に固定しつつ該リベット端４１
ａがピストン頂部１３の裏面側まで延設するように構成
する。これによりヘッド４０Ａ側に伝熱した圧縮熱がリ
ベット４１を介してピストン１下方に放熱させたり、又
ピストン本体４０Ｂ全体へ拡散させる事が可能になり、
ヘッド４０Ａを薄肉化させた場合の熱かかる実施例にお
いては前記実施例と同様な効果を得る事が出来ると共に
、前記ヘッド４０Ａと本体間を良熱伝導性のリベット２
５で固定しつつ該リベット端４１ａがピストン頂部１３
の裏面側まで延設するように構成する。これによりヘッ
ド４０Ａ側に伝熱した圧縮熱がリベット４１を介してピ
ストン１下方に放熱させたり、又ピストン本体４０Ｂ全
体へ拡散させる事が可能になり、ヘッド４０Ａを薄肉化
させた場合の熱的不具合を解消出来る。That is, the head 40A holds the piston 1 in the ring groove 1.
1. It has a disk shape cut horizontally from the upper surface side, and its diameter is slightly smaller than the diameter of the piston body 40B made of a self-lubricating resin material located below, and the head 40A and the piston body 40B, as shown in FIGS. 7(b) and 7(c), are integrally fixed with four rivets 41 with good thermal conductivity, and the rivet ends 41
a extends to the back side of the piston top 13. As a result, the compression heat transferred to the head 40A side can be radiated downward through the piston 1 via the rivet 41, or can be diffused to the entire piston body 40B.
In an embodiment where the head 40A is made thinner and requires heat, the same effect as the above embodiment can be obtained, and a rivet 2 with good thermal conductivity is connected between the head 40A and the main body.
5, the rivet end 41a is attached to the piston top 13.
It is configured to extend to the back side of the. As a result, the compression heat transferred to the head 40A side can be dissipated to the lower part of the piston 1 via the rivet 41, or can be diffused to the entire piston body 40B. Problems can be resolved.
第８図及び第９図は、第３発明が適用される単段式無給
油往復圧縮機の要部構成を示す。FIG. 8 and FIG. 9 show the main part configuration of a single-stage oilless reciprocating compressor to which the third invention is applied.
ピストン５０は前記第１実施例と同様にＣＯＰＮＡ樹脂
）を樹脂骨格に特つコンパウンド化した粒状レジンに黒
鉛を４０％混合した成型材料を一体成形して形成され、
第９図に示すようにその外周面上に、ピストンリング溝
５１と、ピストンピン挿入用のピン孔１２が削成若しく
は穿設されている。As in the first embodiment, the piston 50 is formed by integrally molding a molding material made by mixing 40% graphite with a compounded granular resin having a resin skeleton (COPNA resin), as in the first embodiment.
As shown in FIG. 9, a piston ring groove 51 and a pin hole 12 for inserting a piston pin are cut or bored on the outer peripheral surface thereof.
そして前記リング溝５１はその断面形状を上下端部及び
側端部を面取りする事なく断面コの字状をなし、そして
そのリング形状をピストン１の全周面に対し円周状に形
成するのではなくＣの字状に形成し、そのリング溝５１
が形成されない部位（離間部位５２）がピン孔１２挿設
方向に対し直交する一の線上に位置するように作成する
。The ring groove 51 has a U-shaped cross section without chamfering the upper and lower ends and side ends, and the ring groove 51 is formed in a circular shape around the entire circumferential surface of the piston 1. The ring groove 51 is formed in a C-shape instead of a
The pin hole 12 is formed so that the portion where the pin hole 12 is not formed (separated portion 52) is located on a line perpendicular to the direction in which the pin hole 12 is inserted.
言い換えればピストン１全周面全てが前記リング溝５１
により分断される事なく前記一の直交線上においてのみ
軸方向に連続する様に前記リング溝５１の位置設定を行
っている。In other words, the entire circumferential surface of the piston 1 is covered by the ring groove 51.
The position of the ring groove 51 is set so that it is continuous in the axial direction only on the one orthogonal line without being separated by.
一方ピストンリング５は公知の様にＰＴＦＥ樹脂でで形
成すると共に、その断面形状をリング溝５１に合わせて
上下端部及び側端部を面取りする事なく断面矩形状をな
し、そしてその平面形状は該リング５を前記リング溝５
１に嵌合／圧縮変形させた際に前記リング溝５１と同形
になるように且つ、その端部の合い口５ａを前記リング
溝５１の終端にきっちり密着するように形成する。On the other hand, the piston ring 5 is made of PTFE resin as is well known, and has a rectangular cross-sectional shape without chamfering the upper and lower ends and side ends to match the ring groove 51, and its planar shape is The ring 5 is inserted into the ring groove 5.
1, so that it has the same shape as the ring groove 51 when it is fitted/compressed and deformed, and the abutment 5a at the end thereof is formed in such a way that it tightly contacts the terminal end of the ring groove 51.
そして前記ピストン１にピストンリング５を嵌合させた
後、前記離間部位５２が、圧縮工程（上昇工程）時にシ
リンダ２と密接するサイドスラスト部Ｓ１−Ｓ’１に位
置する様にシリンダ２内にピストン５０を組み込む。After fitting the piston ring 5 to the piston 1, the piston ring 5 is inserted into the cylinder 2 so that the separated portion 52 is located at the side thrust portion S1-S'1 that comes into close contact with the cylinder 2 during the compression process (ascending process). Incorporate the piston 50.
かかる実施例によれば、ピストンの離間部位５２が、圧
縮工程時にシリンダ２と密接するサイドスラスト部２０
に位置している為に、サイドスラスト部２０は前記離間
部位５２を含むピストン５０周面自体で封止され、そし
てピストンリング５は周方向に移動する事なく、該離間
部位５２でその合いロ部５０が位置保持されている為に
、該離間部５２を接点とする内接円がピストン５０とピ
ストンリング５との間で形成出来る。According to this embodiment, the separated portion 52 of the piston is located at the side thrust portion 20 that comes into close contact with the cylinder 2 during the compression process.
Since the side thrust portion 20 is located at the spaced apart portion 52, the side thrust portion 20 is sealed by the circumferential surface of the piston 50 itself, including the separated portion 52, and the piston ring 5 does not move in the circumferential direction, and its mating portion is closed at the separated portion 52. Since the portion 50 is held in position, an inscribed circle can be formed between the piston 50 and the piston ring 5 with the separation portion 52 as a contact point.
この結果、前記サイドスラスト部Ｓ１−Ｓ’１以外の部
位では、ピストン５０とシリンダ２間は離間しているが
、その部分では前記ピストンリング５がシリンダ２周面
に内接しているために、該リング溝５１の離間部位５２
とピストンリングの組合せにおいてシリンダ２全周に亙
ってシールされる円状になり、該シール円を利用して前
記シリンダ２を気密的にシール可能に構成する事が出来
る。As a result, although the piston 50 and the cylinder 2 are apart from each other in areas other than the side thrust portion S1-S'1, since the piston ring 5 is inscribed in the circumferential surface of the cylinder 2 in that area, Separated portion 52 of the ring groove 51
The combination of the piston ring and the piston ring form a circular shape that is sealed over the entire circumference of the cylinder 2, and the cylinder 2 can be configured to be airtightly sealed using this sealing circle.
第１０図は本第３発明を無給油式単段往復膨張機に適用
した他の実施例で、前記圧縮機の場合は、ピストン５０
上面側に圧縮空気を受圧する為にクランク軸７の回転方
向が左回りの場合は左側にサイドスラスト部Ｓ１−Ｓ’
１が存在するが、膨張機の場合は前記圧縮機と異なり、
膨張工程はピストン下降工程時に存在する為に、クラン
ク軸７の回転方向と逆側、即ち回転方向が左回りの場合
は右側にサイドスラスト部Ｓ１−Ｓ’１が存在する事と
なり、この結果膨張機の場合は前記離間部位５２を前記
圧縮機と逆側のピストン周面上に形成する。FIG. 10 shows another embodiment in which the third invention is applied to an oil-free single-stage reciprocating expander.
When the rotation direction of the crankshaft 7 is counterclockwise in order to receive compressed air on the upper surface side, the side thrust part S1-S' is on the left side.
1 exists, but in the case of an expander, unlike the compressor,
Since the expansion process exists during the piston lowering process, the side thrust portion S1-S'1 exists on the opposite side to the rotation direction of the crankshaft 7, that is, on the right side when the rotation direction is counterclockwise, and as a result, the expansion In the case of a compressor, the separation portion 52 is formed on the circumferential surface of the piston on the opposite side from the compressor.
尚前記膨張機の場合は耐熱性を考慮する必要がないため
にピストン本体の成型材料はＣＯＰＮＡ樹脂若しくはそ
の複合材のみに限定される事なく、ポリテトラフルオロ
エチレン（ＰＴＦＥ）系樹脂若しくはその複合材で形成
する事も可能である。In the case of the above-mentioned expander, there is no need to consider heat resistance, so the molding material for the piston body is not limited to COPNA resin or its composite material, but may also be polytetrafluoroethylene (PTFE) resin or its composite material. It is also possible to form a
第１１図は本発明を無給油式二段往復圧縮機に適用した
他の実施例で、二段圧縮機の場合は吸込工程時において
も低圧側で圧縮された空気圧が高圧側ピストンにかかり
、この結果吸込工程におけるサイドスラスト部Ｓ１−Ｓ
’１は圧縮工程におけるサイドスラスト部Ｓ１−Ｓ’１
と１８０゜隔てた逆側に位置する事になる。FIG. 11 shows another embodiment in which the present invention is applied to an oil-free two-stage reciprocating compressor. In the case of a two-stage compressor, air pressure compressed on the low pressure side is applied to the high pressure side piston even during the suction process. As a result, the side thrust part S1-S in the suction process
'1 is the side thrust part S1-S'1 in the compression process
It will be located on the opposite side, separated by 180 degrees.
従って高圧側にピストン５０Ａ／シリンダ２Ａ間には吸
込工程でも圧縮工程でも何れの場合でも気密シールを図
る必要があり、この為本実施例においては前記リング溝
５１Ａ、５１Ｂを上下に二本設けると共に、該リング溝
５１Ａ、５１Ｂを１８０゜対称に削成し、夫々前記実施
例と同様に形成したピストンリング５Ａ、５Ｂを嵌合さ
せる。Therefore, it is necessary to provide an airtight seal between the piston 50A and the cylinder 2A on the high pressure side in both the suction process and the compression process.For this reason, in this embodiment, two ring grooves 51A and 51B are provided above and below, and The ring grooves 51A and 51B are cut 180 degrees symmetrically, and piston rings 5A and 5B formed in the same manner as in the previous embodiment are fitted therein.
この結果、例えば高段側の吸込工程時（第１１図Ａ参照
）ではトップリング５Ａ側のサイドスラスト部５３Ａが
シールされ、高段側の圧縮工程時（第１１図Ｂ参照）に
はセカンドリング５Ｂ側のサイドスラスト部５３Ｂがシ
ールされる事となり、結果として吸込工程と圧縮工程の
何れの工程でも確実なシールが可能となる。As a result, for example, during the suction process on the high stage side (see Figure 11A), the side thrust part 53A on the top ring 5A side is sealed, and during the compression process on the high stage side (see Figure 11B), the side thrust part 53A is sealed. The side thrust portion 53B on the 5B side is sealed, and as a result, reliable sealing is possible in both the suction process and the compression process.
「発明の効果」
以上記載した如く本第１発明によれば、熱硬化性縮合多
環多核芳香族を用いることによって、従来工業用の圧縮
機において不可能であった全樹脂製の、もしくは摺動部
全体を樹脂としたピストンを用いた圧縮機が可能となり
、ピストンの軽量化による前述の如き効果、素材による
摺動面の形成による構造の単純化に加えピストンの耐久
性が大きく向上するとともに長期の使用によって摩耗が
進行しても、致命的な欠陥が生ずること無く長期間ノー
メンテナンスが可能となり、かじりや圧縮効率（膨張効
率）が低下する事のない無給油式往復圧縮機／膨張機を
提供する事出来る。"Effects of the Invention" As described above, according to the first invention, by using a thermosetting condensed polycyclic polynuclear aromatic, all-resin or sliding It has become possible to create a compressor using a piston whose entire moving part is made of resin, which has the above-mentioned effect of reducing the weight of the piston, simplifies the structure by forming the sliding surface with material, and greatly improves the durability of the piston. An oil-free reciprocating compressor/expander that does not cause fatal defects even if wear progresses over long-term use, and allows long-term maintenance-free operation without galling or reducing compression efficiency (expansion efficiency). We can provide the following.
また、本第２発明によれば、シリンダとの円滑な摺動機
能と、吐出／吸込弁と対面する頂部、言い変えれば圧縮
熱と接触するピストン頂部側の耐熱機能を分離し、外周
部の内少なくともシリンダと摺擦される部位を自己潤滑
性耐熱材料で、又ピストン頂部をアルミ等の前記耐熱材
料より熱伝導性の高い良熱伝導性材料で夫々形成した為
に、かじりや圧縮効率が低下する事がなく而も高い圧縮
熱がピストン頂部と接触する場合でもピストン頂部を吸
気時の冷気で冷却が繰り返されるためピストン頂部の温
度を低減出来、よって摺動面となるピストン外周及びピ
ストン孔への温度伝播による温度上昇を押えることでピ
ストンの変形や劣化等が生じる事のない無給油式往復圧
縮機を提供するのない無給油式往復圧縮機を提供する事
が出来る。Further, according to the second invention, the smooth sliding function with the cylinder and the heat resistance function of the top part facing the discharge/suction valve, in other words, the top part of the piston that comes into contact with the compression heat, are separated, and the outer peripheral part At least the part that rubs against the cylinder is made of a self-lubricating heat-resistant material, and the top of the piston is made of a material with good thermal conductivity that is higher in heat conductivity than the heat-resistant material, such as aluminum, which reduces galling and compression efficiency. Even when the high compression heat does not drop and comes into contact with the top of the piston, the top of the piston is repeatedly cooled by cold air during intake, so the temperature of the top of the piston can be reduced. It is possible to provide an oil-free reciprocating compressor that does not cause piston deformation or deterioration by suppressing temperature rise due to temperature propagation.
更に、本第３発明によれば、従来の無給油式流体機械に
比較してピストンリング合い口よりのガス洩れを完全に
封止し、而も前記ピストンリングの廻り止めとして機能
する離間部位はピストン自体に一体に形成されているた
めに、構成が極めて簡単且つ永続的に劣化が生じないの
みならず、長年使用により却ってなじみ性が出、長期に
亙って高圧縮効率を維持し得る。Furthermore, according to the third invention, gas leakage from the piston ring joint is completely sealed compared to conventional oil-free fluid machines, and the separated portion that functions as a rotation stopper for the piston ring is Since it is formed integrally with the piston itself, it is not only extremely simple in construction and permanently free from deterioration, but also becomes more compatible with long-term use and can maintain high compression efficiency over a long period of time.
等の種々の著効を有す。It has various effects such as
第１図は本発明が適用される無給油往復圧縮機を示す断
面図、第２図は第１発明の実施例に係る無給油式往復圧
縮機の要部構成を示す断面図、第３図は従来技術の無給
油式往復圧縮機の要部構成を示す断面図、第４図、第５
図及び第６図はいずれも第２発明の夫々の実施例に係る
ピストンを示す断面図である。
第７図は他の実施例に係るピストンを示し（ａ）は半断
面図、（ｂ）は底面図、（ｃ）は（ｂ）のＡ−Ａ’線断
面図である。
第８図は第３発明を無給油式単板往復圧縮機に適用した
一の実施例を示す正面断面図とそのＡ−Ａ’線断面図、
第９図はそのピストン周面形状を示す要部斜視図、第１
０図は第３発明を無給油式単段往復膨張機に適用した他
の実施例を示す概略図とそのＢ−Ｂ’線断面図である。
第１１図は本発明を無給油式二段往復圧縮機に適用した
他の実施例を示す概略図で（Ａ）は高段側の吸込工程を
、（Ｂ）は高段側の圧縮工程にある場合にピストンとシ
リンダ間の摺接状況を示す。
特許出願人：岩田塗装機工業株式会社
代理人：弁理士 高橋昌久FIG. 1 is a cross-sectional view showing an oil-free reciprocating compressor to which the present invention is applied, FIG. 2 is a cross-sectional view showing the main structure of an oil-free reciprocating compressor according to an embodiment of the first invention, and FIG. 4 and 5 are cross-sectional views showing the main parts of a conventional oil-free reciprocating compressor.
Both FIG. 6 and FIG. 6 are sectional views showing pistons according to respective embodiments of the second invention. FIG. 7 shows a piston according to another embodiment; (a) is a half sectional view, (b) is a bottom view, and (c) is a sectional view taken along the line AA' in (b). FIG. 8 is a front cross-sectional view showing an embodiment in which the third invention is applied to an oil-free single-plate reciprocating compressor, and a cross-sectional view taken along line A-A'thereof;
Figure 9 is a perspective view of the main parts showing the shape of the piston's circumferential surface;
FIG. 0 is a schematic view showing another embodiment in which the third invention is applied to an oil-free single-stage reciprocating expander, and a sectional view thereof taken along the line BB'. FIG. 11 is a schematic diagram showing another embodiment in which the present invention is applied to an oil-free two-stage reciprocating compressor, in which (A) shows the suction process on the high stage side, and (B) shows the compression process on the high stage side. In some cases, the sliding contact situation between the piston and cylinder is shown. Patent applicant: Iwata Painting Machine Industry Co., Ltd. Agent: Patent attorney Masahisa Takahashi
Claims (13)
が 嵌合されたピストン体と金属製のシリンダからなる無給
油式往復圧縮機／膨張機において、前記ピストンを熱硬
化性縮合多環多核芳香族樹脂と、黒鉛その他の摺動性を
高める耐熱材料とを含む自己潤滑性複合材で形成した事
を特徴とする無給油往復圧縮機／膨張機1. An oil-free reciprocating compressor/expander comprising a piston body fitted with a piston ring made of a self-lubricating material and a metal cylinder, wherein the piston is made of a thermosetting condensed polycyclic polynuclear aromatic material. An oil-free reciprocating compressor/expander characterized by being made of a self-lubricating composite material containing a group resin and graphite or other heat-resistant material that improves sliding properties.
、 軸受けを介する事なくピストンピンを直接軸支させた請
求項１）記載の無給油往復圧縮機／膨張機2. The oil-free reciprocating compressor/expander according to claim 1, wherein the piston pin is directly supported in a pin hole penetrated through the body of the piston body without using a bearing.
少なくともピストン頂部附近におけるピスト ン／シリンダ間のクリアランスをピストン直径に対し常
温で０．１〜０．５％の範囲に設定した請求項１）記載
の無給油往復圧縮機／膨張機[Claim 3]
The oil-free reciprocating compressor/expander according to claim 1), wherein the clearance between the piston and the cylinder at least near the top of the piston is set in the range of 0.1 to 0.5% of the piston diameter at room temperature.
小 に形成した請求項１）記載の無給油往復圧縮機／膨張機4. The oil-free reciprocating compressor/expander according to claim 1, wherein the diameter of the upper part of the piston is smaller than the diameter of the lower part.
が 嵌合されたピストン体と金属製のシリンダからなる無給
油式往復圧縮機／膨張機において、前記ピストン外周部
の内少なくともシリンダと摺擦される部位とピストンピ
ン孔部を自己潤滑性耐熱材料で、又ピストン頂部を良熱
伝導性材料で夫々形成した事を特徴とする無給油式往復
圧縮機／膨張機5. An oil-free reciprocating compressor/expander comprising a piston body fitted with a piston ring made of a self-lubricating material and a metal cylinder, wherein the piston has an outer peripheral portion that slides at least with the cylinder. An oil-free reciprocating compressor/expander characterized in that the piston pin hole and the piston pin hole are made of a self-lubricating heat-resistant material, and the piston top is made of a good heat conductive material.
のピストンリング 上方のトップランド部を良熱伝導材料で形成するととも
に、該トップランド部の外径を、その下方のピストン径
より僅かに小に設定した事を特徴とする請求項５）記載
の無給油式往復圧縮機／膨張機6. A top land portion above the first piston ring together with the top of the piston is formed of a material with good thermal conductivity, and the outer diameter of the top land portion is set to be slightly smaller than the diameter of the piston below the top land portion. The oil-free reciprocating compressor/expander according to claim 5), characterized in that
材料で形成したピストン芯体周囲 に、熱硬化性縮合多環多核芳香族樹脂と、黒鉛その他の
摺動性を高める耐熱材料とを含む自己潤滑性複合材を一
体成形してピストンを形成した事を特徴とする請求項５
）記載の無給油式往復圧縮機／膨張機Claim 7: A self-lubricating composite material containing a thermosetting condensed polycyclic polynuclear aromatic resin and a heat-resistant material such as graphite that improves sliding properties is placed around the piston core made of a material with good thermal conductivity. Claim 5 characterized in that the piston is formed by integral molding.
) Oil-free reciprocating compressor/expander described in )
体 の、ピストン頂部側に良熱伝導体を配し、両者間を任意
の固定手段を用いて一体化した事を特徴とする請求項５
）記載の無給油式往復圧縮機／膨張機8. Claim 5, characterized in that the piston body is made of a self-lubricating heat-resistant material, and a good heat conductor is disposed on the top side of the piston, and the two are integrated using any fixing means.
) Oil-free reciprocating compressor/expander described in )
頂部側の良熱伝導体を実質的にピストン 頂部の裏面側まで延設した請求項５）記載の無給油式往
復圧縮機／膨張機9. The oil-free reciprocating compressor/expander according to claim 5, wherein the good heat conductor on the top side extends substantially to the back side of the top of the piston.
グが嵌合されたピストンを含む無給油式単段往復圧縮機
において、少なくともピストン又は／及びシリンダの摺
動面を自己潤滑性材料で形成するとともに、該ピストン
の周面上に形成されるリング溝を、その両端間が小間隔
で離間するＣの字状に形成し、該離間部位が、圧縮工程
時にシリンダと密接するサイドスラスト部に位置する様
にピストンを組み込み、該離間部位とピストンリングの
組合せにおいて、前記シリンダを気密的にシール可能に
構成したことを特徴とする無給油式単段往復圧縮機10. An oil-free single-stage reciprocating compressor including a piston fitted with a piston ring made of a self-lubricating material, wherein at least the sliding surface of the piston and/or the cylinder is made of a self-lubricating material. In addition, a ring groove formed on the circumferential surface of the piston is formed in a C-shape in which both ends thereof are spaced apart at a small distance, and the spaced apart portion is located at a side thrust portion that comes into close contact with the cylinder during the compression process. An oil-free single-stage reciprocating compressor, characterized in that a piston is incorporated in the compressor, and the cylinder is configured to be airtightly sealed in combination with the separated portion and the piston ring.
グが嵌合されたピストンを含む無給油式単段往復膨張機
において、少なくともピストン又は／及びシリンダの摺
動面を自己潤滑性材料で形成するとともに、該ピストン
の周面上に形成されるリング溝を、その両端間が小間隔
で離間するＣの字状に形成し、該離間部位が、膨張工程
時にシリンダと密接するサイドスラスト部に位置する様
にピストンを組み込み、該離間部位とピストンリングの
組合せにおいて、対応するシリンダを気密的にシール可
能にしたことを特徴とする無給油式単板往復圧縮機11. An oil-free single-stage reciprocating expander including a piston fitted with a piston ring made of a self-lubricating material, wherein at least the sliding surface of the piston and/or cylinder is made of a self-lubricating material. In addition, a ring groove formed on the circumferential surface of the piston is formed in a C-shape in which both ends thereof are spaced apart at a small distance, and the spaced apart portion is located at a side thrust portion that comes into close contact with the cylinder during the expansion process. An oil-free single-plate reciprocating compressor, characterized in that a piston is incorporated in such a way that the piston ring is combined with the piston ring, and the corresponding cylinder can be airtightly sealed.
材料で形成したピストンリングが嵌合されたピストンを
含む無給油式多段往復圧縮機において、少なくとも低段
側も高段側もピストン又は／及びシリンダの摺動面を自
己潤滑性材料で形成するとともに、該ピストンの周面上
に形成されるリング溝を、その両端間が小間隔で離間す
るＣの字状に形成し、低段側においてはピストン上昇工
程時のシリンダと密接するサイドスラスト部に、又高段
側においてはピストン上昇工程と下降工程の両サイドス
ラスト部に、夫々前記離間部位が位置するようにピスト
ンを組み込み、該離間部位とピストンリングの組合せに
おいて、対応する各シリンダを気密的にシール可能にし
たことを特徴とする無給油式多段往復圧縮機12. An oil-free multi-stage reciprocating compressor including a piston in which a piston ring formed of a self-lubricating material is fitted on both the low stage side and the high stage side, wherein at least the low stage side and the high stage side are fitted with a piston ring formed of a self-lubricating material. In addition, the sliding surface of the piston and/or cylinder is formed of a self-lubricating material, and the ring groove formed on the circumferential surface of the piston is formed in a C-shape with both ends spaced apart at a small interval. , the piston is arranged so that the separated portions are located at the side thrust part in close contact with the cylinder during the piston rising stroke on the low stage side, and at both side thrust parts during the piston raising stroke and the lowering stroke on the high stage side. An oil-free multi-stage reciprocating compressor characterized in that each corresponding cylinder can be airtightly sealed in the combination of the separated part and the piston ring.
グが嵌合されたピストンを含む無給油式往復圧縮機／膨
張機において、ピストン周面の少なくともシリンダと摺
動する部位を自己潤滑性材料で形成すると共に、該ピス
トンの周面上に形成されたリング溝を、その両端間が小
間隔で離間するＣの字状に形成した事を特徴とする無給
油式往復圧縮機／膨張機Claim 13: In an oil-free reciprocating compressor/expander including a piston fitted with a piston ring formed of a self-lubricating material, at least a portion of the circumferential surface of the piston that slides with the cylinder is made of a self-lubricating material. An oil-free reciprocating compressor/expander characterized in that a ring groove formed on the circumferential surface of the piston is formed in a C-shape with a small distance between both ends of the ring groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2108837A JPH089985B2 (en) | 1989-04-28 | 1990-04-26 | Oil-free reciprocating compressor and expander |
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11027689 | 1989-04-28 | ||
| JP15823689 | 1989-06-22 | ||
| JP1-110276 | 1990-03-31 | ||
| JP8291790 | 1990-03-31 | ||
| JP2-82917 | 1990-03-31 | ||
| JP1-158236 | 1990-03-31 | ||
| JP2108837A JPH089985B2 (en) | 1989-04-28 | 1990-04-26 | Oil-free reciprocating compressor and expander |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04214970A true JPH04214970A (en) | 1992-08-05 |
| JPH089985B2 JPH089985B2 (en) | 1996-01-31 |
Family
ID=27466758
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2108837A Expired - Lifetime JPH089985B2 (en) | 1989-04-28 | 1990-04-26 | Oil-free reciprocating compressor and expander |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH089985B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0771545A (en) * | 1993-09-06 | 1995-03-17 | Ntn Corp | Belt tension adjusting device |
| WO1995018345A1 (en) * | 1993-12-30 | 1995-07-06 | Institut Français Du Petrole | Method and apparatus for liquefying natural gas |
| WO2003085263A1 (en) * | 2002-04-08 | 2003-10-16 | Kmc Ltd. | Piston pump |
| JP2005133696A (en) * | 2003-10-31 | 2005-05-26 | Anest Iwata Corp | Oilless reciprocating fluid machine |
| WO2006032463A1 (en) * | 2004-09-24 | 2006-03-30 | Linde Aktiengesellschaft | Method for compressing a gaseous medium and piston compressor |
| JP2008064115A (en) * | 1997-09-24 | 2008-03-21 | Hitachi Ltd | Reciprocating type compressor |
| WO2023176040A1 (en) * | 2022-03-15 | 2023-09-21 | 株式会社日立産機システム | Compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5052948B2 (en) | 2007-04-26 | 2012-10-17 | アネスト岩田株式会社 | Piston ring and fluid suction / discharge device using the piston ring |
| KR101414159B1 (en) * | 2012-08-14 | 2014-07-01 | 한국표준과학연구원 | A smallscale mechanical compressor for onebatch gas compression, analysis system and analysis method including the compressor |
| CN103591002A (en) * | 2012-08-16 | 2014-02-19 | 句容市康顺铜业有限公司 | Full oilless air compressor compression high temperature blocking method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54152734A (en) * | 1978-05-24 | 1979-12-01 | Nippon Kokuen Kogyo Kk | Oilless bearing |
-
1990
- 1990-04-26 JP JP2108837A patent/JPH089985B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54152734A (en) * | 1978-05-24 | 1979-12-01 | Nippon Kokuen Kogyo Kk | Oilless bearing |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0771545A (en) * | 1993-09-06 | 1995-03-17 | Ntn Corp | Belt tension adjusting device |
| WO1995018345A1 (en) * | 1993-12-30 | 1995-07-06 | Institut Français Du Petrole | Method and apparatus for liquefying natural gas |
| FR2714722A1 (en) * | 1993-12-30 | 1995-07-07 | Inst Francais Du Petrole | Method and apparatus for liquefying a natural gas |
| JP2008064115A (en) * | 1997-09-24 | 2008-03-21 | Hitachi Ltd | Reciprocating type compressor |
| WO2003085263A1 (en) * | 2002-04-08 | 2003-10-16 | Kmc Ltd. | Piston pump |
| CN100458157C (en) * | 2002-04-08 | 2009-02-04 | 日本罗斯马克斯医药株式会社 | Piston pump |
| US7766631B2 (en) | 2002-04-08 | 2010-08-03 | KMC Litd. | Piston pump |
| JP2005133696A (en) * | 2003-10-31 | 2005-05-26 | Anest Iwata Corp | Oilless reciprocating fluid machine |
| JP4615845B2 (en) * | 2003-10-31 | 2011-01-19 | アネスト岩田株式会社 | Oil-free reciprocating fluid machine |
| WO2006032463A1 (en) * | 2004-09-24 | 2006-03-30 | Linde Aktiengesellschaft | Method for compressing a gaseous medium and piston compressor |
| WO2023176040A1 (en) * | 2022-03-15 | 2023-09-21 | 株式会社日立産機システム | Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH089985B2 (en) | 1996-01-31 |
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