JPS63198785A - Valve gear for gas compressor - Google Patents
Valve gear for gas compressorInfo
- Publication number
- JPS63198785A JPS63198785A JP62291655A JP29165587A JPS63198785A JP S63198785 A JPS63198785 A JP S63198785A JP 62291655 A JP62291655 A JP 62291655A JP 29165587 A JP29165587 A JP 29165587A JP S63198785 A JPS63198785 A JP S63198785A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- discharge valve
- discharge
- valve seat
- angle
- 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
- 230000006835 compression Effects 0.000 claims description 42
- 238000007906 compression Methods 0.000 claims description 41
- 230000002093 peripheral effect Effects 0.000 claims description 28
- 239000000463 material Substances 0.000 claims description 17
- 238000005192 partition Methods 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 15
- 238000004537 pulping Methods 0.000 description 10
- 230000009471 action Effects 0.000 description 8
- 239000012530 fluid Substances 0.000 description 8
- 230000000694 effects Effects 0.000 description 6
- 230000007246 mechanism Effects 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 210000005069 ears Anatomy 0.000 description 4
- 239000011347 resin Substances 0.000 description 4
- 229920005989 resin Polymers 0.000 description 4
- 229920003223 poly(pyromellitimide-1,4-diphenyl ether) Polymers 0.000 description 3
- 229920001721 polyimide Polymers 0.000 description 3
- 230000002829 reductive effect Effects 0.000 description 3
- 239000004962 Polyamide-imide Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 239000004760 aramid Substances 0.000 description 2
- 229920003235 aromatic polyamide Polymers 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 229920002312 polyamide-imide Polymers 0.000 description 2
- 229920000728 polyester Polymers 0.000 description 2
- 239000009719 polyimide resin Substances 0.000 description 2
- 229920000642 polymer Polymers 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000002441 reversible effect Effects 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- 239000004642 Polyimide Substances 0.000 description 1
- 239000004734 Polyphenylene sulfide Substances 0.000 description 1
- 229920013632 Ryton Polymers 0.000 description 1
- 239000004736 Ryton® Substances 0.000 description 1
- UCKMPCXJQFINFW-UHFFFAOYSA-N Sulphide Chemical compound [S-2] UCKMPCXJQFINFW-UHFFFAOYSA-N 0.000 description 1
- 239000004963 Torlon Substances 0.000 description 1
- 229920003997 Torlon® Polymers 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000000748 compression moulding Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000003365 glass fiber Substances 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 235000013372 meat Nutrition 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 229920000069 polyphenylene sulfide Polymers 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 208000024891 symptom Diseases 0.000 description 1
- 229920001169 thermoplastic Polymers 0.000 description 1
- 239000004416 thermosoftening plastic Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Check Valves (AREA)
- Lift Valve (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
退Ｊ」」Ｌ
この発明は、圧力応動バルブ装置、より詳しく言うと冷
凍用圧縮機のような往復動ピストン型圧縮機において用
いるのに好適したパルプ装置に、関するものである。DETAILED DESCRIPTION OF THE INVENTION This invention relates to a pressure-responsive valve device, and more particularly to a pulp device suitable for use in a reciprocating piston type compressor, such as a refrigeration compressor. It is.
従来の技術
往復動ピストン型圧縮機は典型的に、シリンダ端におい
てヘッドとシリンダハウジング間で支持して、圧力応動
型の吸入及び吐出弁機構を設けて、あるものと、されて
いる。この櫨のパルプ装置を設計するにあたっては、所
与の時間内で、且つ、認容できる小圧力降下の下で、最
大容量の流体流を可能とするに十分に大である刀で一ト
面積を附与することが、系全体としての性能上から極め
て重要である。このことは特に、空調システム中に用い
られている冷凍用圧縮機において、空調システムでは一
般に比較的多量の流量が要求されることから、肝心なこ
とである。BACKGROUND OF THE INVENTION Reciprocating piston type compressors are typically supported at the cylinder end between a head and a cylinder housing and are provided with pressure responsive suction and discharge valve mechanisms. In designing this oak pulping equipment, the goal was to create an area with a blade that was large enough to allow the maximum volume of fluid flow in a given time and under an acceptably small pressure drop. It is extremely important from the viewpoint of the performance of the system as a whole. This is particularly important in refrigeration compressors used in air conditioning systems, since air conditioning systems generally require relatively large flow rates.
所与寸法のシリンダについてボート面積を最大とすると
いった要請と関連し、且つ、背反する要求として、可動
弁部材の重量を、該部材の慣性効果を制限するために減
少させるといった要求が、ある。運転に伴なう騒音の発
生も、最小限とすべきである。これらの要求ないし要請
は、高速圧縮機に関連して、ますます重要となって来て
いる。Related to, and contrary to, the desire to maximize boat area for a given size cylinder is the desire to reduce the weight of the movable valve member in order to limit the inertial effects of that member. Noise generation associated with operation should also be minimized. These requirements are becoming increasingly important in connection with high speed compressors.
上記のような要求に関連してガス圧縮機用の圧力応動パ
ルプ装置における吐出弁機構についてみると、この種の
吐出弁機構は一般に、圧縮チャンバーを部分的に仕切る
内面を備えた弁板と、この弁板全貫通している吐出通路
と、この吐出通路中に、横断面形状が円形の弁座であっ
て上記圧縮チャンバーから遠ざかる向きに沿い直径を大
とする弁座を、形成する手段と、上記吐出通路内に配設
され、上記弁座に対し密封的に接当する吐出弁と、上記
吐出９Ｆを上記弁座に対し着座する向きに移動附勢する
圧縮スプリングとを、設けてあるものに構成されている
が、従来は上記した吐出弁が、例えば米国特許＆２，０
２５，２４０に開示されているように、金属等の剛性素
材から、弁座の開口の側周壁の傾斜角度と等しい傾斜角
度を有する周端面を備えているものに、形成されていた
。Regarding the discharge valve mechanism in a pressure-responsive pulping device for a gas compressor in connection with the above-mentioned requirements, this type of discharge valve mechanism generally includes a valve plate having an inner surface that partially partitions a compression chamber; A discharge passage that completely penetrates the valve plate, and means for forming a valve seat in the discharge passage, which has a circular cross-sectional shape and whose diameter increases in the direction away from the compression chamber. , a discharge valve disposed in the discharge passage and in sealing contact with the valve seat, and a compression spring that biases the discharge valve 9F to move in a direction in which it seats against the valve seat. However, conventionally, the above-mentioned discharge valve was disclosed in, for example, US Pat.
25, 240, it is made of a rigid material such as metal and has a circumferential end surface having an inclination angle equal to the inclination angle of the side circumferential wall of the opening of the valve seat.
発明が解決しようとする問題点
このような吐出弁機構では、吐出弁閉鎖時における必要
なシール度を得るためのシール長を確保するためには、
吐出弁の厚さをかな〕大きくする必要があった。しかし
金属等の剛性素材から成る吐出弁をして厚さが大きいも
のとすると、その重量が増し、吐出弁の慣性効果が高め
られ、吐出弁の静止状態からのパルプ作用が遅延すると
共に、吐出弁が動いている状態から停止したときの衝撃
による騒音の発生も著しくなる。このような不都合は、
ボート面積を増すぺ〈吐出弁を大型のものとすると、い
っそう甚だしくなる。Problems to be Solved by the Invention In such a discharge valve mechanism, in order to secure a seal length to obtain the necessary degree of sealing when the discharge valve is closed,
It was necessary to increase the thickness of the discharge valve. However, if the discharge valve is made of a rigid material such as metal and has a large thickness, its weight will increase, the inertia effect of the discharge valve will be increased, the pulp action from the discharge valve's stationary state will be delayed, and the pulp action will be delayed. There is also significant noise generation due to the impact when the valve stops moving. This kind of inconvenience is
If the area of the boat is increased and the discharge valve is made larger, the problem becomes even more serious.
この発明の目的とするところは、軽量であシながら必要
なシール度を確保させる吐出弁を有する吐出弁機構を備
えていて上記のような不都合を解消する、ガス圧縮機用
の新規な圧力応動パルプ装置を、提供するにある。The object of this invention is to provide a novel pressure-responsive pressure-responsive mechanism for a gas compressor that eliminates the above-mentioned disadvantages by being lightweight and equipped with a discharge valve mechanism that ensures the necessary degree of sealing. is to provide pulp equipment.
問題点を解決するための技術的手段
この目的の下に開発された本発明パルプ装置は、ガス圧
縮機用の圧力応動パルプ装置であり、Ａ、圧縮チャ／パ
ーを部分的に仕切る内面を備えた弁板と、
Ｂ、上記弁板を貫通している吐出通路と、Ｃ０上記吐出
通路中に設けられた横断面形状円形の弁座であって上記
圧縮チャンバーから遠去かる向きに沿い直径を大とする
弁座と、
Ｄ、上記吐出通路内に配設され、上記弁座に対し密封的
に接当するように形成された周端面を有する吐出弁と、
Ｅ、上記吐出弁を上記弁座に対し着座する向きに移動附
勢する圧縮スプリングと、
を設けてあるパルプ装置であって、
前記吐出弁を比較的弾性変形性に富む隅分子素材から、
肉密であって前記周端面が連続した単一の傾斜を有して
いて前記圧縮チャンバーから遠去かる向きに溢い直径を
大とする截頭円錐状のものに形成すると共に、該吐出弁
の周端面の開先角度を前記弁座の開口の側周壁の開先角
度に対し相対的に、吐出升非圧縮状即て吐出弁周端面の
開先角度の方が弁座開口の側周壁の開先角度よりも適当
量だけ大であって弁座に対する吐出弁の完全な着座が吐
出弁の変形により該吐出弁の内面が前記した弁板の内面
とほぼ同一平面上に位置しつつ吐出弁の周端面の全面で
行なわれると共に該変形によって吐出弁に生ぜしめられ
るところの弁座に対する弾発力が前記圧縮スプリングの
附勢力よりも大となるような角度に設定したこと、
をｔ！！ｊ徴としてなる。Technical means for solving the problem The pulping device of the present invention developed for this purpose is a pressure-responsive pulping device for a gas compressor, comprising: A. an inner surface that partially partitions the compressed chamber/par; B. A discharge passage passing through the valve plate; C. A valve seat with a circular cross section provided in the discharge passage and having a diameter along the direction away from the compression chamber. D. a discharge valve disposed within the discharge passage and having a circumferential end surface formed to sealingly abut against the valve seat; E. the discharge valve as described above; A pulp apparatus is provided with a compression spring that moves and biases the seat in the direction of seating, and the discharge valve is made of a corner molecular material that is relatively elastically deformable.
The discharge valve is formed into a truncated conical shape that is dense and has a single continuous slope at the circumferential end face and overflows in a direction away from the compression chamber and increases in diameter. Relative to the groove angle of the peripheral end surface of the valve seat opening, the groove angle of the peripheral end surface of the discharge valve is in a non-compressible state, that is, the groove angle of the peripheral end surface of the discharge valve is larger than the groove angle of the side peripheral wall of the valve seat opening. is larger than the groove angle of the valve plate by an appropriate amount, and the discharge valve is completely seated against the valve seat so that the inner surface of the discharge valve is located on almost the same plane as the inner surface of the valve plate due to the deformation of the discharge valve, and the discharge valve is discharged. t! is set at an angle such that the elastic force against the valve seat, which is generated on the discharge valve by the deformation and is performed on the entire circumferential end surface of the valve, is greater than the biasing force of the compression spring. ! It becomes a symptom.
作用と効果
上記構成の本発明によれば圧縮チャンバーから遠去かる
向きに浴い直径を大とする弁座が設けられているのに対
し、吐出弁を射弾性変形性の高分子素材から肉密であっ
て周端面が単一の傾斜を有する截頭円錐状のものに形成
すると共に、この吐出弁の周端面の開先角度と弁座開口
の側周壁の開先角度との関係を上記のように設定しであ
ることから、吐出弁閉鎖過程中に吐出弁は、先ずその直
径が大きな部分でのみ弁座に接当し、次いで弁座によシ
圧縮され全体として変形して行き、変形に基づく弾発力
でもって弁座に対し密着し良状態で該弁座に着座するこ
ととなる。Effects and Effects According to the present invention having the above configuration, the valve seat is provided with a valve seat whose diameter increases in the direction away from the compression chamber, whereas the discharge valve is made of elastically deformable polymeric material. The discharge valve is formed into a truncated conical shape with a single inclination on the peripheral end surface, and the relationship between the groove angle of the peripheral end surface of this discharge valve and the groove angle of the side peripheral wall of the valve seat opening is determined as described above. Therefore, during the discharge valve closing process, the discharge valve first comes into contact with the valve seat only at its large diameter portion, and then is compressed by the valve seat and deforms as a whole. Due to the elastic force generated by the deformation, it comes into close contact with the valve seat and is seated on the valve seat in good condition.
したがって吐出弁はその閉鎖位置で、弁座に対して極〈
強固に押付けられ、このためシール長を短縮しても必要
なシール度が確保されることとなって、吐出弁の厚さを
従来のものよりかなり小さくでき、吐出弁が従来の場合
よシずつと軽量化される。また該吐出弁は、比較的変形
性に富む高分子素材がそれ自体で軽量のものであること
からしても、軽量化される。このように吐出弁が軽量化
されることで、吐出弁の慣性効果が制限され、吐出弁の
静止状態からのパルプ作用が迅速に行なわれると共に、
吐出弁が動いている状態から停止したときの衝撃による
騒音の発生が、吐出弁の変形による緩衝作用も相まって
、大巾に減せしめられる。そして高分子素材から成る肉
密の吐出弁は、それを大型化するほど変形性が増すから
、ボート面積を増すべく吐出弁を大型のものとしたとき
、それによる重量増加が吐出弁の変形性増大でカバーさ
れる。さらに上記したパルプ作用の迅速化についてみる
と、吐出弁の周端面の開先角度が前記したように１弁座
に対する該吐出弁の完全な着座状態での変形によって同
吐出弁に生ぜしめられるところの弁座に対する弾発力が
吐出ｆｆｔ−弁座向きに移動附勢するスプリングの附勢
力よりも大となるような角度に設定されていることから
、吐出弁による閉鎖状縣から核弁内外の圧力差が逆転し
始めたとき、つ′＝１シ吸入サイクルの完了後で排出サ
イクルの初期に、吐出弁が弁座に対し弾発する復元力で
該弁座から即座に引離され、これによシ吐出升がその全
面で圧縮チャンバー内の開放圧力を直ちに受けることと
なって、升開放動が促進されることから、パルプ作用の
迅速化といった長所がいっそう高められる。Therefore, in its closed position, the discharge valve is located at a pole with respect to the valve seat.
Because of this, the required sealing degree can be maintained even if the seal length is shortened, and the thickness of the discharge valve can be made considerably smaller than that of conventional ones. and becomes lighter. Furthermore, the discharge valve is lightweight because the relatively deformable polymeric material itself is lightweight. By reducing the weight of the discharge valve in this way, the inertial effects of the discharge valve are limited, and the pulping action from a stationary state of the discharge valve is performed quickly.
Coupled with the buffering effect of the deformation of the discharge valve, the noise generated by the impact when the discharge valve stops from a moving state can be greatly reduced. A dense discharge valve made of a polymeric material becomes more deformable as it becomes larger. Therefore, when a discharge valve is made larger to increase the boat area, the resulting weight increase causes the deformability of the discharge valve. Covered by increase. Furthermore, regarding the acceleration of the pulp action described above, the bevel angle of the peripheral end surface of the discharge valve is caused by the deformation of the discharge valve in the fully seated state with respect to one valve seat, as described above. Since the elastic force against the valve seat is set at an angle that is greater than the urging force of the spring that moves and urges the discharge fft - toward the valve seat, the inside and outside of the core valve from the closed state of the discharge valve. When the pressure difference begins to reverse, at the beginning of the discharge cycle after the completion of the suction cycle, the discharge valve is immediately pulled away from the valve seat by the restoring force against the valve seat. Since the discharged cell immediately receives the opening pressure in the compression chamber over its entire surface, the cell opening movement is promoted, and the advantage of speeding up the pulping action is further enhanced.
また吐出弁の周端面の開先角度が前記のように、該吐出
弁の弁座に対する完全な着座が吐出弁の変形により吐出
弁周端面の全面で行なわれるような角度に設定されてい
ることから、該吐出弁は圧縮チャンバーに対し吐出弁の
円面（圧縮チャンバー側の端面）のみで対面して該圧縮
チャンバーを閉封することとなり、そのような内面は、
吐出弁が圧縮チャンバーから遠去かる向きに沿い直径を
大とする截頭円錐状のものであることからして吐出弁に
おいて面積を最小とする面となっている。したがって吐
出弁は圧縮チャンバー内の再膨張容積を小さくし、また
吐出弁が前記のように軽量のものに形成されるのに対し
該吐出弁はその面積が最小となる部分で圧縮チャンバー
内外の圧力差を受けることになってそのような圧力差に
基づく応力に対抗する抵抗性が大で疲労とか損傷を受は
馴い。Furthermore, the bevel angle of the circumferential end surface of the discharge valve is set at such an angle that the entire circumferential end surface of the discharge valve is completely seated on the valve seat due to deformation of the discharge valve, as described above. Therefore, the discharge valve faces the compression chamber only with the circular surface (end surface on the compression chamber side) of the discharge valve to close the compression chamber, and such an inner surface is
Since the discharge valve has a frusto-conical shape with a diameter increasing in the direction away from the compression chamber, this is the surface with the smallest area in the discharge valve. Therefore, the discharge valve reduces the re-expansion volume within the compression chamber, and while the discharge valve is formed to be lightweight as described above, the discharge valve has a minimum area that reduces the pressure inside and outside the compression chamber. It has a high resistance to stress caused by such a pressure difference and is less prone to fatigue and damage.
さらに吐出弁の開先角度を前記のように、弁座に対する
完全な着座状慇で該吐出弁の内面が９Ｐ′ＪｆＬの内面
とほぼ同一平面上に位置するように設定していることか
ら、圧縮チャンバー内の再膨張容積吐出弁の内面が弁板
内面とほぼ同一平面上に位置することによって弁板に設
けられた弁座開口中には吐出弁内面側、つ１り圧縮チャ
ンバー側において空隙が存在しなくなるため、圧縮チャ
ンバー６つ再膨張容積が最小とされるからである。Furthermore, since the opening angle of the discharge valve is set as described above so that the inner surface of the discharge valve is located almost on the same plane as the inner surface of 9P'JfL when it is perfectly seated against the valve seat, Since the inner surface of the re-expansion volume discharge valve in the compression chamber is located on almost the same plane as the inner surface of the valve plate, there is a gap in the valve seat opening provided in the valve plate on the inner side of the discharge valve and on the compression chamber side. This is because the re-expansion volume of the six compression chambers is minimized because there are no more.
！−」１−ノー
第１−３（８）には、この発明に従ったバルブ装置の一
実施例が、参照数字１０で全体を示して、図示されてい
る。このバルブ装置１０は、通例の弁板１２を備えてお
り、該弁板１２は、互に離れている１対の吸入通路１４
及び１６であって弁板１２を貫通している吸入通路１４
及び１６と、弁座１８を備えた吐出通路とを、有してい
る。通例のＩＪ −ド型吸入弁２０も設けられており、
該吸入弁２０は、吸入通路１４及び１６に対し該通路１
４．１６についての調節を行なうように重ね合せて配置
しである一端部２２と、弁板１２に固定しである他端部
２４と、中央部の細長い開口２６であって弁座１８を備
えた吐出通路と重なり合うように配置されている開口２
６とを、有している。シリンダ穴中には、吸入弁２０が
開くときに該−ｆｆ２０のたわみを許容するための隙間
を附与する凹溝２９を、設けてある。弁板１２は、シリ
ンダブロック２７によって区画されている圧縮機シリン
ダ上に、通例の方法でのせられている。第１図では、シ
リンダ穴位置を想像線で示しである。! 1-3 (8), an embodiment of a valve arrangement according to the invention is illustrated, indicated in its entirety by the reference numeral 10. The valve device 10 includes a conventional valve plate 12 which includes a pair of suction passages 14 spaced apart from each other.
and 16 and passing through the valve plate 12.
and 16, and a discharge passage provided with a valve seat 18. A usual IJ-type suction valve 20 is also provided,
The suction valve 20 is connected to the suction passages 14 and 16.
4.16, having one end 22 which is arranged one above the other, the other end 24 being fixed to the valve plate 12, and a central elongated opening 26 with a valve seat 18. an opening 2 arranged so as to overlap the discharge passage;
6. A groove 29 is provided in the cylinder hole to provide a gap for allowing deflection of the -ff20 when the suction valve 20 opens. The valve plate 12 is mounted in the customary manner on the compressor cylinder, which is delimited by a cylinder block 27. In FIG. 1, the cylinder hole positions are shown with imaginary lines.
第２．３図に示すように、弁座１８はその開口を、外向
きに拡開する側周壁２８によって囲まれ九截頭円錐形の
ものとされている。截頭円錐形の吐出弁３０が該吐出通
路内に、該吐出弁３０の周端ａ３２を弁座１８の開口の
側周壁２８に密封的に接当させて、配設されている。こ
の吐出弁３０は図示のように、その下面３４が弁板１２
の下面３６と実質的に同一平面上に位置するように、弁
座１８の開口に対応した寸法及び形状のものに、形成さ
れている。吐出弁３０にはまた、その上面４０において
凹溝３８を設けてあり、該凹溝３８は、つる巻き圧縮ば
ね４４から成る附勢手段の一端４２を受けている。圧縮
ばね４４の他端４６は。As shown in FIG. 2.3, the valve seat 18 has an opening surrounded by a side peripheral wall 28 which widens outward and has a nine-truncated conical shape. A frusto-conical discharge valve 30 is disposed within the discharge passage with a circumferential end a32 of the discharge valve 30 in sealing contact with a side circumferential wall 28 of the opening of the valve seat 18. As shown in the figure, this discharge valve 30 has a lower surface 34 connected to the valve plate 12.
The valve seat 18 is sized and shaped to correspond to the opening of the valve seat 18 so as to be substantially flush with the lower surface 36 of the valve seat 18 . The discharge valve 30 is also provided with a groove 38 in its upper surface 40 which receives one end 42 of a biasing means consisting of a helical compression spring 44. The other end 46 of the compression spring 44 is.
上方へ延びて、橋状のリテーナ５０に設けた凹溝４８に
係合させである。升３０は本質的に圧力で作動せしめら
れるものであり上記の圧縮ばね４４は、復元力並びに初
期シールを達成する初期閉鎖附勢力及び予負荷を与える
ように、選択される。It extends upward and engages with a groove 48 provided in the bridge-like retainer 50. The cell 30 is essentially pressure actuated and the compression spring 44 described above is selected to provide a restoring force and an initial closing bias and preload to achieve an initial seal.
コイルばね以外の他の形のスプリングも勿論、上記し丸
目的のために使用できる。升３０の開放動を規制するス
トッパーとしても機能する上記リテーナ５０は、適宜の
締付具５２及び５４によって弁板１２へと固定されてい
る。Other forms of springs than coil springs can, of course, be used for the circular purpose described above. The retainer 50, which also functions as a stopper for restricting the opening movement of the cell 30, is fixed to the valve plate 12 by appropriate fasteners 52 and 54.
一般的に言って、吐出弁３０は、高性能高分子材、特に
ポリイミド、アラミド（ａｒａｍｉｄ ） 、ポリエス
テル、ポリフェニレンサルファイド、ポリ・アミド−イ
ミド樹脂等の成形可能な樹脂から、製作するのが望まし
い。これらの素材は、高強度、耐高温性及び比較的軽量
のものであり、且つ、非反応性であると共に比較的に易
変形性である。吐出弁３０のための素材についての望ま
しいパラメータの全てを数値的に表示するのは困難であ
るが、最良の結果は、抗張力対重量比が約１０１８ｋＰ
ａ／ ｇよシ大であり、曲げ強さと弾性率（ｍｏｄｕｌ
ｕｓ ｏｆ ｅｌａｓｔｉ−ｃｉｔｙ ）が約０．０４
よυ小である素材を用いたときに、得られるように、判
断される。また該素材は、２３２℃よシ高い熱破壊温度
、高摩耗抵抗、高内部緩衝特性（騒音減少及びシールの
ため）、環境への適応性、製作の容易性（例えば圧縮或
は射出成形により。）、低クリープ比、及び高衝撃強さ
く約０．８よシ大きな切欠きアイゾツト衝撃強さ−ｎｏ
ｔｃｈｅｄ Ｉｚｏｄ ｉｍｐａｃｔ ｓｔｒｅｎｇｔ
ｂ−を有するのが、望ましい。＞ｔ、備えているべきで
ある。Generally speaking, the discharge valve 30 is preferably fabricated from high performance polymeric materials, particularly moldable resins such as polyimide, aramid, polyester, polyphenylene sulfide, polyamide-imide resins, and the like. These materials are high strength, high temperature resistant, relatively lightweight, non-reactive and relatively easily deformable. Although it is difficult to numerically represent all of the desired parameters for the material for the discharge valve 30, the best results indicate that the tensile strength to weight ratio is approximately 1018 kP.
It is larger than a/g, and the bending strength and modulus of elasticity are
us of elasti-city) is approximately 0.04
It is judged as obtained when using a material that is small. The material also has a thermal breakdown temperature higher than 232°C, high abrasion resistance, high internal damping properties (for noise reduction and sealing), environmental adaptability, and ease of fabrication (eg, by compression or injection molding). ), low creep ratio, and high impact strength, large notch impact strength of approximately 0.8 - no.
tched Izod impact strength
It is desirable to have b-. >t, should be provided.
現在のところ、弁３０のための好適した素材は、米国、
プラウエア州、ウイルミングトンのデュポン−カンパニ
ー （ＤｕＰｏｎｔ Ｃｏｍｐａｎｙ ）から発売され
ているポリイミド樹脂である「Ｖｅｓｐｅｌ Ｊである
。Currently, the preferred materials for the valve 30 are
Vespel J is a polyimide resin sold by DuPont Company of Wilmington, Praue.
ｒｓＰ−ＩＪ及びｌ’−５Ｐ−２ｉと特定されている組
成物が優れ九結果を与えることを、見出した。It has been found that compositions identified as rsP-IJ and l'-5P-2i give excellent results.
吐出弁３０のためにかかる高分子組成物を用いることに
よって、成形等による製作が容易となシ、ま九吐出５ｆ
３０が比較的＠量となることから、升の慣性力が減ぜし
められて高速作動が得られると共に軽るいスプリングを
用いることが可能となり、また弁と弁座間の接触による
騒音の発生も抑えられる。上記した素材［Ｖｅｓｐｅｌ
Ｊは、比較的高い温度に耐えて劣化せず、また冷凍ガ
スにも潤滑油にも影響されず、本用途に理想的に適して
いる。冷媒及び潤滑油を、その損傷を招くことなくさら
せる最高作動温度は、 「Ｖｅｓｐｅｌ ｊの同様の最
高作動温度よりも低いことを、見出した。「Ｖｅｓｐｅ
ｌ ｊはまた、永久変形を生じることなしに十分にシー
ルを達成するように易変形性である。By using such a polymer composition for the discharge valve 30, manufacturing by molding etc. is easy.
30 is relatively small, the inertial force of the square is reduced, high-speed operation is achieved, and a light spring can be used, and noise caused by contact between the valve and the valve seat is also suppressed. It will be done. The above material [Vespel
J is ideally suited for this application as it can withstand relatively high temperatures without deterioration and is unaffected by refrigerated gases or lubricating oils. We have found that the maximum operating temperature to which refrigerants and lubricants can be exposed without incurring damage is lower than the similar maximum operating temperature of Vespel j.
l j is also sufficiently deformable to achieve a seal without causing permanent deformation.
使用可能と信じられる前述特性を有する他の適当な高分
子材としては、市販に係る商品名もしくは商標名で宮っ
て［Ｖｅｓｐｅ［Ｊ Ｋ Ｓ （デュポン・カンパニー
の販売に係るアラミド樹脂） 、ｒ Ｓｐａｒｍｏｎ
Ｊ（米国、オハイオ州、ドウパーのスバータ・マニュフ
ァクチャリング・カンパニー（５ｐａｒｔａ Ｍｆｇ・
Ｃ０６）の販売に係るポリイミド樹脂） ＪＶａｌｏｘ
Ｊ４２０または４２０−３ＥＵ （米国、マサチュウ
セツツ州、ビックフィールドのゼネラル・エレクトリッ
ク・カンバー１−−（Ｇｅｎｅｒａｌ Ｅｌｅｃｔｒｉ
ｃ Ｃｏ、）の販売に係るガラス繊維強化熱可塑性ポリ
エステル）、「Ｒｙｔｏｎ Ｊ （米国、オクラホマ
州、パートレスビレのブイリップス ピトロリュウム・
カンパニー（Ｐｈ１ｌｌｉｐｓ Ｐｅｔｒｏｌｅｕｍ
Ｃｏ、）の販売に係るポリ７−ｃニレン・サルファイド
）及び「Ｔｏｒｌｏｎ Ｊ （米５］、イリノイ州、シ
カゴのアモコ・ケミカルス・コーポレーション（Ａｍｏ
ｃ’ｏ Ｃｈｅｍｉｃａｌｓ Ｃｏｒｐ 、 ）の販売
に係るポリ・アミド−イミド樹脂）がある。Other suitable polymeric materials having the above-mentioned properties that are believed to be of use include commercially available trade names or trade names such as Vespe [JKS (aramid resins marketed by DuPont Company), r Spamon
J (5parta Mfg., Daupar, Ohio, USA)
Polyimide resin related to sales of C06) JValox
J420 or 420-3EU (General Electric Cumber 1, Bickfield, Massachusetts, USA)
Glass fiber reinforced thermoplastic polyester), "Ryton J (Buy Lips Pitrolume, Partlessville, Oklahoma, USA)"
Company (Ph1llips Petroleum
Poly7-c nylene sulfide) and Torlon J (USA 5), Amoco Chemicals Corporation (Amoco Co., Chicago, Illinois)
There are polyamide-imide resins sold by c'o Chemicals Corp.
第４図に示すように、吐出弁３０の周端面３２は、参照
数字５５で示す弁座１８の中心線に対し、弁座１８の開
口の側周壁２８の傾斜角度５８よりも、（非圧縮状態の
下で）僅かに大きな角度５６だけ、傾斜せしめられてい
る。初期シールは、吐出ｆｆ３０が第４図に図示の位置
に接近したとき、つ′！シ周端面３２の薄い外側シール
周縁６０が先ず側周壁２８に接当したときに、達成され
る。閉鎖サイクルの大部分の間、升３０内外の圧力差は
比較的小さいので、主たる閉鎖力は、ばね４４によって
及ぼされる力である２、シかし初期シールが一旦達成さ
れると、圧縮機ピストンが上死点から下降し始めるにつ
れて、弁３０内外に実質的な圧力差が生ぜしめられる。As shown in FIG. 4, the circumferential end surface 32 of the discharge valve 30 is less than the inclination angle 58 of the side circumferential wall 28 of the opening of the valve seat 18 with respect to the center line of the valve seat 18 indicated by the reference numeral 55. (under conditions) by a slightly greater angle 56. The initial seal is activated when the discharge ff30 approaches the position shown in FIG. 4! This is achieved when the thin outer sealing periphery 60 of the circumferential end face 32 first abuts the side circumferential wall 28. During most of the closing cycle, the pressure differential across cell 30 is relatively small, so the primary closing force is the force exerted by spring 442; however, once an initial seal is achieved, the compressor piston As the valve 30 begins to descend from top dead center, a substantial pressure difference is created across the valve 30.
この圧力差により実質的な閉鎖力が生ぜしめられ、升３
０が、第４図に図示の初期シール位置から第２．３．５
図に図示の完全な着座位置へと、移動せしめられる。This pressure difference creates a substantial closing force,
2.3.5 from the initial sealing position shown in FIG.
It is moved to the fully seated position shown in the figure.
第４図に示す弁３０の初期シール位置と第２図に示す弁
３０の完全着座状態との対比から明らかなように、弁３
０の初期シール位置では該弁３０の周端面３２と弁座開
口の側周壁２８間、及び弁３０の下面（内面）３４と弁
板１２の下面（内面）３６が位置する平面との間にそれ
ぞれ、圧縮チャンバー内に連通ずる空隙が残されている
のに対し、弁３０の完全着座状態では弁３０の下面（内
面）３４が弁板１２の下面（内面）３６とほぼ同一平面
上に位置しつつ弁３０がその周端面３２の全面でもって
弁座１８に着座するように変形していて、上記した何れ
の空隙も残されないように、ｆｆ３０の周端面３２の開
先角度が設定されている。As is clear from the comparison between the initial sealing position of the valve 30 shown in FIG. 4 and the fully seated state of the valve 30 shown in FIG.
In the initial seal position 0, there is a gap between the peripheral end surface 32 of the valve 30 and the side peripheral wall 28 of the valve seat opening, and between the lower surface (inner surface) 34 of the valve 30 and the plane where the lower surface (inner surface) 36 of the valve plate 12 is located. In each case, a gap is left that communicates with the compression chamber, whereas when the valve 30 is fully seated, the lower surface (inner surface) 34 of the valve 30 is located approximately on the same plane as the lower surface (inner surface) 36 of the valve plate 12. At the same time, the groove angle of the peripheral end surface 32 of the ff30 is set so that the valve 30 is deformed so as to sit on the valve seat 18 with the entire surface of its peripheral end surface 32, and none of the above-mentioned gaps are left. There is.
９Ｐ３０とばね４４とは、Ｆｆ’３０への作用圧力が減
じ該９Ｐ３０が完全着座位置から第４図に図示の位置へ
と移動するときに弁３０によって及ぼされる上昇力が、
この初期開放動中にばね４４により３Ｐ３０に対し及ぼ
される下降力よりも、実質的に大であるように、設定さ
れる。このように設定することで、弁３０の開放が有意
義に援けられる。9P30 and spring 44 ensure that the upward force exerted by valve 30 as the pressure on Ff'30 decreases and 9P30 moves from the fully seated position to the position shown in FIG.
It is set to be substantially greater than the downward force exerted on 3P30 by spring 44 during this initial opening movement. By setting in this way, opening of the valve 30 is meaningfully assisted.
何故なら、−ｙＰ３０内外の圧力差が逆転し始めると直
ちに、（つ壕り、吸入サイクルの完了後で排出サイクル
の初期に、）弁３０中の残留応力が該升３０を直ちに弁
座１８から弾性的に、ｉｇ４図に図示位置方向へと引離
す（ばね４４の力に打克っての作用。）こととなるから
である。これによシ升３０の全面積が、圧縮チャンバー
内に発生せしめられた開放圧力を直ちに受けることとな
る。このように升３０の最大有効面積が開放ないし上昇
圧力を受けることで、弁開放が促進され、よシ高速での
作動が可能となる。また、弁３０が上昇動するにつれて
側周壁２８と周端面３２との間の通路域が増加して行き
、これにより所与のボート面積で流体吐出のための極め
て大きな面積が提供されることとなる。これによって、
所与の圧縮機速度で物質流量が有意義に増大せしめられ
る。This is because as soon as the pressure difference between the inside and outside of the P30 begins to reverse (at the beginning of the evacuation cycle after the completion of the suction cycle), the residual stresses in the valve 30 immediately pull the cell 30 away from the valve seat 18. This is because it is elastically pulled away in the direction of the position shown in Figure ig4 (an action that overcomes the force of the spring 44). This causes the entire area of the cell 30 to be immediately exposed to the opening pressure created in the compression chamber. In this way, the maximum effective area of the cell 30 is opened or subjected to rising pressure, which promotes opening of the valve and enables high-speed operation. Also, as the valve 30 moves upward, the passage area between the side wall 28 and the end surface 32 increases, thereby providing an extremely large area for fluid delivery for a given boat area. Become. by this,
At a given compressor speed the material flow rate is significantly increased.
吐出弁３０が完全に着座しているとき（ＷＪ２゜３．５
図に図示の位置にあるとき）には、圧力差にさらされる
該９Ｐ３０の有効面積は、弁座１８によって囲まれた領
域の面積、つまり−ｆｆ３０の外周縁によって囲１れた
領域の面積よりもずっと小さな面積、である事実が、留
意されるべきである。When the discharge valve 30 is fully seated (WJ2゜3.5
In the position shown in the figure), the effective area of the 9P30 exposed to the pressure difference is greater than the area of the area surrounded by the valve seat 18, that is, the area of the area surrounded by the outer periphery of -ff30. It should be noted that the area is also much smaller.
弁作用促進を最大限に得るために重量を極力軽減するこ
とが望ましいことから、材質強度及び構造設計を考慮し
て升３０を、吐出通路１８の内周縁によって囲まれた比
較的小さな面積の内外に作用する圧力間の最大圧力差に
該弁３０が耐え得る限り、仮に着座時に弁３０の最大有
効面積へとｆｆ３０内外の最大圧力差が作用したとする
と抜弁３０が過度の変形成は永久変形が起ることなしに
は該圧力差を受入れ不可能であるように、十分に軽量に
構成して差支えない。逆に言うと、５Ｐ３０は、弁座１
８への着座時に全横断面に対し内外の圧力差が作用する
とすれば、より堅牢な（したがってまたより重い）もの
とされることとなる。升３０と弁座１８間の前記した傾
斜角度差も、閉鎖時の衝撃を緩和して、升３０が軽量で
あることと相筐って、騒音及び摩耗を減少させるのに役
立つ。Since it is desirable to reduce the weight as much as possible in order to maximize the promotion of valve action, the square 30 is placed inside and outside a relatively small area surrounded by the inner periphery of the discharge passage 18, taking into consideration material strength and structural design. As long as the valve 30 can withstand the maximum pressure difference between the pressures acting on the ff30, if the maximum pressure difference between the inside and outside of the ff30 acts on the maximum effective area of the valve 30 when seated, excessive deformation of the removed valve 30 will result in permanent deformation. It may be constructed to be sufficiently lightweight so that the pressure difference cannot be accommodated without this occurring. Conversely, 5P30 is valve seat 1
If the entire cross section is subjected to internal and external pressure differences when seated on the seat 8, it will be made more robust (and therefore also heavier). The above-mentioned difference in angle of inclination between the cell 30 and the valve seat 18 also helps to reduce the impact upon closing and, together with the light weight of the cell 30, reduces noise and wear.
吐出弁３０は、周端面３２でもって側周壁２８を適切に
シールするために、また周端面３２中に部分的に或は完
全に環状である溝が摩耗形成されないようにするために
、弁板１２の厚さよりも小さい厚さを備えているのが、
望ましい。上記のような溝が摩耗形成されると、核溝は
、弁３０の正しい着座及びシール作用の少なくとも倒れ
かを阻害し得る。またシール周縁６０には、小さな丸み
ないし面取りを施して、該丸みないし面取り部により、
例え升３０がその閉鎖中に僅かに変位ないし開放動せし
められたとしても適切なシールが確保されるように、図
るのが望筐しい。さらに圧縮ばね４４は、その端４２．
４６を角形とし研磨すると共に弁３０の直径との比較で
極力大きな直径を有するものとして、該ばね４４によっ
て及ぼされる附勢力がシール用の周端壁３２に、極力近
接する部分で作用し、且つ、弁３０がその作動中に進退
、回転その他の変位を起すのを阻止するように、図るの
が望ましい。The discharge valve 30 is fitted with a valve plate in order to properly seal the side circumferential wall 28 with the circumferential end surface 32 and to prevent the wear formation of partially or fully annular grooves in the circumferential end surface 32. The one with a thickness smaller than the thickness of 12 is
desirable. When grooves such as those described above wear out, the core grooves can interfere with proper seating and sealing of the valve 30, or at least collapse. Further, the seal peripheral edge 60 is provided with a small roundness or chamfer, and the roundness or chamfer allows for
It is desirable to ensure that a proper seal is maintained even if the cell 30 is slightly displaced or moved open during its closure. Furthermore, the compression spring 44 is compressed at its end 42 .
46 is square and polished, and has a diameter as large as possible compared to the diameter of the valve 30, so that the biasing force exerted by the spring 44 acts as close as possible to the sealing peripheral end wall 32, and the valve It is desirable to prevent 30 from moving forward or backward, rotating or otherwise displacing during operation.
第１−４図に図示の実施例では、この発明に係るパルプ
装置の吐出弁３０を、リード型吸入弁と組合せて利用し
たが、この発明に係るバルブ装置における新規な吐出弁
は、第５図に示す実施例において参照数字６４で一般的
に示されているように、通例のリング型吸入升と共に用
いるのにも、適している。該バルブ装置６４は、弁板６
６を備えていて、この弁板６６は、比較的大きくて不規
則な形状の、概して環状である凹み部６８であって弁板
下面７０中に吸引空間を形成する凹み部６８を、有して
いる。截頭円錐形の吐出通路７２も設けられていて、該
吐出通路７２は、半径方向内方向きに傾斜して弁板６６
の上面７６と下面７０間を連らねている側周壁７４によ
って、筐わりを仕切られている。該側周壁７４の表面７
８は、吐出弁３０′用の弁座を附与する。吐出弁３０′
は該弁座７８に対し、ガス圧力並びに９Ｐ３０’とげね
リテーナ５０′間に配設せるばね４４′によって密封的
に係合せしめられる。ばね４４′、弁３０’及びはねリ
テーナ５０′は、第１−４図に図示の実施例に２ける相
当する部材と実質的に等しいｔのと、されている。In the embodiment illustrated in FIGS. 1-4, the discharge valve 30 of the pulp apparatus according to the present invention was used in combination with a reed-type suction valve, but the novel discharge valve in the valve apparatus according to the present invention is a fifth valve. It is also suitable for use with a conventional ring-shaped suction chamber, as indicated generally by the reference numeral 64 in the embodiment shown. The valve device 64 includes a valve plate 6
6, the valve plate 66 has a relatively large, irregularly shaped, generally annular recess 68 forming a suction space in the lower surface 70 of the valve plate. ing. A frusto-conical discharge passage 72 is also provided which slopes radially inwardly toward the valve plate 66.
The housing is partitioned by a side peripheral wall 74 that extends between the upper surface 76 and the lower surface 70 of the housing. Surface 7 of the side peripheral wall 74
8 provides a valve seat for the discharge valve 30'. Discharge valve 30'
is sealingly engaged to the valve seat 78 by gas pressure and a spring 44' disposed between the 9P30' and barb retainers 50'. Spring 44', valve 30' and spring retainer 50' are of substantially the same length as the corresponding members in the embodiment illustrated in FIGS. 1-4.
概して環状の弁板挿入物８０が凹み部６８内に配設され
ており、該挿入物８０を通して締結具８２が、パルプ装
置６４全シリンダハウジング８４へと固定するために、
設けられている。また弁板挿入物８０を貫通させて複数
個の間隔付けられた切欠き部ないし放射方向スロット（
図示せず）が、吸入流体が半径方向の内側と外側間で流
れ得るようにすべく、設けられている。A generally annular valve plate insert 80 is disposed within the recess 68 through which fasteners 82 are secured to the full cylinder housing 84 of the pulping apparatus 64.
It is provided. There are also a plurality of spaced apart notches or radial slots (
(not shown) are provided to allow suction fluid to flow between the radially inner and outer sides.
環状リング８６に形成された第２の挿入物も設けられて
おシ、このリング８６は、弁板挿入物８０の下面９０に
半径方向の内端部で形成された環状切欠き８Ｂに受けら
れて＆υ、また該リング８６には、半径方向内方向きに
延びて側周壁７４の面９４と接当している複数個の補強
リプ９２を、間隔をあけて設けてある。A second insert formed in an annular ring 86 is also provided, which ring 86 is received in an annular notch 8B formed at a radially inner end in a lower surface 90 of the valve plate insert 80. Additionally, the ring 86 is provided with a plurality of spaced apart reinforcing lips 92 that extend radially inward and abut against the surface 94 of the side peripheral wall 74.
側周壁７４の末端９６は、弁板６６の下面７０、弁板挿
入物８０の下面９０及び環状リング８６の下面９８と同
一平面上にあるように、図られている。環状リング状の
吸入リード升１００が上記した下面９６及び９８に対し
、環状リング８６と面９４間から圧縮チャンバー１０２
円へと流体が移行しないようにするために、密封的に接
当させである。この吸入リード升１００中には中心・開
口１０４を設けてあシ、該開口１０４は吐出通路７２と
同心的に配置されていて、圧縮チャンバー１０２と吐出
９Ｐ３０’の下面３４′との間の直接的な流体連通を可
能とする。磐≠念輿第６図から明瞭にみてとれるように
、吸入リード９Ｐ１００も一直径上で対向位置する１対
の半径方向外方向きの耳部１０８及び１１０を有してお
り、該各耳部１０８，１１０にはそれを貫通する適宜の
穴１１２が設けられている。第５図に示すように、耳部
１０８及び１１０は、シリンダハウジング８４の切欠き
溝１１４及び１１６に受けられており、該耳部１０Ｂ、
１１０の上記穴１１２に前記締結具８２を挿入して、吸
入リード、７Ｐ１００を位置保持しである。The distal end 96 of the side peripheral wall 74 is configured to be flush with the lower surface 70 of the valve plate 66, the lower surface 90 of the valve plate insert 80, and the lower surface 98 of the annular ring 86. The annular ring-shaped suction lead box 100 is connected to the compression chamber 102 from between the annular ring 86 and the surface 94 with respect to the lower surfaces 96 and 98.
Abut sealingly to prevent fluid migration into the circle. A center opening 104 is provided in this suction lead box 100, and the opening 104 is arranged concentrically with the discharge passage 72 and directly between the compression chamber 102 and the lower surface 34' of the discharge 9P30'. allows for fluid communication. As can be clearly seen from FIG. 6, the suction lead 9P100 also has a pair of radially outward facing ears 108 and 110 located opposite each other on one diameter. , 110 are provided with suitable holes 112 passing therethrough. As shown in FIG. 5, the ears 108 and 110 are received in cutout grooves 114 and 116 of the cylinder housing 84, and the ears 10B,
The fastener 82 is inserted into the hole 112 of 110 to hold the suction lead 7P100 in position.
ｌｆｍｆヤ／バー１０２内に配設されている往復動ピス
トン（図示せず）が吸入ストローク中にパルプ装置６４
から遠去かるように動くにつれて、圧縮チャンバー１０
２と前記凹み部６８間の圧力差によって吸入リード９Ｐ
１００が、圧縮チャン、ノ（−１０２側からみて内向き
へとたわまされ、これにより凹み部６８から入口通路１
０６ｔｌ−通して圧縮チャンバー１０２中へと流体が流
入可能となる。A reciprocating piston (not shown) disposed within the lfmf shaft 102 engages the pulp device 64 during the suction stroke.
As it moves away from the compression chamber 10
2 and the recessed portion 68 causes the suction lead 9P to
100 is deflected inwardly when viewed from the compression chamber, -102 side, thereby opening the inlet passage 1 from the recess 68.
06tl- allows fluid to flow into the compression chamber 102.
吸入リード９１００の耳部１０８及び１１０のみが圧縮
チャンバー１０２の側壁面１１８を越えて外方向きに突
出していることから、吸入流体は、吸入リード升１００
及び＃升１００の全内外周１わりの面９８及び９６間か
らチャンバー１０２１四へと容易に流入する。ピストン
の圧縮ストロークが開始されると、吸入リード升１００
は面９６及び９８へと密封的に接当せしめられ、また吐
出弁３０′は、第１−４図について前述したのと同様に
作用し始める。図示の同心的配置からして、圧縮チャン
バー１０２上にのっている実質的に全ての利用可能な面
積が吸入及び吐出作用のために利用され、かくして、圧
縮チャンバー１０２に対する最大限の流体の流入、流出
が達成される。Since only the ears 108 and 110 of the suction lead 9100 protrude outward beyond the side wall surface 118 of the compression chamber 102, the suction fluid flows through the suction lead square 100.
And it easily flows into the chamber 10214 from between the surfaces 98 and 96, which correspond to the entire inner and outer circumferences of the #cell 100. When the compression stroke of the piston begins, the suction lead 100
is brought into sealing abutment against surfaces 96 and 98, and discharge valve 30' begins to operate in the same manner as described above with respect to FIGS. 1-4. Due to the illustrated concentric arrangement, substantially all of the available area resting on the compression chamber 102 is utilized for suction and exhalation operations, thus maximizing fluid inflow into the compression chamber 102. , outflow is achieved.
以上に説明した第１−４図に図示の一実施例及び第５図
に図示の他の実施例では何れも、前記のように軽量のも
のとできる吐出９Ｐｋさらに軽量としている。すなわち
第２図と第５図、そしてこれらの図に示す吐出弁３０．
３０’を完全開放位置においた状１！！？図示している
第６図（ａ） 、 （ｂ）に例示するように、吐出弁３
０．３０’は弁杆部を有しないと共に弁座■、８．７８
の開口の深さＤよりも小さな厚さＴを有するものに形成
されている。このため吐出弁３０．３０’が第２．５図
に図示の弁座１８゜７８に対する完全な着座状態にある
ときは該吐出９３０．３０’が図示のようにその全体で
弁座１８゜７８の開口内に位１ｊ＆することとなるが、
該吐出弁３０．３０’が第６図（ａ） 、 ｆｂｌに図
示の完全開放位置にあるとき吐出弁３０．３０’がなお
、第６図値）に示す吐出弁３０のようにその一部で、或
は第６図ｆｂ）に示す吐出弁３０’のように全体で、弁
座１８゜７８の開口内に位置するように吐出弁３０．３
０’の移動を制限するストッパー手［５０ａ 、 ５０
’ａｆｃ設ばている。すなわち該ストッパー手Ｊ＆５０
ａ。In both the embodiment illustrated in FIGS. 1-4 and the other embodiment illustrated in FIG. 5 described above, the discharge 9Pk, which can be made lightweight as described above, is further made lighter. That is, FIGS. 2 and 5, and the discharge valve 30 shown in these figures.
30' in the fully open position 1! ! ? As illustrated in FIGS. 6(a) and 6(b), the discharge valve 3
0.30' does not have a valve stem part and has a valve seat ■, 8.78
It is formed to have a thickness T smaller than the depth D of the opening. Thus, when the discharge valve 30.30' is fully seated against the valve seat 18.78 as shown in FIG. It will be placed within the opening of
When the discharge valve 30.30' is in the fully open position shown in FIG. or the discharge valve 30.3, such as the discharge valve 30' shown in FIG.
Stopper hand [50a, 50
'afc is set up. That is, the stopper hand J&50
a.
５０′ａは圧縮チャンバー１０２から遠去かる方向への
吐出弁３０，３０’の移動を制限して、該吐出５Ｆ３０
．３０’がその完全開放位置でなお、少なくとも一部分
でもって弁座１８．７８の開口内に位置することとする
。50'a limits movement of the discharge valves 30, 30' in a direction away from the compression chamber 102, and the discharge valve 5F30
．． 30' in its fully open position still lies at least partially within the opening of the valve seat 18.78.
このように完全開放位置でなお弁座１８．７８の開口内
に位置する截頭円錐状吐出弁３０．３０’は次いでの圧
縮機吸入サイクルにおいて、円錐面状をなす弁座１８．
７８開口の側周壁に対し圧縮スプリング４４ 、４４’
の附勢力下で接当し該側周壁にガイドされつつ弁座１８
．７８と正しく軸線を合致して、最終的には第２．５図
に図示の完全な着座状態へと至る。つまり吐出弁３０．
３０’をその移動時にガイドする弁杆部を該吐出弁３０
゜３０’に設けていないにも拘らず、吐出弁３０．３０
’が正しくガイドされるのである。The frusto-conical discharge valve 30.30', which is thus still located within the opening of the valve seat 18.78 in the fully open position, will be removed during the next compressor suction cycle by the conical valve seat 18.78.
78 compression springs 44, 44' against the side peripheral wall of the opening.
The valve seat 18 is brought into contact with the side peripheral wall under the applied force and guided by the side peripheral wall.
．． 78 and finally into the fully seated position shown in FIG. 2.5. In other words, the discharge valve 30.
30' when moving the valve rod part that guides the discharge valve 30.
Even though it is not provided at ゜30', the discharge valve 30.30
' is correctly guided.
このように図示のパルプ装置では上述のようなストッパ
一手段５０’ａ、５０’ａを設けることで吐出弁３０．
３０’から弁杆部を無くしている。つまり前述のように
本発明バルブ装置は吐出弁３０゜３０′のシール長を短
縮しても必要なシール度を確保させることからして、図
示のように吐出弁３０゜３０′の厚さＴを弁座１８，７
８の深さＤより小さくしてもシール度の点で不具合は招
かないが、厚さを小さくするほどそのガイドが問題とな
る吐出弁について従来のように弁杆部に依るのではなく
、前述ストッパ一手段５０ａ、５０’ａを設けることで
弁座１８，７８がガイドとなるように図っているのであ
る。このように厚さ小でしかも弁杆部を有しない吐出弁
は極〈軽量となるから、慣性効果の制限、騒音発生の抑
制、パルプ作用の迅速化等の前述長所が大きく高められ
ている。In the illustrated pulp apparatus, the above-mentioned stopper means 50'a, 50'a are provided to control the discharge valve 30.
The valve rod is removed from 30'. In other words, since the valve device of the present invention secures the necessary degree of sealing even if the sealing length of the discharge valve 30°30' is shortened as described above, the thickness T of the discharge valve 30°30' can be reduced as shown in the figure. The valve seat 18,7
Even if the depth is smaller than the depth D of 8, there will be no problem in terms of sealing, but as the thickness becomes smaller, the guide becomes a problem.For the discharge valve, instead of relying on the valve stem as in the past, By providing the stopper means 50a, 50'a, the valve seats 18, 78 serve as guides. Since such a discharge valve having a small thickness and having no valve stem is extremely lightweight, the above-mentioned advantages such as limiting inertial effects, suppressing noise generation, and speeding up pulp action are greatly enhanced.
以上の２実施例において、圧縮機中で弁板は通例の方法
で用いられてお夛、またピストン、シリンダ、吸入弁、
マニホルド等は、通例のものとされている。所望の場合
には、ピストンの頂部を、該ピストンが上死点にあると
きに吸入弁の中心部の小さくて薄い空隙を満九して再膨
張容積をさらに減少させるような形状のものとできる。In the above two embodiments, the valve plate is used in the conventional manner in the compressor, and the piston, cylinder, suction valve,
The manifold etc. are considered to be conventional ones. If desired, the top of the piston can be shaped to fill the small thin air gap in the center of the intake valve when the piston is at top dead center, further reducing the re-expansion volume. .
第１図は、この発明に従った圧力応動バルブ装置であっ
て、高分子材製吐出弁をリード型吸入弁と組合せて構成
してなるパルプ装置を、シリンダ室内方向からみて画い
た底面図である。
第２図は、第１図の２−２線に浦って切断した、第１図
に図示のパルプ装置の断面図である。
第３図は、第１肉の３−３線に沼って切断した、第１図
に図示のパルプ装置の断面図である。
第４図は、第１図に図示のパルプ装置における弁座と関
連する吐出弁との一部を示す拡大部分断面図で、互に係
合する面の傾斜角度間の関係を実際よりも誇張して画い
である図であり、また吐出弁がちょうど弁座へ看座し始
めた状態で画いである図である。
第５図は、第２図に類似の断面図であるが、吐出弁をリ
ング型吸入升と組合せである、この発明の他の実施例を
示す図である。
第６図（ａ）及び第６図Ｃｂ）はそれぞれ、第２図及び
第５図と同一の部分を拡大して画いた図で、第２図及び
第５図とは異なシ吐出弁が完全開放位置にある状Ｕを示
している。
ｌＯ・・・パルプ装置、１２・・・弁板、１４．１６・
・・吸入通路、１８・・・弁座、２０・・・リード型吸
入弁、２８・・・弁座の開口の側周壁、３０．３０’・
・・吐出弁、３２・・・吐出弁の周端面、３４．３４’
・・・吐出弁下面（内面）、３６・・・弁板上面（内面
）、４４．４４’・・・つる巻き圧縮ばね、５０．５０
’・・・リテーナ、５０ａ、５０ｂ・・・ストッパ一手
段、６０・・・外側シール周縁、６４・・・パルプ装置
、６６・・・弁板、６８・・・凹み部、７０・・・弁板
上面（内面）、７２・・・吐出通路、７６・−・弁板上
面（外面）、７４・・・吐出通路の側周壁、７８・・・
弁座、８６・・・環状リング、１００・・・吸入リード
升、１０４・・・開口。FIG. 1 is a bottom view of a pulp device, which is a pressure-responsive valve device according to the present invention, and is constructed by combining a polymer discharge valve with a reed-type suction valve, as viewed from the direction of the cylinder chamber. be. 2 is a cross-sectional view of the pulping apparatus shown in FIG. 1 taken along line 2--2 in FIG. 1; FIG. 3 is a cross-sectional view of the pulping apparatus shown in FIG. 1 taken along line 3--3 of the first meat. FIG. 4 is an enlarged partial cross-sectional view of a portion of the valve seat and associated discharge valve in the pulping apparatus shown in FIG. FIG. 6 is a drawing showing the state in which the discharge valve is just beginning to sit on the valve seat. FIG. 5 is a sectional view similar to FIG. 2, but showing another embodiment of the invention in which the discharge valve is combined with a ring-shaped suction chamber. Figure 6(a) and Figure 6Cb) are enlarged views of the same parts as Figures 2 and 5, respectively, and differ from Figures 2 and 5 in that the discharge valve is completely The figure U is shown in the open position. lO...Pulp device, 12...Valve plate, 14.16.
... Suction passage, 18... Valve seat, 20... Reed type suction valve, 28... Side peripheral wall of opening of valve seat, 30.30'.
...Discharge valve, 32... Circumferential end surface of discharge valve, 34.34'
...Discharge valve lower surface (inner surface), 36...Valve plate upper surface (inner surface), 44.44'... Helical compression spring, 50.50
'... Retainer, 50a, 50b... Stopper means, 60... Outer seal periphery, 64... Pulp device, 66... Valve plate, 68... Recessed portion, 70... Valve Plate top surface (inner surface), 72...Discharge passage, 76...Valve plate top surface (outside surface), 74...Side peripheral wall of discharge passage, 78...
Valve seat, 86... Annular ring, 100... Suction lead square, 104... Opening.
Claims (1)
縮チャンバーを部分的に仕切る内面を備えた弁板と、 Ｂ、上記弁板を貫通している吐出通路と、 Ｃ、上記吐出通路中に設けられた横断面形状円形の弁座
であつて上記圧縮チャンバーか ら遠去かる向きに沿い直径を大とする弁座 と、 Ｄ、上記吐出通路内に配設され、上記弁座に対し密封的
に接当するように形成された周 端面を有する吐出弁と、 Ｅ、上記吐出弁を上記弁座に対し着座する向きに移動附
勢する圧縮スプリングと、 を設けてあるバルブ装置であつて、 前記吐出弁を比較的弾性変形性に富む高分子素材から、
肉密であると共に前記周端面が連続した単一の傾斜を有
していて前記圧縮チャンバーから遠去かる向きに沿い直
径を大とする截頭円錐状のものに形成し、該吐出弁の周
端面の開先角度を前記弁座の開口の側周壁の開先角度に
対し相対的に、吐出弁非圧縮状態で吐出弁周端面の開先
角度の方が弁座開口の側周壁の開先角度よりも適当量だ
け大であつて弁座に対する吐出弁の完全な着座が吐出弁
の変形により該吐出弁の内面が前記した弁板の内面とほ
ぼ同一平面上に位置しつつ吐出弁の周端面の全面で行な
われると共に該変形によつて吐出弁に生ぜしめられると
ころの弁座に対する弾発力が前記圧縮スプリングの附勢
力よりも大となるような角度に設定したこと、 を特徴としてなるバルブ装置。[Scope of Claims] 1. A pressure-responsive valve device for a gas compressor, comprising: A. a valve plate having an inner surface that partially partitions a compression chamber; B. a discharge passage passing through the valve plate; , C. a valve seat with a circular cross-section, which is provided in the discharge passage and whose diameter increases in the direction away from the compression chamber; D. a valve seat disposed in the discharge passage; , a discharge valve having a circumferential end surface formed to sealingly abut against the valve seat, and E. a compression spring that urges the discharge valve to move in a direction in which it seats against the valve seat. In the valve device, the discharge valve is made of a polymeric material having relatively high elastic deformability.
The periphery of the discharge valve is formed into a truncated conical shape that is dense and has a single continuous slope at the peripheral end surface and whose diameter increases in the direction away from the compression chamber. Relative to the groove angle of the end face with respect to the groove angle of the side peripheral wall of the opening of the valve seat, when the discharge valve is in an uncompressed state, the groove angle of the peripheral end face of the discharge valve is larger than the groove angle of the side peripheral wall of the valve seat opening. The angle is larger than the angle by an appropriate amount, and the complete seating of the discharge valve against the valve seat is such that due to the deformation of the discharge valve, the inner surface of the discharge valve is located approximately on the same plane as the inner surface of the aforementioned valve plate, and the circumference of the discharge valve is The deformation is performed on the entire end surface and is set at an angle such that the elastic force generated on the valve seat by the deformation is greater than the biasing force of the compression spring. Valve device.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US97130978A | 1978-12-20 | 1978-12-20 | |
| US971,309 | 1978-12-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63198785A true JPS63198785A (en) | 1988-08-17 |
| JPH0154554B2 JPH0154554B2 (en) | 1989-11-20 |
Family
ID=25518200
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16395579A Granted JPS5597572A (en) | 1978-12-20 | 1979-12-17 | Valve device for gas compressor |
| JP62291655A Granted JPS63198785A (en) | 1978-12-20 | 1987-11-18 | Valve gear for gas compressor |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16395579A Granted JPS5597572A (en) | 1978-12-20 | 1979-12-17 | Valve device for gas compressor |
Country Status (16)
| Country | Link |
|---|---|
| JP (2) | JPS5597572A (en) |
| AR (1) | AR222060A1 (en) |
| AT (1) | AT388974B (en) |
| AU (1) | AU523545B2 (en) |
| BE (1) | BE880746A (en) |
| BR (1) | BR7908354A (en) |
| CA (1) | CA1179575A (en) |
| DE (2) | DE2951462C2 (en) |
| DK (2) | DK156093C (en) |
| ES (1) | ES487055A1 (en) |
| FR (1) | FR2444820B1 (en) |
| GB (1) | GB2039004B (en) |
| IT (1) | IT1194601B (en) |
| MX (1) | MX150936A (en) |
| PH (1) | PH16984A (en) |
| SE (3) | SE7910405L (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100323526B1 (en) * | 2000-03-03 | 2002-02-19 | 구자홍 | Discharge Apparatus of Compressor |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4385872A (en) | 1980-01-22 | 1983-05-31 | Copeland Corporation | Compressor |
| US4329125A (en) | 1980-01-22 | 1982-05-11 | Copeland Corporation | Discharge valve |
| CA1214758A (en) * | 1981-02-13 | 1986-12-02 | Copeland Corporation | Discharge valve assembly |
| JPS6463669A (en) * | 1987-09-02 | 1989-03-09 | Toyoda Automatic Loom Works | Compressor |
| JPH0313153U (en) * | 1989-06-22 | 1991-02-08 | ||
| EP2275680A1 (en) * | 2001-07-13 | 2011-01-19 | Delaware Capital Formation, Inc. | Elastomeric sealing element for gas compressor valve |
| DE102016011058B4 (en) | 2016-09-12 | 2018-03-29 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
| DE102016011059B4 (en) | 2016-09-12 | 2024-05-23 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE213136C (en) * | ||||
| US1718350A (en) * | 1929-06-25 | Valve fob pump assemblies | ||
| US1490141A (en) * | 1921-07-21 | 1924-04-15 | Leigh W Morris | Compressor valve |
| US1514233A (en) * | 1922-12-01 | 1924-11-04 | Searles | Valve and the method of making it |
| DE452903C (en) * | 1924-10-22 | 1927-11-22 | Aaron Montgomery Searles | Poppet valve |
| US2358950A (en) * | 1941-11-04 | 1944-09-26 | Bendix Aviat Corp | Valve |
| US2366004A (en) * | 1942-10-29 | 1944-12-26 | Westinghouse Air Brake Co | Compressor valve |
| US2341709A (en) * | 1943-05-20 | 1944-02-15 | Morley V Friedell | Valve |
| FR940160A (en) * | 1946-01-31 | 1948-12-06 | Climax Rock Drill & Engineering Works Ltd | Valve enhancements for air compressors and pneumatic tools |
| GB679079A (en) * | 1950-09-15 | 1952-09-10 | Compressor Acdessories Ltd | Improvements in, or relating to, automatic valves for compressors and similar apparatus |
| US2900999A (en) * | 1955-07-21 | 1959-08-25 | Weatherhead Co | Valve seal |
| US3092139A (en) * | 1960-04-14 | 1963-06-04 | American Iron & Machine Works | Valve with means for controlling and indicating wear |
| DE1856211U (en) * | 1962-05-25 | 1962-08-09 | Ritzau Pari Werk Kg Paul | DIAPHRAGM VACUUM PUMP FOR VACUUM EXTRACTION FOR OBSTETRICS. |
| DE1550254A1 (en) * | 1966-06-23 | 1969-07-31 | Gerdts Gustav F Kg | Check valve |
| GB1199523A (en) * | 1968-01-13 | 1970-07-22 | Nat Res Dev | Valve Damping Means. |
| US3548868A (en) * | 1968-02-14 | 1970-12-22 | Sealol | Check valve with spring assisted flexible auxiliary valve seat |
| AT292906B (en) * | 1970-07-08 | 1971-09-10 | Hoerbiger Ventilwerke Ag | Lamella valve for reciprocating compressors |
| US3770009A (en) * | 1971-12-29 | 1973-11-06 | Victor Equipment Co | Sensitive check valve |
| DE2443030A1 (en) * | 1973-09-15 | 1975-03-20 | Bendix Westinghouse Ltd | COMPRESSOR |
| US4115044A (en) * | 1976-10-04 | 1978-09-19 | Tecumseh Products Company | Valve arrangement for compressor |
-
1979
- 1979-12-06 CA CA000341333A patent/CA1179575A/en not_active Expired
- 1979-12-07 IT IT27990/79A patent/IT1194601B/en active
- 1979-12-13 AU AU53778/79A patent/AU523545B2/en not_active Expired
- 1979-12-17 JP JP16395579A patent/JPS5597572A/en active Granted
- 1979-12-18 GB GB7943570A patent/GB2039004B/en not_active Expired
- 1979-12-18 SE SE7910405A patent/SE7910405L/en unknown
- 1979-12-19 AR AR279369A patent/AR222060A1/en active
- 1979-12-19 BE BE0/198659A patent/BE880746A/en not_active IP Right Cessation
- 1979-12-19 ES ES487055A patent/ES487055A1/en not_active Expired
- 1979-12-19 BR BR7908354A patent/BR7908354A/en not_active IP Right Cessation
- 1979-12-19 DK DK544379A patent/DK156093C/en not_active IP Right Cessation
- 1979-12-19 FR FR7931154A patent/FR2444820B1/en not_active Expired
- 1979-12-20 DE DE2951462A patent/DE2951462C2/en not_active Expired
- 1979-12-20 PH PH23443A patent/PH16984A/en unknown
- 1979-12-20 AT AT0806479A patent/AT388974B/en not_active IP Right Cessation
- 1979-12-20 DE DE2954518A patent/DE2954518C2/de not_active Expired
-
1980
- 1980-01-02 MX MX180609A patent/MX150936A/en unknown
-
1985
- 1985-12-20 DK DK596885A patent/DK161476C/en active
- 1985-12-30 SE SE8506153A patent/SE463731B/en not_active IP Right Cessation
-
1986
- 1986-03-17 SE SE8601230A patent/SE8601230D0/en unknown
-
1987
- 1987-11-18 JP JP62291655A patent/JPS63198785A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100323526B1 (en) * | 2000-03-03 | 2002-02-19 | 구자홍 | Discharge Apparatus of Compressor |
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